JP2011179658A - Vehicular electric brake device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent grease from inflowing from a deceleration room to a motor room with a simple structure capable of preventing a cost increase, in a vehicular electric brake device in which a motor case is composed of a bottomed cylindrical yoke with a flange, a brush holder made of resin, a lid member for sandwiching the brush holder between itself and the yoke, and the flange, which allows the peripheral portion of the brush holder to be interposed between itself and a caliper body, forms the deceleration room between the caliper body and the motor case to be fastened to the caliper body, and then a ball bearing with a seal for preventing grease from inflowing to a portion between a motor shaft and the lid member is interposed therebetween, and further a motion conversion mechanism for converting a rotative power into an axial reciprocation of a brake piston is coupled to the motor shaft via a reduction gear housed in the deceleration room. <P>SOLUTION: A labyrinthine communicating path 123 for coupling the deceleration room 59 and the motor room 84 together is formed in the periphery of the motor case 83. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  According to the present invention, a motor case provided in an electric motor includes a bottomed cylindrical yoke having a flange portion at an open end, a resin brush holder disposed so as to close the open end of the yoke, and the brush The flange portion, which is composed of a lid member that sandwiches the holder between the yoke and the outer periphery of the brush holder between the caliper body, forms a deceleration chamber between the caliper body and the motor case. Thus, the grease is prevented from flowing into the motor chamber from the speed reduction chamber between the lid and the motor shaft that is fastened to the caliper body and rotatably supported by the motor case and enters the speed reduction chamber. A motion conversion mechanism that includes a ball bearing with a seal to convert the rotational power into the axial movement of the brake piston is housed in the deceleration chamber. An electric brake system for a vehicle via a reduction gear is connected to the motor shaft to be.

  Such an electric brake device for a vehicle is known from Patent Document 1.

JP 2007-40462 A

  In the above-mentioned Patent Document 1, since a ball bearing with a seal for preventing the inflow of grease from the deceleration chamber to the motor chamber is interposed between the motor shaft and the lid member, The speed reduction chamber formed between the caliper bodies and the motor chamber in the motor case should basically be sealed, but the sealed ball bearing, the lid member, and the motor shaft If there is a minute gap between them, a pressure difference is generated between the deceleration chamber and the motor chamber, and the grease in the deceleration chamber may flow into the motor chamber. Therefore, conventionally, in order to prevent such grease from flowing into the motor chamber, a dedicated seal member is required to securely seal between the ball bearing with seal and the lid member and the motor shaft. Therefore, it is necessary to increase the dimensional accuracy of the press-fitting portion, resulting in an increase in cost.

  The present invention has been made in view of such circumstances, and provides an electric brake device for a vehicle that prevents inflow of grease from a reduction chamber to a motor chamber with a simple structure that can prevent an increase in cost. The purpose is to provide.

  In order to achieve the above object, the present invention provides a motor case included in an electric motor in which a bottomed cylindrical yoke having a flange portion at an open end and a resin disposed so as to close the open end of the yoke. The flange portion is made of a brush holder made of metal and a lid member that sandwiches the brush holder between the yoke and the caliper body with the outer peripheral portion of the brush holder interposed between the caliper body and the caliper body. The motor is fastened to the caliper body so as to form a deceleration chamber between the motor cases, is rotatably supported by the motor case, and enters the deceleration chamber, and the motor from the deceleration chamber between the lid member. A ball bearing with a seal is installed to prevent grease from flowing into the chamber, and the motion change that converts the rotational power into the axial movement of the brake piston. In a vehicular electric brake device that is connected to the motor shaft via a speed reducer housed in the speed reduction chamber, a labyrinth-like structure that connects the speed reduction chamber and the motor chamber is formed on the outer periphery of the motor case. The first feature is that a communication path is formed.

  According to the present invention, in addition to the configuration of the first feature, a brush holding cylinder that slidably holds a brush that is in sliding contact with a commutator provided on the motor shaft is provided facing the motor chamber. In addition, a cylindrical portion that is disposed outside the brush holding cylinder along the radial direction of the yoke and that is close to and opposed to the inner periphery of the opening end of the yoke is integrally provided, and the inner periphery of the opening end of the yoke and the cylindrical portion A second feature is that an annular gap forming a part of the communication path is formed between the outer circumferences of the two.

  Furthermore, in addition to the first or second feature of the present invention, the brush holder is provided integrally with the brush holder so that a coupler for supplying power to the electric motor protrudes outward. According to a third aspect of the present invention, the brush holder is provided with an external communication path that allows the motor chamber to communicate with the outside.

  According to the first feature of the present invention, since the communication path connecting the speed reduction chamber and the motor chamber is formed in the outer peripheral portion of the motor case, there is no pressure difference between the speed reduction chamber and the motor chamber. There is no need for processing to increase the sealing accuracy in the vicinity of the ball bearing with a seal interposed between the cover member and other sealing parts, and there is no need to add other sealing parts. It is possible to prevent the grease from flowing into the motor chamber with a simple structure that avoids an increase in cost. Moreover, since the communication path is a labyrinth, it is possible to prevent grease from flowing into the motor chamber via the communication path.

  According to the second aspect of the present invention, the brush holder is integrally provided with the cylindrical portion disposed on the outer side of the brush holding tube along the radial direction of the yoke and facing the inner periphery of the opening end of the yoke. An annular gap that constitutes a part of the communication path is formed between the inner periphery of the opening end and the outer periphery of the cylindrical part. Therefore, even if grease should flow into the communication path, the grease will reach the sliding contact part of the brush to the commutator. It does not reach, and the sliding contact portion of the brush to the commutator is not affected by the grease.

  Furthermore, according to the third feature of the present invention, the brush holder is provided with an external communication path that allows the motor chamber to communicate with the outside through the coupler unit integral with the brush holder. The movement of the grease can be prevented by setting the pressure to be the same as the atmospheric pressure. In addition, since an external connector is connected to the coupler portion, water, dust and the like do not enter the motor chamber from the external communication path.

It is a longitudinal cross-sectional view of the electric brake device for vehicles. FIG. 2 is a sectional view taken along line 2-2 of FIG. 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. It is sectional drawing which shows the engagement state of the 12 angle | corner socket to an output member. It is the front view which looked at the brush holder from the motor chamber side. It is the rear view which looked at the brush holder from the reduction gear side. It is the front view which expanded the principal part of FIG. 8 in order to show a capacitor | condenser holding | maintenance part. It is a perspective view of a capacitor | condenser holding | maintenance part. It is a principal part enlarged view of FIG. It is sectional drawing corresponding to FIG. 12 in the coupler part vicinity.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to FIGS. 1 to 13. 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 formed at least in part 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. A second carrier 69 that is rotatably supported, and a flat plate ring-shaped output member 70 whose outer periphery is serrated to the inner periphery of the second carrier 69 are provided.

  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.

  Moreover, the first planetary gear 65 is opposed to the disk portion 88b of the lid member 88 in the motor case 83 that constitutes a part of the gear case 60, but the disk portion 88b of the lid member 88 is opposed to the disk portion 88b. An annular recess 91 formed by bending so that a part thereof is recessed to the side opposite to the speed reducer 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 output member 70 is directly press-fitted into a press-fitting hole 79 provided in the central portion. Thus, the second carrier 69 in the second planetary gear mechanism 62 is connected to the screw shaft 45 so as not to rotate relative to the screw shaft 45 via the output member 70 whose outer periphery is serrated to the inner periphery.

  By the way, when the electric motor 22 is removed 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, it is possible to disassemble the speed reducer 23 while leaving the output member 70 into which the connecting shaft portion 45 a integrally connected to the screw shaft 45 of the screw mechanism 24 is press-fitted in the housing recess 35. As shown in FIG. 7, the output member 70 is formed so as to be able to engage with a twelve-angle socket 80 which is a rotary operation tool. That is, the outer periphery of the output member 70 is serrated to the inner periphery of the second carrier 69, and a plurality of teeth 81, 81. It is formed so as to engage with the inner periphery so as not to be relatively rotatable.

  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 cylindrical shape with a bottom, and a brush holder 87 made of a resin, for example, a synthetic resin, which closes the open end of the yoke 86 so that the outer peripheral portion is brought into contact with the flange portion 86a. And a metal lid member 88 that sandwiches the brush holder 87 with the yoke 86.

  Collars 89 formed in a cylindrical shape with metal are embedded at a plurality of, for example, three places spaced apart in the circumferential direction of the outer peripheral portion of the brush holder 87, and the flange portion 86 a and the brush holder 87 are embedded therein. Bolts 90 inserted through the collars 89 are screwed into the housing portion 26a of the caliper body 26. That is, the motor case 83 of the electric motor 22 is detachably fastened to the housing part 26a of the caliper body 26 with bolts 90.

  The lid member 88 is formed by bending a metal plate, and includes a cylindrical bearing housing portion 88a, a disc portion 88b extending outward from the bearing housing portion 88a, and the disc portion 88b. A cylindrical portion 88c that extends perpendicularly to the outer periphery and extends toward the speed reducer 23 is integrally formed, and a part of the cylindrical portion 88c is fitted to the brush holder 87 so as to protrude from the brush holder 87 toward the speed reducer 23. The portion of the cylindrical portion 88 c that protrudes from the brush holder 87 is fitted into the housing portion 26 a of the caliper body 26.

  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. Therefore, 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 disk portion 88b of the lid member 88. Since the circumferential movement of the ring gear 64 is restricted by engaging the concave and convex portions, the ring gear 64 is substantially fixed to the gear case 60 by restricting the axial movement by the partition wall 36 and the disk portion 88b. become.

  In addition, an annular seal member 92 having a larger diameter than the inner periphery of the housing recess 35 is interposed between the housing portion 26a of the caliper body 26 and the brush holder 87 outside the cylindrical portion 88c of the lid member 88. An annular seal member 93 is interposed between the flange portion 86 a of the yoke 86 and the brush holder 87 so as to be located inward of the place where the bolt 90 is disposed.

  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 penetrates the brush holder 87 and the lid member 88 rotatably 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. A ball bearing 97 with a seal is interposed between the bearing housing portion 88 a of the lid member 88 and the motor shaft 95 in order to prevent inflow of grease from the deceleration chamber 59 to the motor chamber 84.

  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 86 at a portion corresponding to the armature 99.

  Referring to FIGS. 8 and 9 together, a central hole 101 into which a part of the commutator 98 is inserted is provided at the center of the brush holder 87 so as to penetrate the motor shaft 95. The brushes 102 and 102 that are in sliding contact with the commutator 98 are slidable along the radial direction of the commutator 98 at two positions around the center hole 101 on the surface facing the motor chamber 84. The fitting holding cylinders 103 are fitted integrally with the commutator 98 so as to extend long along the radial direction of the commutator 98, and each brush 102 is contracted between the fitting holding cylinders 103. It is urged | biased by the side which contacts the commutator 98 by the spring (not shown) which is carried out.

  Capacitor holding portions 105... Are provided at a plurality of, for example, three locations around the center hole 101 at equal intervals on the surface of the brush holder 87 facing the motor chamber 84. A capacitor 104 for reducing radio noise is held by the capacitor holding unit 105 selected from the holding units 105..., And in this embodiment, two capacitor holding units 105 adjacent to the brush holding unit 103. Is done.

  Referring to FIG. 10 and FIG. 11 together, the capacitor holding portion 105 is formed along a plane orthogonal to the axis of the electric motor 22 and the surface of the capacitor 104 is brought into contact therewith. The electric motor 22 includes a support surface 106 formed on the brush holder 87 and a pair of hooks 107 and 108 that are formed integrally with the brush holder 87 and sandwich the capacitor 104 between the support surface 106. The capacitor 104 is configured to be restricted from moving in a plane perpendicular to the axis.

  The support surface 106 is formed as a bottom surface of a rectangular recess 109 provided on a surface of the brush holder 87 facing the motor chamber 84, and a substantially half portion on the one surface side of the capacitor 104 is formed on the support surface 106. It is inserted into the recess 109. By inserting approximately half of the capacitor 104 into the recess 109, the movement of the capacitor 104 in a plane perpendicular to the axis of the electric motor 22 is restricted.

  The hooks 107 and 108 are formed integrally with the brush holder 87 so as to rise from the opening end side edge of the recess 109 in order to prevent the capacitor 104 from being detached from the recess 109. The mold holders 110 and 111 for extracting the molds forming the hooks 107 and 108 are formed in the brush holder 87 so as to open to the bottom surface of the recess 109, that is, the support surface 106. Thus, one hook 107 is arranged so as to rise from the opening end side edge of the recess 109 on one side of the intermediate portion of the recess 109 along the insertion direction 119 of the capacitor 104 into the recess 109. 108 is arranged to rise from the opening end side edge of the recess 109 on the other side of the front end of the recess 109 along the insertion direction 119.

  The pair of terminals 104a and 104b extending from the capacitor 104 has a pair of grooves 112 and 112 formed in the brush holder 87 so that one end is connected to the recess 109 on the side opposite to the side where the hook 1108 is disposed. The wall 114 provided in the brush holder 87 so as to separate the grooves 112 and 113 is inclined so as to guide the capacitor 104 when the capacitor 104 is inserted into the recess 109. A guide surface 114a is formed.

  The other ends of the grooves 112 and 113 are continuous with the windows 115 and 116 provided on the brush holder 87 across both surfaces of the brush holder 87, and a part of the windows 115 and 116 faces the windows 115 and 116. The bus bars 117 and 118 are embedded in the brush holder 87, and the terminals 104a and 104b of the capacitor 104 are electrically connected to the bus bars 117 and 118 by soldering or the like at the portions facing the windows 115 and 116, respectively.

  Incidentally, as shown in FIG. 4, a heat insulating space 121 is disposed between the motor chamber 84 formed in the motor case 83 of the electric motor 22 and the reduction chamber 59 that houses the reduction gear 23. Thus, the motor chamber of the brush holder 87 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 opening end of the housing recess 35. A heat insulation space recess 122 is provided on the surface opposite to the surface 84, and the heat insulation space 121 is formed by the heat insulation space recess 122 and the lid member 88 sandwiching the brush holder 87 between the yoke 86. Is done.

  Referring to FIG. 12 and FIG. 13 together, a labyrinth-like communication path 123 that connects between the deceleration chamber 59 and the motor chamber 84 is formed in the outer peripheral portion of the motor case 83.

  The communication passages 123 are provided at a plurality of circumferential positions on the connecting portion of the disc portion 88 b and the cylindrical portion 88 c in the lid member 88 constituting a part of the motor case 83, and communicate with the speed reduction chamber 59. One communication hole 124, an annular passage 125 formed between the disk portion 88b of the lid member 88 and the brush holder 87 and communicating with the first communication hole 124, and one end of the annular passage 125. An annular space 127 formed between the opening end of the brush holder 87 and the yoke 86 so as to connect the second communication hole 126 provided in the brush holder 87, the second communication hole 126, and the motor chamber 84. It consists of.

  The brush holder 87 is integrally provided with a cylindrical portion 87a that is disposed on the outer side of the fitting holding cylinder 103 along the radial direction of the yoke 86 and that is close to the inner periphery of the opening end of the yoke 86. 86 is formed between the inner periphery of the open end of 86 and the outer periphery of the cylindrical portion 87a, and a plurality of, for example, two second communication holes 126... The brush holder 87 is provided so as to connect the annular passage 125 in a straight line.

  The brush holder 87 is integrally provided with a coupler portion 87b for supplying power to the electric motor 22 so as to protrude outward, and the inside of the motor chamber 84 is passed through the coupler portion 87b. An external communication path 128 communicating with the outside is provided in the brush holder 87.

  The external communication path 128 includes a third communication hole 129 provided in the brush holder 87 so as to open at one end to the motor chamber 84 inside the cylindrical portion 87a at a portion corresponding to the coupler portion 87b. The fourth communication hole 130 extends linearly so as to connect the other end of the communication hole 129 and the coupler 87b.

  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. Are provided so as to open to the opposite sides with a partition wall 36 interposed therebetween, and are connected to the output member 70 of the speed reducer 23, which is partly accommodated in the accommodation recess 35, in a relatively non-rotatable manner and coaxially. A screw mechanism 24 having a screw shaft 45 that rotatably passes through the partition wall 36 is provided between the speed reducer 23 and the brake piston 38 so as to convert the rotation of the screw shaft 45 into an axial advance / retreat operation of the brake piston 38. The electric motor 22 for inputting rotational power to the speed reducer 23 is attached to the caliper body 26 and is provided integrally with the screw shaft 45 in the cylinder hole 34. Between the flange portion 45b facing the partition wall 36 and the partition wall 36, a sliding bearing 54 formed in a flat ring shape is interposed, but the surface of the flange portion 45b facing the partition wall 36 is fitted. A recess 56 is formed, 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 an output member 70 that is coaxial with the screw shaft 45, and an end portion of a connecting shaft portion 45 a that the screw shaft 45 integrally and coaxially is press-fitted coaxially and directly to the output member 70. Therefore, the axial displacement of the screw shaft 45 with respect to the output member 70 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, thereby reducing the number of processing steps. be able to.

  Further, the speed reducer 23 includes an output member 70 and a second carrier 69 that coaxially surrounds the output member 70, and the outer periphery of the output member 70 is serrated to the inner periphery of the second carrier 69. Even if the axis of the shaft 45 is slightly inclined with respect to the output member 70, the second carrier 69 can be automatically aligned, and the rotation of the components of the speed reducer 23 is stabilized.

  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. A second carrier 69 that supports, in which and a said output member 70.

  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 reducing chamber 59 for accommodating the speed reducer 23 is formed, and the ring gear 64 is prevented from moving in the axial direction by the disc portion 88b of the lid member 88 and the caliper body 26 constituting a part of the motor case 83. The ring gear 64 is inserted into the deceleration chamber 59 in such a manner that the end of the ring gear 64 opposite to the electric motor 22 is engaged with the caliper body 26 so as to restrict the rotation of the ring gear 64 about the axis. Therefore, the ring gear 64 common to the first and second planetary gear mechanisms 61 and 62 is used as a gear case. It can be substantially fixed to the caliper body 26 which constitutes a part of a 0.

  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, since an annular seal member 92 having a diameter larger than the inner periphery of the housing recess 35 is interposed between the brush holder 87 constituting a part of the motor case 83 and the caliper body 26, the minimum 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 flat plate portion 88b of the lid member 88 which is a part of the motor case 83 that constitutes the gear case 60 together with the caliper body 26, so that the first carrier 66 moves in the axial direction relative to the first planetary gears 68. Thus, 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 first planetary gears 68 from contacting the inner surface of the gear case 60. Thereby ensuring first 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 can be released with a relatively small manual operating force parking brake state.

  The synthetic resin brush holder 87 provided in the electric motor 22 is provided with capacitor holding portions 105 for holding capacitors 104 for reducing radio noise. Accordingly, the capacitors 104 are held by the capacitor holding portions 105, so that the capacitors 104 are prevented from being shaken by vibration, and the electrical connection of the capacitors 104 is released, or the terminals 104a of the capacitors 104 ... ..., 104b ... can be prevented from breaking. Further, since the capacitors 104 can be held by the capacitor holding portions 105, it is not necessary to hold the capacitors 104 when the terminals 104a, 104b, etc. of the capacitors 104 are electrically connected, and the assembling workability can be improved. In addition, no adhesive or the like is required for holding the capacitors 104... On the brush holder 87, and the cost can be reduced.

  In addition, the capacitor holding portion 105 is formed along a plane orthogonal to the axis of the electric motor 22 and also has a support surface 106 formed on the brush holder 87 so as to abut one surface of the capacitor 104, and the brush holder. 87 and hooks 107 and 108 sandwiching the capacitor 104 between the support surface 106 and the support surface 106, and restricting the movement of the capacitor 104 in a plane perpendicular to the axis of the electric motor 22. The capacitors 104 can be held in the brush holder 87 with a simple structure.

  A heat insulating space 121 is disposed 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. Therefore, heat transfer from the electric motor 22 to the speed reducer 23 side can be suppressed, and even if the parts constituting the speed reducer 23 are made of synthetic resin, thermal deformation and strength reduction can be suppressed.

  Further, the heat insulation is provided on the brush holder 87 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 insulation space recess 122 for forming the space 121 is provided, it is possible to reduce the weight of the brush holder 87 and thus the motor case 83 while forming the heat insulation space 121, and further reduce the cost by reducing the material. Can be achieved.

  A ball bearing with a seal for preventing the inflow of grease from the speed reduction chamber 59 to the motor chamber 84 is provided between the cover member 88 constituting a part of the motor case 83 in the electric motor 22 and the motor shaft 95. 97 is interposed, but a communication path 123 connecting the speed reduction chamber 59 and the motor chamber 84 is formed in the outer peripheral portion of the motor case 83, so that a pressure difference is generated between the speed reduction chamber 59 and the motor chamber 84. There is no need to increase the sealing accuracy near the ball bearing 97 with seal interposed between the motor shaft 95 and the cover member 88, or to add another seal part. Further, it is possible to prevent the grease from flowing into the motor chamber 84 with a simple structure that avoids an increase in cost by simply forming the communication path 123 in the outer peripheral portion of the motor case 83. It can be. Moreover, since the communication path 123 has a maze shape, it is possible to prevent grease from flowing into the motor chamber 84 via the communication path 123.

  Further, the brush holder 87 is provided with a fitting holding cylinder 103 slidably holding a brush 102 slidably contacting a commutator 98 provided on the motor shaft 95 so as to face the motor chamber 84, and a yoke in the motor case 83. A cylindrical portion 87a that is disposed outside the fitting holding cylinder 103 along the radial direction of the 86 and is opposed to the inner periphery of the open end of the yoke 86 is integrally provided. The inner periphery of the open end of the yoke 86 and the cylindrical portion 87a Since an annular gap 127 constituting a part of the communication path 123 is formed between the outer circumferences of the two, the grease reaches the sliding contact portion of the brush 102 to the commutator 98 even if the grease should flow into the communication path 123. In other words, the sliding contact portion of the brush 102 with the commutator 98 is not affected by the grease.

  Further, the brush holder 87 is integrally provided with a coupler portion 87b for supplying power to the electric motor 22 so as to protrude outward, and the inside of the motor chamber 84 is communicated to the outside through the coupler portion 87b. Since the external communication path 128 is provided in the brush holder 87, the movement of the grease can be prevented by setting the motor chamber 84 and the deceleration chamber 59 to the same pressure as the external pressure. In addition, since an external connector is connected to the coupler portion 87b, water, dust and the like do not enter the motor chamber 84 from the external communication path 128.

  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.

22 ... Electric motor 23 ... Reducer 24 ... Screw mechanism 26 which is a motion conversion mechanism ... Caliper body 38 ... Brake piston 59 ... Deceleration chamber 83 ... Motor case 86a ... · Flange portion 86 · · · yoke 87 · · · brush holder 87a · · · cylindrical portion 87b · · · coupler portion 88 · · · lid member 95 · · · motor shaft 97 · · · ball bearing 98 · · · commutator 102 ... Brush 103 ... Brush holding cylinder 123 ... Communication path 127 ... Annular gap 128 ... External communication path

Claims (3)

  A motor case (83) provided in the electric motor (22) is disposed so as to close a bottomed cylindrical yoke (86) having a flange portion (86a) at an open end and the open end of the yoke (86). A resin brush holder (87) and a lid member (88) sandwiching the brush holder (87) between the yoke (86), and the outer periphery of the brush holder (87) is a caliper. The flange portion (86a) interposed between the body (26) and the caliper body (26) forms a deceleration chamber (59) between the caliper body (26) and the motor case (83). ), Is rotatably supported by the motor case (83), and is inserted into the deceleration chamber (59) from the deceleration chamber (59) between the motor shaft (95) and the lid member (88). The mode A ball bearing (97) with a seal for preventing the inflow of grease into the chamber (84) is interposed, and a motion conversion mechanism (24) for converting the rotational power into the axial movement of the brake piston (38) is provided. In the vehicular electric brake device connected to the motor shaft (95) via the speed reducer (23) accommodated in the speed reduction chamber (59), the speed reduction chamber is formed on the outer periphery of the motor case (83). (59) and a maze-like communication path (123) connecting the motor chamber (84) is formed.   A brush holding cylinder (103) that slidably holds a brush (102) slidably contacting a commutator (98) provided on the motor shaft (95) faces the motor chamber (84). And a cylindrical portion (87a) which is disposed outside the brush holding tube (103) along the radial direction of the yoke (86) and which is close to and faces the inner periphery of the open end of the yoke (86). An annular gap (127) constituting a part of the communication path (123) is formed between the inner periphery of the open end of the yoke (86) and the outer periphery of the cylindrical portion (87a). The vehicle electric brake device according to claim 1.   A coupler part (87b) for supplying power to the electric motor (22) is integrally provided on the brush holder (87) so as to protrude outward, and the motor is interposed through the coupler part (87b). The electric brake device for a vehicle according to claim 1 or 2, wherein an external communication path (128) for allowing the inside of the chamber (84) to communicate with the outside is provided in the brush holder (87).

Images