JP2009133382A - Cyclo speed reducer - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cyclo speed reducer wherein inside gears can be manufactured more inexpensive than manufactured with sintering or machining work. <P>SOLUTION: The first inside gear 80 and the second inside gear 86 are molded from plate metal members with pressing work to eliminate facilities and manhours which are conventionally required when manufacturing the inside gears with sintering or machining work. Thus, they can be manufactured more inexpensive than manufactured with sintering and machining work. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a cyclo reducer, and more particularly to a technique for reducing the manufacturing cost of a cyclo reducer.

  For example, as shown in Patent Document 1, the cyclo reducer (a) rotates around the first axis, and is formed with an outer peripheral surface centered on the second axis that is eccentric from the first axis. And (b) an inner gear supported by the eccentric part of the input shaft so as to be capable of relative rotation. And (c) an annular outer gear provided with a fixed position coaxially with the first shaft center and having inner peripheral teeth meshing with the outer peripheral teeth of the inner gear, and (d) a protrusion of the inner gear is loosely fitted. And an output shaft that rotates about the first axis, and (e) decelerates the rotation of the input shaft and outputs it from the output shaft.

In the cyclo reducer as described above, for example, as shown in FIG. 9 of Patent Document 1, the inner gear includes a boss portion protruding in the thickness direction so as to be rotatably supported by the eccentric portion of the input shaft, The protrusion (inner pin 144) is provided, and the inner gear is usually manufactured by sintered metal processing or machining in order to form the shape of the inner gear.
JP 2006-283916 A

  However, in the case where the inner gear is manufactured by sintered metal processing as described above, the metal powder after molding is added to give strength after the metal powder is filled in the mold and molded by press working. Since a heat treatment step for sintering is required, it takes equipment and man-hours, and it is difficult to reduce the manufacturing cost of the cyclo reducer. Further, even when manufacturing by machining, equipment and man-hours such as a lathe and a gear cutting machine are required, and it has been difficult to reduce the manufacturing cost of the cyclo reducer as well.

  The present invention has been made against the background of the above circumstances, and the object of the present invention is to provide a cyclo reducer that can manufacture an inner gear at a lower cost than that produced by sintering or machining. It is to provide.

  The gist of the invention according to claim 1 for achieving this object is as follows: (a) an outer periphery centering around a second axis that rotates about the first axis and is eccentric from the first axis. An input shaft having an eccentric portion formed with a surface, and (b) a protrusion and an outer peripheral tooth projecting in a thickness direction on one circumference around the second axis, and the eccentric portion of the input shaft An inner gear supported so as to be rotatable relative to the inner gear; and (c) an annular outer gear provided with a fixed position coaxially with the first axis and having inner peripheral teeth meshing with the outer peripheral teeth of the inner gear; An output shaft having a hole portion into which the protrusion of the inner gear is loosely fitted and rotating about the first axis, and (e) a cyclone that decelerates the rotation of the input shaft and outputs it from the output shaft (F) The inner gear is formed by pressing a flat metal member.

  The gist of the invention according to claim 2 is that, in the invention according to claim 1, the outer gear is formed from a flat metal member by pressing.

  Further, the gist of the invention according to claim 3 is that, in the invention according to claim 1 or 2, (a) the inner gear is eccentric from the hole portion into which the protrusion is loosely fitted and the first axis. An intermediate shaft having an eccentric portion formed with an outer peripheral surface centered on the third axis and rotating about the first axis; and (b) a thickness on a circumference of the third axis. A second inner gear provided with a protrusion projecting in the direction and supported by the eccentric part of the intermediate shaft so as to be relatively rotatable; and (c) a first fixed gear provided coaxially with the first axis. And an annular second outer gear having inner peripheral teeth meshing with the outer peripheral teeth of the second inner gear, and (d) the protrusion of the second inner gear is loosely fitted in the hole of the output shaft. (E) The second inner gear and the second outer gear are formed from a flat metal member by pressing.

  A gist of the invention according to claim 4 is that, in the invention according to any one of claims 1 to 3, (a) the input shaft is rotationally driven by an electric motor, and (b) the The output shaft is connected to a cam member disposed between one end portions of a pair of brake shoes of the drum brake so as not to rotate relative to each other. (C) By driving the electric motor, As the cam member rotates, the one end portions of the pair of brake shoes are separated, and the drum brake brakes.

  Further, the gist of the invention according to claim 5 is that, in the invention according to claim 4, (a) the cam member has a shaft portion extended so as to penetrate the backing plate of the drum brake, (b) The tip portion of the shaft portion is connected to the output shaft so as not to rotate relative to the output shaft. (c) The backing plate is configured such that the shaft portion of the cam member is rotatable about its axis. An anchor member having a through hole opened at one end for fitting and a receiving hole formed at a diameter larger than the through hole and opened at the other end following the through hole for receiving the cyclo reducer Is fixed.

  Further, the gist of the invention according to claim 6 is that, in the invention according to claim 5, (a) between the input shaft and the shaft portion of the cam member, it rotates around the axis. A possible columnar or cylindrical intermediate member is disposed, and (b) a bearing is disposed between the intermediate member, the input shaft, and the second inner gear.

  The gist of the invention according to claim 7 is that, in the invention according to claim 5 or 6, the outer gear and the second outer gear are fitted into the accommodation hole of the anchor member, and the accommodation is performed. When the opening edge of the hole is plastically deformed inward, the outer gear and the second outer gear are caulked to the anchor member so as to press the side surface of the outer gear.

  According to the cyclo reducer of the invention according to claim 1, (f) the inner gear is formed by pressing from a flat metal member, and thus the conventional inner gear is subjected to sintering or machining. Since the equipment and man-hours required for manufacturing can be omitted, the cyclo reducer can be manufactured at a lower cost than manufacturing by sintering or machining.

  According to the cyclo reducer of the invention according to claim 2, since the outer gear is formed by pressing from a flat metal member, the inner gear and the outer gear which are gears of the cyclo reducer. A gear can be shape | molded from a flat metal member, and a cyclo reducer can be manufactured further cheaply. Further, since the distance in the thickness direction of the outer gear is shorter than the inner gear and the outer gear of the conventional cyclo reducer, the cyclo reducer can be suitably downsized.

  According to the cyclo reducer of the invention according to claim 3, (a) the outer periphery centered on the third shaft center eccentric from the first shaft center and the hole portion in which the protrusion of the inner gear is loosely fitted. An intermediate shaft having an eccentric portion formed with a surface and rotating about the first axis; and (b) a projection protruding in the thickness direction on a circumference of the third axis. And a second inner gear supported by the eccentric portion of the intermediate shaft so as to be relatively rotatable, and (c) meshed with the outer peripheral teeth of the second inner gear provided coaxially with the first axis and fixed in position. An annular second outer gear having an inner peripheral tooth; (d) a projection of the second inner gear is loosely fitted in the hole of the output shaft; and (e) the first Since the inner gear 2 and the second outer gear are formed by pressing from a flat metal member, the gear of the cyclo reducer of the two-stage gear is flat. Can be prepared from a metal member, the distance of which the thickness direction is shorter than the gears of the Cyclo reducer of the conventional two-stage gear, it is possible to further reduce the size of the Cyclo Drive double gear.

  According to the cyclo reducer of the invention according to claim 4, (a) the input shaft is rotationally driven by an electric motor, and (b) the output shaft is one end portion of a pair of brake shoes of a drum brake. (C) by driving the electric motor, the cam member is rotated via the cyclo reducer and the pair of brake shoes of the pair of brake shoes are coupled to each other. Since the one end portions are separated and the drum brake is braked, the manufacturing cost of the drum brake using the cyclo reducer can be suitably reduced.

  According to the cyclo reducer of the invention according to claim 5, (a) the cam member has a shaft portion extending so as to penetrate the backing plate of the drum brake, and (b) The distal end portion is connected to the output shaft so as not to rotate relative to the output shaft, and (c) is opened at one end of the backing plate so that the shaft portion of the cam member can be pivoted about its axis. An anchor member having a through hole that is formed and a receiving hole that is formed to have a diameter larger than the through hole and that opens to the other end following the through hole for receiving the cyclo reducer is fixed. From the above, since the cam member and the cyclo reducer can be integrally held by the receiving hole and the through hole provided in the anchor member, the rotation output from the output shaft of the cyclo reducer is preferable. To the above It can be transmitted to the arm member.

  According to the cyclo reducer of the invention according to claim 6, (a) a columnar shape or a cylindrical shape that is rotatable around the axis between the input shaft and the shaft portion of the cam member. (B) Since a bearing is provided between the intermediate member and the input shaft and the second inner gear, a cyclo reducer with two-stage gears is provided. The rotation of the inner gear can be suitably transmitted to the second inner gear.

  According to the cyclo reducer of the invention according to claim 7, the outer gear and the second outer gear are fitted into the accommodation hole of the anchor member, and the opening edge of the accommodation hole is plastic inward. Since the outer gear and the second outer gear are caulked to the anchor member so as to press the side surface of the outer gear by being deformed, for example, the outer gear is a flat metal When the outer gear is warped, the opening edge of the receiving hole is plastically deformed inward and the side surface of the outer gear is pressed and formed by press working when the outer gear is warped. Warping is preferably suppressed.

  Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings. In the following embodiments, the drawings are appropriately simplified or modified, and the dimensional ratios, shapes, and the like of the respective parts are not necessarily drawn accurately.

  FIG. 1 shows a hat-type disk and caliper (not shown) of a duo-servo type drum-in-disc brake 12 having a parking brake drum brake (hereinafter referred to as drum brake) 10 according to an embodiment of the present invention in the center. FIG. The hat-type disc has a disc-shaped outer peripheral portion and a bottomed cylindrical central portion, the disc-shaped outer peripheral portion functions as a friction plate for a disc brake, and the bottomed cylindrical central portion serves as a rotating drum 14. Configured to work. The rotating drum 14 is represented by two concentric circles indicated by a one-dot chain line in FIG. 1, and the circle on the center side of the drum brake 10 of the two circles indicates the inner peripheral surface 16 of the rotating drum 14. Yes.

  The drum brake 10 has a substantially disk shape, and includes a backing plate 18 that is integrally fixed to a non-rotating member that is a vehicle body side member such as an axle tube, an axle housing, and a suspension device (not shown). A disk cover 20 is secured to the backing plate 18 to protect the disk-shaped outer periphery of the hat type disk.

  Further, the drum brake 10 includes a pair of arc-shaped brake shoes 22 and 24 disposed substantially symmetrically so as to be able to approach and separate from each other in a posture in which the convex side is outward on the left and right outer peripheral portions of the backing plate 18, and the pair The brake shoe widening mechanism 26 provided in a fixed position on the backing plate 18 between one end of the brake shoes 22 and 24, that is, the upper end in FIG. 1, and the direction in which one end of the pair of brake shoes 22 and 24 approaches each other 1 and the other end of the pair of brake shoes 22, 24, that is, the lower end of FIG. A gap adjusting device 30 that adjusts the shoe gap by being interposed between them and being extended in length along with the rotation of the adjusting wheel 30a. A coil-like spring stretched between the other ends of the brake shoes 22 and 24 in order to generate an urging force for holding the gap adjusting device 30 by constantly urging the other end portions toward each other. 32.

  An intermediate portion of the spring 32 is brought into contact with the adjustment wheel 30a of the gap adjusting device 30 so that the adjustment wheel 30a does not rotate due to vibration or the like. Since the gap adjusting device 30 and the spring 32 connect the other end portions of the pair of brake shoes 22 and 24 so as to be relatively rotatable, they function as a connecting device having a gap adjusting function.

  Each of the pair of brake shoes 22 and 24 has a flat plate shape substantially parallel to the plate surface of the backing plate 18, and shoe webs 34 and 36 that are entirely curved in an arc shape in the front view shown in FIG. Arc-shaped shoe rims 38, 40 that are integrally fixed so that the cross-section is substantially T-shaped along the outer peripheral side edge forming the arc shape, and the outer peripheral surface of these shoe rims 38, 40 with an adhesive or the like The linings 42 and 44 are made of friction materials that are integrally fixed to each other. Further, the pair of brake shoes 22 and 24 are pressed toward the backing plate 18 by shoe hold-down devices 46 and 48 disposed on the shoe webs 34 and 36, respectively. It is held relative to each other. The backing plate 18, the shoe webs 34 and 36, and the shoe rims 38 and 40 are all pressed parts that are punched from a steel plate and subjected to predetermined bending.

  FIG. 2 is an enlarged view of the brake shoe expansion mechanism 26 of the drum brake 10 of FIG. 1, and illustrates the brake shoe expansion mechanism 26. 3 and 4 are a cross-sectional view taken along line III-III in FIG. 2 and a cross-sectional view taken along line IV-IV in FIG.

  As shown in FIGS. 2 to 4, the brake shoe spreading mechanism 26 includes, for example, an electric motor 50 that is driven by an operation of a parking lever (not shown) to rotate the rotating shaft 50 a, and an input shaft that is driven by the rotation of the electric motor 50. 52 is rotated, the rotation input to the input shaft 52 is decelerated, the torque is increased, and the cyclo reducer 56 output from the output shaft 54 is connected between one end of the pair of brake shoes 22 and 24. A cam member 58 disposed and rotated by the output of the output shaft 54 and spaced from one end of the pair of brake shoes 22 and 24, and the cam member 58 are supported so as to be rotatable about its axis. And an anchor member 60 that receives one end of the pair of brake shoes 22 and 24 when the drum brake 10 is braked or not braked. It has been made. Further, the brake shoe spreading mechanism 26 includes a mounting plate 62 attached to the electric motor 50 and a case member 64 disposed between the mounting plate 62 and the backing plate 18. The plate 62, the case member 64, the backing plate 18, and the anchor member 60 are fixed by a pair of bolts 66.

  As shown in FIG. 3, the anchor member 60 is fixed to one surface of the backing plate 18 and fixed by the pair of bolts 66, and one surface of the fixing portion 60a opposite to the backing plate 18 side. A shoe receiving portion 60b projecting from the through hole 60c, a through hole 60c that opens at the tip of the shoe receiving portion 60b, that is, one end portion of the anchor member 60, and into which the cam member 58 is rotatably fitted around its axis. In order to accommodate the cyclo reducer 56, which is inserted into the through hole 18a penetrating from the one surface of the fixing portion 60a on the backing plate 18 side to the predetermined position of the backing plate 18 and projecting from the back surface and communicating with the through hole 60c therein. And a mounting portion 60e having a substantially cylindrical accommodation hole 60d opened at the other end. The shoe receiving portion 60b is formed in a stepped cylindrical shape whose tip side is smaller in diameter than the base side, and the shoe webs 34, 36 of the pair of brake shoes 22, 24 are outer peripheral surfaces of the small diameter portions, that is, shoe receiving surfaces 68. Abut.

  As shown in FIGS. 3 and 4, the cam member 58 includes a substantially T-shaped rod 70 inserted into the through hole 60 c of the anchor member 60 and a slide disposed on the T-shaped rod 70. The cam 72 is constituted.

  The T-shaped rod 70 has a T-shape including a shaft portion 70a having a substantially cylindrical shape as a whole and a guide protrusion 70b having a rectangular cross section extending along one radial direction at one end thereof. Further, the T-shaped rod 70 is pierced through the through hole 60c in the shaft portion 70a so as to be rotatable around the shaft center, and the lower surface 70c of the guide projection 70b contacts the opening end surface 60f of the shoe receiving portion 60b. ing.

  Further, an O-ring 74 is disposed between the T-shaped rod 70 and the through hole 60b of the anchor member 60 to prevent water from entering the anchor member 60 from the backing plate 18. A bearing 76 is disposed between the shaft portion 70a of the T-shaped rod 70 and the inner peripheral surface of the through hole 60c of the anchor member 60, and the cam member 58, that is, the T-shaped rod is disposed in the through hole 60c. 70 can rotate smoothly around its axis. The bearing 76 is provided with a C-ring 78 that prevents the cover of the bearing 76 from falling off.

  As shown in FIGS. 2 and 4, the slide cam 72 includes a plate-like portion 72a having a shape in which a part of a circular peripheral portion is cut off by two straight lines that are parallel to each other and symmetrical with respect to the center, and an outer peripheral edge thereof. Of these, a pair of legs 72b projecting from one surface of the plate-like portion 72a in the vertical direction, that is, on the backing plate 18 side, at two positions where the arc shape remains and is symmetrical with respect to the center.

  As shown in FIGS. 3 and 4, the plate-like portion 72a has another portion, that is, an arc shape, in the center portion in the direction connecting the midpoints of the pair of arcs on one surface opposite to the leg portion 72b. 2 that is higher than the portion 72c in the vicinity of the outer peripheral edge of FIG. 2 and includes a stepped portion 72d that is rectangular, and extends along the direction perpendicular to the direction connecting the midpoints to the central portion of one surface on the leg 72b side. A groove 72e is provided. The guide groove 72e is fitted with the guide protrusion 70b of the T-shaped rod 70 so as to be relatively movable along the vertical direction, that is, the guide direction.

  As shown in FIG. 4, the pair of leg portions 72b includes a cam portion 72f extending from one surface of the plate-like portion 72a in the vertical direction, that is, the backing plate 18 side, and an arc shape of the plate-like portion 72a from the distal end portion of the cam portion 72f. A pair of guide portions 72g extending substantially along the outer peripheral edge and parallel to one surface thereof are provided. Further, the cam portion 72f has a substantially rectangular cross section as shown in FIG. 2, and the width dimension in the longitudinal direction of the guide groove 72e is that of the shoe webs 34, 36 of the pair of brake shoes 22, 24 at the time of non-braking. The distance substantially coincides with the distance between the end portions (see FIGS. 2 and 4).

  Further, the slide cam 72 has its guide groove 72e fitted into the guide projection 70b of the T-shaped rod 70, and the pair of leg portions 72b is positioned on the outer peripheral side of the small diameter portion of the shoe receiving portion 60d. 60 on the opening end face 60f. Therefore, the slide cam 72 is engaged with the T-shaped rod 70 so as to be relatively movable along the longitudinal direction of the guide groove 72e and not to be relatively rotatable around the axis of the shaft portion 70a.

  The cyclo reducer 56 is accommodated in the accommodation hole 60d of the anchor member 60, and rotates around a first axis L1 that is coaxial with the axis of the rotating shaft 50a of the electric motor 50, as shown in detail in FIG. In addition, an input shaft 52 having an eccentric portion 52b formed with an outer peripheral surface 52a centered on a second axis L2 eccentric from the first axis L1 by a predetermined amount of eccentricity e, is provided in the thickness direction. A first inner gear (inner gear) 80 that is provided with a columnar protrusion 80a and is fitted to the outer peripheral surface 52a so as to be rotatable relative to the eccentric portion 52b of the input shaft 52, and a first axis L1. And an annular first outer gear (outer gear) 82 having an inner peripheral tooth (outer pin) 92 which is provided coaxially and fixedly in position and meshes with an outer peripheral tooth 80b of the first inner gear 80, and a protrusion of the first inner gear 80 A circular hole 84a into which 80a is loosely fitted; An intermediate shaft 84 having an eccentric portion 84c formed with an outer peripheral surface 84b centered on a third axis L3 that is eccentric from the one axis L1 by a predetermined eccentric amount e, and rotating about the first axis L1; The second inner gear (second second gear) is provided with a cylindrical protrusion 86a projecting in the thickness direction and supported by the eccentric portion 84c of the intermediate shaft 84 so as to be relatively rotatable by being fitted to the outer peripheral surface 84b. (Inner gear) 86 and an annular second outer gear (second pin) having an inner peripheral tooth (outer pin 98) that is provided in a fixed position coaxially with first axis L1 and meshes with outer peripheral tooth 86b of second inner gear 86. (Inner gear) 88 and an output shaft 54 having a circular hole 54a into which the protrusion 86a of the second inner gear 86 is loosely fitted and rotating around the first axis L1.

  The input shaft 52 is provided with a connecting hole 52c having triangular tooth-like inner peripheral teeth, and a triangular tooth-like serration portion 50b provided on the outer peripheral surface of the distal end portion of the rotating shaft 50a of the electric motor 50. The input shaft 52 and the rotary shaft 50a are connected around the first axis L1 in a relatively non-rotatable manner because they are fitted into the connecting hole 52c so as not to be relatively rotatable and movable in the axial direction.

  The output shaft 54 is provided with a connecting hole 54b having a triangular tooth-shaped inner peripheral tooth, and a triangular tooth-shaped serration portion provided on the outer peripheral surface of the tip portion of the shaft portion 70a of the T-shaped rod 70. Since 70c is fitted in the connecting hole 54b so as not to be relatively rotatable and movable in the axial direction, the output shaft 52 and the shaft portion 70a of the T-shaped rod 70 are not relatively rotatable around the first axis L1. To be linked.

  As shown in FIG. 6, the first inner gear 80 includes, for example, epitrochoidal outer peripheral teeth 80b meshed with the inner peripheral teeth (outer pins 92) of the first outer gear 82, and one around the second axis L2. A plurality (eight in this embodiment) of projecting portions 80a projecting on the output shaft 54 side on the circumference and fitted on the outer peripheral surface of the projecting portions 80a so as to be rotatable relative to the projecting portions 80a. And a plurality of (30 in this embodiment) columnar shapes arranged at equal intervals on the outer peripheral surface 52a of the eccentric portion 52b of the input shaft 52. Via the roller 90, it is supported by the eccentric part 52b so that it can rotate relative to the input shaft 52 around the second axis L2.

  As shown in FIG. 6, the first outer gear 82 is a plurality of (36 in this embodiment) cylinders provided on the inner peripheral surface of the first outer gear 82 that meshes with the outer peripheral teeth 80 b of the first inner gear 80. The inner peripheral teeth formed by arranging the outer pins 92 having a shape at uniform intervals and the outer peripheral surfaces of the outer pins 92 are fitted so as to be rotatable relative to the outer pins 92. And a cylindrical metal bearing that is not fixed, and is fitted to the inner peripheral surface 60g of the mounting portion 60e of the accommodation hole 60d of the anchor member 60 in a fixed manner.

  The intermediate shaft 84 has a predetermined diameter larger than the diameter of the protrusion 80a of the first inner gear 80, and a plurality of holes (eight in this embodiment) are dug on one circumference around the first axis L1. A portion 84a and an eccentric portion 84c formed with an outer peripheral surface 84b centered on the third axis L3 that is eccentric from the first axis L1, and rotates about the first axis L1. is there.

  As shown in FIG. 7, the second inner gear 86 includes, for example, epitrochoidal outer peripheral teeth 86b meshed with the inner peripheral teeth (outer pins 98) of the second outer gear 88, and one around the third axis L3. A plurality of (eight in this embodiment) protrusions 86a located on the circumference, and a cylindrical shape fitted on the outer peripheral surface of the protrusions 86a so as to be relatively rotatable with respect to the protrusions 86a. And a plurality of (30 in this embodiment) columnar rollers 96 disposed at equal intervals on the outer peripheral surface 84b of the eccentric portion 84c of the intermediate shaft 84. Thus, it is supported by the eccentric portion 84c so as to be rotatable about the third axis L3 so as to be rotatable relative to the intermediate shaft 84.

  As shown in FIG. 7, the second outer gear 88 includes a plurality of (36 in this embodiment) cylinders provided on the inner peripheral surface of the second outer gear 88 that meshes with the outer peripheral teeth 86 b of the second inner gear 86. Inner peripheral teeth formed by arranging outer pins 98 having a shape at regular intervals, and the outer peripheral surfaces of the outer pins 98 are fitted so as to be rotatable relative to the outer pins 98. And a cylindrical metal bearing that is not fixed to the inner peripheral surface 60g of the accommodation hole 60d of the mounting portion 60e of the anchor member 60.

  As shown in FIG. 5, a ring-shaped spacer 104 is disposed between the first outer gear 82 and the second outer gear 88, and the intermediate shaft 84, the first inner gear 80, and the like are arranged by the spacer 104. A slight gap is formed between the second inner gear 86 and the rotation of the first inner gear 80 can be suitably transmitted to the second inner gear 86 via the intermediate shaft 84.

  Further, as shown in FIG. 5, the anchor member 60 includes a cam member 58, that is, a through hole 60 c that passes through the shaft portion 70 a of the T-shaped rod 70 so as to be rotatable about its axis, and a housing hole in which the cyclo reducer 56 is attached. Since it has the mounting portion 60e provided with 60d, the cam member 58 and the cyclo reducer 56 can be integrally held by the receiving hole 60d and the through hole 60c of the mounting portion 60e provided in the anchor member 60. The rotation output from the output shaft 54 of the speed reducer 56 can be suitably transmitted to the T-shaped rod 70 of the cam member 58. Further, as shown in FIG. 5, a stepped stepped portion 60 i that holds the first outer gear 82, the spacer 104, and the second outer gear 88 is arranged on the inner peripheral surface 60 g of the accommodation hole 60 d of the anchor member 60. The stepped portion 60i restricts the movement of the first outer gear 82, the spacer 104, and the second outer gear 88 on the output shaft 54 side in the direction of the first axis L1.

  Further, as shown in FIG. 5, the first outer gear 82, the second outer gear 88, and a part of the outer peripheral surface of the spacer 104 are provided with groove portions 82b, 88b, 104a dug into a semicircular cross section, A part of the inner peripheral surface 60g of the anchor member 60 is provided with a groove 60h having substantially the same shape as the grooves 82b, 88b, 104a. Therefore, the first outer gear 82, the second outer gear 88, and the spacer 104 are first with respect to the anchor member 60 by fitting the cylindrical knock pin 106 into the grooves 82b, 88b, 104a, 60h. It is fixed so as not to rotate around the axis L1.

  As shown in FIGS. 6 and 7, between the input shaft 52 and the cam member 58, that is, the shaft portion 70a of the T-shaped rod 70, a cylindrical shape that can be rotated around the shaft center, that is, the first shaft center L1. Alternatively, the cylindrical intermediate member 100 is disposed, and the needle bearings 102 are disposed between the intermediate member 100 and the input shaft 52 and the intermediate shaft 84. Therefore, the input shaft 52 and the intermediate shaft 84 are disposed. Can rotate with high accuracy around the first axis L 1, and the rotation of the first inner gear 80 can be suitably transmitted to the second inner gear 86 via the intermediate shaft 84.

  As shown in FIGS. 5 to 7, the second axis L2 and the third axis L3 are symmetrical with respect to the first axis L1, and the second axis L2 and the third axis with respect to the first axis L1. The eccentric amount e of the center L3 is the same. Further, the first inner gear 80 and the second inner gear 86 have the same shape except for the axial center position, and the first outer gear 82 and the second outer gear 88 have the same shape. Therefore, the diameter of the hole portion 84a of the intermediate shaft 84 and the hole portion 54a of the output shaft 54 are the same, and the size of the diameter is, for example, that of the first inner gear 80 or the second inner gear 86. Changes in the distance from the first axis L1 to the protrusion 80a of the first inner gear 80 or the protrusion 86a of the second inner gear 86 when the input shaft 52 or the intermediate shaft 84 rotates to the outer diameter of the metal bearings 89 and 94. It is obtained by adding a distance twice as large as the amount of eccentricity e.

  According to the cyclo reducer 56 configured in this way, when rotation is input from the rotation shaft 50a of the electric motor 50 to the input shaft 52, the input shaft 52 rotates around the first axis L1 and the first inner gear. 80 slides the projection 80a on the inner peripheral surface of the hole 84a of the intermediate shaft 84 via the eccentric portion 52b of the input shaft 52 and rotates it around the second axis L2 to rotate the projection 80a. To the intermediate shaft 84. When the rotation of the first inner gear 80 is transmitted to the intermediate shaft 84, the intermediate shaft 84 rotates around the first axis L1 and the second inner gear 86 moves the eccentric portion 84c of the intermediate shaft 84. The protrusion 86a is slid on the inner peripheral surface of the hole 54a of the output shaft 54 and rotated around the third axis L3, and the rotation is transmitted to the output shaft 54 via the protrusion 86a.

  FIG. 8 is a perspective view of the first inner gear 80 and the second inner gear 86. As shown in FIG. 8, the first inner gear 80 and the second inner gear 86 are formed by punching a flat metal plate such as a steel plate by press working, so that the outer peripheral teeth 80b and 86b and the cylindrical through holes 80c and 86c. After that, as shown in FIG. 10, a substantially cylindrical protrusion protruded in the thickness direction by half blanking for making a convex shape while stopping punching by pressing, 80a and 86a are formed. That is, the first inner gear 80 and the second inner gear 86 are integrally formed into a flat plate shape by pressing. The order of punching and half blanking may be reversed.

  Therefore, the first inner gear 80 and the inner gear 80 manufactured by a sintering process or a machining process in which a conventional sintered metal is filled in a mold and formed by press working, and then strength is imparted by a heat treatment process, are compared with those of the first inner gear 80 and Since the second inner gear 86 can be produced by pressing a flat metal member only, it does not require equipment and man-hours unlike the sintering and machining, and is produced by the sintering and machining. The inner gear can be manufactured at a lower cost than the above.

  FIG. 9 is a perspective view of the first outer gear 82 and the second outer gear 88. As shown in FIG. 9, the first outer gear 82 and the second outer gear 88 press a flat metal plate. The grooves 82b and 88b into which the inner peripheral surfaces 82a and 88a on which the outer pins 92 and 98, which are inner peripheral teeth can be disposed, and the lock pins 106 are fitted are formed by punching.

  Since the first inner gear 80, the second inner gear 86, the first outer gear 82, and the second outer gear 88 are formed from a flat metal member into a flat plate shape by pressing, the thickness direction, i. Since the distance in the direction of the single axis L1 is shorter than the inner gear and the outer gear of the conventional cyclo reducer, the cyclo reducer 56 can be suitably downsized.

  As shown in FIG. 5, in the attachment portion 60e of the anchor member 60, the side edge portion 60h, which is the opening edge portion of the accommodation hole 60d, is a first outer gear 82 using a caulking device (not shown) as shown by a one-dot chain line. Since the first outer gear 82 and the second outer gear 88 are deformed by caulking inward toward the first outer gear 82 so as to press the side surfaces of the first outer gear 82 in the axial direction, the first outer gear 82 and the second outer gear 88 are punched from a flat metal member by pressing. Even if the first outer gear 82 and the second outer gear 88 are warped, for example, both sides of the first outer gear 82 and the second outer gear 88 are attached to the spacer 104 and the anchor member 60 by the caulking. Since it is pressed through the portion 60e, it is pressed between the caulking deformed portion of the side edge portion 60h and the stepped portion 60i in the accommodation hole 60d. Warpage generated by punching and suitably suppressed thereby improving their accuracy of outer gears 82 and 88.

  In the drum brake 10 having the brake shoe expansion mechanism 26 configured as described above, when the braking operation of the parking brake is performed, the rotating shaft 50a of the electric motor 50 is rotated, and the T-character is formed via the cyclo reducer 56. The rod 70 is rotated about its axis, and the slide cam 72, that is, the cam member 58 is rotated in the R direction together with the T-shaped rod 70 as shown in FIG.

  Thereby, one end portions of the shoe webs 34 and 36 of the brake shoes 22 and 24 are pressed toward the outer peripheral side of the drum brake 10 by the side surfaces of the cam portion 72f, that is, the pair of pressing surfaces 108, respectively. 24 are rotated in the directions of arrows P1 and P2, respectively. That is, it is expanded. At this time, the brake shoes 22 and 24 rotate substantially symmetrically. Note that the pressing surface 108 is provided on the bottom surface of a recess formed between the plate-like portion 72a and the guide portion 72g, as is apparent from comparison with FIG.

  FIG. 12 shows a stage in which the brake shoes 22, 24 are expanded as described above, and in FIG. 12, the brake shoes 24 are pressed against the inner peripheral surface 16 of the rotary drum 14. ing. If the T-shaped rod 70 is further rotated in the R direction from this state, the brake shoe 22 is not yet in contact with the inner peripheral surface 16 of the rotating drum 14 and thus is rotated to the outer peripheral side. The brake shoe 24 that is pressed against the inner peripheral surface 16 cannot rotate.

  For this reason, the reaction force that the slide cam 72 receives from the brake shoes 22, 24 is relatively increased when the slide cam 72 acts from the brake shoe 24, so that the slide cam 72 receives a large reaction force from the brake shoe 24. In response to this, the T-rod 70 is moved in the arrow S direction while rotating in the R direction. As described above, the slide cam 72 is fitted to the guide protrusion 70b of the T-shaped rod 70 in the guide groove 72e so as to be relatively movable in the longitudinal direction. It is slid with respect to the rod 70. Thus, only the brake shoe 22 is rotated in the direction of the arrow P1 while the brake shoe 24 remains in the illustrated position.

  FIG. 13 shows a stage where the expansion is completed by the brake shoe 22 being pressed against the inner peripheral surface 16 of the rotary drum 14. In FIG. 13, the brake shoe 24 remains at the same position as that shown in FIG. 12, but the slide cam 72 is rotated and moved toward the brake shoe 22 along the longitudinal direction of the guide groove 72e, that is, the guide direction. Since the brake shoe 22 is pressed toward the outer peripheral side by the pressing surface 108 by being moved, it can be seen that the brake shoe 22 is further rotated than the stage shown in FIG. When a rotational force is transmitted to the rotary drum 14 in this state, one end of either one of the brake shoes 22 and 24 comes into contact with the shoe receiving surface 68 of the anchor member 60 and a braking force is generated in the drum brake 10.

  The above-described operation is performed when the shoe gaps of the pair of brake shoes 22 and 24 are different. When the shoe gaps are the same, the pressing surface 108 of the slide cam 72 causes the pair of brake shoes 22 to move. , 24, the pair of brake shoes 22 and 24 are simultaneously pressed against the inner peripheral surface 16 of the rotary drum 14 while receiving a reaction force of the same magnitude. Therefore, in this case, relative movement of the slide cam 72 with respect to the T-shaped rod 70 does not occur.

  According to the cyclo reducer 56 of the present embodiment, the first inner gear 80 and the second inner gear 86 are formed by pressing from a flat metal member, so that the conventional inner gear can be sintered and processed. Since the equipment and man-hours required for manufacturing by machining can be omitted, the cyclo reducer 56 can be manufactured at a lower cost than manufacturing by sintering or machining.

  Further, according to the cyclo reducer 56 of the present embodiment, the first outer gear 82 and the second outer gear 88 are formed by pressing from a flat metal member. The inner gears 80 and 86 and the outer gears 82 and 88 can be formed from a flat metal member, and the cyclo reducer 56 can be manufactured at a lower cost. Further, since the distance in the thickness direction of the outer gears 82 and 88 is shorter than the inner gear and the outer gear of the conventional cyclo reducer, the cyclo reducer 56 can be suitably downsized.

  Further, according to the cyclo reducer 56 of this embodiment, (a) the hole 84a into which the protrusion 80a of the first inner gear 80 is loosely fitted and the third axis L3 eccentric from the first axis L1 are the center. An intermediate shaft 84 having an eccentric portion 84c formed with an outer peripheral surface 84b and rotating about the first axis L1, and (b) projecting in a thickness direction on a circumference of the third axis L3. A second inner gear 86 provided with a protrusion 86a provided and supported so as to be rotatable relative to the eccentric portion 84c of the intermediate shaft 84; and (c) a first fixed gear provided coaxially with the first axis L1. 2 further includes an annular second outer gear 88 having inner peripheral teeth (outer pins 98) meshing with the outer peripheral teeth 86b of the inner gear 86, and (d) the second inner gear 86 in the hole 54a of the output shaft 54. (E) The second inner gear 86 and the second outer gear 88 are flat metal members. Since it is formed by press working, the inner gears 80 and 86 and the outer gears 82 and 88 of the cyclo reducer 56 of the two-stage gear can be manufactured from a flat metal member, and the distance in the thickness direction thereof is the conventional distance. Since it becomes shorter than the inner gear and the outer gear of the two-stage gear cyclo reducer, the two-stage gear cyclo reducer 56 can be further miniaturized.

  According to the cyclo reducer 56 of the present embodiment, (a) the input shaft 52 is rotationally driven by the electric motor 50, and (b) the output shaft 54 is a pair of brake shoes 22, 24 of the drum brake 10. (C) When the electric motor 50 is driven, the cam member 58 is rotated via the cyclo reducer 56 and a pair of Since the one end portions of the brake shoes 22 and 24 are separated from each other and the drum brake 10 is braked, the manufacturing cost of the drum brake 10 using the cyclo reducer 56 can be suitably reduced.

  Further, according to the cyclo reducer 56 of the present embodiment, (a) the cam member 58 has a shaft portion 70a extending so as to penetrate the backing plate 18 of the drum brake 10, and (b) the shaft portion 70a The distal end portion is connected to the output shaft 54 so as not to rotate relative to the output shaft 54. (c) The shaft portion 70a of the cam member 58 is fitted to the backing plate 18 so as to be rotatable about its axis. An anchor member 60 having a through hole 60c that opens and a receiving hole 60d that has a diameter larger than that of the through hole 60c and opens at the other end following the through hole 60c to receive the cyclo reducer 56 is fixed. Since the cam member 58 and the cyclo reducer 56 can be integrally held by the receiving hole 60d and the through hole 60c provided in the anchor member 60, the cyclo reducer 5 is provided. It can be of the transmission to the shaft portion 70a of suitably cam member 58 rotating output from the output shaft 54.

  Further, according to the cyclo reducer 56 of the present embodiment, (a) the input shaft 52 and the shaft portion 70a of the cam member 58 can be rotated around their axis, that is, the first axis L1. A cylindrical or cylindrical intermediate member 100 is disposed, and (b) a needle bearing 102 is disposed between the intermediate member 100 and the input shaft 52 and the second inner gear 86, respectively. The rotation of the first inner gear 80 can be suitably transmitted to the second inner gear 86 in the two-stage gear cyclo reducer 56.

  Further, according to the cyclo reducer 56 of the present embodiment, the first outer gear 82 and the second outer gear 88 are fitted into the accommodation hole 60d of the anchor member 60, and the opening edge of the accommodation hole 60d is fitted. When one side edge 60 h is plastically deformed inward, the first outer gear 82 and the second outer gear 88 are caulked to the anchor member 60 so as to press the side surfaces of the first outer gear 82 and the second outer gear 88. For example, when the first outer gear 82 and the second outer gear 88 are formed from a flat metal member by stamping, the first outer gear 82 and the second outer gear 88 are attached. Even if warpage occurs, the side edge 60h of the mounting portion 60e is plastically deformed inward, and the side surfaces of the first outer gear 82 and the second outer gear 88 are pressed and pressed. Warpage generated Te is suitably suppressed.

  As mentioned above, although the Example of this invention was described based on drawing, this invention is applied also in another aspect.

  For example, the cyclo reducer 56 of the present embodiment is applied to the drum brake 10, but there is no problem even if it is applied to other things.

  The cyclo reducer 56 of this embodiment is a two-stage gear cyclo reducer 56 having a first inner gear 80, a second inner gear 86, a first outer gear 82, and a second outer gear 88. The reduction gear 56 is not limited to two stages, and may have any number of stages.

  Although not illustrated one by one, the present invention can be implemented in variously modified and improved modes based on the knowledge of those skilled in the art.

It is a figure which shows the drum brake which functions as a brake device for parking using the cyclo reducer of this invention. It is a figure explaining the brake shoe expansion mechanism of the drum brake of the Example of FIG. It is the III-III sectional view taken on the line in FIG. FIG. 4 is a sectional view taken along line IV-IV in FIG. 2. It is a figure explaining the cyclo reducer with which the brake shoe expansion mechanism of the Example of FIG. 3 was equipped. FIG. 6 is a sectional view taken along line VI-VI in FIG. 5. FIG. 7 is a sectional view taken along the line VII-VII in FIG. 6. It is a perspective view explaining the 1st inner side gear and the 2nd inner side gear with which the cyclo reduction gear of Drawing 5 was equipped. It is a perspective view explaining the 1st outer side gear and the 2nd outer side gear with which the cyclo reduction gear of Drawing 5 was equipped. FIG. 9 is a sectional view taken along line XX in FIG. 8. It is a figure which shows the time of the brake shoe expansion start by a brake shoe expansion mechanism. It is a figure which shows the stage in the expansion process in which one side of the brake shoe was pressed on the rotating drum inner peripheral surface. It is a figure which shows the step which the expansion was complete | finished when a brake shoe was pressed on the internal peripheral surface of a rotating drum.

Explanation of symbols

10: drum brake 18: backing plate 22, 24: pair of brake shoes 50: electric motor 52: input shaft 52a: outer peripheral surface 52d: eccentric portion 54: output shaft 54a: hole 56: cyclo reducer 58: cam member 60: Anchor member 60c: Through hole 60d: Housing hole 60h: Side edge portion 70a: Shaft portion 80: Inner gear (first inner gear)
80a: Projection 80b: Outer peripheral tooth 82: Outer gear (first outer gear)
84: Intermediate shaft 84a: Hole portion 84b: Outer peripheral surface 84c: Eccentric portion 86: Second inner gear (second inner gear)
86a: Projection 86b: Outer peripheral tooth 88: Second outer gear (second outer gear)
100: Intermediate member 102: Bearing (needle bearing)
L1: First axis L2: Second axis L3: Third axis

Claims (7)

An input shaft that rotates around the first axis and has an eccentric portion formed with an outer peripheral surface centered on the second axis that is eccentric from the first axis, and a circumference around the second axis An inner gear provided with a protrusion projecting in the thickness direction on the top and an outer peripheral tooth; and supported by a eccentric portion of the input shaft so as to be relatively rotatable; and provided in a fixed position coaxially with the first axis. An annular outer gear having inner peripheral teeth that mesh with outer peripheral teeth of the inner gear, and an output shaft that includes a hole portion in which a protrusion of the inner gear is loosely fitted and rotates about the first axis, A cyclo reducer that decelerates rotation of the input shaft and outputs from the output shaft,
The cyclo reducer according to claim 1, wherein the inner gear is formed by pressing from a flat metal member.   The cyclo reducer according to claim 1, wherein the outer gear is formed from a flat metal member by pressing. A hole portion into which the protruding portion of the inner gear is loosely fitted and an eccentric portion formed with an outer peripheral surface centering on a third axis that is eccentric from the first axis, and around the first axis. A rotating intermediate shaft,
A second inner gear provided with a protrusion projecting in a thickness direction on one circumference around the third axis and supported by the eccentric part of the intermediate shaft so as to be relatively rotatable;
An annular second outer gear provided with a fixed inner position coaxially with the first axis and having an inner peripheral tooth meshing with an outer peripheral tooth of the second inner gear;
A protrusion of the second inner gear is loosely fitted in the hole of the output shaft,
The cyclo reducer according to claim 1 or 2, wherein the second inner gear and the second outer gear are formed from a flat metal member by pressing. The input shaft is rotationally driven by an electric motor,
The output shaft is connected to a cam member disposed between one end portions of a pair of brake shoes of the drum brake so as not to be relatively rotatable,
4. The drum brake is braked by driving the electric motor to rotate a cam member via the cyclo reducer and to separate one end portions of the pair of brake shoes. 5. 1 cyclo reducer. The cam member has a shaft portion extending so as to penetrate the backing plate of the drum brake,
The tip portion of the shaft portion is connected to the output shaft so as not to be relatively rotatable,
The backing plate has a through-hole that opens at one end for fitting the shaft portion of the cam member so as to be rotatable about its axis, and the through-hole that follows the through-hole to accommodate the cyclo reducer. The cyclo reducer according to claim 4, wherein an anchor member having a receiving hole formed at a diameter larger than the hole and opened at the other end is fixed. Between the input shaft and the shaft portion of the cam member, a columnar or cylindrical intermediate member that is rotatable around the axis is disposed.
The cyclo reducer according to claim 5, wherein a bearing is provided between each of the intermediate member, the input shaft, and the second inner gear.   The outer gear and the second outer gear are fitted into the accommodation hole of the anchor member, and the opening edge of the accommodation hole is plastically deformed inward to press the side surface of the outer gear. The cyclo reducer according to claim 5 or 6, wherein the outer gear and the second outer gear are caulked to the anchor member.

Images