WO2012060333A1 - Vehicle door drive device - Google Patents

Vehicle door drive device Download PDF

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Publication number
WO2012060333A1
WO2012060333A1 PCT/JP2011/075086 JP2011075086W WO2012060333A1 WO 2012060333 A1 WO2012060333 A1 WO 2012060333A1 JP 2011075086 W JP2011075086 W JP 2011075086W WO 2012060333 A1 WO2012060333 A1 WO 2012060333A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
shaft
planetary
sun gear
carrier
Prior art date
Application number
PCT/JP2011/075086
Other languages
French (fr)
Japanese (ja)
Inventor
守 丸谷
Original Assignee
アイシン精機 株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by アイシン精機 株式会社 filed Critical アイシン精機 株式会社
Publication of WO2012060333A1 publication Critical patent/WO2012060333A1/en

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F15/00—Power-operated mechanisms for wings
    • E05F15/60—Power-operated mechanisms for wings using electrical actuators
    • E05F15/603—Power-operated mechanisms for wings using electrical actuators using rotary electromotors
    • E05F15/632—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for horizontally-sliding wings
    • E05F15/643—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for horizontally-sliding wings operated by flexible elongated pulling elements, e.g. belts, chains or cables
    • E05F15/646—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for horizontally-sliding wings operated by flexible elongated pulling elements, e.g. belts, chains or cables allowing or involving a secondary movement of the wing, e.g. rotational or transversal
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2201/00—Constructional elements; Accessories therefor
    • E05Y2201/20—Brakes; Disengaging means; Holders; Stops; Valves; Accessories therefor
    • E05Y2201/218—Holders
    • E05Y2201/22—Locks
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2201/00—Constructional elements; Accessories therefor
    • E05Y2201/60—Suspension or transmission members; Accessories therefor
    • E05Y2201/622—Suspension or transmission members elements
    • E05Y2201/71—Toothed gearing
    • E05Y2201/72—Planetary gearing
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2400/00—Electronic control; Electrical power; Power supply; Power or signal transmission; User interfaces
    • E05Y2400/10—Electronic control
    • E05Y2400/30—Electronic control of motors
    • E05Y2400/3013—Electronic control of motors during manual wing operation
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2900/00—Application of doors, windows, wings or fittings thereof
    • E05Y2900/50—Application of doors, windows, wings or fittings thereof for vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/14—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising conical gears only
    • F16H1/145—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising conical gears only with offset axes, e.g. hypoïd gearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion

Definitions

  • the present invention relates to a vehicle door drive device for driving a vehicle door that opens and closes a door opening formed in a vehicle body.
  • the vehicle door drive device described in Patent Document 1 selectively uses a vehicle door movable along a guide rail fixed to the vehicle body, a drive unit fixed to the vehicle door, and the drive unit. And a cable to be wound and fed out. Both ends of the cable are respectively connected to the vehicle body at the front end and the rear end of the guide rail.
  • the drive selectively winds up and unwinds the cable, the vehicle door opens and closes.
  • Patent Document 2 describes a drive unit applicable to such a vehicle door drive device.
  • the drive unit includes a planetary gear mechanism as a reduction mechanism.
  • this planetary gear mechanism includes a sun gear, a ring gear surrounding the sun gear, a plurality of planetary gears meshing with the sun gear and the ring gear, and a carrier rotating with revolution of the planetary gear.
  • This planetary gear mechanism has a sun gear directly connected to the rotation shaft of the motor as a drive shaft, a ring gear connected integrally with the drum as a driven shaft as a driven shaft, and a carrier as a fixed shaft. It is transmitted to The cable is taken up and fed out with the rotation of the drum, whereby the vehicle door is opened and closed.
  • the planetary gear mechanism When the planetary gear mechanism is used as a speed reduction mechanism, a configuration in which the sun gear is used as a drive shaft, the ring gear is used as a fixed shaft, and the carrier is used as a driven shaft can be considered.
  • the sun gear is rotatably supported on the support shaft.
  • the drum and the carrier are coupled to the support shaft so as to be integrally rotatable on the support shaft.
  • the carrier is provided with a planetary shaft, via which the planetary gear is rotatably supported. Further, the ring gear is supported on the drum in a state of being locked for rotation.
  • the support shaft in order to transmit the revolution of the planetary gear to the drum, the support shaft is provided with a carrier that can rotate integrally with the support shaft separately from the other components of the planetary gear mechanism.
  • the rotation of the carrier is transmitted to the drum via the support shaft. Therefore, the number of parts of the vehicle door drive device is increased by the amount of the carrier on the support shaft, and the structure of the drive device is complicated. These are obstacles to the cost reduction and weight reduction of the vehicle door drive device.
  • Such a problem may occur similarly in a configuration in which the ring gear is used as a drive shaft and the sun gear is used as a fixed shaft and the carrier is used as a driven shaft.
  • An object of the present invention is to provide a vehicle door drive device capable of simplifying the structure as well as reducing the number of parts.
  • an embodiment of the present invention provides a door drive apparatus for a vehicle that decelerates the rotation of a motor and transmits it to an output member to rotate the output member, thereby opening and closing a vehicle door.
  • This vehicle door drive device includes a planetary gear mechanism having a sun gear, a ring gear that surrounds the sun gear, a planetary gear that meshes with the sun gear and the ring gear, and a carrier that rotates with revolution of the planetary gear.
  • One of the sun gear and the ring gear is a drive shaft rotationally driven by a motor, and the other is a fixed shaft.
  • the carrier is a driven shaft.
  • a part of the output member constitutes a carrier.
  • FIG. 2 is a cross-sectional view taken along line 2-2 of FIG.
  • ruptures and shows one part about the drive part of the door drive device for vehicles of FIG. (A) is sectional drawing along 5a-5a line of FIG. 4, (b) is sectional drawing which expands and shows the C section of (a).
  • Explanatory drawing which shows the meshing relationship of the transmission gear and pinion in the drive part of FIG.
  • a door opening 10 a is formed on the side of the vehicle body 10.
  • the upper rail 11 and the lower rail 12 are installed along the upper edge and the lower edge of the door opening 10a, respectively.
  • a center rail 13 extending in the vehicle front-rear direction (hereinafter, the front-rear direction) is installed on the quarter panel 10 b on the rear side of the door opening 10 a.
  • a slide door 15 as a vehicle door is supported by the upper rail 11, the lower rail 12 and the center rail 13 via a guide roller unit 14 so as to be movable in the front-rear direction.
  • the slide door 15 opens and closes the door opening 10a in accordance with the movement in the front-rear direction.
  • the center rail 13 is disposed at a height near the door belt line of the vehicle.
  • a cable guide 16 is installed on the quarter panel 10 b so as to extend along the lower edge of the center rail 13 along the entire length of the center rail 13.
  • the drive unit 20 is fixed in the slide door 15 at a height near the door belt line by fastening using, for example, a bolt and a nut. More specifically, as shown in FIG. 2, in the door thickness direction (vehicle width direction), as shown in FIG. 2, the door trim 17 constituting the lining of the sliding door 15 and the door inner panel constituting the door inner plate 18 is fixed to the door inner panel 18 in such a manner as to be sandwiched therebetween.
  • the door window glass DW for moving up and down the inside of the slide door 15 is disposed outside (outside in the vehicle width direction) the door inner panel 18. That is, although the drive part 20 is arrange
  • the drive unit 20 includes a motor 22 composed of a brush motor, and a drum 23 as an output member rotationally driven by the motor 22.
  • a first cable 24 and a second cable 25 as rope members are respectively wound around the drum 23. That is, each of the first and second cables 24 and 25 is wound around the drum 23 in a state where the first end is locked to the drum 23 respectively.
  • the first and second cables 24 and 25 are selectively wound and fed out by the drive unit 20.
  • the drive unit 20 also includes an intermediate pulley 26 as a pulley mechanism.
  • Each of the first and second cables 24 and 25 is passed from the slide door 15 to the vehicle body 10 through the intermediate pulley 26 and the guide pulley 27 connected to the guide roller unit 14 moving the center rail 13. It is routed along the guide 16 in the front-rear direction.
  • the intermediate pulley 26 and the guide pulley 27 are disposed at a height near the door belt line, at a position behind the drum 23 and at a position further behind the drum.
  • the first cable 24 is guided by the cable guide 16 and routed on the front side, and for example a bolt and a nut for the vehicle body 10 at the front end of the cable guide 16 via the tensioner 28 connected to the second end.
  • the second cable 25 is guided by the cable guide 16 and routed rearward, and is connected to the vehicle body 10 at the rear end of the cable guide 16 via the tensioner 29 connected to the second end, for example, a bolt and a nut It is connected by the conclusion using.
  • the structure of the drive unit 20 will be further described.
  • the drive unit 20 has a case 30 which has an outer shape and accommodates and supports various components.
  • the case 30 includes a case main body 31 forming a housing space for various components, and a first cover 32 and a second cover closing an opening of the case main body 31 which opens in opposite directions (vehicle width direction). 33 (see FIG. 3).
  • the drive unit 20 is fixed to and supported by the door inner panel 18 by fastening the case body 31 to the door inner panel 18.
  • Each of the case body 31, the first cover 32, and the second cover 33, which are constituent members of the case 30, is formed of, for example, a resin material.
  • the case body 31 integrally has a motor holder 31a, a gear housing 31b, a lever housing 31d, a substrate housing 31e, and a pair of pulley housings 31f, 31g.
  • the motor holder portion 31 a is disposed at the vehicle front upper edge portion of the case main body 31.
  • the gear accommodating portion 31 b has a bottom portion and has a substantially cylindrical shape, and is disposed adjacent to the lower rear side of the motor holder portion 31 a.
  • the lever accommodating portion 31d has a bottom portion and has a substantially sectoral cylindrical shape, and is disposed adjacent to the rear side of the gear accommodating portion 31b.
  • the board accommodating portion 31e has a lid portion and is cylindrical, and is disposed adjacent to the lower side of the gear accommodating portion 31b in such a manner as to extend between the gear accommodating portion 31b and the lever accommodating portion 31d.
  • the two pulley accommodating portions 31f and 31g are disposed above the lever accommodating portion 31d and on the vehicle rear side of the gear accommodating portion 31b.
  • the gear accommodating portion 31 b and the lever accommodating portion 31 d communicate with each other in such a manner that a part of a circular cylinder portion is overlapped. Further, the pulley accommodating portions 31f and 31g communicate with the gear accommodating portion 31b.
  • the motor 22 is assembled to the motor holder portion 31a.
  • the rotation shaft 22b of the motor 22 has an axis extending in a direction offset with respect to the direction toward the center of the gear housing 31b.
  • a pinion 34 is connected to the rotation shaft 22 b so as to be integrally rotatable with the pinion 34.
  • the pinion 34 is rotatably supported on the motor holder portion 31a by a rolling bearing 35 (FIG. 5).
  • the pinion 34 is formed with a threaded portion (a so-called high speed reduction helical gear with a small number of teeth) 34 a having two threads (even number of threads).
  • the number of lines of the pinion 34 may be an even number of four or more, or may be an odd number other than one.
  • the case main body 31 and the first cover 32 have a substantially cylindrical support shaft extending in the vehicle width direction (the vertical direction in FIGS. 5A and 5B).
  • 36 are rotatably supported. More specifically, a circular bearing hole 31j is formed at the center of the bottom of the gear housing 31b.
  • a circular bearing hole 32 b is formed in the first cover 32 at a position facing the bearing hole 31 j.
  • shaft portions 36a and 36b having a substantially cylindrical shape are formed at both end portions of the support shaft 36, respectively.
  • the shaft portion 36a is pivotally supported by the bearing hole 31j, and the shaft portion 36b is pivotally supported by the bearing hole 32b.
  • a serration 36c is formed at a location different from the location where the transmission gear 38 described later is supported, in this embodiment, a location adjacent to the first cover 32 side than the shaft 36a.
  • the drum 23 is coupled to the support shaft 36 so as to be integrally rotatable at a location. That is, the substantially cylindrical drum 23 opens toward the first cover 32 and has a bottom wall at one end in the axial direction.
  • the drum 23 has a circular accommodation space S inside its cylindrical outer peripheral wall. In the central portion of the bottom wall portion 23a of the drum 23, an insertion hole 23b having a serration 23c penetrates.
  • the support shaft 36 is inserted into the insertion hole 23 b, and the serration 23 c of the drum 23 is engaged with the serration 36 c of the support shaft 36.
  • the support shaft 36 is axially adjacent to the shaft portion 36b and includes a shaft portion 36d having a diameter larger than that of the coaxial portion 36b.
  • a transmission gear 38 is rotatably supported on the shaft portion 36 d as an input member rotationally driven by the motor 22. That is, a substantially cylindrical bearing 38 a is provided at the central portion of the transmission gear 38, and the bearing 38 a is rotatably fitted on the shaft 36 d of the support shaft 36.
  • the transmission gear 38 extends from the end of the bearing 38a near the first cover 32 radially outward of the bearing 38a.
  • a disc gear portion 38b is provided to cover the open end face of the gear housing portion 31b.
  • a plurality of tooth portions 38c arranged in an annular shape are provided on the outer peripheral edge portion of the disc gear portion 38b and on the surface facing the pinion 34 (the lower side in FIGS. 5A and 5B). It is formed.
  • the teeth 38c are formed to have a twist so as to mesh with the screw 34a of the pinion 34 in a rolling contact (line contact) state.
  • a sun gear 38d is formed on the outer peripheral surface of the bearing portion 38a at a location adjacent to the serration 36c.
  • a portion closer to the first cover 32 than the sun gear 38d that is, on the transmission gear (input member) 38 and opposite to the drum 23 (output member) with the sun gear 38d interposed therebetween.
  • a gear member 39 is rotatably supported at the upper part of FIG. 5 (b).
  • the gear member 39 has a substantially disk shape and includes a lid 39a covering the open end face of the drum 23, and an annular ring gear 39b which protrudes from the lid 39a toward the drum 23 and surrounds the sun gear 38d.
  • a circular bearing hole 39c is formed at the center of the lid 39a.
  • the lid 39a is rotatably fitted around the bearing 38a in the bearing hole 39c.
  • a plurality of locking teeth 39d each having a substantially triangular shape is formed on the outer peripheral surface of the lid 39a.
  • the ring gear 39 b is accommodated in the accommodation space S of the drum 23. Internal teeth are formed on the inner peripheral surface of the ring gear 39b.
  • a plurality of (three in this embodiment) planetary gears 41 are disposed between the bottom wall 23a of the drum 23 and the lid 39a in a state of being engaged with the sun gear 38d of the transmission gear 38 and the ring gear 39b.
  • the bottom wall 23a of the drum 23 functions as a shaft attachment. That is, while a plurality of attachment holes 23d are penetrated at equal angle intervals in the bottom wall portion 23a, the end portions 42a of the plurality of planetary shafts 42 arranged in parallel to the support shaft 36 are inserted into the corresponding attachment holes 23d. It is locked so that it can not fall off.
  • the planetary gear 41 is rotatably supported on each of the planetary shafts 42.
  • each planetary gear 41 In the planetary shaft 42 of each planetary gear 41, a flange 42c is formed at an end opposite to the end 42a near the bottom wall 23a.
  • the planetary gear 41 is sandwiched from both sides in the axial direction by the flange portion 42c and the bottom wall portion 23a.
  • Each planetary gear 41 can rotate (revolution) around the sun gear 38 d while rotating (rotation) around the planetary shaft 42.
  • the bottom wall portion 23 a (shaft attached portion) to which the planetary shaft 42 is attached functions as a carrier that rotates along with the revolution of the planetary gear 41.
  • the bottom wall portion 23a of the drum 23 functioning as a carrier that rotates with the revolution of the planetary gear 41 and the planetary gear 41 meshing with the sun gear 38d, the ring gear 39b surrounding the sun gear 38d, the sun gear 38d and the ring gear 39b
  • a planetary gear mechanism G1 as a reduction mechanism is configured by the attachment portion).
  • the switching lever 43 in which the cam hole 43 a is formed is rotatably supported by the lever housing portion 31 d.
  • An engagement / disengagement block 44 is disposed between the switching lever 43 and the gear member 39 so as to be movable in the radial direction of the gear member 39.
  • An engagement pin 44a provided on the engagement / disengagement block 44 is inserted into the cam hole 43a.
  • the engagement / disengagement block 44 is formed with a plurality of locking teeth 44 b that can be engaged with the locking teeth 39 d of the gear member 39.
  • Pulleys 45 and 46 having outer diameters different from each other are rotatably supported by the pulley accommodating portions 31 f and 31 g.
  • the two pulleys 45 and 46 constitute the intermediate pulley 26.
  • the first and second cables 24 and 25 wound and unwound from the drum 23 are hung on the two pulleys 45 and 46, respectively.
  • the two pulleys 45 and 46 pass the first and second cables 24 and 25 to the guide pulley 27 through the dustproof cable grommet 47.
  • An ECU (Electronic Control Units) substrate (not shown) is accommodated in the substrate accommodation portion 31e.
  • An ECU or the like mainly composed of a microcomputer is mounted on the ECU substrate.
  • a bus bar (not shown) for electrically connecting the power feeding portion of the motor 22 held by the motor holder portion 31a and the ECU substrate is embedded.
  • the locking tooth 44b of the engagement / disengagement block 44 is engaged with the locking tooth 39d, and the motor 22 rotates in a state in which the ring gear 39b (gear member 39) is locked in a non-rotatable manner.
  • the rotation of the motor 22 is transmitted to the transmission gear 38 after being decelerated at the first stage through the pinion 34 and the disc gear portion 38 b.
  • the rotation of the transmission gear 38 (the disk gear portion 38b) uses the sun gear 38d of the transmission gear 38 as a drive shaft, the carrier (bottom wall 23a of the drum 23) as a driven shaft, and the ring gear 39b as a fixed shaft.
  • the second stage is decelerated at the reduction ratio and transmitted to the drum 23.
  • the respective planetary gears 41 meshed with the sun gear 38d and the ring gear 39b form the bottom wall portion 23a of the drum 23 (shaft attached portion While rotating (rotation) around a planetary shaft 42 attached to the shaft as an axis, it rotates (revolutions) around a sun gear 38d.
  • the planetary shaft 42 is displaced around the sun gear 38d in accordance with this revolution.
  • the bottom wall portion 23a which constitutes a part of the drum 23 functions as a carrier. Therefore, when the planetary gear 41 and the planetary shaft 42 revolve around the sun gear 38d as described above, a force to rotate the drum 23 is transmitted to the drum 23 through the bottom wall portion 23a. This force causes the drum 23 to rotate about the sun gear 38d.
  • the rotation of the motor 22 is sufficiently decelerated and transmitted to the drum 23 via the pinion 34, the disc gear portion 38b, and the planetary gear mechanism G1.
  • the drum 23 rotates, the first cable 24 and the second cable 25 are wound up and fed out, and the slide door 15 is opened and closed. Therefore, in order to transmit the revolution of the planetary gear 41 to the drum 23 for rotation, it is not necessary to separately provide a carrier.
  • each planetary shaft 42 The planetary gear 41 supported by each planetary shaft 42 is sandwiched between the bottom wall 23 a of the drum 23 and the flange portion 42 c of the planetary shaft 42, and the movement in the direction along the planetary shaft 42 is restricted.
  • the sun gear 38d of the planetary gear mechanism G1 is used as a drive shaft to be rotationally driven by the motor 22, and the ring gear 39b is used as a fixed shaft, and the carrier is used as a driven shaft to reduce the rotation of the motor 22 It is transmitted to the drum 23 as an output member to rotate the drum 23, and the slide door 15 is operated to open and close.
  • a part of the drum 23 functions as a carrier.
  • a part of the drum 23 functions as a carrier. Therefore, the rotation (revolution) of the planetary gear 41 can be directly transmitted to the drum 23 without the support shaft 36.
  • the bottom wall portion 23a of the drum 23 is used as a shaft attachment portion, and the planetary shaft 42 is attached thereto.
  • a planetary gear 41 is supported on each planetary shaft 42.
  • the structure which attaches the planetary shaft 42 to the bottom wall part 23a as mentioned above does not consist, when the ring gear 39b interposes between the bottom wall part 23a and the planetary shaft 42.
  • the lid 39a is supported on the transmission gear 38 at a position opposite to the drum 23 with the sun gear 38d interposed therebetween, and the ring gear 39b is protruded from the lid 39a toward the drum 23. . Since the space which arrange
  • a flange 42c is formed at the end opposite to the end 42a near the bottom wall 23a (shaft attached portion).
  • the planetary gear 41 is sandwiched between the bottom wall portion 23a and the flange portion 42c to restrict the movement of the planetary gear 41 in the direction along the axis of the planetary shaft 42, and the planetary gear 41 is engaged with the sun gear 38d and the ring gear 39b. Can be held.
  • the ring gear 39b is a drive shaft rotationally driven by the motor 22, the carrier is a driven shaft, and the sun gear 38d is a fixed shaft to reduce the rotation of the motor 22.
  • the present invention can also be applied to a vehicle door drive device that transmits and rotates the drum 23 as an output member to open and close the vehicle door.
  • the planetary shaft 42 is directly attached to the bottom wall portion 23a of the drum 23, and the planetary gear 41 is supported on the planetary shaft 42, so that the bottom wall portion 23a functions as a carrier. Also in this case, the same operation and advantage as the above embodiment can be obtained.
  • the drive unit 20 may be fixed to the vehicle body 10 side.
  • the drive unit 20 when the drive unit 20 is mounted on the quarter panel 10 b, it is more preferable to connect the tensioners 28 and 29 to the drive unit 20.
  • a mechanism for transmitting the rotation of the motor 22 to the transmission gear 38 a mechanism different from the above embodiment (face gear including the disk gear portion 38b and the pinion 34), for example, a combination of spur gears, a worm gear, etc. may be used. .
  • the present invention is applicable not only to the slide door 15 but also to a vehicle door drive device for opening and closing a hinged vehicle door.

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Abstract

This vehicle door drive device causes an opening/closing operation of a vehicle door by means of causing the rotation of an output member by decelerating and transmitting the rotation of a motor to the output member. The vehicle door drive device is provided with an epicyclic gear mechanism having: a sun gear; a ring gear that encircles the sun gear; a planetary gear that meshes with the sun gear and the ring gear; and a carrier that rotates with the rotation of the planetary gear. One of either the sun gear or the ring gear is the drive shaft driven to rotate by the motor, and the other is a fixed shaft. The carrier is the driven shaft. A portion of the output member configures the carrier.

Description

車両用ドア駆動装置Vehicle door drive
　本発明は、車両ボディに形成されたドア開口を開閉する車両ドアを駆動する車両用ドア駆動装置に関する。 The present invention relates to a vehicle door drive device for driving a vehicle door that opens and closes a door opening formed in a vehicle body.
　従来では、種々の車両用ドア駆動装置が提案されている。例えば特許文献１に記載された車両用ドア駆動装置は、車両ボディに固定されたガイドレールに沿って移動可能な車両ドアと、車両ドアに固定される駆動部と、同駆動部により選択的に巻取り及び繰出しされるケーブルとを備えている。同ケーブルの両端末は、ガイドレールの前端及び後端において車両ボディにそれぞれ連結されている。従って、駆動部がケーブルを選択的に巻取り及び繰出しすると、車両ドアが開閉作動する。 Conventionally, various vehicle door drive devices have been proposed. For example, the vehicle door drive device described in Patent Document 1 selectively uses a vehicle door movable along a guide rail fixed to the vehicle body, a drive unit fixed to the vehicle door, and the drive unit. And a cable to be wound and fed out. Both ends of the cable are respectively connected to the vehicle body at the front end and the rear end of the guide rail. Thus, when the drive selectively winds up and unwinds the cable, the vehicle door opens and closes.
　特許文献２には、こうした車両用ドア駆動装置に適用可能な駆動部について記載されている。この駆動部は、減速機構として遊星歯車機構を備える。この遊星歯車機構は、周知のように、サンギヤと、サンギヤを取り囲むリングギヤと、サンギヤ及びリングギヤに噛合する複数のプラネタリギヤと、プラネタリギヤの公転とともに回転するキャリアとを備える。この遊星歯車機構は、モータの回転軸に直結されたサンギヤを駆動軸とし、ドラムに一体回転可能に連結されたリングギヤを従動軸とし、キャリアを固定軸とした減速比で、モータの回転をドラムに伝達している。このドラムの回転に伴いケーブルが巻取り・繰出しされることで、車両ドアが開閉作動する。 Patent Document 2 describes a drive unit applicable to such a vehicle door drive device. The drive unit includes a planetary gear mechanism as a reduction mechanism. As is well known, this planetary gear mechanism includes a sun gear, a ring gear surrounding the sun gear, a plurality of planetary gears meshing with the sun gear and the ring gear, and a carrier rotating with revolution of the planetary gear. This planetary gear mechanism has a sun gear directly connected to the rotation shaft of the motor as a drive shaft, a ring gear connected integrally with the drum as a driven shaft as a driven shaft, and a carrier as a fixed shaft. It is transmitted to The cable is taken up and fed out with the rotation of the drum, whereby the vehicle door is opened and closed.
特開２００３－８２９２７号公報Japanese Patent Application Laid-Open No. 2003-82927 特表２００９－５２３９８３号公報Japanese Patent Publication No. 2009-523983
　遊星歯車機構を減速機構として用いる場合、上記特許文献２に記載された構成以外にも、サンギヤを駆動軸とするとともにリングギヤを固定軸とし、キャリアを従動軸とする構成が考えられる。 When the planetary gear mechanism is used as a speed reduction mechanism, a configuration in which the sun gear is used as a drive shaft, the ring gear is used as a fixed shaft, and the carrier is used as a driven shaft can be considered.
　この場合、支持軸上にサンギヤが回転自在に支持される。また、該支持軸上に、ドラム及びキャリアが支持軸と一体回転可能にそれぞれ連結される。キャリアにはプラネタリシャフトが設けられ、該プラネタリシャフトを介してプラネタリギヤが回転可能に支持される。さらに、ドラム上にリングギヤが回転を係止された状態で支持される。 In this case, the sun gear is rotatably supported on the support shaft. Further, the drum and the carrier are coupled to the support shaft so as to be integrally rotatable on the support shaft. The carrier is provided with a planetary shaft, via which the planetary gear is rotatably supported. Further, the ring gear is supported on the drum in a state of being locked for rotation.
　上記の遊星歯車機構では、サンギヤがモータによって回転駆動されると、そのサンギヤの回転がプラネタリギヤに伝達され、各プラネタリギヤがプラネタリシャフトを軸として回転（自転）しながらサンギヤの回りを回転（公転）する。これらのプラネタリギヤの公転とともにキャリアが回転する。このキャリアの回転が支持軸に伝達されて、同支持軸がドラムを伴って回転する。 In the above planetary gear mechanism, when the sun gear is rotationally driven by the motor, the rotation of the sun gear is transmitted to the planetary gear, and each planetary gear rotates around the sun gear (rotation) while rotating about the planetary shaft (rotation). . The carrier rotates with the revolution of these planetary gears. The rotation of the carrier is transmitted to the support shaft, which rotates with the drum.
　上記の構成では、プラネタリギヤの公転をドラムに伝達するために、遊星歯車機構の他の構成部材とは別に、支持軸に同支持軸と一体回転可能なキャリアが設けられている。このキャリアの回転が支持軸を介してドラムに伝達される。そのため、支持軸上のキャリアの分、車両用ドア駆動装置の部品点数が多くなるとともに、同駆動装置の構造が複雑となる。これらのことが、車両用ドア駆動装置の低コスト化及び軽量化の障害となっている。 In the above-described configuration, in order to transmit the revolution of the planetary gear to the drum, the support shaft is provided with a carrier that can rotate integrally with the support shaft separately from the other components of the planetary gear mechanism. The rotation of the carrier is transmitted to the drum via the support shaft. Therefore, the number of parts of the vehicle door drive device is increased by the amount of the carrier on the support shaft, and the structure of the drive device is complicated. These are obstacles to the cost reduction and weight reduction of the vehicle door drive device.
　このような問題は、リングギヤを駆動軸とするとともにサンギヤを固定軸とし、キャリアを従動軸とした構成においても同様に起こり得る。 Such a problem may occur similarly in a configuration in which the ring gear is used as a drive shaft and the sun gear is used as a fixed shaft and the carrier is used as a driven shaft.
　本発明の目的は、部品点数を削減するとともに、構造の簡略化を図ることのできる車両用ドア駆動装置を提供することにある。 An object of the present invention is to provide a vehicle door drive device capable of simplifying the structure as well as reducing the number of parts.
　上記目的を達成するため、本発明の一実施形態では、モータの回転を減速して出力部材に伝達して同出力部材を回転させ、それによって車両ドアを開閉作動させる車両用ドア駆動装置を提供する。この車両用ドア駆動装置は、サンギヤと、サンギヤを取り囲むリングギヤと、サンギヤ及びリングギヤに噛合するプラネタリギヤと、プラネタリギヤの公転とともに回転するキャリアとを有する遊星歯車機構を備える。サンギヤ及びリングギヤの一方は、モータにより回転駆動される駆動軸であり、他方は固定軸である。キャリアは従動軸である。出力部材の一部がキャリアを構成する。 In order to achieve the above object, an embodiment of the present invention provides a door drive apparatus for a vehicle that decelerates the rotation of a motor and transmits it to an output member to rotate the output member, thereby opening and closing a vehicle door. Do. This vehicle door drive device includes a planetary gear mechanism having a sun gear, a ring gear that surrounds the sun gear, a planetary gear that meshes with the sun gear and the ring gear, and a carrier that rotates with revolution of the planetary gear. One of the sun gear and the ring gear is a drive shaft rotationally driven by a motor, and the other is a fixed shaft. The carrier is a driven shaft. A part of the output member constitutes a carrier.
本発明の一実施形態における車両用ドア駆動装置を示す模式図。BRIEF DESCRIPTION OF THE DRAWINGS The schematic diagram which shows the door drive device for vehicles in one Embodiment of this invention. 図１の２－２線に沿った断面図。FIG. 2 is a cross-sectional view taken along line 2-2 of FIG. 図１の車両用ドア駆動装置における駆動部の分解斜視図。The disassembled perspective view of the drive part in the door drive device for vehicles of FIG. 図１の車両用ドア駆動装置の駆動部について、一部を破断して示す正面図。The front view which fractures | ruptures and shows one part about the drive part of the door drive device for vehicles of FIG. （ａ）は図４の５ａ－５ａ線に沿った断面図、（ｂ）は（ａ）のＣ部を拡大して示す断面図。(A) is sectional drawing along 5a-5a line of FIG. 4, (b) is sectional drawing which expands and shows the C section of (a). 図３の駆動部における伝達ギヤ及びピニオンの噛合関係を示す説明図。Explanatory drawing which shows the meshing relationship of the transmission gear and pinion in the drive part of FIG.
　以下、本発明を具体化した一実施形態について、図面を参照して説明する。 Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
　図１に示すように、車両ボディ１０の側部にはドア開口１０ａが形成されている。ドア開口１０ａの上縁及び下縁に沿ってそれぞれアッパレール１１及びロアレール１２が設置されている。ドア開口１０ａの後方のクォータパネル１０ｂには、車両前後方向（以下、前後方向）に延在するセンターレール１３が設置されている。これらアッパレール１１、ロアレール１２及びセンターレール１３には、それぞれガイドローラユニット１４を介して、車両ドアとしてのスライドドア１５が前後方向に移動可能に支持されている。このスライドドア１５は、前後方向への移動に伴ってドア開口１０ａを開閉する。 As shown in FIG. 1, a door opening 10 a is formed on the side of the vehicle body 10. The upper rail 11 and the lower rail 12 are installed along the upper edge and the lower edge of the door opening 10a, respectively. A center rail 13 extending in the vehicle front-rear direction (hereinafter, the front-rear direction) is installed on the quarter panel 10 b on the rear side of the door opening 10 a. A slide door 15 as a vehicle door is supported by the upper rail 11, the lower rail 12 and the center rail 13 via a guide roller unit 14 so as to be movable in the front-rear direction. The slide door 15 opens and closes the door opening 10a in accordance with the movement in the front-rear direction.
　なお、センターレール１３は、車両のドアベルトライン付近の高さに配置されている。クォータパネル１０ｂには、センターレール１３の下縁に沿って同センターレール１３の全長にわたり延びるように、ケーブルガイド１６が設置されている。 The center rail 13 is disposed at a height near the door belt line of the vehicle. A cable guide 16 is installed on the quarter panel 10 b so as to extend along the lower edge of the center rail 13 along the entire length of the center rail 13.
　スライドドア１５内には、前記ドアベルトライン付近の高さにおいて、例えばボルト及びナットを用いた締結により駆動部２０が固定されている。より詳細には、図２に示すように、駆動部２０は、ドア厚さ方向（車両幅方向）において、スライドドア１５のドア内張りを構成するドアトリム１７と、ドア内板を構成するドアインナパネル１８との間に挟まれる態様で、そのドアインナパネル１８に固定されている。 The drive unit 20 is fixed in the slide door 15 at a height near the door belt line by fastening using, for example, a bolt and a nut. More specifically, as shown in FIG. 2, in the door thickness direction (vehicle width direction), as shown in FIG. 2, the door trim 17 constituting the lining of the sliding door 15 and the door inner panel constituting the door inner plate 18 is fixed to the door inner panel 18 in such a manner as to be sandwiched therebetween.
　なお、スライドドア１５の内部を昇降するドアウインドガラスＤＷは、ドアインナパネル１８よりも外側（車両幅方向外側）に配置されている。すなわち、駆動部２０は、ドアウインドガラスＤＷと重なるような高さに配置されるものの、そのドアウインドガラスＤＷの昇降動作を妨げることはない。 The door window glass DW for moving up and down the inside of the slide door 15 is disposed outside (outside in the vehicle width direction) the door inner panel 18. That is, although the drive part 20 is arrange | positioned in the height which overlaps with the door window glass DW, it does not prevent the raising / lowering operation of the door window glass DW.
　図１に示すように、駆動部２０は、ブラシモータからなるモータ２２と、そのモータ２２により回転駆動される出力部材としてのドラム２３とを備えている。ドラム２３には、ロープ部材としての第１ケーブル２４及び第２ケーブル２５がそれぞれ巻回されている。すなわち、第１及び第２ケーブル２４，２５の各々は、第１の端末がドラム２３にそれぞれ係止された状態でそのドラム２３に巻回されている。第１及び第２ケーブル２４，２５は、駆動部２０により選択的に巻取り及び繰出しされる。 As shown in FIG. 1, the drive unit 20 includes a motor 22 composed of a brush motor, and a drum 23 as an output member rotationally driven by the motor 22. A first cable 24 and a second cable 25 as rope members are respectively wound around the drum 23. That is, each of the first and second cables 24 and 25 is wound around the drum 23 in a state where the first end is locked to the drum 23 respectively. The first and second cables 24 and 25 are selectively wound and fed out by the drive unit 20.
　また、駆動部２０は、プーリ機構としての中間プーリ２６を備えている。第１及び第２ケーブル２４，２５の各々は、中間プーリ２６と、センターレール１３を移動するガイドローラユニット１４に連結された案内プーリ２７とを経てスライドドア１５から車両ボディ１０へ渡され、ケーブルガイド１６に沿って前後方向に配索されている。中間プーリ２６及び案内プーリ２７は、前記ドアベルトライン付近の高さにおいて、ドラム２３より後方の位置、及びさらにその後方の位置にそれぞれ配置されている。 The drive unit 20 also includes an intermediate pulley 26 as a pulley mechanism. Each of the first and second cables 24 and 25 is passed from the slide door 15 to the vehicle body 10 through the intermediate pulley 26 and the guide pulley 27 connected to the guide roller unit 14 moving the center rail 13. It is routed along the guide 16 in the front-rear direction. The intermediate pulley 26 and the guide pulley 27 are disposed at a height near the door belt line, at a position behind the drum 23 and at a position further behind the drum.
　第１ケーブル２４は、ケーブルガイド１６に案内されて前側に配索され、第２の端末に連結されたテンショナー２８を介して、ケーブルガイド１６の前端で車両ボディ１０に、例えばボルト及びナットを用いた締結によって連結されている。第２ケーブル２５は、ケーブルガイド１６に案内されて後側に配索され、第２の端末に連結されたテンショナー２９を介して、ケーブルガイド１６の後端で車両ボディ１０に、例えばボルト及びナットを用いた締結によって連結されている。 The first cable 24 is guided by the cable guide 16 and routed on the front side, and for example a bolt and a nut for the vehicle body 10 at the front end of the cable guide 16 via the tensioner 28 connected to the second end. Were linked by the contract. The second cable 25 is guided by the cable guide 16 and routed rearward, and is connected to the vehicle body 10 at the rear end of the cable guide 16 via the tensioner 29 connected to the second end, for example, a bolt and a nut It is connected by the conclusion using.
　このような構成にあって、例えば駆動部２０が第１ケーブル２４を繰出しつつ第２ケーブル２５を巻き取ると、スライドドア１５はドア開口１０ａを開放すべく後方に移動する。一方、駆動部２０が第１ケーブル２４を巻き取りつつ第２ケーブル２５を繰出すと、スライドドア１５はドア開口１０ａを閉鎖すべく前方に移動する。 In such a configuration, for example, when the drive unit 20 unwinds the first cable 24 and winds up the second cable 25, the slide door 15 moves rearward to open the door opening 10a. On the other hand, when the drive unit 20 unwinds the second cable 25 while winding up the first cable 24, the slide door 15 moves forward to close the door opening 10a.
　ドラム２３から巻取り及び繰出しされる第１及び第２ケーブル２４，２５の延在方向が第１及び第２ケーブル２４，２５が案内プーリ２７に渡される方向に一致する場合には、中間プーリ２６は割愛されてもよい。 When the extension direction of the first and second cables 24 and 25 wound and unwound from the drum 23 coincides with the direction in which the first and second cables 24 and 25 are passed to the guide pulley 27, the intermediate pulley 26 is May be omitted.
　上記駆動部２０の構造についてさらに説明する。 The structure of the drive unit 20 will be further described.
　図３～図５（ａ），（ｂ）に示すように、駆動部２０は、その外形をなすとともに各種構成部品を収容及び支持するケース３０を備える。このケース３０は、各種構成部品の収容空間を形成するケース本体３１と、そのケース本体３１の互いに相反する方向（車両幅方向）に開口する開口部をそれぞれ閉塞する第１カバー３２及び第２カバー３３（図３参照）とを備えている。駆動部２０は、ケース本体３１がドアインナパネル１８に締結されることで、そのドアインナパネル１８に固定及び支持される。ケース３０の構成部材であるケース本体３１、第１カバー３２及び第２カバー３３の各々は、例えば樹脂材によって成形されている。 As shown in FIGS. 3 to 5 (a) and 5 (b), the drive unit 20 has a case 30 which has an outer shape and accommodates and supports various components. The case 30 includes a case main body 31 forming a housing space for various components, and a first cover 32 and a second cover closing an opening of the case main body 31 which opens in opposite directions (vehicle width direction). 33 (see FIG. 3). The drive unit 20 is fixed to and supported by the door inner panel 18 by fastening the case body 31 to the door inner panel 18. Each of the case body 31, the first cover 32, and the second cover 33, which are constituent members of the case 30, is formed of, for example, a resin material.
　ケース本体３１は、モータホルダ部３１ａ、ギヤ収容部３１ｂ、レバー収容部３１ｄ、基板収容部３１ｅ及び一対のプーリ収容部３１ｆ，３１ｇを一体的に有する。図４に示すように、モータホルダ部３１ａは、ケース本体３１の車両前側上縁部に配置されている。ギヤ収容部３１ｂは、底部を有するとともに略円筒状をなし、モータホルダ部３１ａの車両後下側に隣接配置されている。レバー収容部３１ｄは、底部を有するとともに略扇形筒状をなし、ギヤ収容部３１ｂの車両後側に隣接配置されている。基板収容部３１ｅは蓋部を有するとともに筒状をなし、ギヤ収容部３１ｂ及びレバー収容部３１ｄ間に延在する態様で同ギヤ収容部３１ｂの下側に隣接配置されている。両プーリ収容部３１ｆ，３１ｇは、レバー収容部３１ｄの上側であってギヤ収容部３１ｂの車両後側に上下に並べられた状態で配設されている。なお、ギヤ収容部３１ｂ及びレバー収容部３１ｄは、円形の筒部の一部が重なる態様で互いに連通している。さらに、プーリ収容部３１ｆ，３１ｇは、ギヤ収容部３１ｂにそれぞれ連通している。 The case body 31 integrally has a motor holder 31a, a gear housing 31b, a lever housing 31d, a substrate housing 31e, and a pair of pulley housings 31f, 31g. As shown in FIG. 4, the motor holder portion 31 a is disposed at the vehicle front upper edge portion of the case main body 31. The gear accommodating portion 31 b has a bottom portion and has a substantially cylindrical shape, and is disposed adjacent to the lower rear side of the motor holder portion 31 a. The lever accommodating portion 31d has a bottom portion and has a substantially sectoral cylindrical shape, and is disposed adjacent to the rear side of the gear accommodating portion 31b. The board accommodating portion 31e has a lid portion and is cylindrical, and is disposed adjacent to the lower side of the gear accommodating portion 31b in such a manner as to extend between the gear accommodating portion 31b and the lever accommodating portion 31d. The two pulley accommodating portions 31f and 31g are disposed above the lever accommodating portion 31d and on the vehicle rear side of the gear accommodating portion 31b. The gear accommodating portion 31 b and the lever accommodating portion 31 d communicate with each other in such a manner that a part of a circular cylinder portion is overlapped. Further, the pulley accommodating portions 31f and 31g communicate with the gear accommodating portion 31b.
　図４～図６に示すように、モータホルダ部３１ａには上記モータ２２が組付けられている。モータ２２の回転軸２２ｂは、ギヤ収容部３１ｂの中心に向かう方向に対しオフセットした方向へ延びている軸線を有する。回転軸２２ｂには、ピニオン３４がピニオン３４と一体回転可能に連結されている。ピニオン３４は転がり軸受３５（図５）によりモータホルダ部３１ａに対し回転自在に支持されている。ピニオン３４には、２条（偶数条数）のねじ部（いわゆる歯数の少ない高減速ヘリカルギヤ）３４ａが形成されている。ピニオン３４の条数は、４以上の偶数であってもよいし、１を除く奇数であってもよい。 As shown in FIGS. 4 to 6, the motor 22 is assembled to the motor holder portion 31a. The rotation shaft 22b of the motor 22 has an axis extending in a direction offset with respect to the direction toward the center of the gear housing 31b. A pinion 34 is connected to the rotation shaft 22 b so as to be integrally rotatable with the pinion 34. The pinion 34 is rotatably supported on the motor holder portion 31a by a rolling bearing 35 (FIG. 5). The pinion 34 is formed with a threaded portion (a so-called high speed reduction helical gear with a small number of teeth) 34 a having two threads (even number of threads). The number of lines of the pinion 34 may be an even number of four or more, or may be an odd number other than one.
　図５（ａ），（ｂ）に示すように、ケース本体３１及び第１カバー３２には、車両幅方向（図５（ａ），（ｂ）の上下方向）に延びる略円柱状の支持軸３６が回転自在に支持されている。より詳しくは、ギヤ収容部３１ｂの底部中央には円形の軸受孔３１ｊが形成されている。第１カバー３２において上記軸受孔３１ｊと対向する箇所には、円形の軸受穴３２ｂが形成されている。一方、支持軸３６の両端部には、それぞれ略円柱状をなす軸部３６ａ，３６ｂが形成されている。軸部３６ａが軸受孔３１ｊに軸支され、軸部３６ｂが軸受穴３２ｂに軸支されている。 As shown in FIGS. 5A and 5B, the case main body 31 and the first cover 32 have a substantially cylindrical support shaft extending in the vehicle width direction (the vertical direction in FIGS. 5A and 5B). 36 are rotatably supported. More specifically, a circular bearing hole 31j is formed at the center of the bottom of the gear housing 31b. A circular bearing hole 32 b is formed in the first cover 32 at a position facing the bearing hole 31 j. On the other hand, shaft portions 36a and 36b having a substantially cylindrical shape are formed at both end portions of the support shaft 36, respectively. The shaft portion 36a is pivotally supported by the bearing hole 31j, and the shaft portion 36b is pivotally supported by the bearing hole 32b.
　支持軸３６において、後述する伝達ギヤ３８が支持される箇所とは異なる箇所、本実施形態では、軸部３６ａよりも第１カバー３２側に隣接する箇所にはセレーション３６ｃが形成されており、同箇所に上記ドラム２３が支持軸３６と一体回転可能に連結されている。すなわち、略円筒状のドラム２３は、前記第１カバー３２に向けて開口するとともに、その軸線方向一端に底壁を有する。ドラム２３は、その円筒状外周壁の内側に円形の収容空間Ｓを有している。ドラム２３の底壁部２３ａの中央部には、セレーション２３ｃを有する挿通孔２３ｂが貫通している。支持軸３６がこの挿通孔２３ｂに挿通され、ドラム２３のセレーション２３ｃが支持軸３６のセレーション３６ｃに係合されている。 In the support shaft 36, a serration 36c is formed at a location different from the location where the transmission gear 38 described later is supported, in this embodiment, a location adjacent to the first cover 32 side than the shaft 36a. The drum 23 is coupled to the support shaft 36 so as to be integrally rotatable at a location. That is, the substantially cylindrical drum 23 opens toward the first cover 32 and has a bottom wall at one end in the axial direction. The drum 23 has a circular accommodation space S inside its cylindrical outer peripheral wall. In the central portion of the bottom wall portion 23a of the drum 23, an insertion hole 23b having a serration 23c penetrates. The support shaft 36 is inserted into the insertion hole 23 b, and the serration 23 c of the drum 23 is engaged with the serration 36 c of the support shaft 36.
　支持軸３６は、前記軸部３６ｂに軸線方向に隣接し同軸部３６ｂよりも大径の軸部３６ｄを備える。この軸部３６ｄ上には、モータ２２によって回転駆動される入力部材として、伝達ギヤ３８が回転自在に支持されている。すなわち、伝達ギヤ３８の中心部分には略円筒状の軸受部３８ａが設けられており、この軸受部３８ａが支持軸３６の軸部３６ｄ上に回転自在に外嵌されている。 The support shaft 36 is axially adjacent to the shaft portion 36b and includes a shaft portion 36d having a diameter larger than that of the coaxial portion 36b. A transmission gear 38 is rotatably supported on the shaft portion 36 d as an input member rotationally driven by the motor 22. That is, a substantially cylindrical bearing 38 a is provided at the central portion of the transmission gear 38, and the bearing 38 a is rotatably fitted on the shaft 36 d of the support shaft 36.
　図５（ａ），（ｂ）及び図６に示すように、伝達ギヤ３８は、上記軸受部３８ａの第１カバー３２寄りの端部から、同軸受部３８ａの径方向外側へ延出して、ギヤ収容部３１ｂの開口端面を覆う円盤ギヤ部３８ｂを有している。円盤ギヤ部３８ｂの外周縁部であって、ピニオン３４に対向する側（図５（ａ），（ｂ）の下側）の面には、円環状に配設された複数の歯部３８ｃが形成されている。これら歯部３８ｃは、ピニオン３４のねじ部３４ａに対して転がり接触（線接触）の状態で歯合するようにねじれを有するように成形されている。そのため、ピニオン３４（ねじ部３４ａ）が回転すると、その回転がねじ部３４ａの条数と円盤ギヤ部３８ｂとの歯数との比に応じて減速されて伝達ギヤ３８に伝達され、これによって同伝達ギヤ３８が回転する。 As shown in FIGS. 5 (a), 5 (b) and 6, the transmission gear 38 extends from the end of the bearing 38a near the first cover 32 radially outward of the bearing 38a. A disc gear portion 38b is provided to cover the open end face of the gear housing portion 31b. A plurality of tooth portions 38c arranged in an annular shape are provided on the outer peripheral edge portion of the disc gear portion 38b and on the surface facing the pinion 34 (the lower side in FIGS. 5A and 5B). It is formed. The teeth 38c are formed to have a twist so as to mesh with the screw 34a of the pinion 34 in a rolling contact (line contact) state. Therefore, when the pinion 34 (screw portion 34a) rotates, the rotation is decelerated according to the ratio of the number of threads of the screw portion 34a to the number of teeth of the disc gear portion 38b and transmitted to the transmission gear 38. The transmission gear 38 rotates.
　なお、ねじ部３４ａ及び円盤ギヤ部３８ｂの一方が樹脂で作製され、他方が金属で作製されていると、回転による異音が生じにくい。 When one of the screw portion 34a and the disk gear portion 38b is made of resin and the other is made of metal, abnormal noise due to rotation is less likely to occur.
　図３、図４及び図５（ａ），（ｂ）に示すように、軸受部３８ａの外周面において、セレーション３６ｃと隣接する箇所にはサンギヤ３８ｄが形成されている。軸受部３８ａの外周面において、サンギヤ３８ｄよりも第１カバー３２寄りの部分、すなわち、伝達ギヤ（入力部材）３８上であって、サンギヤ３８ｄを挟んでドラム２３（出力部材）とは反対側（図５（ｂ）の上側）の部分には、ギヤ部材３９が回転自在に支持されている。ギヤ部材３９は、略円盤状をなし、かつドラム２３の開口端面を覆う蓋部３９ａと、その蓋部３９ａからドラム２３に向けて突出し、サンギヤ３８ｄを取り囲む円環状のリングギヤ３９ｂとを備える。蓋部３９ａの中央部には、円形の軸受孔３９ｃが形成されている。蓋部３９ａは、この軸受孔３９ｃにおいて上記軸受部３８ａに対し回転自在に外嵌されている。蓋部３９ａの外周面には、それぞれ略三角形状をなす複数の係止歯３９ｄが形成されている。 As shown in FIGS. 3, 4 and 5A and 5B, a sun gear 38d is formed on the outer peripheral surface of the bearing portion 38a at a location adjacent to the serration 36c. On the outer peripheral surface of the bearing portion 38a, a portion closer to the first cover 32 than the sun gear 38d, that is, on the transmission gear (input member) 38 and opposite to the drum 23 (output member) with the sun gear 38d interposed therebetween. A gear member 39 is rotatably supported at the upper part of FIG. 5 (b). The gear member 39 has a substantially disk shape and includes a lid 39a covering the open end face of the drum 23, and an annular ring gear 39b which protrudes from the lid 39a toward the drum 23 and surrounds the sun gear 38d. A circular bearing hole 39c is formed at the center of the lid 39a. The lid 39a is rotatably fitted around the bearing 38a in the bearing hole 39c. A plurality of locking teeth 39d each having a substantially triangular shape is formed on the outer peripheral surface of the lid 39a.
　リングギヤ３９ｂは、ドラム２３の上記収容空間Ｓに収容されている。リングギヤ３９ｂの内周面には内歯が形成されている。 The ring gear 39 b is accommodated in the accommodation space S of the drum 23. Internal teeth are formed on the inner peripheral surface of the ring gear 39b.
　ドラム２３の底壁部２３ａと蓋部３９ａとの間には、複数（本実施形態では３つ）のプラネタリギヤ４１が、伝達ギヤ３８のサンギヤ３８ｄとリングギヤ３９ｂとに噛合した状態で配設されている。ドラム２３の底壁部２３ａはシャフト被着部として機能する。すなわち、この底壁部２３ａに複数の取付孔２３ｄが等角度間隔で貫通されるとともに、支持軸３６に平行に配置された複数本のプラネタリシャフト４２の端部４２ａが対応する取付孔２３ｄに挿入されて、抜け落ち不能に係止されている。各プラネタリシャフト４２上には、上記プラネタリギヤ４１が回転自在に支持されている。 A plurality of (three in this embodiment) planetary gears 41 are disposed between the bottom wall 23a of the drum 23 and the lid 39a in a state of being engaged with the sun gear 38d of the transmission gear 38 and the ring gear 39b. There is. The bottom wall 23a of the drum 23 functions as a shaft attachment. That is, while a plurality of attachment holes 23d are penetrated at equal angle intervals in the bottom wall portion 23a, the end portions 42a of the plurality of planetary shafts 42 arranged in parallel to the support shaft 36 are inserted into the corresponding attachment holes 23d. It is locked so that it can not fall off. The planetary gear 41 is rotatably supported on each of the planetary shafts 42.
　プラネタリギヤ４１毎のプラネタリシャフト４２について、底壁部２３ａ寄りの端部４２ａとは反対側の端部には、鍔部４２ｃが形成されている。この鍔部４２ｃと底壁部２３ａとによって、プラネタリギヤ４１が軸線方向についての両側から挟み込まれている。各プラネタリギヤ４１は、プラネタリシャフト４２の回りで回転（自転）しつつサンギヤ３８ｄの回りを回転（公転）可能である。上記プラネタリシャフト４２が取付けられた底壁部２３ａ（シャフト被着部）は、プラネタリギヤ４１の公転とともに回転するキャリアとして機能する。 In the planetary shaft 42 of each planetary gear 41, a flange 42c is formed at an end opposite to the end 42a near the bottom wall 23a. The planetary gear 41 is sandwiched from both sides in the axial direction by the flange portion 42c and the bottom wall portion 23a. Each planetary gear 41 can rotate (revolution) around the sun gear 38 d while rotating (rotation) around the planetary shaft 42. The bottom wall portion 23 a (shaft attached portion) to which the planetary shaft 42 is attached functions as a carrier that rotates along with the revolution of the planetary gear 41.
　上記のように、サンギヤ３８ｄと、サンギヤ３８ｄを取り囲むリングギヤ３９ｂと、サンギヤ３８ｄ及びリングギヤ３９ｂに噛合するプラネタリギヤ４１と、プラネタリギヤ４１の公転とともに回転するキャリアとして機能するドラム２３の底壁部２３ａ（シャフト被着部）とによって、減速機構としての遊星歯車機構Ｇ１が構成されている。 As described above, the bottom wall portion 23a of the drum 23 functioning as a carrier that rotates with the revolution of the planetary gear 41 and the planetary gear 41 meshing with the sun gear 38d, the ring gear 39b surrounding the sun gear 38d, the sun gear 38d and the ring gear 39b A planetary gear mechanism G1 as a reduction mechanism is configured by the attachment portion).
　図３及び図４に示すように、レバー収容部３１ｄには、カム孔４３ａが形成された切替えレバー４３が回転自在に支持されている。切替えレバー４３とギヤ部材３９との間には、係脱ブロック４４が同ギヤ部材３９の径方向への移動可能に配置されている。この係脱ブロック４４に設けられた係合ピン４４ａが上記カム孔４３ａに挿通されている。係脱ブロック４４には、上記ギヤ部材３９の係止歯３９ｄに係合し得る複数の係止歯４４ｂが形成されている。 As shown in FIGS. 3 and 4, the switching lever 43 in which the cam hole 43 a is formed is rotatably supported by the lever housing portion 31 d. An engagement / disengagement block 44 is disposed between the switching lever 43 and the gear member 39 so as to be movable in the radial direction of the gear member 39. An engagement pin 44a provided on the engagement / disengagement block 44 is inserted into the cam hole 43a. The engagement / disengagement block 44 is formed with a plurality of locking teeth 44 b that can be engaged with the locking teeth 39 d of the gear member 39.
　切替えレバー４３が回転されることにより、カム孔４３ａにおける係合ピン４４ａの位置が変化し、係脱ブロック４４がギヤ部材３９に接近又は離間させられる。モータ２２によってドラム２３を回転させてスライドドア１５を開閉作動させる際には、係脱ブロック４４がギヤ部材３９へ向けて押し出され、その係止歯４４ｂがギヤ部材３９の係止歯３９ｄに噛合い、ギヤ部材３９を回転不能に係止する。 By rotating the switching lever 43, the position of the engagement pin 44a in the cam hole 43a is changed, and the engagement / disengagement block 44 is moved closer to or away from the gear member 39. When the drum 22 is rotated by the motor 22 to open and close the slide door 15, the engagement / disengagement block 44 is pushed toward the gear member 39, and the engagement tooth 44b is engaged with the engagement tooth 39d of the gear member 39. And the gear member 39 is non-rotatably locked.
　手動でドラム２３を回転させてスライドドア１５を開閉作動させる際には、係脱ブロック４４が切替えレバー４３へ向けて引き戻され、係止歯４４ｂの係止歯３９ｄとの噛合が解除され、これによって、ギヤ部材３９が回転可能になる。図５（ａ），（ｂ）では、切替えレバー４３の一部のみが図示されている。 When the drum 23 is manually rotated to open and close the slide door 15, the engagement / disengagement block 44 is pulled back toward the switching lever 43, and the engagement between the engagement tooth 44b and the engagement tooth 39d is released. Thus, the gear member 39 becomes rotatable. In FIGS. 5A and 5B, only a part of the switching lever 43 is illustrated.
　プーリ収容部３１ｆ，３１ｇには、互いに異なる外径を有するプーリ４５，４６が回転自在に支持されている。両プーリ４５，４６は、前記中間プーリ２６を構成する。両プーリ４５，４６には、ドラム２３から巻取り及び繰出しされる第１ケーブル２４及び第２ケーブル２５がそれぞれ案内される態様で掛けられる。両プーリ４５，４６は、第１及び第２ケーブル２４，２５を、防塵用のケーブルグロメット４７を介して前記案内プーリ２７に渡す。 Pulleys 45 and 46 having outer diameters different from each other are rotatably supported by the pulley accommodating portions 31 f and 31 g. The two pulleys 45 and 46 constitute the intermediate pulley 26. The first and second cables 24 and 25 wound and unwound from the drum 23 are hung on the two pulleys 45 and 46, respectively. The two pulleys 45 and 46 pass the first and second cables 24 and 25 to the guide pulley 27 through the dustproof cable grommet 47.
　基板収容部３１ｅには、ＥＣＵ（ｅｌｅｃｔｒｏｎｉｃ　ｃｏｎｔｒｏｌ　ｕｎｉｔｓ）基板（図示略）が収容されている。このＥＣＵ基板には、マイクロコンピュータから主として構成されたＥＣＵ等が実装されている。 An ECU (Electronic Control Units) substrate (not shown) is accommodated in the substrate accommodation portion 31e. An ECU or the like mainly composed of a microcomputer is mounted on the ECU substrate.
　前記ケース本体３１には、モータホルダ部３１ａに保持されたモータ２２の給電部と前記ＥＣＵ基板とを電気的に接続するためのバスバー（図示略）が埋設されている。 In the case main body 31, a bus bar (not shown) for electrically connecting the power feeding portion of the motor 22 held by the motor holder portion 31a and the ECU substrate is embedded.
　上記車両用ドア駆動装置の作用について説明する。 The operation of the vehicle door drive device will be described.
　係脱ブロック４４の係止歯４４ｂが係止歯３９ｄに噛合されて、リングギヤ３９ｂ（ギヤ部材３９）が回転不能に係止されている状態でモータ２２が回転する。モータ２２の回転は、ピニオン３４及び円盤ギヤ部３８ｂを介して第１段の減速がなされて伝達ギヤ３８に伝達される。伝達ギヤ３８（円盤ギヤ部３８ｂ）の回転は、遊星歯車機構Ｇ１において、伝達ギヤ３８のサンギヤ３８ｄを駆動軸とし、キャリア（ドラム２３の底壁部２３ａ）を従動軸とし、リングギヤ３９ｂを固定軸とした減速比で第２段の減速がなされてドラム２３に伝達される。すなわち、伝達ギヤ３８（円盤ギヤ部３８ｂ）の回転に伴いサンギヤ３８ｄが回転されると、同サンギヤ３８ｄ及びリングギヤ３９ｂに噛合された各プラネタリギヤ４１が、ドラム２３の底壁部２３ａ（シャフト被着部）に取付けられたプラネタリシャフト４２を軸としてその回りを回転（自転）しながら、サンギヤ３８ｄの回りを回転（公転）する。この公転に伴い、プラネタリシャフト４２がサンギヤ３８ｄの回りを変位する。 The locking tooth 44b of the engagement / disengagement block 44 is engaged with the locking tooth 39d, and the motor 22 rotates in a state in which the ring gear 39b (gear member 39) is locked in a non-rotatable manner. The rotation of the motor 22 is transmitted to the transmission gear 38 after being decelerated at the first stage through the pinion 34 and the disc gear portion 38 b. In the planetary gear mechanism G1, the rotation of the transmission gear 38 (the disk gear portion 38b) uses the sun gear 38d of the transmission gear 38 as a drive shaft, the carrier (bottom wall 23a of the drum 23) as a driven shaft, and the ring gear 39b as a fixed shaft. The second stage is decelerated at the reduction ratio and transmitted to the drum 23. That is, when the sun gear 38d is rotated with the rotation of the transmission gear 38 (the disk gear portion 38b), the respective planetary gears 41 meshed with the sun gear 38d and the ring gear 39b form the bottom wall portion 23a of the drum 23 (shaft attached portion While rotating (rotation) around a planetary shaft 42 attached to the shaft as an axis, it rotates (revolutions) around a sun gear 38d. The planetary shaft 42 is displaced around the sun gear 38d in accordance with this revolution.
　本実施形態では、ドラム２３の一部を構成する底壁部２３ａがキャリアとして機能する。そのため、上記のようにプラネタリギヤ４１及びプラネタリシャフト４２がサンギヤ３８ｄの回りで公転すると、底壁部２３ａを通じてドラム２３に対し、ドラム２３を回転させようとする力が伝わる。この力がドラム２３をサンギヤ３８ｄの回りで回転させる。 In the present embodiment, the bottom wall portion 23a which constitutes a part of the drum 23 functions as a carrier. Therefore, when the planetary gear 41 and the planetary shaft 42 revolve around the sun gear 38d as described above, a force to rotate the drum 23 is transmitted to the drum 23 through the bottom wall portion 23a. This force causes the drum 23 to rotate about the sun gear 38d.
　このように、モータ２２の回転は、ピニオン３４及び円盤ギヤ部３８ｂと、遊星歯車機構Ｇ１とを介して十分に減速されてドラム２３に伝達される。ドラム２３の回転に伴い、第１ケーブル２４及び第２ケーブル２５が巻取り及び繰出しされ、スライドドア１５が開閉作動する。従って、プラネタリギヤ４１の公転をドラム２３に伝達して回転させるために、キャリアを別途設ける必要がない。 Thus, the rotation of the motor 22 is sufficiently decelerated and transmitted to the drum 23 via the pinion 34, the disc gear portion 38b, and the planetary gear mechanism G1. As the drum 23 rotates, the first cable 24 and the second cable 25 are wound up and fed out, and the slide door 15 is opened and closed. Therefore, in order to transmit the revolution of the planetary gear 41 to the drum 23 for rotation, it is not necessary to separately provide a carrier.
　リングギヤ３９ｂが回転不能に係止されている上記状態でスライドドア１５を手動で開閉操作する場合、仮に係脱ブロック４４によるリングギヤ３９ｂの係止状態が維持されたとしても、スライドドア１５の開閉作動に伴うドラム２３の回転は、遊星歯車機構Ｇ１、ピニオン３４及び円盤ギヤ部３８ｂを通じて効率よく伝達される。そのため、ある程度の操作力によりモータ２２（回転軸２２ｂ）等を回転させつつスライドドア１５を開閉操作することが可能となる。 When the slide door 15 is manually opened and closed in the above state in which the ring gear 39b is non-rotatably locked, even if the locking state of the ring gear 39b by the engagement / disengagement block 44 is maintained, the opening / closing operation of the slide door 15 is performed. The rotation of the drum 23 accompanying with the above is efficiently transmitted through the planetary gear mechanism G1, the pinion 34 and the disc gear portion 38b. Therefore, it is possible to open and close the slide door 15 while rotating the motor 22 (rotation shaft 22b) and the like with a certain amount of operation force.
　一方、係脱ブロック４４によるリングギヤ３９ｂの係止状態が解除されている状態で、スライドドア１５を手動で開閉操作する場合、スライドドア１５の開閉に伴うドラム２３（キャリア）の回転はリングギヤ３９ｂ（ギヤ部材３９）を空転させつつ許容される。このように、係脱ブロック４４等によりドラム２３からの回転トルクのモータ２２の回転軸２２ｂへの伝達を遮断することで、軽微な操作力によるスライドドア１５の開閉操作が可能となる。 On the other hand, when the slide door 15 is manually opened and closed while the locked state of the ring gear 39b is released by the engagement / disengagement block 44, the rotation of the drum 23 (carrier) accompanying the opening and closing of the slide door 15 is ring gear 39b ( It is permitted while the gear member 39) is idled. As described above, by blocking the transmission of the rotational torque from the drum 23 to the rotational shaft 22b of the motor 22 by the engagement / disengagement block 44 or the like, the slide door 15 can be opened and closed by a slight operation force.
　各プラネタリシャフト４２に支持されたプラネタリギヤ４１は、ドラム２３の底壁部２３ａと同プラネタリシャフト４２の鍔部４２ｃとによって挟み込まれた状態となり、同プラネタリシャフト４２に沿う方向の動きを規制される。 The planetary gear 41 supported by each planetary shaft 42 is sandwiched between the bottom wall 23 a of the drum 23 and the flange portion 42 c of the planetary shaft 42, and the movement in the direction along the planetary shaft 42 is restricted.
　以上詳述した本実施形態によれば、次の利点が得られる。 According to the embodiment described above, the following advantages can be obtained.
　（１）遊星歯車機構Ｇ１のサンギヤ３８ｄを、モータ２２によって回転駆動される駆動軸とするとともに、リングギヤ３９ｂを固定軸とし、キャリアを従動軸とすることで、モータ２２の回転を減速して、出力部材としてのドラム２３に伝達して同ドラム２３を回転させ、スライドドア１５を開閉作動させる。このように構成した車両用ドア駆動装置において、ドラム２３の一部がキャリアとして機能する。 (1) The sun gear 38d of the planetary gear mechanism G1 is used as a drive shaft to be rotationally driven by the motor 22, and the ring gear 39b is used as a fixed shaft, and the carrier is used as a driven shaft to reduce the rotation of the motor 22 It is transmitted to the drum 23 as an output member to rotate the drum 23, and the slide door 15 is operated to open and close. In the vehicle door drive device configured as described above, a part of the drum 23 functions as a carrier.
　そのため、プラネタリギヤ４１の公転をドラム２３に伝達してドラム２３を回転させるために、キャリアを別途設ける必要がない。その分、車両用ドア駆動装置の部品点数が少なくなるとともに、構造が簡単になる。これに伴い、車両用ドア駆動装置のコストの低減、及び軽量化を図ることもできる。 Therefore, in order to transmit the revolution of the planetary gear 41 to the drum 23 to rotate the drum 23, it is not necessary to separately provide a carrier. Accordingly, the number of parts of the vehicle door drive device is reduced and the structure is simplified. Along with this, it is possible to reduce the cost and weight of the vehicle door drive device.
　通常の遊星歯車機構では、キャリアはプラネタリシャフト４２の軸線方向についての両側に設けられる。本実施形態では、このキャリアを設ける必要がないことから、同軸線方向についての駆動部２０の小型化を図ることができる。 In a conventional planetary gear mechanism, carriers are provided on both sides of the planetary shaft 42 in the axial direction. In the present embodiment, since it is not necessary to provide this carrier, it is possible to miniaturize the drive unit 20 in the coaxial line direction.
　（２）通常の遊星歯車機構では、キャリアを別途設ける場合には、そのキャリアはドラムとともに支持軸に一体回転可能に連結される。支持軸上には、サンギヤが回転自在に支持される。ドラム上には、リングギヤが回転を係止された状態で支持される。 (2) In a conventional planetary gear mechanism, when the carrier is separately provided, the carrier is coupled to the support shaft together with the drum so as to be integrally rotatable. A sun gear is rotatably supported on the support shaft. A ring gear is supported on the drum in a rotationally locked state.
　上記の遊星歯車機構では、サンギヤがモータによって回転駆動されると、そのサンギヤの回転がプラネタリギヤに伝達され、各プラネタリギヤが自転しながらサンギヤの回りで公転する。これらのプラネタリギヤの公転とともにキャリアが回転する。このキャリアの回転が支持軸に一旦伝達されて、同支持軸がドラムを伴って回転する。このように、キャリアの回転が支持軸を介してドラムに伝達される。 In the above-described planetary gear mechanism, when the sun gear is rotationally driven by the motor, the rotation of the sun gear is transmitted to the planetary gear, and each planetary gear revolves around the sun gear while rotating on its own. The carrier rotates with the revolution of these planetary gears. The rotation of the carrier is once transmitted to the support shaft, and the support shaft rotates with the drum. Thus, the rotation of the carrier is transmitted to the drum via the support shaft.
　これに対し、本実施形態では、ドラム２３の一部をキャリアとして機能させている。そのため、プラネタリギヤ４１の回転（公転）を、支持軸３６を介さずにドラム２３に直接伝達することができる。 On the other hand, in the present embodiment, a part of the drum 23 functions as a carrier. Therefore, the rotation (revolution) of the planetary gear 41 can be directly transmitted to the drum 23 without the support shaft 36.
　（３）本実施形態では、ドラム２３の底壁部２３ａをシャフト被着部とし、ここにプラネタリシャフト４２を取付ける。各プラネタリシャフト４２上にプラネタリギヤ４１を支持している。 (3) In the present embodiment, the bottom wall portion 23a of the drum 23 is used as a shaft attachment portion, and the planetary shaft 42 is attached thereto. A planetary gear 41 is supported on each planetary shaft 42.
　これによって、プラネタリシャフト４２を通じて底壁部２３ａに各プラネタリギヤ４１の公転が伝達されたときに、同底壁部２３ａをキャリアとして機能させ、同底壁部２３ａを含むドラム２３を回転させることができる。その結果、上記（１），（２）の利点が確実に得られるようになる。 By this, when the revolution of each planetary gear 41 is transmitted to the bottom wall portion 23a through the planetary shaft 42, the bottom wall portion 23a can function as a carrier, and the drum 23 including the bottom wall portion 23a can be rotated. . As a result, the advantages of the above (1) and (2) can be reliably obtained.
　なお、上記のように底壁部２３ａにプラネタリシャフト４２を取付ける構成は、同底壁部２３ａとプラネタリシャフト４２との間にリングギヤ３９ｂが介在していては成り立たない。本実施形態では、蓋部３９ａを、伝達ギヤ３８上であってサンギヤ３８ｄを挟んでドラム２３とは反対側となる箇所に支持し、この蓋部３９ａからドラム２３へ向けてリングギヤ３９ｂを突出させる。これによって、ドラム２３と蓋部３９ａとの間に、プラネタリシャフト４２及びプラネタリギヤ４１を配置する空間が形成されるので、上記の構成を成立させることができる。 In addition, the structure which attaches the planetary shaft 42 to the bottom wall part 23a as mentioned above does not consist, when the ring gear 39b interposes between the bottom wall part 23a and the planetary shaft 42. As shown in FIG. In this embodiment, the lid 39a is supported on the transmission gear 38 at a position opposite to the drum 23 with the sun gear 38d interposed therebetween, and the ring gear 39b is protruded from the lid 39a toward the drum 23. . Since the space which arrange | positions the planetary shaft 42 and the planetary gear 41 is formed between the drum 23 and the cover part 39a by this, the said structure can be materialized.
　（４）プラネタリギヤ４１毎のプラネタリシャフト４２について、底壁部２３ａ（シャフト被着部）寄りの端部４２ａとは反対側の端部に鍔部４２ｃを形成している。 (4) As for the planetary shaft 42 for each planetary gear 41, a flange 42c is formed at the end opposite to the end 42a near the bottom wall 23a (shaft attached portion).
　そのため、この底壁部２３ａと鍔部４２ｃとによって、プラネタリギヤ４１を挟み込んで、プラネタリシャフト４２の軸線に沿う方向のプラネタリギヤ４１の動きを規制し、プラネタリギヤ４１をサンギヤ３８ｄ及びリングギヤ３９ｂに噛合した状態に保持することができる。 Therefore, the planetary gear 41 is sandwiched between the bottom wall portion 23a and the flange portion 42c to restrict the movement of the planetary gear 41 in the direction along the axis of the planetary shaft 42, and the planetary gear 41 is engaged with the sun gear 38d and the ring gear 39b. Can be held.
　なお、上記実施形態は以下のように変更してもよい。 The above embodiment may be modified as follows.
　本発明の車両用ドア駆動装置は、リングギヤ３９ｂを、モータ２２によって回転駆動される駆動軸とし、キャリアを従動軸とし、サンギヤ３８ｄを固定軸とすることで、モータ２２の回転を減速して、出力部材としてのドラム２３に伝達して回転させ、車両ドアを開閉作動させる車両用ドア駆動装置にも適用可能である。 In the door drive apparatus for a vehicle according to the present invention, the ring gear 39b is a drive shaft rotationally driven by the motor 22, the carrier is a driven shaft, and the sun gear 38d is a fixed shaft to reduce the rotation of the motor 22. The present invention can also be applied to a vehicle door drive device that transmits and rotates the drum 23 as an output member to open and close the vehicle door.
　この場合にも、ドラム２３の底壁部２３ａにプラネタリシャフト４２を直接取付け、同プラネタリシャフト４２上にプラネタリギヤ４１を支持することで、同底壁部２３ａをキャリアとして機能させる。この場合にも、前記実施形態と同様の作用及び利点が得られる。 Also in this case, the planetary shaft 42 is directly attached to the bottom wall portion 23a of the drum 23, and the planetary gear 41 is supported on the planetary shaft 42, so that the bottom wall portion 23a functions as a carrier. Also in this case, the same operation and advantage as the above embodiment can be obtained.
　駆動部２０を車両ボディ１０側に固定してもよい。例えばクォータパネル１０ｂに駆動部２０を搭載する場合には、その駆動部２０にテンショナー２８，２９を繋ぐことがより好ましい。また、ドア開口１０ａの踏み台となるステップに駆動部２０を搭載する場合には、出力部材としてのベルトプーリ及びロープ部材としてのベルトを採用することがより好ましい。 The drive unit 20 may be fixed to the vehicle body 10 side. For example, when the drive unit 20 is mounted on the quarter panel 10 b, it is more preferable to connect the tensioners 28 and 29 to the drive unit 20. Moreover, when mounting the drive part 20 in the step used as the step of the door opening 10a, it is more preferable to employ | adopt the belt pulley as an output member, and the belt as a rope member.
　モータ２２の回転を伝達ギヤ３８に伝達する機構として、上記実施形態（円盤ギヤ部３８ｂ及びピニオン３４からなるフェースギヤ）とは異なる機構、例えば平歯車の組合わせ、ウォームギヤ等が用いられてもよい。 As a mechanism for transmitting the rotation of the motor 22 to the transmission gear 38, a mechanism different from the above embodiment (face gear including the disk gear portion 38b and the pinion 34), for example, a combination of spur gears, a worm gear, etc. may be used. .
　本発明は、スライドドア１５に限らず、ヒンジ式の車両ドアを開閉作動させる車両用ドア駆動装置にも適用可能である。 The present invention is applicable not only to the slide door 15 but also to a vehicle door drive device for opening and closing a hinged vehicle door.

Claims (4)

  1. 　モータの回転を減速して出力部材に伝達して同出力部材を回転させ、それによって車両ドアを開閉作動させる車両用ドア駆動装置であって、
    　サンギヤと、前記サンギヤを取り囲むリングギヤと、前記サンギヤ及び前記リングギヤに噛合するプラネタリギヤと、前記プラネタリギヤの公転とともに回転するキャリアとを有する遊星歯車機構を備え、
    　前記サンギヤ及び前記リングギヤの一方は、前記モータにより回転駆動される駆動軸であり、他方は固定軸であり、前記キャリアは従動軸であり、
    　前記出力部材の一部が前記キャリアを構成する、車両用ドア駆動装置。     A vehicle door drive device for decelerating the rotation of a motor and transmitting it to an output member to rotate the output member, thereby opening and closing a vehicle door,
    The planetary gear mechanism has a sun gear, a ring gear that surrounds the sun gear, a planetary gear that meshes with the sun gear and the ring gear, and a carrier that rotates along with the revolution of the planetary gear.
    One of the sun gear and the ring gear is a drive shaft rotationally driven by the motor, the other is a fixed shaft, and the carrier is a driven shaft.
    A door drive apparatus for a vehicle, wherein a part of the output member constitutes the carrier.
  2. 　前記プラネタリギヤをそれぞれ支持するプラネタリシャフトをさらに備え、
    　前記出力部材はシャフト被着部を備え、前記プラネタリシャフトは前記シャフト被着部に取付けられており、同シャフト被着部が前記キャリアを構成する請求項１に記載の車両用ドア駆動装置。     The system further comprises a planetary shaft supporting the planetary gears,
    The door driving apparatus for a vehicle according to claim 1, wherein the output member comprises a shaft attachment portion, the planetary shaft is attached to the shaft attachment portion, and the shaft attachment portion constitutes the carrier.
  3. 　前記プラネタリシャフトは、前記シャフト被着部寄りの第１端部と、同第１端部とは反対側の第２端部とを有し、同第２端部には鍔部が形成されている請求項２に記載の車両用ドア駆動装置。 The planetary shaft has a first end near the shaft attachment and a second end opposite to the first end, and a collar is formed at the second end. The vehicle door drive device according to claim 2.
  4. 　支持軸と、同支持軸上に支持されかつ前記モータにより回転駆動される入力部材と、前記サンギヤを挟んで前記出力部材とは反対側において前記入力部材上に支持された蓋部とをさらに備え、
    　前記サンギヤは、前記入力部材の一部に形成され、
    　前記出力部材は、前記入力部材とは異なる軸方向位置において前記支持軸上に支持され、
    　前記リングギヤは、前記蓋部に形成されており、
    　前記プラネタリギヤは前記出力部材と前記蓋部との間に配置されて、前記リングギヤ及び前記サンギヤに噛合されている請求項１～３のいずれか一項に記載の車両用ドア駆動装置。     The apparatus further comprises a support shaft, an input member supported on the support shaft and rotationally driven by the motor, and a lid supported on the input member on the opposite side to the output member across the sun gear. ,
    The sun gear is formed on a part of the input member,
    The output member is supported on the support shaft at an axial position different from the input member.
    The ring gear is formed on the lid portion,
    The vehicle door drive device according to any one of claims 1 to 3, wherein the planetary gear is disposed between the output member and the lid portion and engaged with the ring gear and the sun gear.
PCT/JP2011/075086 2010-11-04 2011-10-31 Vehicle door drive device WO2012060333A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021080654A1 (en) * 2019-10-25 2021-04-29 Raytheon Company Compact modular right-angle drive gear aligned actuator
US11359696B2 (en) 2019-10-25 2022-06-14 Raytheon Company Compact modular right-angle drive gear aligned actuator
US11703107B2 (en) 2019-10-25 2023-07-18 Raytheon Company Compact modular right-angle drive gear aligned actuator

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JP5625762B2 (en) 2014-11-19

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