WO2018012362A1 - Drive force transmission mechanism and opening/closing member drive device - Google Patents

Drive force transmission mechanism and opening/closing member drive device Download PDF

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Publication number
WO2018012362A1
WO2018012362A1 PCT/JP2017/024603 JP2017024603W WO2018012362A1 WO 2018012362 A1 WO2018012362 A1 WO 2018012362A1 JP 2017024603 W JP2017024603 W JP 2017024603W WO 2018012362 A1 WO2018012362 A1 WO 2018012362A1
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WO
WIPO (PCT)
Prior art keywords
gear
tooth
driving force
force transmission
tooth portion
Prior art date
Application number
PCT/JP2017/024603
Other languages
French (fr)
Japanese (ja)
Inventor
昭夫 石水
Original Assignee
日本電産サンキョー株式会社
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 日本電産サンキョー株式会社 filed Critical 日本電産サンキョー株式会社
Publication of WO2018012362A1 publication Critical patent/WO2018012362A1/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
    • E05F15/611—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings
    • E05F15/614—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings operated by meshing gear wheels, one of which being mounted at the wing pivot axis; operated by a motor acting directly on the wing pivot axis
    • 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
    • F16H1/06—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/06—Use of materials; Use of treatments of toothed members or worms to affect their intrinsic material properties
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/12—Toothed members; Worms with body or rim assembled out of detachable parts
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47K—SANITARY EQUIPMENT NOT OTHERWISE PROVIDED FOR; TOILET ACCESSORIES
    • A47K13/00—Seats or covers for all kinds of closets
    • A47K13/10—Devices for raising and lowering, e.g. tilting or lifting mechanisms; Collapsible or rotating seats or covers

Definitions

  • the present invention relates to a driving force transmission mechanism having a rotational position detector and an opening / closing member driving device for driving an opening / closing member such as a lid or a door.
  • the opening / closing member driving apparatus of the same document includes a motor, a gear mechanism that transmits the driving force of the motor to an output shaft connected to the opening / closing member, and a rotation angle position detector for detecting the rotation angle position of the output shaft.
  • the rotation angle position detector is a potentiometer provided with a potentiometer gear, and the potentiometer gear meshes with one of a plurality of gears constituting a gear mechanism.
  • the opening / closing member driving device grasps the rotational angle position of the output shaft based on the output from the potentiometer and controls the drive of the motor. Accordingly, the opening / closing member driving device moves the opening / closing member between the predetermined open position and the closed position.
  • Each gear of the gear mechanism that transmits driving force is usually coated with a lubricant such as grease to prevent wear.
  • a lubricant such as grease to prevent wear.
  • the rotation angle position detector is a potentiometer
  • the lubricant applied to the gear meshed with the potentiometer gear is transmitted through the potentiometer gear and adheres to the circuit board of the detector, the detector malfunctions. May occur.
  • an object of the present invention is to provide a driving force transmission mechanism and an opening / closing member driving device capable of suppressing lubricant from adhering to a rotation angle position detection gear of a rotation angle position detector.
  • a driving force transmission mechanism of the present invention includes a rotation angle position detector including a rotation angle position detection gear and a detection unit that detects a rotation angle position of the rotation angle position detection gear, and a drive.
  • a first tooth portion for transmitting force a second tooth portion spaced apart from the first tooth portion in the axial direction, and a tooth loss portion provided between the first tooth portion and the second tooth portion.
  • a driving force transmission gear provided, and a lubricant, wherein the lubricant is applied to the first tooth portion, and the rotational angle position detecting gear meshes with the second tooth portion.
  • the driving force transmission gear includes a first tooth portion and a second tooth portion at positions spaced apart in the axial direction, and the first tooth portion engages with another gear in order to transmit the driving force;
  • the second tooth portion is a tooth portion that meshes with the rotation angle position detecting gear.
  • a lubricant is applied to the first tooth portion meshing with another gear in order to suppress tooth wear, but a tooth missing portion is provided between the first tooth portion and the second tooth portion. Therefore, the lubricant is difficult to be transmitted from the first tooth portion to the second tooth portion side.
  • the tooth defect portion has an outer peripheral surface at a height different from the tooth bottom of the first tooth portion and the tooth bottom of the second tooth portion in the radial direction. In this way, a step is provided between the tooth bottom of the first tooth portion and the tooth bottom of the second tooth portion, so that the lubricant applied to the first tooth portion is transmitted to the second tooth side. Can be suppressed more.
  • the outer peripheral surface may be located on the inner side in the radial direction from the bottom of the first tooth portion and the bottom of the second tooth portion. If it does in this way, when meshing another gear with the 1st tooth part, it can avoid that a tooth missing part and other gears interfere.
  • the outer peripheral surface may be located on the outer side in the radial direction from the bottom of the first tooth portion and the bottom of the second tooth portion. If it does in this way, the lubricant which is going to flow from the 1st tooth part side to the 2nd tooth part side can be dammed up by a tooth loss part.
  • the driving force transmission gear includes a first gear member and a second gear member that are coaxially connected, and the first gear member includes the first tooth portion, and the second gear member. May comprise the second tooth part and the tooth defect part. If it does in this way, since the 1st tooth part is provided in the member different from the 2nd tooth part, it is easy to make the number of teeth etc. of the 1st tooth part and the 2nd tooth part different. . As a result, the ratio between the rotational speed of the driving force transmission gear and the rotational speed of the rotational position detecting gear meshing with the second tooth portion can be set to a desired value, so that the detection accuracy of the rotational angle position can be changed. It becomes easy.
  • the first gear member can be made of metal, and the second gear member can be made of resin. If it does in this way, in order to transmit driving force, the intensity of the 1st tooth part which meshes with other gears can be raised. Further, when the strength of the first tooth portion is improved, the manufacturing cost of the driving force transmission gear can be suppressed as compared with the case where the entire driving force transmission gear is made of metal.
  • the first gear member and the second gear member are arranged in the axial direction, and the second gear member is spaced apart in the circumferential direction of the end face on the first gear member side.
  • a first protrusion and a second protrusion protruding in the axial direction at a location, wherein the first gear member has a first recess capable of receiving the first protrusion on an end surface of the second gear member;
  • a second recess capable of receiving the second protrusion from the axial direction, the first protrusion and the second protrusion have different sizes, and the first protrusion is inserted into the first recess.
  • it is desirable that the first protrusion is fitted in the first recess without a gap in the circumferential direction.
  • the 1st projection will be inserted in the 1st crevice, and the 2nd projection will be inserted in the 2nd crevice, and the phase of the 1st tooth part and the phase of the 2nd tooth part will be in a predetermined relation. Can be set.
  • the rotation angle position detector may be a potentiometer provided with a potentiometer gear as the rotation angle position detection gear.
  • a potentiometer if a lubricant adheres to a resistor or a brush constituting a detection unit, it may cause a malfunction or a decrease in detection accuracy. According to the present invention, such a malfunction can be prevented or suppressed. .
  • an opening / closing member driving device of the present invention includes the above-described driving force transmission mechanism, a motor, and a gear mechanism that transmits the driving force of the motor to an output shaft connected to the opening / closing member.
  • One gear of the plurality of gears constituting the row is the driving force transmission gear.
  • the opening / closing member can be disposed at a desired closed position or open position.
  • the lubricant detects the rotational angle position of the driving force transmission gear. It is prevented or suppressed from adhering to the detector. Therefore, it is possible to prevent or suppress the malfunction of the rotation angle position detector.
  • FIG. 10 is a perspective view of an output gear, an output shaft, and a fifth compound gear when the opening / closing member is operated by a person. It is a perspective view of the 5th compound gear of a modification.
  • FIG. 1A is an explanatory diagram of the opening / closing member driving device
  • FIG. 1B is an explanatory diagram of the closing operation of the lid by the opening / closing member driving device.
  • the opening / closing member driving device 1 includes an automatic closing device 4 to which the opening / closing member 2 is connected, a switch 5, a detector 6, and a control unit 7.
  • the opening / closing member 2 has a 90 ° angle range between an open position 2 ⁇ / b> B standing up with respect to the box 3 and a closed position 2 ⁇ / b> A flattening along the box 3. Rotates in both directions.
  • the opening / closing member driving device 1 rotates and arranges the opening / closing member 2 such as a lid or a door in an open state at a predetermined closed position 2A.
  • the opening / closing member 2 is arranged at the closed position 2 ⁇ / b> A, the storage portion provided in the box 3 is in a state of being sealed by the opening / closing member 2.
  • the position and angle range of the closed position 2A and the open position 2B of the opening / closing member 2 are not limited to the embodiment, and are set according to the application.
  • the automatic closing device 4 includes a case 10 and an output shaft 11 to which the opening / closing member 2 is coupled.
  • the connecting portion 12 of the output shaft 11 with the opening / closing member 2 is exposed to the outside from the bearing hole 13 of the case 10.
  • the opening / closing member 2 has a rotation center shaft coaxially connected to the output shaft 11.
  • the axis of the output shaft 11 is L0
  • the direction along the axis L0 in the automatic closing device 4 is the X direction.
  • the first direction in the X direction is defined as a first direction X1
  • the opposite side of the first direction X1 is defined as a second direction X2.
  • FIG. 2 is a perspective view when the automatic closing device 4 with the case removed is viewed from the second direction X2.
  • FIG. 3 is a perspective view when the automatic closing device 4 with the case removed is viewed from the first direction X1.
  • a motor 15 that is a driving source of the automatic closing device 4
  • an output shaft 11 to which the opening / closing member 2 is connected, and a driving force of the motor 15 are applied to the output shaft 11.
  • a transmission gear mechanism (driving force transmission mechanism) 16 and a potentiometer (rotational angle position detector) 17 are housed.
  • the gear mechanism 16 is a speed reduction mechanism.
  • the potentiometer 17 includes a potentiometer gear (rotation angle position detection gear) 18 and a detection unit 19 that detects the rotation angle position of the potentiometer gear 18.
  • the motor 15 is disposed in the case 10 in a posture in which the motor output shaft 15a protrudes in the first direction X1.
  • the gear mechanism 16 includes a pinion 22 attached to the motor output shaft 15a, a first compound gear 23 that meshes with the pinion 22, a second compound gear (torque limiter) 24 that meshes with the first compound gear 23, and a second A third compound gear 25 meshed with the compound gear 24, a fourth compound gear 26 meshed with the third compound gear 25, a fifth compound gear (driving force transmission gear) 27 meshed with the fourth compound gear 26, An output gear 28 meshing with the fifth compound gear 27 is provided.
  • the first compound gear 23 includes a first large-diameter gear portion 23a meshing with the pinion 22, and a first coaxial gear provided on the second direction X2 side of the first large-diameter gear portion 23a.
  • a small-diameter gear portion 23b is provided.
  • the second compound gear 24 includes a second large-diameter gear portion 24a that meshes with the first small-diameter gear portion 23b, and a second small-diameter gear portion that is provided coaxially on the second direction X2 side of the second large-diameter gear portion 24a. 24b.
  • the third compound gear 25 includes a third large-diameter gear portion 25a meshing with the second small-diameter gear portion 24b, and a third small-diameter gear portion provided coaxially on the first direction X1 side of the third large-diameter gear portion 25a. 25b.
  • the fourth compound gear 26 includes a fourth large-diameter gear portion 26a that meshes with the third small-diameter gear portion 25b, and a fourth small-diameter gear portion that is provided coaxially on the first direction X1 side of the fourth large-diameter gear portion 26a. 26b.
  • the fifth compound gear 27 includes a fifth large-diameter gear portion 27a meshing with the fourth small-diameter gear portion 26b, and a fifth small-diameter gear portion provided coaxially on the second direction X2 side of the fifth large-diameter gear portion 27a. 27b.
  • the fifth small-diameter gear portion 27b includes a first tooth portion 27c and a second tooth portion 27d provided at positions separated in the X direction (the axial direction of the fifth small-diameter gear portion 27b).
  • the 1st tooth part 27c is located in the 1st direction X1 side of the 2nd tooth part 27d.
  • the output gear 28 meshes with the first tooth portion 27c of the fifth small diameter gear portion 27b.
  • the potentiometer gear 18 of the potentiometer 17 meshes with the second tooth portion 27d of the fifth small diameter gear portion 27b.
  • the first compound gear 23 is rotatably supported by a first support shaft 31 extending in the X direction.
  • the second compound gear 24 is rotatably supported by a second support shaft 32 extending in the X direction.
  • the third compound gear 25 is rotatably supported by a third support shaft 33 extending in the X direction.
  • the fourth compound gear 26 is rotatably supported by a fourth support shaft 34 extending in the X direction.
  • the fifth compound gear 27 is rotatably supported by a fifth support shaft 35 extending in the X direction.
  • Both end portions in the X direction of the first support shaft 31, the second support shaft 32, the third support shaft 33, the fourth support shaft 34, and the fifth support shaft 35 are support portions (not shown) provided in the case 10, respectively. It is supported by.
  • the output gear 28 is a sector gear.
  • the output gear 28 and the output shaft 11 are arranged coaxially. In other words, the axis L0 of the output shaft 11 and the output gear 28 coincide.
  • a bearing hole 29 penetrating in the X direction is provided at the main part (rotation center) of the output gear 28 (fan gear).
  • the output shaft 11 includes an output shaft main body portion 37 extending in the X direction along the axis L0, and an arm portion 38 protruding from the output shaft main body portion 37 in a direction orthogonal to the axis L0.
  • the output shaft main body portion 37 and the arm portion 38 rotate integrally.
  • the output shaft main body 37 is provided with a connecting portion 12 for connecting the opening / closing member 2.
  • the connecting portion 12 is a through hole that penetrates the output shaft main body portion 37 in the X direction.
  • the opening shape when the connecting portion 12 (through hole) is viewed from the X direction is a D-shape.
  • the output shaft main body 37 is rotatably supported in the bearing hole 29 of the output gear 28.
  • the output shaft 11 is rotatably supported by the case 10.
  • each gear (the pinion 22, the first compound gear 23, the second compound gear 24, the third compound gear 25, the fourth compound gear 26, the fifth compound gear 27, and the output gear 28), the other gears are Grease (lubricant) is applied to the meshing teeth except for the second tooth 27d meshing with the potentiometer gear 18.
  • Grease lubricant
  • FIGS. 4 (a) is a perspective view of the second compound gear 24 when viewed from the second direction X2, and FIG. 4 (b) is a cross-sectional view of the second compound gear 24 cut along its axis.
  • FIG. 4C is a cross-sectional view taken along the line AA in FIG.
  • FIG. 5 is an exploded perspective view of the second compound gear 24.
  • FIG. 6A is a perspective view of the large-diameter gear constituting the second compound gear 24 as viewed from the second direction X2, and
  • FIG. 6B shows the small-diameter gear constituting the second compound gear 24 as the first gear. It is a perspective view at the time of seeing from 1 direction X1.
  • the second compound gear 24 includes a large-diameter gear (second gear) 41 and a small-diameter gear (first gear) 42 that are rotatably supported by the second support shaft 32, and a large-diameter gear 41. And a rotation transmission mechanism 43 that transmits rotation between the small-diameter gear 42 and the small-diameter gear 42.
  • the large-diameter gear 41 has a cylindrical portion 45 having a large-diameter tooth portion (second tooth portion) 41 a meshing with the first compound gear 23 on the outer peripheral surface, and an inner periphery of the cylindrical portion 45.
  • An annular plate portion 46 projecting radially inward from an intermediate position in the X direction of the surface (position close to the opening in the first direction X1), and the inner peripheral side of the tube portion 45 from the plate portion 46 in the second direction.
  • an annular wall 47 projecting to X2.
  • a through hole 48 through which the second support shaft 32 passes is provided at the center of the plate portion 46.
  • the cylindrical portion 45 and the annular wall portion 47 are provided coaxially with a gap in the radial direction.
  • the end of the annular wall portion in the second direction X2 is located on the inner peripheral side of the cylindrical portion 45.
  • the annular wall portion 47 includes a small-diameter portion 49 having a small outer diameter at the end portion in the second direction X2. Further, the annular wall portion 47 includes a tapered chamfered surface 49a that is inclined toward the inner peripheral side in the second direction X2 at the end in the second direction X2. A radius 50 is provided at a boundary portion between the annular wall portion 47 and the plate portion 46. In other words, the annular wall portion 47 includes a thick portion (R 50) whose thickness dimension increases toward the plate portion 46 side at the end portion on the plate portion 46 side.
  • the small-diameter gear 42 includes a shaft portion 53 including a small-diameter tooth portion (first tooth portion) 53 a that meshes with the third compound gear 25, and the large-diameter gear 41.
  • the insertion portion 54 to be inserted on the inner peripheral side of the annular wall portion 47, the annular plate portion 55 extending in the radial direction from between the shaft portion 53 and the insertion portion 54, and the outer periphery of the annular plate portion 55 in the first direction X1.
  • An annular cylinder portion 56 is provided.
  • the small-diameter gear 42 includes a through hole 42a that penetrates the shaft portion 53 and the insertion portion 54 in the X direction.
  • the second support shaft 32 passes through the through hole 42a.
  • the insertion portion 54 is located on the side of the shaft portion 53 in the first direction X1.
  • the insertion portion 54 includes an annular outer peripheral surface 54 a that is coaxial with the second support shaft 32.
  • the annular cylindrical portion 56 is coaxial with the shaft portion 53 and the insertion portion 54 and is positioned on the outer peripheral side of the end portion of the insertion portion 54 in the second direction X2.
  • An annular stepped portion 57 cut out from the distal end side is provided on the inner peripheral side of the distal end portion of the annular cylindrical portion 56 in the first direction X1.
  • the annular step portion 57 includes an annular peripheral wall surface 57a facing the inner peripheral side and an annular end surface 57b facing the first direction X1.
  • the tip portion of the annular cylinder portion 56 in the first direction X1 is the large diameter gear 41.
  • the end face in the second direction X2 of the annular plate portion 55 is inserted between the tubular portion 45 and the annular wall portion 47, and the end face in the second direction X2 of the tubular portion 45 of the large-diameter gear 41 is located on the same plane. .
  • the small-diameter gear 42 includes a first member 58 and a second member 59 that are coaxially connected in the X direction.
  • the first member 58 includes a shaft portion 53, an annular plate portion 55, and an annular cylinder portion 56.
  • the first member 58 includes a rectangular recess 60 on the end surface of the shaft portion 53 in the first direction X1.
  • the second member 59 includes an insertion portion 54.
  • the second member 59 includes a rectangular convex portion 61 on the end surface of the insertion portion 54 in the second direction X2.
  • the rotation transmission mechanism 43 includes four slits 63 provided in the annular wall portion 47 of the large-diameter gear 41 and four metal shafts 64 respectively inserted into the slits 63.
  • each slit 63 is provided by cutting out the annular wall portion 47 from the end of the annular wall portion 47 in the second direction X2 toward the plate portion 46.
  • Each slit 63 extends in the X direction and reaches the plate portion 46.
  • the four slits 63 are provided at equiangular intervals around the axis L1 of the second support shaft 32 (around the axis L1 of the second compound gear 24).
  • the annular wall portion 47 is composed of four circular arc walls 65 arranged at equal intervals in the circumferential direction.
  • each shaft 64 has a cylindrical shape and extends in the X direction.
  • Each shaft 64 is made of metal.
  • the four shafts 64 are respectively inserted into the slits 63.
  • the diameter of each shaft 64 is shorter than the circumferential width of each slit 63.
  • the diameter of each shaft 64 is longer than the thickness of the annular wall part 47 (arc wall 65) in the radial direction.
  • the length dimension of each shaft 64 is shorter than the height dimension from the plate portion 46 to the small diameter portion 49 of the annular wall portion 47.
  • the rotation transmission mechanism 43 includes four groove portions 66 provided on the outer peripheral surface 54 a of the insertion portion 54 of the small diameter gear 42, and the cylindrical portion of the large diameter gear 41. And a coil spring 67 inserted between the annular wall 47 and the annular wall 47.
  • the four groove portions 66 are provided at equiangular intervals around the axis L ⁇ b> 1 of the second compound gear 24.
  • the inner peripheral side portion of each shaft 64 inserted into each slit 63 is inserted into each groove 66.
  • the coil spring 67 is inserted between the cylindrical portion 45 and the annular wall portion 47 so that the inner peripheral side thereof is in contact with the outer peripheral surface 54 a of the annular wall portion 47.
  • the coil spring 67 exerts a biasing force that biases the shaft 64 toward the inner peripheral side when the shaft 64 protrudes from the annular wall portion 47 toward the outer peripheral side.
  • the rotation transmission mechanism 43 includes a restricting portion 68 (a restricting member) that restricts displacement of the end of the annular wall portion 47 in the second direction X2 toward the outer peripheral side. ), A shaft movement restricting portion 69 that defines the movement range of the shaft 64 in the X direction, and a coil spring movement restricting portion 70 that defines the movement range of the coil spring 67 in the X direction.
  • the restricting portion 68, the shaft movement restricting portion 69, and the coil spring movement restricting portion 70 are provided in the annular cylindrical portion 56 of the small diameter gear 42.
  • the regulating portion 68 is a portion adjacent to the annular step portion 57 in the second direction X2 in the annular cylindrical portion 56.
  • the restricting portion 68 is opposed to the outer side in the radial direction of the small diameter portion 49 of the annular cylindrical portion 56 with a very small gap.
  • the shaft movement restricting portion 69 is an annular end surface 57 b that faces the first direction X ⁇ b> 1 in the annular step portion 57 of the annular cylindrical portion 56.
  • the shaft movement restricting portion 69 is located outside the small diameter portion 49 in the radial direction. Thus, the shaft movement restricting portion 69 is opposed to the shaft 64 inserted in the slit 63 with a gap in the X direction.
  • the annular peripheral wall surface 57a of the annular step portion 57 is provided at a position where it does not interfere with the shaft 64 even when the shaft 64 moves to the outer peripheral side as will be described later.
  • the shafts 64 are inserted between the four slits 63 of the annular wall portion 47 of the large-diameter gear 41.
  • the coil spring 67 is disposed between the annular wall portion 47 and the cylindrical portion 45.
  • the first member 58 insertion portion 54
  • the first member 58 is inserted into the inner peripheral side of the annular wall portion 47 in alignment with the angular position between the groove portion 66 of the insertion portion 54 of the first member 58 and the slit 63.
  • each of the four shafts 64 is in a state where a part of the inner peripheral side thereof is fitted in each groove 66 of the insertion portion 54.
  • the coil spring 67 located on the outer peripheral side of the annular wall 47 exhibits a biasing force that biases each shaft 64 toward the inner peripheral side.
  • the second member 59 is connected to the first member 58.
  • the assembly of the second compound gear 24 is completed.
  • the large-diameter gear 41 constitutes the second large-diameter gear portion 24a
  • the small-diameter gear 42 constitutes the second small-diameter gear portion 24b.
  • the second compound gear 24 is normally maintained in a state where each of the four shafts 64 is fitted in each groove 66 of the insertion portion 54 by the biasing force of the coil spring 67. Therefore, the large diameter gear 41 and the small diameter gear 42 rotate together.
  • the position of the groove portion 66 of the insertion portion 54 of the small-diameter gear 42 is shifted in the circumferential direction from the slit 63 of the large-diameter gear 41, so that the shaft 64 is disengaged from the groove portion 66 toward the outer peripheral side against the urging force of the coil spring 67. Then, it rides on the outer peripheral surface 54a of the insertion portion 54. Thereby, the relative rotation of the small diameter gear 42 and the large diameter gear 41 is allowed. Therefore, an excessive force input from the output shaft 11 side is attenuated by the second compound gear 24, and an excessive force is not transmitted to the upstream side (motor 15 side) in the driving force transmission direction.
  • the second compound gear 24 functions as a torque limiter.
  • FIG. 7 is a perspective view showing the fifth compound gear 27 and the potentiometer 17 taken out.
  • the fifth compound gear 27 and the potentiometer 17 are viewed from the first direction X1.
  • FIG. 8A is an exploded perspective view of the fifth compound gear 27, and
  • FIG. 8B is a perspective view of the second gear constituting the fifth compound gear 27 as viewed from the second direction X2. As shown in FIG.
  • the fifth compound gear 27 includes a large-diameter gear 75 constituting the fifth large-diameter gear portion 27a and a small-diameter gear (driving force transmission gear) 76 constituting the fifth small-diameter gear portion 27b.
  • the large diameter gear 75 and the small diameter gear 76 are connected coaxially.
  • the large-diameter gear 75 is cylindrical and includes a large-diameter tooth portion 75 a that meshes with the fourth compound gear 26.
  • the small-diameter gear 76 includes a first gear member 77 having a first tooth portion 77 a with which the output gear 28 is engaged, and a second gear member 78 having a second tooth portion 78 a with which the potentiometer gear 18 is engaged. Is provided.
  • the first gear member 77 and the second gear member 78 are arranged on the axis L2 of the fifth compound gear 27 and are connected coaxially.
  • the 1st tooth part 77a and the 2nd tooth part 78a are provided with the same tooth. That is, the first tooth portion 77a and the second tooth portion 78a have the same root circle, tip circle, number of teeth, and tooth formation pitch.
  • the first gear member 77 includes a shaft portion 79 having a first tooth portion 77a on the outer peripheral surface, and a projecting portion 80 that protrudes coaxially from the shaft portion 79 in the first direction X1.
  • the protrusion 80 includes flat surfaces extending in parallel to each other on both sides of the axis L2.
  • the center hole 75 b of the large-diameter gear 75 has a shape that fits with the convex portion 80.
  • the second gear member 78 includes a cylindrical tooth missing portion 81 adjacent to the second tooth portion 78a on the first direction X1 side. Therefore, when the first gear member 77 and the second gear member 78 are connected to form the small-diameter gear 76, the small-diameter gear 76 is separated from the first tooth portion 77a and the first tooth portion 77a in the X direction. 78a and a tooth loss part 81 provided between the first tooth part 77a and the second tooth part 78a.
  • the tooth missing part 81 includes an outer peripheral surface 81a positioned at a height different from the tooth bottom 77b of the first tooth part 77a and the tooth bottom 78b of the second tooth part 78a in the radial direction.
  • the outer peripheral surface 81a is located on the radially inner peripheral side with respect to the tooth bottom 77b of the first tooth portion 77a and the tooth bottom 77b of the second tooth portion 78a.
  • the large-diameter gear 75 is made of resin
  • the first gear member 77 is made of metal
  • the second gear member 78 is made of resin.
  • the second gear member 78 includes a first protrusion 82a and a second protrusion 82b that protrude in the X direction at two locations that are spaced apart from each other in the circumferential direction of the end surface on the first gear member 77 side.
  • the first gear member 77 includes a first recess 83a capable of receiving the first protrusion 82a on the end surface on the second gear member 78 side, and a second protrusion 82b from the axial direction. 2nd recessed part 83b which can receive this.
  • the first protrusion 82a and the second protrusion 82b have different sizes, and the second protrusion 82b is larger than the first protrusion 82a.
  • the second protrusion 82b has a size that cannot be inserted into the first recess 83a.
  • the first protrusion 82a fits in the first recess 83a without any gap in the circumferential direction.
  • the phase of the 1st tooth part 77a and the phase of the 2nd tooth part 78b can be set to the predetermined relationship.
  • FIGS. 9 and 10 are perspective views of the output gear 28, the output shaft 11, and the fifth compound gear 27 as viewed from the first direction X1.
  • 9A shows a state of the output gear 28 and the output shaft 11 when the opening / closing member 2 is arranged at the open position 2B
  • FIG. 9B shows a case where the opening / closing member 2 is arranged at the closed position 2A.
  • the states of the output gear 28 and the output shaft 11 are shown.
  • FIG. 10 shows an output gear 28 when the opening / closing member 2 is operated by a person and placed in the closed position 2A when the opening / closing member 2 is moved halfway between the open position 2B and the closed position 2A by the opening / closing member driving device 1.
  • the state of the output shaft 11 is shown.
  • the output gear 28 is a sector gear.
  • the output gear 28 includes a tooth portion 28a having an angular range corresponding to an angular range in which the opening / closing member 2 rotates.
  • the output gear 28 rotates in the first rotation direction S1 (CW direction in FIG. 9) when the automatic closing device 4 drives the opening / closing member 2 toward the closed position 2A.
  • the first rotation direction S1 (CW direction) of the output gear 28 is opposite to the first rotation direction R1 (CCW direction) of the fifth compound gear 27 that meshes with the output gear 28.
  • the output gear 28 is notched in the end surface 28b in the first direction X1 from the front end surface 28c in the first rotation direction S1 toward the second rotation direction S2 opposite to the first rotation direction S1.
  • a cut-out recess 88 is provided.
  • the inner wall surface that defines the end of the notch recess 88 in the second rotation direction S2 opposite to the first rotation direction S1 is a contact portion 88a that can contact the arm portion 38.
  • the output gear 28 moves between the output gear open position 28B shown in FIG. 9 (a) and the output gear closed position shown in FIG. 9 (b) while the opening / closing member 2 moves between the open position 2B and the closed position 2A. Rotate between 28A.
  • the output shaft 11 includes an output shaft main body portion 37 extending in the X direction along the axis L0 and an arm portion 38 extending in the radial direction orthogonal to the axis L0.
  • the shape when the arm portion 38 is viewed from the X direction is tapered as the arm portion 38 is separated from the output shaft main body portion 37.
  • the arm part 38 can be accommodated in the notch recess 88 from the front in the first rotational direction S1.
  • the rear side surface of the arm portion 38 in the first rotation direction S1 is a contacted portion 38a with which a contact portion 88a provided on the output gear 28 contacts from the rear of the first rotation direction S1.
  • the fifth compound gear 27 is moved in the first rotation direction R1 by driving the motor 15 in the positive direction. Rotate.
  • the contact portion 88a of the output gear 28 (the inner wall surface of the notch recess 88) contacts the arm portion 38 of the output shaft 11 from the rear in the first rotation direction S1.
  • the output shaft 11 is rotated around the output gear 28.
  • the control system of the opening / closing member driving device 1 includes a control unit 7 including a CPU and the like. Connected to the input side of the control unit 7 are a switch 5 for causing the automatic closing device 4 to start a closing operation, and a detector 6 for detecting that the opening / closing member 2 is disposed at the closed position 2A where it abuts against the box 3. ing.
  • a detection unit 19 of the potentiometer 17 is connected to the input side of the control unit 7.
  • a motor 15 is connected to the output side of the control unit 7.
  • the control unit 7 drives the motor 15 in the forward direction to drive the opening / closing member 2 toward the closed position 2A. Further, the control unit 7 controls the rotation of the motor 15 by monitoring the position of the opening / closing member 2 based on the output from the detection unit 19 of the potentiometer 17. Furthermore, after driving the motor 15, the control unit 7 stops the motor 15 when the detector 6 detects that the opening / closing member 2 has reached the closed position 2 ⁇ / b> A. Thereafter, the controller 7 drives the motor 15 in the reverse direction to return the output gear 28 to the output gear open position 28B.
  • the output shaft 11 does not rotate while meshing with the output gear 28, but the contact portion 88 a of the output gear 28 contacts the arm portion 38 of the output shaft 11, so that the first rotation direction together with the output gear 28 is achieved. Rotate to S1. Therefore, when the output gear 28 is rotated in the first rotation direction S1 by driving the motor 15 and the output shaft 11 is rotating with the output gear 28 (when the opening and closing member 2 is driven in the closing direction C). ) When the opening / closing member 2 is operated by human power and moves in the closing direction C, as shown in FIG.
  • the control unit 7 drives the motor 15 in the reverse direction to return the output gear 28 to the output gear open position 27B. Therefore, it is possible to avoid the rotation of the output shaft 11 connected to the opening / closing member 2 being transmitted to the output gear 28 when the opening / closing member 2 disposed at the closed position 2A is moved in the opening direction by a person. Therefore, the opening / closing member 2 arranged at the closed position 2A can be moved in the opening direction by a weak force by a person.
  • the gear mechanism 16 includes a torque limiter (second compound gear 24). Therefore, when the output gear 28 is rotated in the first rotation direction S1 by driving the motor 15 and the output shaft 11 is rotating with the output gear 28, the opening / closing member 2 is operated in the direction opposite to the drive direction. For example, an excessive load input from the opening / closing member 2 side to the gear mechanism 16 via the output shaft 11 is attenuated by the torque limiter 24 (second compound gear 24). That is, when an excessive load is input to the torque limiter 24 from the output gear 28 side, relative rotation between the small diameter gear 42 and the large diameter gear 41 is permitted, and the excessive load transmitted to the small diameter gear 42 is large. Transmission to the radial gear 41 can be prevented. Therefore, the gear, the motor 15 and the like constituting the gear mechanism 16 are not damaged by an excessive load from the outside.
  • the fifth compound gear 27 has a first tooth portion 77a meshing with the output gear 28 and a second tooth portion 78a meshing with the potentiometer gear 18 in the X direction (the axis L2 of the fifth compound gear 27). In the direction). Further, a tooth loss part 81 is provided between the first tooth part 77a and the second tooth part 78a. Therefore, the grease applied to the output gear 28 and the first tooth portion 77 is suppressed from adhering to the second tooth portion 78a. As a result, grease can be prevented from reaching the detection unit 19 by being transmitted from the second tooth portion 78a to the potentiometer gear wheel 18, so that the potentiometer 17 can be prevented from malfunctioning.
  • the tooth defect portion 81 includes an outer peripheral surface 81a positioned on the inner peripheral side in the radial direction from the tooth bottom 77b of the first tooth portion 77a and the tooth bottom 78b of the second tooth portion 78a. Accordingly, a step is provided between the tooth bottom 77b of the first tooth portion 77a and the tooth bottom 78b of the second tooth portion 78a, so that the grease applied to the first tooth portion 77a is on the second tooth portion 78a side. It is possible to suppress the transmission more. As a result, the grease can be prevented from reaching the detection unit 19 by being transmitted from the second tooth portion 78a to the potentiometer gear 18, so that the potentiometer 17 can be prevented from malfunctioning. Therefore, the rotational angle position of the opening / closing member 2 can be accurately grasped by the output from the detection unit 19.
  • the first tooth The output gear 28 meshed with the portion 77a does not interfere with the tooth missing portion 81.
  • the first gear member 77 having the first tooth portion 77a meshing with the output gear 28 is made of metal
  • the second gear member having the second tooth portion 78a meshing with the potentiometer gear 18. 78 is made of resin. Therefore, the strength for transmitting the driving force can be improved for the first tooth portion 77a. Further, when the strength of the first tooth portion 77a is improved, the manufacturing cost of the fifth composite gear 27 can be suppressed as compared with the case where the entire fifth composite gear 27 is made of metal.
  • FIG. 11 is a perspective view of a modified fifth compound gear and potentiometer 17.
  • the outer peripheral surface 81a of the tooth missing portion 81 is radially outer than the tooth bottom 77b of the first tooth portion 77a and the tooth bottom 77b of the second tooth portion 78a.
  • Other configurations are the same as those of the fifth compound gear 27. In this way, the grease that tends to flow from the first tooth portion 77a side to the second tooth portion 78a side can be blocked by the tooth loss portion 81.
  • the number of teeth of the first tooth portion 77a and the second tooth portion 78a may be different.
  • the small-diameter gear 76 is composed of two members, a first gear member 77 and a second gear member 78, which are coaxially connected, so that the first tooth portion 77a and the second tooth portion 78a It is easy to make the number of teeth different.
  • the ratio of the rotational speed of the driving force transmission gear 76 and the rotational speed of the potentiometer gear 18 meshing with the second tooth portion 78a can be set to a desired value, so that the detection accuracy of the rotational angle position can be changed. It becomes easy.
  • the second gear member 78 includes the tooth missing portion 81, but the first gear member 77 may include the tooth missing portion 81.
  • grease is used as a lubricant for preventing gear wear, but oil or a coating agent may be used as the lubricant. That is, in each gear (the pinion 22, the first compound gear 23, the second compound gear 24, the third compound gear 25, the fourth compound gear 26, the fifth compound gear 27, and the output gear 28), other gears mesh with each other. Oil or a coating agent may be applied to the tooth portion to be removed, except for the second tooth portion 27d that meshes with the potentiometer gear 18. Even in this case, since these lubricants can be prevented from reaching the detection unit 19 by being transmitted from the second tooth portion 78a to the potentiometer gear 18, it is possible to prevent the potentiometer 17 from malfunctioning.
  • the present invention is applied to the automatic closing device 4.
  • the present invention can also be applied to an automatic opening device in which the opening / closing member 2 is arranged at the open position 2B.
  • the opening / closing member driving device 1 (automatic closing device 4) rotates the opening / closing member 2 in the vertical direction, but the opening / closing member 2 may be rotated in the horizontal direction.

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  • General Engineering & Computer Science (AREA)
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  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
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Abstract

Provided is a drive force transmission mechanism with which it is possible to minimize adhesion of a lubricant to a rotational angle position detection gear of a rotational angle position detector. Specifically, a gear mechanism 16 (drive force transmission mechanism) is provided with a fifth composite gear 27 and a potentiometer 17. A small-diameter gear 76 of the fifth composite gear 27 is provided with a first toothed part 77a that meshes with an output gear 28, a second toothed part 78a separated from the first toothed part 77a along the direction of an axis line L2, and a toothless part 81 provided between the first toothed part 77a and the second toothed part 78a. The output gear 28 and the first toothed part 77a are coated with grease (a lubricant). The potentiometer 17 is provided with a potentiometer gear 18 and a detection unit 19 for detecting the rotational angle position of the potentiometer gear 18. The potentiometer gear 18 meshes with the second toothed part 78a. Because of the toothless part 81, the grease is not transferred from the first toothed part 77a to the second toothed part 78a.

Description

駆動力伝達機構および開閉部材駆動装置Driving force transmission mechanism and opening / closing member driving device
　本発明は、回転位置検出器を備える駆動力伝達機構および蓋や扉などの開閉部材を駆動する開閉部材駆動装置に関する。 The present invention relates to a driving force transmission mechanism having a rotational position detector and an opening / closing member driving device for driving an opening / closing member such as a lid or a door.
　蓋や扉などの開閉部材を開閉する開閉部材駆動装置は特許文献１に記載されている。同文献の開閉部材駆動装置は、モータと、モータの駆動力を開閉部材が連結された出力軸に伝達する歯車機構と、出力軸の回転角度位置を検出するための回転角度位置検出器を備える。回転角度位置検出器は、ポテンショ歯車を備えるポテンショメータであり、ポテンショ歯車は、歯車機構を構成する複数の歯車のうちの一つの歯車に噛合している。開閉部材駆動装置は、ポテンショメータからの出力に基づいて出力軸の回転角度位置を把握してモータを駆動制御する。これにより、開閉部材駆動装置は、開閉部材を所定の開位置と閉位置との間で移動させる。 An opening / closing member driving device for opening / closing an opening / closing member such as a lid or a door is described in Patent Document 1. The opening / closing member driving apparatus of the same document includes a motor, a gear mechanism that transmits the driving force of the motor to an output shaft connected to the opening / closing member, and a rotation angle position detector for detecting the rotation angle position of the output shaft. . The rotation angle position detector is a potentiometer provided with a potentiometer gear, and the potentiometer gear meshes with one of a plurality of gears constituting a gear mechanism. The opening / closing member driving device grasps the rotational angle position of the output shaft based on the output from the potentiometer and controls the drive of the motor. Accordingly, the opening / closing member driving device moves the opening / closing member between the predetermined open position and the closed position.
特開２０１４－２００４５８号公報JP 2014-200458 A
　駆動力を伝達する歯車機構の各歯車には、通常、摩耗を防止するためにグリスなどの潤滑剤が塗布されている。ここで、各歯車に塗布された潤滑剤が電子部品である回転角度位置検出器の検出部に付着した場合には、回転角度位置検出器に誤動作を発生させる場合がある。例えば、回転角度位置検出器がポテンショメータの場合には、ポテンショ歯車が噛合する歯車に塗布された潤滑剤がポテンショ歯車を伝わって、その検出部の回路基板に付着してしまうと、検出部に誤動作が発生することがある。 ∙ Each gear of the gear mechanism that transmits driving force is usually coated with a lubricant such as grease to prevent wear. Here, when the lubricant applied to each gear adheres to the detection unit of the rotation angle position detector that is an electronic component, a malfunction may occur in the rotation angle position detector. For example, when the rotational angle position detector is a potentiometer, if the lubricant applied to the gear meshed with the potentiometer gear is transmitted through the potentiometer gear and adheres to the circuit board of the detector, the detector malfunctions. May occur.
　本発明の課題は、かかる点に鑑みて、回転角度位置検出器の回転角度位置検出用歯車に潤滑剤が付着することを抑制できる駆動力伝達機構および開閉部材駆動装置を提供することにある。 In view of this point, an object of the present invention is to provide a driving force transmission mechanism and an opening / closing member driving device capable of suppressing lubricant from adhering to a rotation angle position detection gear of a rotation angle position detector.
　上記課題を解決するために、本発明の駆動力伝達機構は、回転角度位置検出用歯車および当該回転角度位置検出用歯車の回転角度位置を検出する検出部を備える回転角度位置検出器と、駆動力を伝達するための第１歯部、軸線方向で前記第１歯部と離間する第２歯部、および前記第１歯部と前記第２歯部との間に設けられた歯欠損部を備える駆動力伝達歯車と、潤滑剤と、を有し、前記潤滑剤は、前記第１歯部に塗布され、前記回転角度位置検出用歯車は、前記第２歯部に噛合していることを特徴とする。 In order to solve the above problems, a driving force transmission mechanism of the present invention includes a rotation angle position detector including a rotation angle position detection gear and a detection unit that detects a rotation angle position of the rotation angle position detection gear, and a drive. A first tooth portion for transmitting force, a second tooth portion spaced apart from the first tooth portion in the axial direction, and a tooth loss portion provided between the first tooth portion and the second tooth portion. A driving force transmission gear provided, and a lubricant, wherein the lubricant is applied to the first tooth portion, and the rotational angle position detecting gear meshes with the second tooth portion. Features.
　本発明では、駆動力伝達歯車は、軸線方向に離間する位置に第１歯部と第２歯部を備え、第１歯部が駆動力を伝達するために他の歯車と噛合する歯部とされ、第２歯部が回転角度位置検出用歯車と噛合する歯部とされている。ここで、他の歯車と噛合する第１歯部には、歯の摩耗を抑制するために潤滑剤が塗布されているが、第１歯部と第２歯部との間には歯欠損部が設けられているので、潤滑剤は、第１歯部から第２歯部の側に伝わりにくい。これにより、潤滑剤が第２歯部に噛合する回転角度位置検出用歯車に付着することを抑制できるので、潤滑剤が検出部に付着して検出し回転角度位置検出器に誤動作を発生させることを防止或いは抑制できる。 In the present invention, the driving force transmission gear includes a first tooth portion and a second tooth portion at positions spaced apart in the axial direction, and the first tooth portion engages with another gear in order to transmit the driving force; The second tooth portion is a tooth portion that meshes with the rotation angle position detecting gear. Here, a lubricant is applied to the first tooth portion meshing with another gear in order to suppress tooth wear, but a tooth missing portion is provided between the first tooth portion and the second tooth portion. Therefore, the lubricant is difficult to be transmitted from the first tooth portion to the second tooth portion side. As a result, it is possible to suppress the lubricant from adhering to the rotation angle position detection gear meshing with the second tooth portion, and therefore, the lubricant adheres to the detection portion and is detected to cause the rotation angle position detector to malfunction. Can be prevented or suppressed.
　本発明において、前記歯欠損部は、径方向で前記第１歯部の歯底および前記第２歯部の歯底とは異なる高さにある外周面を備えることが望ましい。このようにすれば、第１歯部の歯底と第２歯部の歯底の間に段差が設けられるので、第１歯部に塗布された潤滑剤が第２歯部の側に伝わることを、より、抑制できる。 In the present invention, it is desirable that the tooth defect portion has an outer peripheral surface at a height different from the tooth bottom of the first tooth portion and the tooth bottom of the second tooth portion in the radial direction. In this way, a step is provided between the tooth bottom of the first tooth portion and the tooth bottom of the second tooth portion, so that the lubricant applied to the first tooth portion is transmitted to the second tooth side. Can be suppressed more.
　この場合において、前記外周面は、前記第１歯部の歯底および前記第２歯部の歯底よりも径方向の内側に位置するものとすることができる。このようにすれば、第１歯部に他の歯車を噛合させる場合に、歯欠損部と他の歯車とが干渉することを回避できる。 In this case, the outer peripheral surface may be located on the inner side in the radial direction from the bottom of the first tooth portion and the bottom of the second tooth portion. If it does in this way, when meshing another gear with the 1st tooth part, it can avoid that a tooth missing part and other gears interfere.
　この場合において、前記外周面は、前記第１歯部の歯底および前記第２歯部の歯底よりも径方向の外側に位置するものとすることができる。このようにすれば、第１歯部の側から第２歯部の側に流れようとする潤滑剤を、歯欠損部によって堰き止めることができる。 In this case, the outer peripheral surface may be located on the outer side in the radial direction from the bottom of the first tooth portion and the bottom of the second tooth portion. If it does in this way, the lubricant which is going to flow from the 1st tooth part side to the 2nd tooth part side can be dammed up by a tooth loss part.
　本発明において、前記駆動力伝達歯車は、同軸に連結された第１歯車部材と第２歯車部材とを有し、前記第１歯車部材は、前記第１歯部を備え、前記第２歯車部材は、前記第２歯部および前記歯欠損部を備えるものとすることができる。このようにすれば、第１歯部が第２歯部とは異なる部材に設けられているので、第１歯部と第２歯部との歯数などを異なるものとすることが容易である。これにより、駆動力伝達歯車の回転数と第２歯部に噛合する回転位置検出用歯車の回転数の比率を所望のものとすることができるので、回転角度位置の検出精度を変更することが容易となる。 In the present invention, the driving force transmission gear includes a first gear member and a second gear member that are coaxially connected, and the first gear member includes the first tooth portion, and the second gear member. May comprise the second tooth part and the tooth defect part. If it does in this way, since the 1st tooth part is provided in the member different from the 2nd tooth part, it is easy to make the number of teeth etc. of the 1st tooth part and the 2nd tooth part different. . As a result, the ratio between the rotational speed of the driving force transmission gear and the rotational speed of the rotational position detecting gear meshing with the second tooth portion can be set to a desired value, so that the detection accuracy of the rotational angle position can be changed. It becomes easy.
　本発明において、前記第１歯車部材は、金属製であり、前記第２歯車部材は、樹脂製とすることができる。このようにすれば、駆動力を伝達するために他の歯車と噛合する第１歯部の強度を向上させることができる。また、第１歯部の強度を向上させたときに、駆動力伝達歯車の全体を金属製とした場合と比較して、駆動力伝達歯車の製造コストを抑制できる。 In the present invention, the first gear member can be made of metal, and the second gear member can be made of resin. If it does in this way, in order to transmit driving force, the intensity of the 1st tooth part which meshes with other gears can be raised. Further, when the strength of the first tooth portion is improved, the manufacturing cost of the driving force transmission gear can be suppressed as compared with the case where the entire driving force transmission gear is made of metal.
　本発明において、前記第１歯車部材と前記第２歯車部材とは、前記軸線方向に配列されており、前記第２歯車部材は、前記第１歯車部材の側の端面の周方向に離間する２か所に前記軸線方向に突出する第１突起と第２突起とを備え、前記第１歯車部材は、前記第２歯車部材の側の端面に前記第１突起を受け入れ可能な第１凹部と、前記軸線方向から前記第２突起を受け入れ可能な第２凹部と、を備え、前記第１突起と前記第２突起とは、大きさが相違し、前記第１突起を前記第１凹部に挿入したときに、前記第１突起は前記第１凹部に周方向で隙間なく嵌合することが望ましい。このようにすれば、第１突起を第１凹部に挿入し、第２突起を第２凹部に挿入することにより、第１歯部の位相と第２歯部の位相とを予め定めた関係に設定できる。 In the present invention, the first gear member and the second gear member are arranged in the axial direction, and the second gear member is spaced apart in the circumferential direction of the end face on the first gear member side. A first protrusion and a second protrusion protruding in the axial direction at a location, wherein the first gear member has a first recess capable of receiving the first protrusion on an end surface of the second gear member; A second recess capable of receiving the second protrusion from the axial direction, the first protrusion and the second protrusion have different sizes, and the first protrusion is inserted into the first recess. In some cases, it is desirable that the first protrusion is fitted in the first recess without a gap in the circumferential direction. If it does in this way, the 1st projection will be inserted in the 1st crevice, and the 2nd projection will be inserted in the 2nd crevice, and the phase of the 1st tooth part and the phase of the 2nd tooth part will be in a predetermined relation. Can be set.
　本発明において、前記回転角度位置検出器は、前記回転角度位置検出用歯車としてポテンショ歯車を備えるポテンショメータとすることができる。ポテンショメータでは、検出部を構成する抵抗体やブラシに潤滑剤が付着すると、誤動作の発生や、検出精度の低下を招く場合があるが、本発明によれば、このような誤動作を防止或いは抑制できる。 In the present invention, the rotation angle position detector may be a potentiometer provided with a potentiometer gear as the rotation angle position detection gear. In a potentiometer, if a lubricant adheres to a resistor or a brush constituting a detection unit, it may cause a malfunction or a decrease in detection accuracy. According to the present invention, such a malfunction can be prevented or suppressed. .
　次に、本発明の開閉部材駆動装置は、上記の駆動力伝達機構と、モータと、前記モータの駆動力を開閉部材が連結される出力軸に伝達する歯車機構と、を有し、前記輪列を構成する複数の歯車のうちの一つの歯車が前記駆動力伝達歯車であることを特徴とする。 Next, an opening / closing member driving device of the present invention includes the above-described driving force transmission mechanism, a motor, and a gear mechanism that transmits the driving force of the motor to an output shaft connected to the opening / closing member. One gear of the plurality of gears constituting the row is the driving force transmission gear.
　本発明によれば、駆動力伝達機構の回転角度位置検出器に誤動作が発生することを防止或いは抑制できる。従って、回転角度位置検出器からの出力に基づいてモータを駆動制御することにより、開閉部材を所望の閉位置や開位置に配置することが可能となる。 According to the present invention, it is possible to prevent or suppress the malfunction of the rotational angle position detector of the driving force transmission mechanism. Therefore, by controlling the drive of the motor based on the output from the rotation angle position detector, the opening / closing member can be disposed at a desired closed position or open position.
　本発明によれば、駆動力伝達歯車において駆動力を伝達する第１歯部に潤滑剤が塗布されていても、その潤滑剤が、駆動力伝達歯車の回転角度位置を検出する回転角度位置検出器の検出部に付着することが防止或いは抑制される。従って、回転角度位置検出器に誤動作が発生することを防止あるいは抑制できる。 According to the present invention, even if the lubricant is applied to the first tooth portion that transmits the driving force in the driving force transmission gear, the lubricant detects the rotational angle position of the driving force transmission gear. It is prevented or suppressed from adhering to the detector. Therefore, it is possible to prevent or suppress the malfunction of the rotation angle position detector.
本発明を適用した開閉部材駆動装置の説明図である。It is explanatory drawing of the opening / closing member drive device to which this invention is applied. ケースを取り除いた自動自動閉装置を第２方向から見た場合の斜視図である。It is a perspective view at the time of seeing the automatic self-closing device which removed the case from the 2nd direction. ケースを取り除いた自動自動閉装置を第１方向から見た場合の斜視図である。It is a perspective view at the time of seeing the automatic self-closing device which removed the case from the 1st direction. 第２複合歯車（トルクリミッタ）の斜視図および断面図である。It is the perspective view and sectional drawing of a 2nd compound gearwheel (torque limiter). 第２複合歯車の分解斜視図である。It is a disassembled perspective view of a 2nd compound gear. 第２複合歯車を構成する大径歯車と小径歯車のそれぞれの斜視図である。It is each perspective view of the large diameter gear and the small diameter gear which comprise the 2nd compound gear. 第５複合歯車およびポテンショメータの斜視図である。It is a perspective view of a 5th compound gear and a potentiometer. 第５複合歯車の分解斜視図および第２歯車部材の斜視図である。It is a disassembled perspective view of a 5th compound gearwheel, and a perspective view of a 2nd gear member. 開閉部材が開位置および閉位置にある場合の、出力歯車、出力軸、および、第５複合歯車の斜視図である。It is a perspective view of an output gear, an output shaft, and the 5th compound gear when an opening-and-closing member exists in an open position and a closed position. 開閉部材が人により操作された場合の出力歯車、出力軸、および、第５複合歯車の斜視図である。FIG. 10 is a perspective view of an output gear, an output shaft, and a fifth compound gear when the opening / closing member is operated by a person. 変形例の第５複合歯車の斜視図である。It is a perspective view of the 5th compound gear of a modification.
　以下、図面を参照して、本発明の実施の一形態である開閉部材駆動装置を説明する。 Hereinafter, an opening / closing member driving device according to an embodiment of the present invention will be described with reference to the drawings.
（全体構成）
　図１（ａ）は開閉部材駆動装置の説明図であり、図１（ｂ）は開閉部材駆動装置による蓋体の閉動作の説明図である。図１（ａ）に示すように、開閉部材駆動装置１は、開閉部材２が連結される自動閉装置４、スイッチ５、検出器６、および、制御部７を備える。図１（ｂ）に示すように、開閉部材２は、箱体３に対して起立する開位置２Ｂと箱体３に沿って平伏する閉位置２Ａとの間を９０°の角度範囲に渡って両方向に回転する。開閉部材駆動装置１は、開状態とされた蓋や扉などの開閉部材２を回動させて所定の閉位置２Ａに配置する。開閉部材２が閉位置２Ａに配置されると、箱体３に設けた収納部が開閉部材２により封鎖された状態となる。なお、開閉部材２の閉位置２Ａと開位置２Ｂの位置及び角度範囲は、実施例に限定されるものではなく、用途に応じて設定される。 (overall structure)
FIG. 1A is an explanatory diagram of the opening / closing member driving device, and FIG. 1B is an explanatory diagram of the closing operation of the lid by the opening / closing member driving device. As shown in FIG. 1A, the opening / closing member driving device 1 includes an automatic closing device 4 to which the opening / closing member 2 is connected, a switch 5, a detector 6, and a control unit 7. As shown in FIG. 1 (b), the opening / closing member 2 has a 90 ° angle range between an open position 2 </ b> B standing up with respect to the box 3 and a closed position 2 </ b> A flattening along the box 3. Rotates in both directions. The opening / closing member driving device 1 rotates and arranges the opening / closing member 2 such as a lid or a door in an open state at a predetermined closed position 2A. When the opening / closing member 2 is arranged at the closed position 2 </ b> A, the storage portion provided in the box 3 is in a state of being sealed by the opening / closing member 2. In addition, the position and angle range of the closed position 2A and the open position 2B of the opening / closing member 2 are not limited to the embodiment, and are set according to the application.
　自動閉装置４は、ケース１０と、開閉部材２が連結される出力軸１１を備える。出力軸１１における開閉部材２との連結部１２はケース１０の軸受孔１３から外側に露出する。開閉部材２はその回転中心軸が出力軸１１に同軸に連結される。以下の説明では、出力軸１１の軸線をＬ０とし、自動閉装置４において軸線Ｌ０に沿う方向をＸ方向とする。また、Ｘ方向の第１方向を第１方向Ｘ１とし、第１方向Ｘ１とは反対側を第２方向Ｘ２とする。 The automatic closing device 4 includes a case 10 and an output shaft 11 to which the opening / closing member 2 is coupled. The connecting portion 12 of the output shaft 11 with the opening / closing member 2 is exposed to the outside from the bearing hole 13 of the case 10. The opening / closing member 2 has a rotation center shaft coaxially connected to the output shaft 11. In the following description, the axis of the output shaft 11 is L0, and the direction along the axis L0 in the automatic closing device 4 is the X direction. The first direction in the X direction is defined as a first direction X1, and the opposite side of the first direction X1 is defined as a second direction X2.
　図２はケースを取り除いた自動閉装置４を第２方向Ｘ２から見た場合の斜視図である。図３はケースを取り除いた自動閉装置４を第１方向Ｘ１から見た場合の斜視図である。図３および図４に示すように、ケース１０内には自動閉装置４の駆動源となるモータ１５と、開閉部材２が連結される出力軸１１と、モータ１５の駆動力を出力軸１１に伝達する歯車機構（駆動力伝達機構）１６と、ポテンショメータ（回転角度位置検出器）１７が収納されている。歯車機構１６は減速機構である。ポテンショメータ１７は、ポテンショ歯車（回転角度位置検出用歯車）１８と、ポテンショ歯車１８の回転角度位置を検出する検出部１９を備える。 FIG. 2 is a perspective view when the automatic closing device 4 with the case removed is viewed from the second direction X2. FIG. 3 is a perspective view when the automatic closing device 4 with the case removed is viewed from the first direction X1. As shown in FIGS. 3 and 4, in the case 10, a motor 15 that is a driving source of the automatic closing device 4, an output shaft 11 to which the opening / closing member 2 is connected, and a driving force of the motor 15 are applied to the output shaft 11. A transmission gear mechanism (driving force transmission mechanism) 16 and a potentiometer (rotational angle position detector) 17 are housed. The gear mechanism 16 is a speed reduction mechanism. The potentiometer 17 includes a potentiometer gear (rotation angle position detection gear) 18 and a detection unit 19 that detects the rotation angle position of the potentiometer gear 18.
　図３に示すように、モータ１５は、ケース１０内において、第１方向Ｘ１にモータ出力軸１５ａが突出する姿勢で配置されている。歯車機構１６は、モータ出力軸１５ａに取り付けられたピニオン２２と、ピニオン２２と噛合する第１複合歯車２３と、第１複合歯車２３と噛合する第２複合歯車（トルクリミッタ）２４と、第２複合歯車２４と噛合する第３複合歯車２５と、第３複合歯車２５と噛合する第４複合歯車２６と、第４複合歯車２６と噛合する第５複合歯車（駆動力伝達歯車）２７と、第５複合歯車２７と噛合する出力歯車２８を備える。 As shown in FIG. 3, the motor 15 is disposed in the case 10 in a posture in which the motor output shaft 15a protrudes in the first direction X1. The gear mechanism 16 includes a pinion 22 attached to the motor output shaft 15a, a first compound gear 23 that meshes with the pinion 22, a second compound gear (torque limiter) 24 that meshes with the first compound gear 23, and a second A third compound gear 25 meshed with the compound gear 24, a fourth compound gear 26 meshed with the third compound gear 25, a fifth compound gear (driving force transmission gear) 27 meshed with the fourth compound gear 26, An output gear 28 meshing with the fifth compound gear 27 is provided.
　第１複合歯車２３は、図３に示すように、ピニオン２２と噛合する第１大径歯車部分２３ａと、第１大径歯車部分２３ａの第２方向Ｘ２の側に同軸に設けられた第１小径歯車部分２３ｂを備える。第２複合歯車２４は、第１小径歯車部分２３ｂと噛合する第２大径歯車部分２４ａと、第２大径歯車部分２４ａの第２方向Ｘ２の側に同軸に設けられた第２小径歯車部分２４ｂを備える。第３複合歯車２５は、第２小径歯車部分２４ｂと噛合する第３大径歯車部分２５ａと、第３大径歯車部分２５ａの第１方向Ｘ１の側に同軸に設けられた第３小径歯車部分２５ｂを備える。第４複合歯車２６は、第３小径歯車部分２５ｂと噛合する第４大径歯車部分２６ａと、第４大径歯車部分２６ａの第１方向Ｘ１の側に同軸に設けられた第４小径歯車部分２６ｂを備える。第５複合歯車２７は、第４小径歯車部分２６ｂと噛合する第５大径歯車部分２７ａと、第５大径歯車部分２７ａの第２方向Ｘ２の側に同軸に設けられた第５小径歯車部分２７ｂを備える。第５小径歯車部分２７ｂは、Ｘ方向（第５小径歯車部分２７ｂの軸線方向）で離間する位置に設けられた第１歯部２７ｃと第２歯部２７ｄを備える。第１歯部２７ｃは第２歯部２７ｄの第１方向Ｘ１の側に位置する。出力歯車２８は第５小径歯車部分２７ｂの第１歯部２７ｃと噛合する。第５小径歯車部分２７ｂの第２歯部２７ｄには、ポテンショメータ１７のポテンショ歯車１８が噛合する。 As shown in FIG. 3, the first compound gear 23 includes a first large-diameter gear portion 23a meshing with the pinion 22, and a first coaxial gear provided on the second direction X2 side of the first large-diameter gear portion 23a. A small-diameter gear portion 23b is provided. The second compound gear 24 includes a second large-diameter gear portion 24a that meshes with the first small-diameter gear portion 23b, and a second small-diameter gear portion that is provided coaxially on the second direction X2 side of the second large-diameter gear portion 24a. 24b. The third compound gear 25 includes a third large-diameter gear portion 25a meshing with the second small-diameter gear portion 24b, and a third small-diameter gear portion provided coaxially on the first direction X1 side of the third large-diameter gear portion 25a. 25b. The fourth compound gear 26 includes a fourth large-diameter gear portion 26a that meshes with the third small-diameter gear portion 25b, and a fourth small-diameter gear portion that is provided coaxially on the first direction X1 side of the fourth large-diameter gear portion 26a. 26b. The fifth compound gear 27 includes a fifth large-diameter gear portion 27a meshing with the fourth small-diameter gear portion 26b, and a fifth small-diameter gear portion provided coaxially on the second direction X2 side of the fifth large-diameter gear portion 27a. 27b. The fifth small-diameter gear portion 27b includes a first tooth portion 27c and a second tooth portion 27d provided at positions separated in the X direction (the axial direction of the fifth small-diameter gear portion 27b). The 1st tooth part 27c is located in the 1st direction X1 side of the 2nd tooth part 27d. The output gear 28 meshes with the first tooth portion 27c of the fifth small diameter gear portion 27b. The potentiometer gear 18 of the potentiometer 17 meshes with the second tooth portion 27d of the fifth small diameter gear portion 27b.
　図２に示すように、第１複合歯車２３は、Ｘ方向に延びる第１支軸３１に回転可能に支持されている。第２複合歯車２４は、Ｘ方向に延びる第２支軸３２に回転可能に支持される。第３複合歯車２５は、Ｘ方向に延びる第３支軸３３に回転可能に支持される。第４複合歯車２６は、Ｘ方向に延びる第４支軸３４に回転可能に支持される。第５複合歯車２７は、Ｘ方向に延びる第５支軸３５に回転可能に支持される。第１支軸３１、第２支軸３２、第３支軸３３、第４支軸３４および第５支軸３５のＸ方向の両端部分は、それぞれケース１０に設けられた支持部（不図示）に支持されている。 As shown in FIG. 2, the first compound gear 23 is rotatably supported by a first support shaft 31 extending in the X direction. The second compound gear 24 is rotatably supported by a second support shaft 32 extending in the X direction. The third compound gear 25 is rotatably supported by a third support shaft 33 extending in the X direction. The fourth compound gear 26 is rotatably supported by a fourth support shaft 34 extending in the X direction. The fifth compound gear 27 is rotatably supported by a fifth support shaft 35 extending in the X direction. Both end portions in the X direction of the first support shaft 31, the second support shaft 32, the third support shaft 33, the fourth support shaft 34, and the fifth support shaft 35 are support portions (not shown) provided in the case 10, respectively. It is supported by.
　出力歯車２８は扇形歯車である。出力歯車２８と出力軸１１は同軸に配置されている。すなわち、出力軸１１と出力歯車２８の軸線Ｌ０は一致している。出力歯車２８（扇形歯車）の要（回転中心）にはＸ方向に貫通する軸受孔２９が設けられている。 The output gear 28 is a sector gear. The output gear 28 and the output shaft 11 are arranged coaxially. In other words, the axis L0 of the output shaft 11 and the output gear 28 coincide. A bearing hole 29 penetrating in the X direction is provided at the main part (rotation center) of the output gear 28 (fan gear).
　図３に示すように、出力軸１１は、軸線Ｌ０に沿ってＸ方向に延びる出力軸本体部３７と、出力軸本体部３７から軸線Ｌ０と直交する方向に突出する腕部３８を備える。出力軸本体部３７と腕部３８とは一体に回転する。出力軸本体部３７には、開閉部材２を連結するための連結部１２が設けられている。連結部１２は出力軸本体部３７をＸ方向に貫通する貫通孔である。連結部１２（貫通孔）をＸ方向から見た場合の開口形状はＤ字形状である。出力軸１１は、出力軸本体部３７が出力歯車２８の軸受孔２９に回転可能に支持されている。また、出力軸１１はケース１０に回転可能に支持されている。 As shown in FIG. 3, the output shaft 11 includes an output shaft main body portion 37 extending in the X direction along the axis L0, and an arm portion 38 protruding from the output shaft main body portion 37 in a direction orthogonal to the axis L0. The output shaft main body portion 37 and the arm portion 38 rotate integrally. The output shaft main body 37 is provided with a connecting portion 12 for connecting the opening / closing member 2. The connecting portion 12 is a through hole that penetrates the output shaft main body portion 37 in the X direction. The opening shape when the connecting portion 12 (through hole) is viewed from the X direction is a D-shape. In the output shaft 11, the output shaft main body 37 is rotatably supported in the bearing hole 29 of the output gear 28. The output shaft 11 is rotatably supported by the case 10.
　ここで、各歯車（ピニオン２２、第１複合歯車２３、第２複合歯車２４と、第３複合歯車２５、第４複合歯車２６、第５複合歯車２７および出力歯車２８）において、他の歯車が噛合する歯部には、ポテンショ歯車１８と噛合する第２歯部２７ｄを除き、グリス（潤滑剤）が塗布されている。 Here, in each gear (the pinion 22, the first compound gear 23, the second compound gear 24, the third compound gear 25, the fourth compound gear 26, the fifth compound gear 27, and the output gear 28), the other gears are Grease (lubricant) is applied to the meshing teeth except for the second tooth 27d meshing with the potentiometer gear 18.
（第２複合歯車）
　図４から図６を参照して第２複合歯車２４を詳細に説明する。図４（ａ）は第２方向Ｘ２から見た場合の第２複合歯車２４の斜視図であり、図４（ｂ）は第２複合歯車２４をその軸線に沿って切断した断面図であり、図４（ｃ）は図４（ａ）のＡ－Ａ線における断面図である。図５は第２複合歯車２４の分解斜視図である。図６（ａ）は第２複合歯車２４を構成する大径歯車を第２方向Ｘ２から見た場合の斜視図であり、図６（ｂ）は第２複合歯車２４を構成する小径歯車を第１方向Ｘ１から見た場合の斜視図である。図４に示すように、第２複合歯車２４は、第２支軸３２に回転可能に支持された大径歯車（第２歯車）４１および小径歯車（第１歯車）４２と、大径歯車４１と小径歯車４２との間で回転を伝達する回転伝達機構４３を備える。 (2nd compound gear)
The second compound gear 24 will be described in detail with reference to FIGS. 4 (a) is a perspective view of the second compound gear 24 when viewed from the second direction X2, and FIG. 4 (b) is a cross-sectional view of the second compound gear 24 cut along its axis. FIG. 4C is a cross-sectional view taken along the line AA in FIG. FIG. 5 is an exploded perspective view of the second compound gear 24. FIG. 6A is a perspective view of the large-diameter gear constituting the second compound gear 24 as viewed from the second direction X2, and FIG. 6B shows the small-diameter gear constituting the second compound gear 24 as the first gear. It is a perspective view at the time of seeing from 1 direction X1. As shown in FIG. 4, the second compound gear 24 includes a large-diameter gear (second gear) 41 and a small-diameter gear (first gear) 42 that are rotatably supported by the second support shaft 32, and a large-diameter gear 41. And a rotation transmission mechanism 43 that transmits rotation between the small-diameter gear 42 and the small-diameter gear 42.
　図４および図５に示すように、大径歯車４１は外周面に第１複合歯車２３と噛合する大径歯部（第２歯部）４１ａを備える筒部４５と、筒部４５の内周面のＸ方向の途中位置（第１方向Ｘ１の開口に近い位置）から径方向を内周側に突出する環状の板部４６と、板部４６から筒部４５の内周側を第２方向Ｘ２に突出する環状壁部４７とを備える。板部４６の中心には第２支軸３２が貫通する貫通孔４８が設けられている。筒部４５と環状壁部４７とは径方向に隙間を開けて同軸に設けられている。環状壁部の第２方向Ｘ２の端は筒部４５の内周側に位置する。 As shown in FIGS. 4 and 5, the large-diameter gear 41 has a cylindrical portion 45 having a large-diameter tooth portion (second tooth portion) 41 a meshing with the first compound gear 23 on the outer peripheral surface, and an inner periphery of the cylindrical portion 45. An annular plate portion 46 projecting radially inward from an intermediate position in the X direction of the surface (position close to the opening in the first direction X1), and the inner peripheral side of the tube portion 45 from the plate portion 46 in the second direction. And an annular wall 47 projecting to X2. A through hole 48 through which the second support shaft 32 passes is provided at the center of the plate portion 46. The cylindrical portion 45 and the annular wall portion 47 are provided coaxially with a gap in the radial direction. The end of the annular wall portion in the second direction X2 is located on the inner peripheral side of the cylindrical portion 45.
　図６（ａ）に示すように、環状壁部４７は、第２方向Ｘ２の端部分に外径寸法が小さい小径部４９を備える。また、環状壁部４７は、第２方向Ｘ２の端に、第２方向Ｘ２に向かって内周側に傾斜するテーパー形状の面取り面４９ａを備える。環状壁部４７と板部４６との境界部分にはアール５０が設けられている。換言すれば、環状壁部４７は、板部４６の側の端部分に、板部４６の側に向かって、厚さ寸法が増加する肉厚部分（アール５０）を備える。 As shown in FIG. 6A, the annular wall portion 47 includes a small-diameter portion 49 having a small outer diameter at the end portion in the second direction X2. Further, the annular wall portion 47 includes a tapered chamfered surface 49a that is inclined toward the inner peripheral side in the second direction X2 at the end in the second direction X2. A radius 50 is provided at a boundary portion between the annular wall portion 47 and the plate portion 46. In other words, the annular wall portion 47 includes a thick portion (R 50) whose thickness dimension increases toward the plate portion 46 side at the end portion on the plate portion 46 side.
　図４（ｂ）および図６（ｂ）に示すように、小径歯車４２は、第３複合歯車２５と噛合する小径歯部（第１歯部）５３ａを備える軸部５３と、大径歯車４１の環状壁部４７の内周側に挿入される挿入部５４と、軸部５３と挿入部５４の間から径方向に広がる環状板部５５と、環状板部５５の外周縁から第１方向Ｘ１に延びる環状筒部５６を備える。また、小径歯車４２は軸部５３および挿入部５４をＸ方向に貫通する貫通孔４２ａを備える。貫通孔４２ａには第２支軸３２が貫通する。 As shown in FIGS. 4B and 6B, the small-diameter gear 42 includes a shaft portion 53 including a small-diameter tooth portion (first tooth portion) 53 a that meshes with the third compound gear 25, and the large-diameter gear 41. The insertion portion 54 to be inserted on the inner peripheral side of the annular wall portion 47, the annular plate portion 55 extending in the radial direction from between the shaft portion 53 and the insertion portion 54, and the outer periphery of the annular plate portion 55 in the first direction X1. An annular cylinder portion 56 is provided. The small-diameter gear 42 includes a through hole 42a that penetrates the shaft portion 53 and the insertion portion 54 in the X direction. The second support shaft 32 passes through the through hole 42a.
　挿入部５４は軸部５３の第１方向Ｘ１の側に位置する。挿入部５４は第２支軸３２と同軸の環状の外周面５４ａを備える。環状筒部５６は、軸部５３および挿入部５４と同軸であり、挿入部５４における第２方向Ｘ２の端部分の外周側に位置する。環状筒部５６の第１方向Ｘ１の先端部分の内周側には、先端側から切り欠かれた環状段部５７が設けられている。環状段部５７は、内周側を向く環状周壁面５７ａと、第１方向Ｘ１を向く環状端面５７ｂを備える。 The insertion portion 54 is located on the side of the shaft portion 53 in the first direction X1. The insertion portion 54 includes an annular outer peripheral surface 54 a that is coaxial with the second support shaft 32. The annular cylindrical portion 56 is coaxial with the shaft portion 53 and the insertion portion 54 and is positioned on the outer peripheral side of the end portion of the insertion portion 54 in the second direction X2. An annular stepped portion 57 cut out from the distal end side is provided on the inner peripheral side of the distal end portion of the annular cylindrical portion 56 in the first direction X1. The annular step portion 57 includes an annular peripheral wall surface 57a facing the inner peripheral side and an annular end surface 57b facing the first direction X1.
　小径歯車４２の挿入部５４を大径歯車４１の環状壁部４７に挿入して第２複合歯車２４を構成した状態では、環状筒部５６の第１方向Ｘ１の先端部分は大径歯車４１の筒部４５と環状壁部４７との間に挿入され、環状板部５５の第２方向Ｘ２の端面が大径歯車４１の筒部４５の第２方向Ｘ２の端面とが同一平面上に位置する。 In a state where the insertion portion 54 of the small diameter gear 42 is inserted into the annular wall portion 47 of the large diameter gear 41 to constitute the second compound gear 24, the tip portion of the annular cylinder portion 56 in the first direction X1 is the large diameter gear 41. The end face in the second direction X2 of the annular plate portion 55 is inserted between the tubular portion 45 and the annular wall portion 47, and the end face in the second direction X2 of the tubular portion 45 of the large-diameter gear 41 is located on the same plane. .
　ここで、図４（ｂ）および図５に示すように、小径歯車４２は、Ｘ方向に同軸に連結された第１部材５８および第２部材５９を備える。第１部材５８は軸部５３、環状板部５５および環状筒部５６を備える。また、第１部材５８は軸部５３の第１方向Ｘ１の端面に矩形の凹部６０を備える。第２部材５９は挿入部５４を備える。また、第２部材５９は挿入部５４の第２方向Ｘ２の端面に矩形の凸部６１を備える。第１部材５８と第２部材５９とを連結する際には、第１部材５８の凹部６０に第２部材５９の凸部６１が挿入される。第１部材５８は樹脂製であり、第２部材５９は焼結金属からなる。 Here, as shown in FIGS. 4B and 5, the small-diameter gear 42 includes a first member 58 and a second member 59 that are coaxially connected in the X direction. The first member 58 includes a shaft portion 53, an annular plate portion 55, and an annular cylinder portion 56. The first member 58 includes a rectangular recess 60 on the end surface of the shaft portion 53 in the first direction X1. The second member 59 includes an insertion portion 54. The second member 59 includes a rectangular convex portion 61 on the end surface of the insertion portion 54 in the second direction X2. When connecting the first member 58 and the second member 59, the convex portion 61 of the second member 59 is inserted into the concave portion 60 of the first member 58. The first member 58 is made of resin, and the second member 59 is made of sintered metal.
　回転伝達機構４３は、図５に示すように、大径歯車４１の環状壁部４７に設けられた４本のスリット６３と、各スリット６３にそれぞれ挿入された金属製の４本のシャフト６４を備える。図６に示すように、各スリット６３は、環状壁部４７の第２方向Ｘ２の端から板部４６に向かって当該環状壁部４７を切り欠いて設けられている。各スリット６３はＸ方向に延びて板部４６に達する。４本のスリット６３は第２支軸３２の軸線Ｌ１回り（第２複合歯車２４の軸線Ｌ１回り）で等角度間隔に設けられている。従って、環状壁部４７は、周方向に等間隔で配列された４枚の円弧壁６５から構成されている。 As shown in FIG. 5, the rotation transmission mechanism 43 includes four slits 63 provided in the annular wall portion 47 of the large-diameter gear 41 and four metal shafts 64 respectively inserted into the slits 63. Prepare. As shown in FIG. 6, each slit 63 is provided by cutting out the annular wall portion 47 from the end of the annular wall portion 47 in the second direction X2 toward the plate portion 46. Each slit 63 extends in the X direction and reaches the plate portion 46. The four slits 63 are provided at equiangular intervals around the axis L1 of the second support shaft 32 (around the axis L1 of the second compound gear 24). Accordingly, the annular wall portion 47 is composed of four circular arc walls 65 arranged at equal intervals in the circumferential direction.
　図５に示すように、各シャフト６４は円柱形状であり、Ｘ方向に延びる。各シャフト６４は金属製である。４本のシャフト６４はそれぞれスリット６３に挿入されている。ここで、図４（ｂ）、図４（ｃ）に示すように、各シャフト６４の直径は、各スリット６３の周方向の幅よりも短い。また、各シャフト６４の直径は、環状壁部４７（円弧壁６５）の径方向の厚みよりも長い。各シャフト６４の長さ寸法は、板部４６から環状壁部４７の小径部４９までの高さ寸法よりも短い。 As shown in FIG. 5, each shaft 64 has a cylindrical shape and extends in the X direction. Each shaft 64 is made of metal. The four shafts 64 are respectively inserted into the slits 63. Here, as shown in FIGS. 4B and 4C, the diameter of each shaft 64 is shorter than the circumferential width of each slit 63. Moreover, the diameter of each shaft 64 is longer than the thickness of the annular wall part 47 (arc wall 65) in the radial direction. The length dimension of each shaft 64 is shorter than the height dimension from the plate portion 46 to the small diameter portion 49 of the annular wall portion 47.
　また、回転伝達機構４３は、図４（ｃ）および図５に示すように、小径歯車４２の挿入部５４の外周面５４ａに設けられた４本の溝部６６と、大径歯車４１の筒部４５と環状壁部４７との間に挿入されたコイルバネ６７と、を備える。４本の溝部６６は第２複合歯車２４の軸線Ｌ１回りで等角度間隔に設けられている。図４（ｃ）に示すように、各溝部６６には、各スリット６３に挿入された各シャフト６４の内周側部分が挿入される。コイルバネ６７は、その内周側が環状壁部４７の外周面５４ａに接触する状態で筒部４５と環状壁部４７との間に挿入されている。コイルバネ６７は、シャフト６４が環状壁部４７から外周側へ突出したときに当該シャフト６４を内周側に付勢する付勢力を発揮する。 Further, as shown in FIGS. 4C and 5, the rotation transmission mechanism 43 includes four groove portions 66 provided on the outer peripheral surface 54 a of the insertion portion 54 of the small diameter gear 42, and the cylindrical portion of the large diameter gear 41. And a coil spring 67 inserted between the annular wall 47 and the annular wall 47. The four groove portions 66 are provided at equiangular intervals around the axis L <b> 1 of the second compound gear 24. As shown in FIG. 4C, the inner peripheral side portion of each shaft 64 inserted into each slit 63 is inserted into each groove 66. The coil spring 67 is inserted between the cylindrical portion 45 and the annular wall portion 47 so that the inner peripheral side thereof is in contact with the outer peripheral surface 54 a of the annular wall portion 47. The coil spring 67 exerts a biasing force that biases the shaft 64 toward the inner peripheral side when the shaft 64 protrudes from the annular wall portion 47 toward the outer peripheral side.
　さらに、回転伝達機構４３は、図４（ｂ）および図６（ｂ）に示すように、環状壁部４７における第２方向Ｘ２の端の外周側への変位を規制する規制部６８（規制部材）、シャフト６４のＸ方向への移動範囲を規定するシャフト移動規制部６９、および、コイルバネ６７のＸ方向への移動範囲を規定するコイルバネ移動規制部７０を備える。規制部６８、シャフト移動規制部６９、および、コイルバネ移動規制部７０は、小径歯車４２の環状筒部５６に設けられている。 Further, as shown in FIGS. 4B and 6B, the rotation transmission mechanism 43 includes a restricting portion 68 (a restricting member) that restricts displacement of the end of the annular wall portion 47 in the second direction X2 toward the outer peripheral side. ), A shaft movement restricting portion 69 that defines the movement range of the shaft 64 in the X direction, and a coil spring movement restricting portion 70 that defines the movement range of the coil spring 67 in the X direction. The restricting portion 68, the shaft movement restricting portion 69, and the coil spring movement restricting portion 70 are provided in the annular cylindrical portion 56 of the small diameter gear 42.
　規制部６８は、環状筒部５６において環状段部５７の第２方向Ｘ２に隣り合う部分である。規制部６８は、環状筒部５６の小径部４９の半径方向の外側に、極僅かな隙間を開けて対向する。これにより、規制部６８は、環状壁部４７の第２方向Ｘ２の端部分が外周側に変位しようとしたときに、当該環状壁部４７の第２方向Ｘ２の端部分に外周側から当接して、その変位を規制する。シャフト移動規制部６９は、環状筒部５６の環状段部５７において第１方向Ｘ１を向く環状端面５７ｂである。シャフト移動規制部６９は小径部４９の半径方向の外側に位置する。これにより、シャフト移動規制部６９はスリット６３に挿入された状態のシャフト６４とＸ方向で隙間を開けて対向する。なお、環状段部５７の環状周壁面５７ａは、後述するようにシャフト６４が外周側に移動した場合でも、シャフト６４と干渉することがない位置に設けられている。 The regulating portion 68 is a portion adjacent to the annular step portion 57 in the second direction X2 in the annular cylindrical portion 56. The restricting portion 68 is opposed to the outer side in the radial direction of the small diameter portion 49 of the annular cylindrical portion 56 with a very small gap. Thus, when the end portion of the annular wall portion 47 in the second direction X2 is about to be displaced toward the outer peripheral side, the restricting portion 68 contacts the end portion of the annular wall portion 47 in the second direction X2 from the outer peripheral side. To regulate the displacement. The shaft movement restricting portion 69 is an annular end surface 57 b that faces the first direction X <b> 1 in the annular step portion 57 of the annular cylindrical portion 56. The shaft movement restricting portion 69 is located outside the small diameter portion 49 in the radial direction. Thus, the shaft movement restricting portion 69 is opposed to the shaft 64 inserted in the slit 63 with a gap in the X direction. The annular peripheral wall surface 57a of the annular step portion 57 is provided at a position where it does not interfere with the shaft 64 even when the shaft 64 moves to the outer peripheral side as will be described later.
　第２複合歯車２４を構成する際には、まず、大径歯車４１の環状壁部４７の４つのスリット６３の間に各シャフト６４を挿入する。次に、環状壁部４７と筒部４５との間にコイルバネ６７を配置する。その後、第１部材５８の挿入部５４の溝部６６とスリット６３との角度位置に位置合わせして、第１部材５８（挿入部５４）を環状壁部４７の内周側に挿入する。これにより、４本のシャフト６４のそれぞれは、その内周側の一部分が挿入部５４の各溝部６６に嵌り込んだ状態となる。また、環状壁部４７の外周側に位置するコイルバネ６７は、各シャフト６４を内周側に向って付勢する付勢力を発揮するものとなる。その後、第２部材５９を第１部材５８と連結する。これにより第２複合歯車２４の組み立てが完了する。第２複合歯車２４が組み立てられると、大径歯車４１は第２大径歯車部分２４ａを構成し、小径歯車４２は第２小径歯車部分２４ｂを構成する。 When configuring the second compound gear 24, first, the shafts 64 are inserted between the four slits 63 of the annular wall portion 47 of the large-diameter gear 41. Next, the coil spring 67 is disposed between the annular wall portion 47 and the cylindrical portion 45. Thereafter, the first member 58 (insertion portion 54) is inserted into the inner peripheral side of the annular wall portion 47 in alignment with the angular position between the groove portion 66 of the insertion portion 54 of the first member 58 and the slit 63. As a result, each of the four shafts 64 is in a state where a part of the inner peripheral side thereof is fitted in each groove 66 of the insertion portion 54. In addition, the coil spring 67 located on the outer peripheral side of the annular wall 47 exhibits a biasing force that biases each shaft 64 toward the inner peripheral side. Thereafter, the second member 59 is connected to the first member 58. Thereby, the assembly of the second compound gear 24 is completed. When the second compound gear 24 is assembled, the large-diameter gear 41 constitutes the second large-diameter gear portion 24a, and the small-diameter gear 42 constitutes the second small-diameter gear portion 24b.
　ここで、第２複合歯車２４は、通常は、コイルバネ６７の付勢力によって、４本のシャフト６４のそれぞれが挿入部５４の各溝部６６に嵌り込んだ状態に維持される。従って、大径歯車４１と小径歯車４２は一体に回転する。 Here, the second compound gear 24 is normally maintained in a state where each of the four shafts 64 is fitted in each groove 66 of the insertion portion 54 by the biasing force of the coil spring 67. Therefore, the large diameter gear 41 and the small diameter gear 42 rotate together.
　一方、例えば、出力軸１１の側から歯車機構１６に過大な力が入力された場合には、この力によって大径歯車４１と小径歯車４２が相対回転する。すなわち、出力軸１１の側から歯車機構１６に過大な力が入力されると、小径歯車４２と大径歯車４１との角度位置が位置合わせした角度位置からずれる。これにより、小径歯車４２の挿入部５４の溝部６６の位置は、大径歯車４１のスリット６３から周方向にずれるので、シャフト６４はコイルバネ６７の付勢力に抗して溝部６６から外周側に外れて、挿入部５４の外周面５４ａに乗り上げる。これにより、小径歯車４２と大径歯車４１の相対回転が許容される。従って、出力軸１１の側から入力された過大な力は第２複合歯車２４で減衰され、駆動力伝達方向の上流側（モータ１５側）に過大な力が伝達されることがない。このように、第２複合歯車２４はトルクリミッタとして機能する。 On the other hand, for example, when an excessive force is input to the gear mechanism 16 from the output shaft 11 side, the large-diameter gear 41 and the small-diameter gear 42 are relatively rotated by this force. That is, when an excessive force is input to the gear mechanism 16 from the output shaft 11 side, the angular positions of the small diameter gear 42 and the large diameter gear 41 are deviated from the aligned angular positions. As a result, the position of the groove portion 66 of the insertion portion 54 of the small-diameter gear 42 is shifted in the circumferential direction from the slit 63 of the large-diameter gear 41, so that the shaft 64 is disengaged from the groove portion 66 toward the outer peripheral side against the urging force of the coil spring 67. Then, it rides on the outer peripheral surface 54a of the insertion portion 54. Thereby, the relative rotation of the small diameter gear 42 and the large diameter gear 41 is allowed. Therefore, an excessive force input from the output shaft 11 side is attenuated by the second compound gear 24, and an excessive force is not transmitted to the upstream side (motor 15 side) in the driving force transmission direction. Thus, the second compound gear 24 functions as a torque limiter.
（第５複合歯車およびポテンショメータ）
　次に、図７および図８を参照して第５複合歯車２７およびポテンショメータ１７を説明する。図７は第５複合歯車２７およびポテンショメータ１７を取り出して示す斜視図である。図７では第５複合歯車２７およびポテンショメータ１７を第１方向Ｘ１から見ている。図８（ａ）は第５複合歯車２７の分解斜視図であり、図８（ｂ）は第５複合歯車２７を構成する第２歯車を第２方向Ｘ２から見た場合の斜視図である。図７に示すように、第５複合歯車２７は、第５大径歯車部分２７ａを構成する大径歯車７５と第５小径歯車部分２７ｂを構成する小径歯車（駆動力伝達歯車）７６を備える。大径歯車７５と小径歯車７６とは同軸に連結されている。大径歯車７５は、筒状であり、第４複合歯車２６と噛合する大径歯部７５ａを備える。 (Fifth compound gear and potentiometer)
Next, the fifth compound gear 27 and the potentiometer 17 will be described with reference to FIGS. 7 and 8. FIG. 7 is a perspective view showing the fifth compound gear 27 and the potentiometer 17 taken out. In FIG. 7, the fifth compound gear 27 and the potentiometer 17 are viewed from the first direction X1. FIG. 8A is an exploded perspective view of the fifth compound gear 27, and FIG. 8B is a perspective view of the second gear constituting the fifth compound gear 27 as viewed from the second direction X2. As shown in FIG. 7, the fifth compound gear 27 includes a large-diameter gear 75 constituting the fifth large-diameter gear portion 27a and a small-diameter gear (driving force transmission gear) 76 constituting the fifth small-diameter gear portion 27b. The large diameter gear 75 and the small diameter gear 76 are connected coaxially. The large-diameter gear 75 is cylindrical and includes a large-diameter tooth portion 75 a that meshes with the fourth compound gear 26.
　図８に示すように、小径歯車７６は、出力歯車２８が噛合する第１歯部７７ａを有する第１歯車部材７７と、ポテンショ歯車１８が噛合する第２歯部７８ａを有する第２歯車部材７８を備える。第１歯車部材７７と第２歯車部材７８は第５複合歯車２７の軸線Ｌ２上に配列されて同軸に連結されている。第１歯部７７ａと第２歯部７８ａとは同一の歯を備える。すなわち、第１歯部７７ａと第２歯部７８ａとは、歯底円、歯先円、歯数および歯の形成ピッチが同一である。 As shown in FIG. 8, the small-diameter gear 76 includes a first gear member 77 having a first tooth portion 77 a with which the output gear 28 is engaged, and a second gear member 78 having a second tooth portion 78 a with which the potentiometer gear 18 is engaged. Is provided. The first gear member 77 and the second gear member 78 are arranged on the axis L2 of the fifth compound gear 27 and are connected coaxially. The 1st tooth part 77a and the 2nd tooth part 78a are provided with the same tooth. That is, the first tooth portion 77a and the second tooth portion 78a have the same root circle, tip circle, number of teeth, and tooth formation pitch.
　第１歯車部材７７は、外周面に第１歯部７７ａを備える軸部７９と、軸部７９から第１方向Ｘ１に同軸に突出する突出部８０を備える。突出部８０は、軸線Ｌ２を挟んだ両側に互いに平行に延びる平面を備える。大径歯車７５の中心孔７５ｂは凸部８０と嵌合する形状を備える。第１歯車部材７７の突出部８０が大径歯車７５の中心孔７５ｂに挿入されることにより、大径歯車７５と小径歯車７６は連結されて一体に回転する。 The first gear member 77 includes a shaft portion 79 having a first tooth portion 77a on the outer peripheral surface, and a projecting portion 80 that protrudes coaxially from the shaft portion 79 in the first direction X1. The protrusion 80 includes flat surfaces extending in parallel to each other on both sides of the axis L2. The center hole 75 b of the large-diameter gear 75 has a shape that fits with the convex portion 80. By inserting the protruding portion 80 of the first gear member 77 into the center hole 75b of the large diameter gear 75, the large diameter gear 75 and the small diameter gear 76 are connected and rotate integrally.
　第２歯車部材７８は第２歯部７８ａの第１方向Ｘ１の側の隣に筒状の歯欠損部８１を備える。従って、第１歯車部材７７と第２歯車部材７８を連結して小径歯車７６を構成すると、小径歯車７６は、第１歯部７７ａ、Ｘ方向で第１歯部７７ａと離間する第２歯部７８ａ、および、第１歯部７７ａと第２歯部７８ａとの間に設けられた歯欠損部８１を備えるものとなる。歯欠損部８１は、径方向で第１歯部７７ａの歯底７７ｂおよび第２歯部７８ａの歯底７８ｂとは異なる高さに位置する外周面８１ａを備える。本例では、外周面８１ａは、第１歯部７７ａの歯底７７ｂおよび第２歯部７８ａの歯底７７ｂよりも径方向の内周側に位置する。ここで、大径歯車７５は樹脂製であり、第１歯車部材７７は金属製であり、第２歯車部材７８は樹脂製である。 The second gear member 78 includes a cylindrical tooth missing portion 81 adjacent to the second tooth portion 78a on the first direction X1 side. Therefore, when the first gear member 77 and the second gear member 78 are connected to form the small-diameter gear 76, the small-diameter gear 76 is separated from the first tooth portion 77a and the first tooth portion 77a in the X direction. 78a and a tooth loss part 81 provided between the first tooth part 77a and the second tooth part 78a. The tooth missing part 81 includes an outer peripheral surface 81a positioned at a height different from the tooth bottom 77b of the first tooth part 77a and the tooth bottom 78b of the second tooth part 78a in the radial direction. In this example, the outer peripheral surface 81a is located on the radially inner peripheral side with respect to the tooth bottom 77b of the first tooth portion 77a and the tooth bottom 77b of the second tooth portion 78a. Here, the large-diameter gear 75 is made of resin, the first gear member 77 is made of metal, and the second gear member 78 is made of resin.
　図８（ｂ）に示すように、第２歯車部材７８は、第１歯車部材７７の側の端面の周方向に離間する２か所にＸ方向に突出する第１突起８２ａと第２突起８２ｂとを備える。一方、図８（ａ）に示すように、第１歯車部材７７は、第２歯車部材７８の側の端面に第１突起８２ａを受け入れ可能な第１凹部８３ａと、軸線方向から第２突起８２ｂを受け入れ可能な第２凹部８３ｂとを備える。ここで、第１突起８２ａと第２突起８２ｂとは大きさが相違しており、第２突起８２ｂは第１突起８２ａよりも大きい。また、第２突起８２ｂは第１凹部８３ａに挿入不能な大きさである。第１突起８２ａを第１凹部８３ａに挿入した場合には、第１突起８２ａは第１凹部８３ａに周方向で隙間なく嵌合する。これにより、第１歯車部材７７と第２歯車部材７８とを連結したときに、第１歯部７７ａの位相と第２歯部７８ｂの位相とを予め定めた関係に設定できる。 As shown in FIG. 8B, the second gear member 78 includes a first protrusion 82a and a second protrusion 82b that protrude in the X direction at two locations that are spaced apart from each other in the circumferential direction of the end surface on the first gear member 77 side. With. On the other hand, as shown in FIG. 8A, the first gear member 77 includes a first recess 83a capable of receiving the first protrusion 82a on the end surface on the second gear member 78 side, and a second protrusion 82b from the axial direction. 2nd recessed part 83b which can receive this. Here, the first protrusion 82a and the second protrusion 82b have different sizes, and the second protrusion 82b is larger than the first protrusion 82a. The second protrusion 82b has a size that cannot be inserted into the first recess 83a. When the first protrusion 82a is inserted into the first recess 83a, the first protrusion 82a fits in the first recess 83a without any gap in the circumferential direction. Thereby, when the 1st gear member 77 and the 2nd gear member 78 are connected, the phase of the 1st tooth part 77a and the phase of the 2nd tooth part 78b can be set to the predetermined relationship.
（出力歯車および出力軸）
　図９および図１０は出力歯車２８、出力軸１１、および、第５複合歯車２７を第１方向Ｘ１から見た場合の斜視図である。図９（ａ）は開閉部材２が開位置２Ｂに配置された場合の出力歯車２８および出力軸１１の状態を示し、図９（ｂ）は開閉部材２が閉位置２Ａに配置された場合の出力歯車２８および出力軸１１の状態を示す。図１０は、開閉部材駆動装置１によって開閉部材２が開位置２Ｂと閉位置２Ａの途中まで移動したときに、開閉部材２が人により操作されて閉位置２Ａに配置された場合の出力歯車２８および出力軸１１の状態を示す。 (Output gear and output shaft)
9 and 10 are perspective views of the output gear 28, the output shaft 11, and the fifth compound gear 27 as viewed from the first direction X1. 9A shows a state of the output gear 28 and the output shaft 11 when the opening / closing member 2 is arranged at the open position 2B, and FIG. 9B shows a case where the opening / closing member 2 is arranged at the closed position 2A. The states of the output gear 28 and the output shaft 11 are shown. FIG. 10 shows an output gear 28 when the opening / closing member 2 is operated by a person and placed in the closed position 2A when the opening / closing member 2 is moved halfway between the open position 2B and the closed position 2A by the opening / closing member driving device 1. And the state of the output shaft 11 is shown.
　図２、図３および図９に示すように、出力歯車２８は扇形歯車である。出力歯車２８は開閉部材２が回動する角度範囲に対応する角度範囲の歯部２８ａを備える。出力歯車２８は、自動閉装置４が開閉部材２を閉位置２Ａに向って駆動する際に第１回転方向Ｓ１（図９におけるＣＷ方向）に回転する。なお、出力歯車２８の第１回転方向Ｓ１（ＣＷ方向）は、当該出力歯車２８と噛合する第５複合歯車２７の第１回転方向Ｒ１（ＣＣＷ方向）とは反対方向である。 As shown in FIGS. 2, 3 and 9, the output gear 28 is a sector gear. The output gear 28 includes a tooth portion 28a having an angular range corresponding to an angular range in which the opening / closing member 2 rotates. The output gear 28 rotates in the first rotation direction S1 (CW direction in FIG. 9) when the automatic closing device 4 drives the opening / closing member 2 toward the closed position 2A. The first rotation direction S1 (CW direction) of the output gear 28 is opposite to the first rotation direction R1 (CCW direction) of the fifth compound gear 27 that meshes with the output gear 28.
　図９に示すように、出力歯車２８は、第１方向Ｘ１の端面２８ｂに、第１回転方向Ｓ１の前端面２８ｃから第１回転方向Ｓ１とは反対の第２回転方向Ｓ２に向って切り欠かれた切り欠き凹部８８を備える。切り欠き凹部８８において第１回転方向Ｓ１とは反対の第２回転方向Ｓ２の端を規定している内壁面は、腕部３８に当接可能な当接部８８ａである。出力歯車２８は、開閉部材２が開位置２Ｂと閉位置２Ａとの間を移動する間に、図９（ａ）に示す出力歯車開位置２８Ｂと、図９（ｂ）に示す出力歯車閉位置２８Ａの間を回転する。 As shown in FIG. 9, the output gear 28 is notched in the end surface 28b in the first direction X1 from the front end surface 28c in the first rotation direction S1 toward the second rotation direction S2 opposite to the first rotation direction S1. A cut-out recess 88 is provided. The inner wall surface that defines the end of the notch recess 88 in the second rotation direction S2 opposite to the first rotation direction S1 is a contact portion 88a that can contact the arm portion 38. The output gear 28 moves between the output gear open position 28B shown in FIG. 9 (a) and the output gear closed position shown in FIG. 9 (b) while the opening / closing member 2 moves between the open position 2B and the closed position 2A. Rotate between 28A.
　出力軸１１は、軸線Ｌ０に沿ってＸ方向に延びる出力軸本体部３７と、軸線Ｌ０と直交する径方向に延びる腕部３８を備える。腕部３８をＸ方向から見た場合の形状は、出力軸本体部３７から離れるのに伴って先細りとなっている。図９に示すように、腕部３８は第１回転方向Ｓ１の前方から切り欠き凹部８８に収容可能である。腕部３８における第１回転方向Ｓ１の後側面は出力歯車２８に設けられた当接部８８ａが第１回転方向Ｓ１の後方から当接する被当接部３８ａである。 The output shaft 11 includes an output shaft main body portion 37 extending in the X direction along the axis L0 and an arm portion 38 extending in the radial direction orthogonal to the axis L0. The shape when the arm portion 38 is viewed from the X direction is tapered as the arm portion 38 is separated from the output shaft main body portion 37. As shown in FIG. 9, the arm part 38 can be accommodated in the notch recess 88 from the front in the first rotational direction S1. The rear side surface of the arm portion 38 in the first rotation direction S1 is a contacted portion 38a with which a contact portion 88a provided on the output gear 28 contacts from the rear of the first rotation direction S1.
　自動閉装置４が開閉部材２を閉方向Ｃに移動させる際には、図９（ａ）に示すように、モータ１５の正方向への駆動により第５複合歯車２７が第１回転方向Ｒ１に回転する。出力歯車２８が第１回転方向Ｓ１に回転すると、出力歯車２８の当接部８８ａ（切り欠き凹部８８の内壁面）が第１回転方向Ｓ１の後方から出力軸１１の腕部３８に当接して、出力軸１１を出力歯車２８に供回りさせる。これにより、開閉部材２が閉位置２Ａに到達すると、図９（ｂ）に示す状態となる。 When the automatic closing device 4 moves the opening / closing member 2 in the closing direction C, as shown in FIG. 9A, the fifth compound gear 27 is moved in the first rotation direction R1 by driving the motor 15 in the positive direction. Rotate. When the output gear 28 rotates in the first rotation direction S1, the contact portion 88a of the output gear 28 (the inner wall surface of the notch recess 88) contacts the arm portion 38 of the output shaft 11 from the rear in the first rotation direction S1. The output shaft 11 is rotated around the output gear 28. Thus, when the opening / closing member 2 reaches the closed position 2A, the state shown in FIG.
（制御系）
　次に、開閉部材駆動装置１の制御系は、図１（ａ）に示すように、ＣＰＵなどを備える制御部７を備える。制御部７の入力側には、自動閉装置４に閉動作を開始させるスイッチ５と、開閉部材２が箱体３と当接する閉位置２Ａに配置されたことを検出する検出器６が接続されている。また、制御部７の入力側にはポテンショメータ１７の検出部１９が接続されている。制御部７の出力側にはモータ１５が接続されている。 (Control system)
Next, as shown in FIG. 1A, the control system of the opening / closing member driving device 1 includes a control unit 7 including a CPU and the like. Connected to the input side of the control unit 7 are a switch 5 for causing the automatic closing device 4 to start a closing operation, and a detector 6 for detecting that the opening / closing member 2 is disposed at the closed position 2A where it abuts against the box 3. ing. A detection unit 19 of the potentiometer 17 is connected to the input side of the control unit 7. A motor 15 is connected to the output side of the control unit 7.
（開閉部材の閉動作）
　制御部７は、スイッチ５が操作されると、モータ１５を正方向に駆動して開閉部材２を閉位置２Ａに向って駆動する。また、制御部７は、ポテンショメータ１７の検出部１９からの出力に基づいて開閉部材２の位置を監視して、モータ１５の回転を制御する。さらに、制御部７は、モータ１５を駆動した後に、検出器６によって開閉部材２が閉位置２Ａに達したことが検出されると、モータ１５を停止させる。その後、制御部７は、モータ１５を逆方向に駆動して出力歯車２８を出力歯車開位置２８Ｂに戻す。 (Opening / closing member closing operation)
When the switch 5 is operated, the control unit 7 drives the motor 15 in the forward direction to drive the opening / closing member 2 toward the closed position 2A. Further, the control unit 7 controls the rotation of the motor 15 by monitoring the position of the opening / closing member 2 based on the output from the detection unit 19 of the potentiometer 17. Furthermore, after driving the motor 15, the control unit 7 stops the motor 15 when the detector 6 detects that the opening / closing member 2 has reached the closed position 2 </ b> A. Thereafter, the controller 7 drives the motor 15 in the reverse direction to return the output gear 28 to the output gear open position 28B.
　自動閉装置４が開閉部材２を閉方向Ｃに移動させる際には、図９（ａ）に示すように、モータ１５の正方向への駆動により第５複合歯車２７が第１回転方向Ｒ１に回転する。これにより、出力軸１１が出力歯車２８に供回する。そして、開閉部材２が閉位置２Ａに到達すると、図９（ｂ）に示す状態となる。 When the automatic closing device 4 moves the opening / closing member 2 in the closing direction C, as shown in FIG. 9A, the fifth compound gear 27 is moved in the first rotation direction R1 by driving the motor 15 in the positive direction. Rotate. Thereby, the output shaft 11 is supplied to the output gear 28. When the opening / closing member 2 reaches the closed position 2A, the state shown in FIG.
　ここで、出力軸１１は出力歯車２８に噛合して回転するのではなく、出力歯車２８の当接部８８ａが出力軸１１の腕部３８に当接することにより、出力歯車２８と共に第１回転方向Ｓ１に回転する。従って、モータ１５の駆動により出力歯車２８が第１回転方向Ｓ１に回転して出力軸１１が出力歯車２８と供回りしているときに（開閉部材２が閉方向Ｃに駆動されているときに）、開閉部材２が人力によって操作されて閉方向Ｃに移動した場合には、図１０に示すように、開閉部材２に連結された出力軸１１と、出力軸１１と一体に回転する腕部３８のみが第１回転方向Ｓ１に回転して、腕部３８の被当接部３８ａが出力歯車２８の当接部８８ａから第１回転方向Ｓ１の前方に離間する。従って、人が開閉部材２を閉方向Ｃに移動させたときに、歯車機構１６において出力軸１１よりも駆動力伝達方向の上流側に位置する歯車機構１６やモータ１５が負荷として作用することがない。よって、開閉部材２を弱い力で閉方向Ｃに移動させることができる。 Here, the output shaft 11 does not rotate while meshing with the output gear 28, but the contact portion 88 a of the output gear 28 contacts the arm portion 38 of the output shaft 11, so that the first rotation direction together with the output gear 28 is achieved. Rotate to S1. Therefore, when the output gear 28 is rotated in the first rotation direction S1 by driving the motor 15 and the output shaft 11 is rotating with the output gear 28 (when the opening and closing member 2 is driven in the closing direction C). ) When the opening / closing member 2 is operated by human power and moves in the closing direction C, as shown in FIG. 10, the output shaft 11 connected to the opening / closing member 2 and the arm portion that rotates integrally with the output shaft 11 Only 38 rotates in the first rotation direction S1, and the contacted portion 38a of the arm portion 38 is separated from the contact portion 88a of the output gear 28 in the first rotation direction S1. Therefore, when a person moves the opening / closing member 2 in the closing direction C, the gear mechanism 16 or the motor 15 located upstream of the output shaft 11 in the driving force transmission direction in the gear mechanism 16 may act as a load. Absent. Therefore, the opening / closing member 2 can be moved in the closing direction C with a weak force.
　また、本例では、開閉部材２が閉位置２Ａに配置されたことが検出されると、制御部７はモータ１５を逆方向に駆動して出力歯車２８を出力歯車開位置２７Ｂに戻す。従って、閉位置２Ａに配置された開閉部材２が人によって開方向に移動させられる場合などに、開閉部材２に連結された出力軸１１の回転が出力歯車２８に伝達されることを回避できる。よって、閉位置２Ａに配置された開閉部材２を、人による弱い力で開方向に移動させることができる。 In this example, when it is detected that the opening / closing member 2 is disposed at the closed position 2A, the control unit 7 drives the motor 15 in the reverse direction to return the output gear 28 to the output gear open position 27B. Therefore, it is possible to avoid the rotation of the output shaft 11 connected to the opening / closing member 2 being transmitted to the output gear 28 when the opening / closing member 2 disposed at the closed position 2A is moved in the opening direction by a person. Therefore, the opening / closing member 2 arranged at the closed position 2A can be moved in the opening direction by a weak force by a person.
　さらに、本例では、歯車機構１６がトルクリミッタ（第２複合歯車２４）を備える。従って、モータ１５の駆動により出力歯車２８が第１回転方向Ｓ１に回転して出力軸１１が出力歯車２８と供回りしているときに開閉部材２が駆動方向とは反対方向に操作された場合などに、開閉部材２の側から出力軸１１を介して歯車機構１６に入力される過度な負荷は、トルクリミッタ２４（第２複合歯車２４）により減衰される。すなわち、トルクリミッタ２４に出力歯車２８の側から過度な負荷が入力されると、小径歯車４２と大径歯車４１との相対回転が許容され、小径歯車４２に伝達された過度な負荷が、大径歯車４１に伝達されることを防止できる。よって、外部からの過度の負荷により歯車機構１６を構成する歯車やモータ１５などを破損させることがない。 Furthermore, in this example, the gear mechanism 16 includes a torque limiter (second compound gear 24). Therefore, when the output gear 28 is rotated in the first rotation direction S1 by driving the motor 15 and the output shaft 11 is rotating with the output gear 28, the opening / closing member 2 is operated in the direction opposite to the drive direction. For example, an excessive load input from the opening / closing member 2 side to the gear mechanism 16 via the output shaft 11 is attenuated by the torque limiter 24 (second compound gear 24). That is, when an excessive load is input to the torque limiter 24 from the output gear 28 side, relative rotation between the small diameter gear 42 and the large diameter gear 41 is permitted, and the excessive load transmitted to the small diameter gear 42 is large. Transmission to the radial gear 41 can be prevented. Therefore, the gear, the motor 15 and the like constituting the gear mechanism 16 are not damaged by an excessive load from the outside.
　また、本例では、第５複合歯車２７は、出力歯車２８と噛合する第１歯部７７ａと、ポテンショ歯車１８が噛合する第２歯部７８ａとをＸ方向（第５複合歯車２７の軸線Ｌ２方向）で離間する位置に備える。さらに、第１歯部７７ａと第２歯部７８ａとの間には歯欠損部８１が設けられている。従って、出力歯車２８および第１歯部７７に塗布されたグリスが、第２歯部７８ａに付着することが抑制される。これにより、グリスが、第２歯部７８ａからポテンショ歯車１８を伝わって、検出部１９に達することを防止できるので、ポテンショメータ１７に誤動作が発生することを防止できる。 Further, in this example, the fifth compound gear 27 has a first tooth portion 77a meshing with the output gear 28 and a second tooth portion 78a meshing with the potentiometer gear 18 in the X direction (the axis L2 of the fifth compound gear 27). In the direction). Further, a tooth loss part 81 is provided between the first tooth part 77a and the second tooth part 78a. Therefore, the grease applied to the output gear 28 and the first tooth portion 77 is suppressed from adhering to the second tooth portion 78a. As a result, grease can be prevented from reaching the detection unit 19 by being transmitted from the second tooth portion 78a to the potentiometer gear wheel 18, so that the potentiometer 17 can be prevented from malfunctioning.
　また、歯欠損部８１は、第１歯部７７ａの歯底７７ｂおよび第２歯部７８ａの歯底７８ｂよりも径方向で内周側に位置する外周面８１ａを備える。これにより、第１歯部７７ａの歯底７７ｂと第２歯部７８ａの歯底７８ｂの間に段差が設けられるので、第１歯部７７ａに塗布されたグリスが第２歯部７８ａの側に伝わることを、より、抑制できる。この結果、グリスが、第２歯部７８ａからポテンショ歯車１８を伝わって、検出部１９に達することを防止できるので、ポテンショメータ１７に誤動作が発生することを防止できる。従って、検出部１９からの出力により開閉部材２の回転角度位置を精度よく把握できる。 Further, the tooth defect portion 81 includes an outer peripheral surface 81a positioned on the inner peripheral side in the radial direction from the tooth bottom 77b of the first tooth portion 77a and the tooth bottom 78b of the second tooth portion 78a. Accordingly, a step is provided between the tooth bottom 77b of the first tooth portion 77a and the tooth bottom 78b of the second tooth portion 78a, so that the grease applied to the first tooth portion 77a is on the second tooth portion 78a side. It is possible to suppress the transmission more. As a result, the grease can be prevented from reaching the detection unit 19 by being transmitted from the second tooth portion 78a to the potentiometer gear 18, so that the potentiometer 17 can be prevented from malfunctioning. Therefore, the rotational angle position of the opening / closing member 2 can be accurately grasped by the output from the detection unit 19.
　さらに、本例では、歯欠損部８１の外周面８１ａが第１歯部７７ａの歯底７７ｂおよび第２歯部７８ａの歯底７８ｂよりも径方向で内周側に位置するので、第１歯部７７ａに噛合させた出力歯車２８が歯欠損部８１と干渉することがない。また、第５複合歯車２７において、出力歯車２８に噛合する第１歯部７７ａを備える第１歯車部材７７は金属製であり、ポテンショ歯車１８と噛合する第２歯部７８ａを備える第２歯車部材７８は樹脂製である。従って、第１歯部７７ａについて、駆動力を伝達するための強度を向上させることができる。また、第１歯部７７ａの強度を向上させたときに、第５複合歯車２７の全体を金属製とした場合と比較して、第５複合歯車２７の製造コストを抑制できる。 Furthermore, in this example, since the outer peripheral surface 81a of the tooth missing part 81 is located on the inner peripheral side in the radial direction with respect to the tooth bottom 77b of the first tooth part 77a and the tooth bottom 78b of the second tooth part 78a, the first tooth The output gear 28 meshed with the portion 77a does not interfere with the tooth missing portion 81. Further, in the fifth compound gear 27, the first gear member 77 having the first tooth portion 77a meshing with the output gear 28 is made of metal, and the second gear member having the second tooth portion 78a meshing with the potentiometer gear 18. 78 is made of resin. Therefore, the strength for transmitting the driving force can be improved for the first tooth portion 77a. Further, when the strength of the first tooth portion 77a is improved, the manufacturing cost of the fifth composite gear 27 can be suppressed as compared with the case where the entire fifth composite gear 27 is made of metal.
（変形例）
　図１１は変形例の第５複合歯車およびポテンショメータ１７の斜視図である。変形例の第５複合歯車２７Ａは、小径歯車７６において、歯欠損部８１の外周面８１ａが、第１歯部７７ａの歯底７７ｂおよび第２歯部７８ａの歯底７７ｂよりも径方向の外側に位置する。他の構成は第５複合歯車２７と同一である。このようにすれば、第１歯部７７ａの側から第２歯部７８ａの側に流れようとするグリスを、歯欠損部８１によって堰き止めることができる。 (Modification)
FIG. 11 is a perspective view of a modified fifth compound gear and potentiometer 17. In the fifth compound gear 27A of the modified example, in the small-diameter gear 76, the outer peripheral surface 81a of the tooth missing portion 81 is radially outer than the tooth bottom 77b of the first tooth portion 77a and the tooth bottom 77b of the second tooth portion 78a. Located in. Other configurations are the same as those of the fifth compound gear 27. In this way, the grease that tends to flow from the first tooth portion 77a side to the second tooth portion 78a side can be blocked by the tooth loss portion 81.
　また、小径歯車７６において、第１歯部７７ａと第２歯部７８ａとの歯数などを異なるものとしてもよい。すなわち、本例では、小径歯車７６は、同軸に連結された第１歯車部材７７と第２歯車部材７８の２つの部材から構成されているので、第１歯部７７ａと第２歯部７８ａとの歯数などを異なるものとすることが容易である。これにより、駆動力伝達歯車７６の回転数と第２歯部７８ａに噛合するポテンショ歯車１８の回転数の比率を所望のものとすることができるので、回転角度位置の検出精度を変更することが容易となる。 In the small-diameter gear 76, the number of teeth of the first tooth portion 77a and the second tooth portion 78a may be different. In other words, in this example, the small-diameter gear 76 is composed of two members, a first gear member 77 and a second gear member 78, which are coaxially connected, so that the first tooth portion 77a and the second tooth portion 78a It is easy to make the number of teeth different. As a result, the ratio of the rotational speed of the driving force transmission gear 76 and the rotational speed of the potentiometer gear 18 meshing with the second tooth portion 78a can be set to a desired value, so that the detection accuracy of the rotational angle position can be changed. It becomes easy.
　また、上記の例では、第２歯車部材７８に歯欠損部８１を備えるが、第１歯車部材７７に歯欠損部８１を備えてもよい。 In the above example, the second gear member 78 includes the tooth missing portion 81, but the first gear member 77 may include the tooth missing portion 81.
　なお、上記の例では、歯車の摩耗を防止するための潤滑剤としてグリスが用いられているが、潤滑剤としてオイルやコーティング剤を用いることができる。すなわち、各歯車（ピニオン２２、第１複合歯車２３、第２複合歯車２４と、第３複合歯車２５、第４複合歯車２６、第５複合歯車２７および出力歯車２８）において、他の歯車が噛合する歯部には、ポテンショ歯車１８と噛合する第２歯部２７ｄを除き、オイルやコーティング剤が塗布されていてもよい。この場合でも、これらの潤滑剤が、第２歯部７８ａからポテンショ歯車１８を伝わって、検出部１９に達することを防止できるので、ポテンショメータ１７に誤動作が発生することを防止できる。 In the above example, grease is used as a lubricant for preventing gear wear, but oil or a coating agent may be used as the lubricant. That is, in each gear (the pinion 22, the first compound gear 23, the second compound gear 24, the third compound gear 25, the fourth compound gear 26, the fifth compound gear 27, and the output gear 28), other gears mesh with each other. Oil or a coating agent may be applied to the tooth portion to be removed, except for the second tooth portion 27d that meshes with the potentiometer gear 18. Even in this case, since these lubricants can be prevented from reaching the detection unit 19 by being transmitted from the second tooth portion 78a to the potentiometer gear 18, it is possible to prevent the potentiometer 17 from malfunctioning.
（その他の実施の形態）
　上記の例は、本発明を自動閉装置４に適用したものであるが、開閉部材２を開位置２Ｂに配置する自動開装置に適用することもできる。また、上記の例では、開閉部材駆動装置１（自動閉装置４）は開閉部材２を上下方向に回動させているが、開閉部材２を水平方向に回動させてもよい。 (Other embodiments)
In the above example, the present invention is applied to the automatic closing device 4. However, the present invention can also be applied to an automatic opening device in which the opening / closing member 2 is arranged at the open position 2B. In the above example, the opening / closing member driving device 1 (automatic closing device 4) rotates the opening / closing member 2 in the vertical direction, but the opening / closing member 2 may be rotated in the horizontal direction.
１・・・開閉部材駆動装置、２・・・開閉部材、１１・・・出力軸、１５・・・モータ、１６・・・歯車機構（駆動力伝達機構）、１７・・・ポテンショメータ（回転角度位置検出器）、１８・・・ポテンショ歯車（転角度位置検出用歯車）、１９・・・検出部、７６・・・第５複合歯車の小径歯車（駆動力伝達歯車）、７７・・・第１歯車部材、７７ａ・・・第１歯部、７８・・・第２歯車部材、７８ａ・・・第２歯部、８１・・・歯欠損部、８２ａ・・・第１突起、８２ｂ・・・第２突起、８３ａ・・・第１凹部、８３ｂ・・・第２凹部、Ｌ２・・・第５複合歯車の軸線（軸線）、Ｘ・・・軸線方向 DESCRIPTION OF SYMBOLS 1 ... Opening / closing member drive device, 2 ... Opening / closing member, 11 ... Output shaft, 15 ... Motor, 16 ... Gear mechanism (driving force transmission mechanism), 17 ... Potentiometer (rotation angle) Position detector), 18 ... potentiation gear (rolling angle position detection gear), 19 ... detection unit, 76 ... small gear (driving force transmission gear) of fifth composite gear, 77 ... first. 1 gear member, 77a ... 1st tooth part, 78 ... 2nd gear member, 78a ... 2nd tooth part, 81 ... tooth missing part, 82a ... 1st protrusion, 82b ... -2nd protrusion, 83a ... 1st recessed part, 83b ... 2nd recessed part, L2 ... Axis line (axis line) of 5th compound gear, X ... Axial direction

Claims (9)

  1. 　回転角度位置検出用歯車および当該回転角度位置検出用歯車の回転角度位置を検出する検出部を備える回転角度位置検出器と、
    　駆動力を伝達するための第１歯部、軸線方向で前記第１歯部と離間する第２歯部、および前記第１歯部と前記第２歯部との間に設けられた歯欠損部を備える駆動力伝達歯車と、
    　潤滑剤と、を有し、
    　前記潤滑剤は、前記第１歯部に塗布され、
    　前記回転角度位置検出用歯車は、前記第２歯部に噛合していることを特徴とする駆動力伝達機構。     A rotation angle position detector comprising a rotation angle position detection gear and a detection unit for detecting the rotation angle position of the rotation angle position detection gear;
    A first tooth portion for transmitting a driving force, a second tooth portion spaced apart from the first tooth portion in the axial direction, and a tooth missing portion provided between the first tooth portion and the second tooth portion A driving force transmission gear comprising:
    A lubricant, and
    The lubricant is applied to the first tooth;
    The driving force transmission mechanism, wherein the rotational angle position detecting gear meshes with the second tooth portion.
  2. 　請求項１において、
    　前記歯欠損部は、径方向で前記第１歯部の歯底および前記第２歯部の歯底とは異なる高さにある外周面を備えることを特徴とする駆動力伝達機構。     In claim 1,
    The driving force transmission mechanism according to claim 1, wherein the tooth loss part includes an outer peripheral surface at a height different from a tooth bottom of the first tooth part and a tooth bottom of the second tooth part in a radial direction.
  3. 　請求項２において、
    　前記外周面は、前記第１歯部の歯底および前記第２歯部の歯底よりも径方向の内側に位置することを特徴とする駆動力伝達機構。     In claim 2,
    The driving force transmission mechanism according to claim 1, wherein the outer peripheral surface is located radially inward from the bottom of the first tooth portion and the bottom of the second tooth portion.
  4. 　請求項２において、
    　前記外周面は、前記第１歯部の歯底および前記第２歯部の歯底よりも径方向の外側に位置することを特徴とする駆動力伝達機構。     In claim 2,
    The driving force transmission mechanism, wherein the outer peripheral surface is located radially outside the tooth bottom of the first tooth portion and the tooth bottom of the second tooth portion.
  5. 　請求項１から４のうちのいずれか一項において、
    　前記駆動力伝達歯車は、同軸に連結された第１歯車部材と第２歯車部材とを有し、
    　前記第１歯車部材は、前記第１歯部を備え、
    　前記第２歯車部材は、前記第２歯部および前記歯欠損部を備えることを特徴とする駆動力伝達機構。     In any one of claims 1 to 4,
    The driving force transmission gear has a first gear member and a second gear member connected coaxially,
    The first gear member includes the first tooth portion,
    The driving force transmission mechanism, wherein the second gear member includes the second tooth portion and the tooth missing portion.
  6. 　請求項５において、
    　前記第１歯車部材は、金属製であり、
    　前記第２歯車部材は、樹脂製であることを特徴とする駆動力伝達機構。     In claim 5,
    The first gear member is made of metal,
    The driving force transmission mechanism, wherein the second gear member is made of resin.
  7. 　請求項５または６において、
    　前記第１歯車部材と前記第２歯車部材とは、前記軸線方向に配列されており、
    　前記第２歯車部材は、前記第１歯車部材の側の端面の周方向に離間する２か所に前記軸線方向に突出する第１突起と第２突起とを備え、
    　前記第１歯車部材は、前記第２歯車部材の側の端面に前記第１突起を受け入れ可能な第１凹部と、前記軸線方向から前記第２突起を受け入れ可能な第２凹部と、を備え、
    　前記第１突起と前記第２突起とは、大きさが相違し、
    　前記第１突起を前記第１凹部に挿入したときに、前記第１突起は前記第１凹部に周方向で隙間なく嵌合することを特徴とする駆動力伝達機構。     In claim 5 or 6,
    The first gear member and the second gear member are arranged in the axial direction,
    The second gear member includes a first protrusion and a second protrusion protruding in the axial direction at two locations spaced apart in the circumferential direction of the end surface on the first gear member side,
    The first gear member includes a first recess capable of receiving the first protrusion on an end surface of the second gear member, and a second recess capable of receiving the second protrusion from the axial direction.
    The first protrusion and the second protrusion are different in size,
    The driving force transmission mechanism according to claim 1, wherein when the first protrusion is inserted into the first recess, the first protrusion is fitted in the first recess with no gap in the circumferential direction.
  8. 　請求項１から７のうちいずれか一項において、
    　前記回転角度位置検出器は、前記回転角度位置検出用歯車としてポテンショ歯車を備えるポテンショメータであることを特徴とする駆動力伝達機構。     In any one of Claims 1-7,
    The rotational angle position detector is a potentiometer provided with a potentiometer gear as the rotational angle position detection gear.
  9. 　請求項１から８のうちのいずれか一項に記載の駆動力伝達機構と、
    　モータと、
    　前記モータの駆動力を開閉部材が連結される出力軸に伝達する歯車機構と、を有し、
    　前記歯車機構を構成する複数の歯車のうちの一つの歯車が前記駆動力伝達歯車であることを特徴とする開閉部材駆動装置。     The driving force transmission mechanism according to any one of claims 1 to 8,
    A motor,
    A gear mechanism that transmits the driving force of the motor to an output shaft to which an opening / closing member is coupled,
    One of the plurality of gears constituting the gear mechanism is the driving force transmission gear, and the opening / closing member driving device.
PCT/JP2017/024603 2016-07-14 2017-07-05 Drive force transmission mechanism and opening/closing member drive device WO2018012362A1 (en)

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CN111503176A (en) * 2019-01-30 2020-08-07 日本电产科宝株式会社 Clutch mechanism, driving force transmission mechanism, and robot
CN114293873A (en) * 2021-12-28 2022-04-08 宁波奥云德电器有限公司 Electric opening self-locking-free actuator for charging small door of new energy automobile

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JP7034023B2 (en) * 2018-07-11 2022-03-11 日立Astemo株式会社 Disc brake
JP2022064378A (en) 2020-10-14 2022-04-26 三井金属アクト株式会社 Actuation transmission structure, detection device with the structure, and automobile door lock device with the detection device

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JP2012219887A (en) * 2011-04-07 2012-11-12 Jtekt Corp Shaft with gear, and method for manufacturing shaft with gear
JP2014200458A (en) * 2013-04-04 2014-10-27 日本電産サンキョー株式会社 Lid body opening/closing device

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Publication number Priority date Publication date Assignee Title
CN111503176A (en) * 2019-01-30 2020-08-07 日本电产科宝株式会社 Clutch mechanism, driving force transmission mechanism, and robot
CN114293873A (en) * 2021-12-28 2022-04-08 宁波奥云德电器有限公司 Electric opening self-locking-free actuator for charging small door of new energy automobile

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