WO2014046334A1 - Clutch gear and mirror actuator - Google Patents

Clutch gear and mirror actuator Download PDF

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Publication number
WO2014046334A1
WO2014046334A1 PCT/KR2012/008681 KR2012008681W WO2014046334A1 WO 2014046334 A1 WO2014046334 A1 WO 2014046334A1 KR 2012008681 W KR2012008681 W KR 2012008681W WO 2014046334 A1 WO2014046334 A1 WO 2014046334A1
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WO
WIPO (PCT)
Prior art keywords
gear
circumferential surface
outer circumferential
pair
double
Prior art date
Application number
PCT/KR2012/008681
Other languages
French (fr)
Korean (ko)
Inventor
고시연
고정우
최병대
박완영
박응석
채성복
신동민
Original Assignee
(주)오앤케이테크
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
Priority claimed from KR1020120106058A external-priority patent/KR101403034B1/en
Priority claimed from KR2020120009060U external-priority patent/KR200471924Y1/en
Application filed by (주)오앤케이테크 filed Critical (주)오앤케이테크
Publication of WO2014046334A1 publication Critical patent/WO2014046334A1/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60R—VEHICLES, VEHICLE FITTINGS, OR VEHICLE PARTS, NOT OTHERWISE PROVIDED FOR
    • B60R1/00—Optical viewing arrangements; Real-time viewing arrangements for drivers or passengers using optical image capturing systems, e.g. cameras or video systems specially adapted for use in or on vehicles
    • B60R1/02—Rear-view mirror arrangements
    • B60R1/06—Rear-view mirror arrangements mounted on vehicle exterior
    • B60R1/062—Rear-view mirror arrangements mounted on vehicle exterior with remote control for adjusting position
    • B60R1/07—Rear-view mirror arrangements mounted on vehicle exterior with remote control for adjusting position by electrically powered actuators
    • B60R1/072—Rear-view mirror arrangements mounted on vehicle exterior with remote control for adjusting position by electrically powered actuators for adjusting the mirror relative to its housing
    • 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
    • F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
    • F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
    • F16H19/04—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack

Definitions

  • the present invention relates to a mirror actuator used to adjust the tilt angle of a rear view mirror or side view mirror of an automobile and a clutch gear included therein.
  • the vehicle is equipped with a rear view mirror or a side view mirror to secure a rear view when driving.
  • the inclination angle must be adjusted according to the driver's characteristics, and in recent years, an electric method that can conveniently adjust the inclination angle with a button operation is preferred to a manual method of holding and adjusting the mirror by hand.
  • a mirror actuator for driving a rear mirror or a side mirror is required.
  • a mirror actuator has a housing in which a motor and gears are accommodated, a rotating shell pivoting with respect to the housing under the action of the motor and gears, and a mirror support plate fixed thereto. .
  • the pivoting shell In order to adjust the tilt angle of the mirror, the pivoting shell must be able to rotate independently about two orthogonal axes.
  • there is a difficulty in properly disposing the motor and gears due to the space constraints inside the housing.
  • there is a lot of power loss in the path where the power of the motor is transmitted from the motor to the rotating shell via the gears and thus the smooth angle adjustment performance may not be exhibited when a high power motor is not used. Accordingly, power consumption is high because a high output motor must be used.
  • a clutch gear is used to transmit the power of the motor to the rack gear.
  • Conventional clutch gears used in mirror actuators include a first gear member engaged with another gear to receive power from a motor, and the rack gear for transmitting power transmitted through the first gear member to the rack gear. And a second gear member to be engaged, and a spring for elastically pressing the first gear member to the second gear member side.
  • the spring provided in the conventional clutch gear was an annular spring, and was poor in workability and assemblability. As a result, the clutch gear assembly cost was increased and assembly productivity was deteriorated.
  • the present invention provides a mirror actuator in which power transmission elements are arranged to minimize power loss of the motor in adjusting the rotation angle of the rotation shell.
  • the present invention also provides a mirror actuator in which drive elements for pivoting independently about two axes orthogonal to the pivoting shell are arranged compactly in the housing.
  • the present invention provides a clutch gear and a mirror actuator having the same, the assemblability is improved when the processability of the spring itself and the clutch gear is assembled.
  • the present invention also provides a clutch gear having a plate-shaped spring of the letter C shape, and a mirror actuator having the same.
  • the mirror actuator of the present invention is disposed inside the housing, a rotatable shell rotatable about a first and a second pivotal axis orthogonal to each other at the geometric center of the housing, and the rotatable shell. And a first rotating force providing unit for rotating the first rotating shaft, and a second rotating force providing unit for rotating the rotating shell with respect to the second rotating shaft.
  • the first rotating force providing unit and the second rotating force providing unit each include a first double gear, a second double gear, a clutch gear, a rack gear, and a fastening protrusion.
  • the first double gear includes a motor in which a worm gear is formed on the rotation shaft; And a motor shaft engagement gear portion engaged with the worm gear, and a second double gear engagement gear portion coaxially rotating with the motor shaft engagement gear portion.
  • the second double gear includes a first double gear meshing gear portion engaged with the second double gear meshing gear portion, and a worm gear portion coaxially rotating with the first double gear meshing gear portion.
  • the clutch gear includes a worm gear part engaging gear part engaged with the worm gear part of the second double gear and a rack gear engaging gear part coaxially rotating with the worm gear part engaging gear part.
  • the rack gear is engaged with the rack gear engagement gear portion, and an upper end portion protrudes out of the housing.
  • a fastening protrusion is formed on an upper end of the rack gear and fastened to the pivoting cell.
  • the extension line of the fastening projection of the first rotational force providing unit coincides with the second rotational axis, and the extension line of the fastening projection of the second rotational force providing unit coincides with the first rotational shaft.
  • the rotating shaft of the motor and the rotating shaft of the clutch gear are parallel to the plane defined by the first rotating shaft and the second rotating shaft, and the rotating shaft of the first double gear and the rotating shaft of the second double gear are the first shaft. It can be orthogonal to the plane defined by the rotating shaft and the said 2nd rotating shaft.
  • the first rotational force providing unit and the second rotational force providing unit may be arranged to occupy half the internal space of the housing.
  • the motor shaft engagement gear portion of the first double gear and the worm gear portion engagement gear portion of the clutch gear may be a helical gear.
  • the number of gear teeth of the motor shaft engagement gear portion is greater than the number of gear teeth of the second double gear engagement gear portion, and the number of gear teeth of the second double gear engagement gear portion and the gear teeth of the first double gear engagement gear portion.
  • the difference in number may be 0 to 3.
  • the number of gear teeth of the worm gear engaging gear unit may be greater than the number of gear teeth of the rack gear engaging gear unit, and the number of gear teeth of the rack gear engaging gear unit may be smaller than the number of gear teeth of the rack gear.
  • the present invention is provided with a first gear member meshed with its upstream gear along the power transmission direction of the motor on the outer circumferential surface thereof, the first gear member having a central hole formed in the center thereof, and the power transmission direction of the motor.
  • a second gear part engaged with the downstream gear of the outer peripheral surface, the one end being penetrated by the central through hole, the one end of which penetrates the central through hole, and at least one outer peripheral face groove formed on the outer peripheral face of the one end;
  • a leaf spring for elastically pressing the second gear member to be in close contact with each other, wherein an inner edge of the at least one uneven portion is at least And a clutch gear seated on one outer circumferential surface groove and in close contact with one side of the outer circumferential surface groove, wherein portions other than the at least one uneven portion are in close contact with the first gear member.
  • the at least one outer circumferential surface groove is provided with a pair, the pair of outer circumferential surface grooves are formed on the opposite outer circumferential surface symmetrically with respect to the longitudinal axis of the second gear member, and the at least one uneven portion is the pair of outer circumferential surface grooves
  • a pair is provided so as to correspond to, wherein the interval between the pair of uneven parts is greater than or equal to the distance between the pair of outer circumferential surface grooves, the inner edge of the pair of uneven parts is a longitudinal direction of the pair of outer circumferential surface grooves It may be configured to enter the pair of outer peripheral surface grooves in a direction parallel to the plate spring is fitted to the pair of outer peripheral surface grooves.
  • the inner circumferential surface of the central through hole is inclinedly extended, the second gear member has an outer circumferential surface inclined at the same inclination angle as the inclination of the inner circumferential surface to contact the inner circumferential surface, and the load received by the second gear member from the downstream gear
  • the predetermined criterion is exceeded, even if the first gear member rotates, the inner circumferential surface of the central through hole may slide with respect to the outer circumferential surface of the second gear member so that the second gear member does not rotate.
  • the outer diameter of the first gear portion and the second gear portion are different from each other, and may be configured to coaxially rotate.
  • the present invention also includes a housing, a rotating shell rotatable with respect to the housing, and at least one rotating force providing unit for rotating the rotating shell, the rotating shell being provided inside the housing, and providing the rotating force.
  • the unit is a rack gear that is engaged with the motor, the above-described clutch gear, to which the power of the motor is transmitted and rotates, and the second gear portion of the clutch gear, and the upper end portion is engaged with the pivoting shell outside the housing. It provides a mirror actuator having a).
  • the rotational force providing unit may further include a double gear positioned between the motor and the clutch gear along the power transmission direction of the motor and engaged with the first gear part of the clutch gear.
  • the mirror actuator according to the present invention uses a plurality of dual gears in succession to transmit the power of the motor to the rack gears to rotate the rotating shell. Therefore, power loss of the motor can be reduced, and satisfactory angle adjustment performance can be realized even with a low output motor.
  • the rotational axes of the rotational shells in the two directions are orthogonal to each other, and the points at which the two rotational axes intersect are coincident with the geometric center of the housing. Therefore, the rotation angle of the rotation shell can be adjusted precisely.
  • the mirror actuator according to the present invention is easy to assemble and disassemble because the drive elements for rotating the pivoting shell independently about two axes perpendicular to each other are arranged compactly in half the space inside the housing.
  • the clutch gear assembly can be easily completed by fitting the spring to the second gear member through an open side of the letter C-shaped spring, and the letter C-shaped spring can be quickly and easily I can process it. Therefore, the productivity of the clutch gear is improved, and the cost is reduced.
  • FIG 1 and 2 are a perspective view and an exploded perspective view of a mirror actuator according to an embodiment of the present invention.
  • FIG. 3 and 4 are a perspective view and a plan view of the lower housing of FIG. 1 and elements for providing a rotational force disposed therein.
  • FIG. 5 and 6 are perspective views showing the clutch gear of FIG. 1 viewed from different directions.
  • FIG. 7 and 8 are exploded perspective views showing the clutch gear of FIG. 1 viewed from different directions.
  • the mirror actuator 10 according to the embodiment of the present invention has a hemispherical housing 11 and a ring-shaped rotating shell which can be rotated with respect to the housing 11. 20 and a mirror support plate 25 fixedly coupled to the rotation shell 20.
  • the housing 11 has a lower housing 12 in the form of a bowl and an upper housing 17 for closing the upper opening of the lower housing 12.
  • the central portion of the upper housing 17 and the central portion of the mirror support plate 25 are in close contact with the hook 33.
  • the pivot cap 28 and the hook 33 are coupled with the hemispherical spring 30 interposed therebetween.
  • the central portion of the mirror support plate 25 is raised above the central portion of the upper housing 17, and the hook 33 coupled with the pivot cap 28 is lowered toward the upper housing 17 so that the lower end of the hook 33 is the upper housing.
  • the center pipe 37 is fitted into the central through hole of the hook 33 and is lowered along the central axis CL parallel to the Z axis so that the lower end thereof is the central hole 13 of the lower housing 12 (see FIG. 4). It is fixed in the
  • the first rotational force providing unit 40 (see FIG. 4) and the second rotational force providing unit 60 (see FIG. 4) are disposed in the inner space of the housing 11.
  • the first rotational force providing unit 40 provides power for rotating the rotational shell 20 about the first rotational shaft R1 (see FIG. 4) parallel to the X axis, and the second rotational force providing unit 60.
  • the fastening protrusion 59 of the first turning force providing unit 40 and the fastening protrusion 79 of the second turning force providing unit 60 are inserted into and fastened to the fastening holes 22 and 23 of the rotating shell 20, respectively. .
  • a mirror (not shown) is attached and supported to the mirror support plate 25, and the mirror actuator 10 is bolted (not shown) inserted into and fastened from the bottom of the lower housing 12 to the center pipe 37. It is fixedly mounted on a support (not shown).
  • the pivoting shell 20 and the mirror support plate 25 are clockwise or relative to the first rotational axis R1 (see FIG. 4). Rotate counterclockwise.
  • the rotation shell 20 and the mirror support plate 25 are clockwise or relative to the second rotational axis R2 (see FIG. 4). Rotate counterclockwise. Independent rotation of the first and second rotation shafts R1 and R2 is possible, so that the inclination angle of the mirror can be freely adjusted.
  • 3 and 4 are a perspective view and a plan view of the lower housing of FIG. 1 and elements for providing a rotational force disposed therein. 2 to 4,
  • the first rotational force providing unit 40 and the second rotational force providing unit 60 refer to an imaginary dividing line HL extending in a straight line across the central axis CL. It is disposed on one side and the other side, respectively.
  • the dividing line HL is a straight line that is orthogonal to each other and forms an isometric angle with respect to the first and second pivoting shafts R1 and R2 that intersect at the central axis CL.
  • the half turning, the first turning force providing unit 40 and the second turning force providing unit 60 occupy one side and the other side of the inner space of the half housing 12 which is half divided. 3 and 4, the first turning force providing unit 40 and the second turning force providing unit 60 are symmetrically arranged with respect to the dividing line HL.
  • the first rotational force providing unit 40 and the second rotational force providing unit 60 are respectively a motor 41, 61, a first double gear 45, 65, a second double gear 50, 70, a clutch. Clutch gears 100A and 100B, rack gears 58 and 78, and fastening protrusions 59 and 79 are provided.
  • the motors 41 and 61 may be DC motors, and worm gears 43 and 63 are formed on the rotating shaft.
  • the imaginary axes P11 and P21 extending in the same direction as the rotation axes of the motors 41 and 61 are parallel to the imaginary plane defined by the first rotating shaft R1 and the second rotating shaft R2. In other words, it is parallel to the XY plane.
  • the first double gears 45 and 65 are disposed at the center of the lower housing 12 and are disposed to face each other in proximity to the dividing line HL.
  • the first double gears 45 and 65 rotate coaxially with the motor shaft engagement gear portions 46 and 66 engaged with the worm gears 43 and 63 and the motor shaft engagement gear portions 46 and 66.
  • Two double gear engagement gear parts 48 and 68 are provided.
  • the diameters of the motor shaft engagement gear portions 46 and 66 are larger than the diameters of the second double gear engagement gear portions 48 and 68.
  • the imaginary axes V11 and V21 extending in the same direction as the rotation axes of the first double gears 45 and 65 are orthogonal to the imaginary plane defined by the first pivot shaft R1 and the second pivot shaft R2. do.
  • Motor shaft engagement gear portions 46, 66 are disposed below, and second double gear engagement gear portions 48, 68 are disposed above.
  • a helical gear having inclined gear teeth is formed so as to be engaged with the worm gears 43 and 63 so as to receive power accurately without loss.
  • the second double gear (50, 70) and the first double gear engagement portion (51, 71) to be engaged with the second double gear engagement gear portion (48, 68), and the first double gear engagement portion (51, 71) Coaxially rotating worm gears 52 and 72 are provided.
  • the imaginary axes V12 and V22 extending in the same direction as the rotation axes of the second double gears 50 and 70 are orthogonal to the imaginary plane defined by the first pivot shaft R1 and the second pivot shaft R2. do. In other words, it is parallel to the Z axis.
  • the first double gear engagement portions 51, 71 are disposed below, and the worm gear portions 52, 72 are disposed above.
  • Clutch gear (100A, 100B) is the first gear portion (102A, 102B) to be engaged with the worm gear portion (52, 72) of the second double gear (50, 70), the first gear portion (102A, 102B) And second gear portions 120A, 120B which coaxially rotate with each other.
  • the outer diameters of the first gear parts 102A and 102B are larger than the outer diameters of the second gear parts 120A and 120B.
  • Virtual axes P12 and P22 extending in the same direction as the rotational axes of the clutch gears 100A and 100B are parallel to the XY plane.
  • a helical gear having an inclined gear tooth is formed on the outer circumferential surfaces of the first gear portions 102A and 102B so as to be engaged with the worm gear portions 52 and 72 so as to receive power accurately without loss.
  • Spur gears meshing with the rack gears 58 and 78 are formed on the outer circumferential surfaces of the second gear portions 120A and 120B.
  • the rack gears 58 and 78 are fixedly supported on the inclined inner wall of the lower housing 12 to extend inclinedly and are engaged with the rack gear engaging gear portions 57 and 77.
  • the upper ends of the rack gears 58 and 78 penetrate the upper housing 17 (see FIG. 2) and protrude out of the housing 11.
  • the fastening protrusions 59.79 are integrally formed with the rack gears 58 and 78 at the upper ends of the rack gears 58 and 78, and the fastening holes 22 of the rotating shell 20 (see FIG. 2) as described above. , 23) is fastened.
  • the imaginary extension line extending in the protruding direction of the fastening protrusion 59 of the first turning force providing unit 40 coincides with the second turning shaft R2, and the fastening protrusion 79 of the second turning force providing unit 60.
  • the imaginary extension line extending in the protruding direction of Ny coincides with the first rotational axis R1. Therefore, the rotating shell 20 (see FIG. 2) and the mirror support plate 25 can be independently rotated by a predetermined angle with respect to the first rotating shaft R1 and the second rotating shaft R2, and the motor ( The power of 41 and 61 is correctly transmitted to the fastening protrusions 59 and 79 so that an operation error does not occur. In addition, damage to the components constituting the first rotational force providing unit 40 and the second rotational force providing unit 60 due to the concentration of the partial load is suppressed.
  • the number of gear teeth is also appropriately selected in order to satisfy the requirements of the rotational force and the rotational speed in the rotation of the mirror support plate 25.
  • the number of teeth of the motor shaft engagement gear portions 46 and 66 of the first double gear 45 and 65 is greater than the number of gear teeth of the second double gear engagement gear portions 48 and 68.
  • the difference between the number of gear teeth of the second double gear engagement gear parts 48 and 68 and the number of gear teeth of the first double gear engagement gear parts 51 and 71 of the second double gear 50 and 70 are 0 to.
  • the number of teeth of the motor shaft engagement gear parts 46 and 66 is 28, the number of gear teeth of the second double gear engagement gear parts 48 and 68 is 16, and the first double gear teeth is meshed.
  • the number of gear teeth of the gear parts 51 and 71 may be 17.
  • the number of gear teeth of the worm gear portion engagement gear portions 55 and 75 of the clutch gears 100A and 100B is greater than the number of gear teeth of the rack gear engagement gear portions 57 and 77, and the rack gear engagement gear The number of gear teeth of the portions 57 and 77 is smaller than the number of gear teeth of the rack gears 58 and 78.
  • the number of gear teeth of the worm gear engaging gears 55 and 75 is 17, the number of gear teeth of the rack gear engaging gears 57 and 77 is 9 and the gears of the rack gears 58 and 78.
  • the number of teeth may be thirteen.
  • the power transmission paths of the motors 41 and 61 are worm gears 43 and 63 ⁇ first double gears 45 and 65 ⁇ second double gears 50 of the motor shaft. , 70) ⁇ clutch gears 100A, 100B ⁇ rack gears 58, 78.
  • the second gear portions 120A, 120B of the clutch gears 100A, 100B meshed with the rack gears 58, 78 can no longer rotate when the rotation shell 20 is rotated to the maximum angle. Therefore, the clutch gears 100A and 100B do not rotate when the electric signals are further input even after the rotational shell 20 rotates to the maximum angle and the motors 41 and 61 rotate.
  • the first gear portions 102A and 102B and the second gear portions 120A and 120B are separated from each other so that only the first gear portions 102A and 102B are rotated.
  • clutch gear 100A, 100B is explained in full detail.
  • FIGS. 7 and 8 are exploded perspective views of the clutch gear of FIG. 1 viewed from different directions.
  • the clutch gears 100A, 100B include a first gear member 101, a second gear member 110, and a leaf spring 130.
  • the first gear member 101 has an outer circumferential surface of the first gear portion 102A, 102B meshed with its upstream gear, that is, the second double gear 50, 70 along the power transmission direction of the motors 41, 61. It is provided in, and the central through-hole 104 is formed in the center.
  • the second gear member 110 is provided on the outer circumferential surface of the second gear portion 120A, 120B meshed with its downstream gear, that is, the rack gears 58, 78 along the power transmission direction of the motors 41, 61. do.
  • the second gear member 110 is fitted into the central through hole 104 of the first gear member 101, and one end thereof passes through the central through hole 104.
  • the second gear member 110 serves as the rotation shaft of the clutch gears 100A and 100B, and the first rotation shaft 115 at the end of the second gear portion 120A and 120B and the second rotation shaft 117 at the opposite end thereof. Each of these is sandwiched and supported by the first rotary shaft holders 145A and 145B (see FIG. 3) and the second rotary shaft holders 148A and 148B (see FIG. 3) formed in the lower housing 12.
  • a pair of outer circumferential grooves 123 is formed on the outer circumferential surface of one end of the second gear member 110 penetrating the central through hole 104.
  • the pair of outer circumferential surface grooves 123 is formed on the opposite outer circumferential surface symmetrically with respect to the longitudinal axes P12 and P22 (see FIG. 3) of the second gear member 110.
  • the outer circumferential surface groove 123 extends along the arc of the second gear member 110 and has a constant width (W).
  • First and second stepped surfaces 124 and 125 are formed at both sides of the width W direction of the outer circumferential surface groove 123, and the depths of the first and second stepped surfaces 124 and 125 are the outer circumferential surface grooves 123.
  • the central part of is deepest and shallower toward the periphery.
  • the leaf spring 130 is formed by pressing a plate-shaped spring steel by pressing.
  • the leaf spring 130 has an alphabet C shape and one side 131 is open.
  • the leaf spring 130 has a pair of distal ends 133 separated from each other due to the open side 131, and a connecting portion 135 connected to the opposite side of the open side 131.
  • between the connecting portion 135 and the pair of distal end portion 133 is provided with a pair of concave-convex portion 137 is bent and raised than the periphery.
  • the raised height H of the uneven portion 137 is smaller than the width W of the outer circumferential surface groove 123.
  • the leaf spring 130 is fitted into the pair of outer circumferential grooves 123 through the open side 131 to elastically press the first gear member 101 and the second gear member 110 to closely contact each other.
  • the inner edges 139 of the pair of uneven parts 137 are seated on the pair of outer circumferential surface grooves 123 to be in close contact with the first step surface 124.
  • the first stepped surface 124 is a stepped surface closer to the second rotation shaft 117 among the pair of stepped surfaces 124 and 125 of the outer circumferential surface groove 123. Portions other than the pair of uneven portions 137, that is, the connecting portion 135 and the pair of end portions 133, are in close contact with the first gear member 101.
  • the gap G2 between the pair of uneven parts 137 of the leaf spring 130 is such that the pair of uneven parts 137 fit into the pair of outer circumferential surface grooves 123. Is greater than or equal to the interval G1).
  • the leaf spring 130 enters a direction orthogonal to the longitudinal direction of the second gear member 110, that is, a direction parallel to the longitudinal direction of the outer circumferential surface groove 123, and is fitted to the pair of outer circumferential surface grooves 123. Accordingly, the inner edge 139 of the pair of uneven parts 137 enters and rests in the pair of outer circumferential surface grooves 123 in a direction parallel to the longitudinal direction of the pair of outer circumferential surface grooves 123.
  • the inner circumferential surface 105 of the central through hole 104 of the first gear member 101 extends inclined so as to decrease the inner diameter toward the direction from the first rotation shaft 115 toward the second rotation shaft 117.
  • the outer circumferential surface 112 of the middle portion of the second gear member 110 fitted to the first gear member 101 extends inclined at the same inclination angle as that of the inner circumferential surface 105 so as to contact the inclined inner circumferential surface 105. Since the leaf spring 130 is fitted into the outer circumferential surface groove 123 and fastened, the inclined inner circumferential surface 105 of the first gear member 101 and the inclined outer circumferential surface 112 of the second gear member 110 are elastically in close contact with each other.
  • the first gear member 101 rotates.
  • the inner circumferential surface 105 of the central through hole 104 slides with respect to the outer circumferential surface 112 of the second gear member 110 such that the second gear member 110 does not rotate.
  • the invention can be used for mirrors of automobiles.

Abstract

Disclosed are a mirror actuator, which is used for adjusting the tilt angle of a rear view mirror or a side view mirror of a vehicle, and a clutch gear included in same. The disclosed mirror actuator comprises: a motor in which a worm gear is formed on a rotary shaft; a motor shaft engagement gear portion which engages the worm gear; a first double gear provided with a second double gear engagement gear portion, which coaxially rotates with the motor shaft engagement gear portion; a first double gear engagement gear portion which engages the second double gear engagement gear portion; a second double gear provided with a worm gear portion, which coaxially rotates with the first double gear engagement gear portion; a worm gear portion engagement gear portion which engages the worm gear portion of the second double gear; the clutch gear comprising a rack gear engagement gear portion which coaxially rotates with the worm gear portion engagement gear portion; a rack gear which engages the rack gear engagement gear portion and the top portion of which protrudes out of a housing of the mirror actuator; and a coupling protrusion which is formed at the upper end of the rack gear and is coupled to a rotating cell.

Description

클러치 기어 및 미러 액추에이터Clutch Gear and Mirror Actuator
본 발명은 자동차의 리어 미러(rear view mirror) 또는 사이드 미러(side view mirror)의 기울임 각을 조정하는 데 사용되는 미러 액추에이터 및 이에 포함되는 클러치 기어에 관한 것이다. BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a mirror actuator used to adjust the tilt angle of a rear view mirror or side view mirror of an automobile and a clutch gear included therein.
자동차에는 운전시 후방 시야 확보를 위한 리어 미러(rear view mirror) 또는 사이드 미러(side view mirror)가 구비된다. 리어 미러나 사이드 미러는 운전자의 특성에 맞춰 기울임 각이 조정되어야 하며, 근래에는 손으로 미러를 잡고 조정하는 매뉴얼 방식보다 버튼(button) 조작으로 편리하게 기울임 각을 조정할 수 있는 전동 방식이 선호되고 있다. 전동 방식에는 리어 미러나 사이드 미러를 구동하는 미러 액추에이터가 요구된다. The vehicle is equipped with a rear view mirror or a side view mirror to secure a rear view when driving. For rear and side mirrors, the inclination angle must be adjusted according to the driver's characteristics, and in recent years, an electric method that can conveniently adjust the inclination angle with a button operation is preferred to a manual method of holding and adjusting the mirror by hand. . In the transmission method, a mirror actuator for driving a rear mirror or a side mirror is required.
일반적으로, 미러 액추에이터는 모터와 기어(gear)들이 수용된 하우징(housing)과, 상기 모터와 기어들의 작용으로 하우징에 대해 회동하는 회동 쉘(shell) 및 이에 고정된 미러 지지 플레이트(plate)를 구비한다. 미러의 기울임 각을 조정하기 위해서는 회동 쉘이 직교하는 2개의 축에 대해 독립적으로 회동할 수 있어야 한다. 그러나, 하우징 내부의 공간적 제약 때문에 모터와 기어들을 적절히 배치하는데 어려움이 있다. 또한, 모터에서 기어들을 거쳐 회동 쉘까지 모터의 동력이 전달되는 경로에서 동력 손실이 많아 고출력의 모터를 사용하지 않는 경우 원활한 각도 조절 성능을 발휘할 수 없다. 이에 따라 고출력의 모터를 사용하여야 하므로 전력 소모가 크다.Generally, a mirror actuator has a housing in which a motor and gears are accommodated, a rotating shell pivoting with respect to the housing under the action of the motor and gears, and a mirror support plate fixed thereto. . In order to adjust the tilt angle of the mirror, the pivoting shell must be able to rotate independently about two orthogonal axes. However, there is a difficulty in properly disposing the motor and gears due to the space constraints inside the housing. In addition, there is a lot of power loss in the path where the power of the motor is transmitted from the motor to the rotating shell via the gears, and thus the smooth angle adjustment performance may not be exhibited when a high power motor is not used. Accordingly, power consumption is high because a high output motor must be used.
한편, 하우징 내부의 기어들 중에서 클러치 기어(clutch gear)는 모터의 동력을 랙 기어(rack gear)에 전달하기 위해 사용된다. 미러 액추에이터에 사용되는 종래의 클러치 기어는, 모터의 동력을 제공받기 위해 다른 기어에 치합되는 제1 기어 부재와, 상기 제1 기어 부재를 통해 전달된 동력을 랙 기어에 전달하기 위해 상기 랙 기어에 치합되는 제2 기어 부재와, 상기 제1 기어 부재를 제2 기어 부재 측으로 탄성 가압하는 스프링(spring)을 구비한다. 그런데, 종래의 클러치 기어에 구비된 스프링은 고리 형상의 스프링으로서 가공성과 조립성이 좋지 않았다. 그래서 클러치 기어 조립 비용이 증대되고 조립 생산성이 열화되었다. Meanwhile, among the gears inside the housing, a clutch gear is used to transmit the power of the motor to the rack gear. Conventional clutch gears used in mirror actuators include a first gear member engaged with another gear to receive power from a motor, and the rack gear for transmitting power transmitted through the first gear member to the rack gear. And a second gear member to be engaged, and a spring for elastically pressing the first gear member to the second gear member side. By the way, the spring provided in the conventional clutch gear was an annular spring, and was poor in workability and assemblability. As a result, the clutch gear assembly cost was increased and assembly productivity was deteriorated.
본 발명은, 회동 쉘의 회동 각도를 조정함에 있어 모터의 동력 손실이 최소화되도록 동력 전달 요소들이 배열된 미러 액추에이터를 제공한다.The present invention provides a mirror actuator in which power transmission elements are arranged to minimize power loss of the motor in adjusting the rotation angle of the rotation shell.
또한 본 발명은, 회동 쉘을 직교하는 2개의 축에 대해 독립적으로 회동시키는 구동 요소들이 하우징 내에 콤팩트(compact)하게 배치된 미러 액추에이터를 제공한다.The present invention also provides a mirror actuator in which drive elements for pivoting independently about two axes orthogonal to the pivoting shell are arranged compactly in the housing.
또한, 본 발명은, 스프링 자체의 가공성과 클러치 기어를 조립할 때 조립성이 향상되는 클러치 기어와, 이를 구비한 미러 액추에이터를 제공한다. In addition, the present invention provides a clutch gear and a mirror actuator having the same, the assemblability is improved when the processability of the spring itself and the clutch gear is assembled.
또한 본 발명은 알파벳 C자 형상의 판형 스프링을 구비한 클러치 기어와, 이를 구비한 미러 액추에이터를 제공한다. The present invention also provides a clutch gear having a plate-shaped spring of the letter C shape, and a mirror actuator having the same.
본 발명의 미러 액추에이터는, 하우징, 상기 하우징의 기하학적 중심에서 서로 직교 교차하는 제1 및 제2 회동축에 대해 회동 가능한 회동 쉘(shell), 및 상기 하우징의 내부에 배치된 것으로, 상기 회동 쉘을 상기 제1 회동축에 대해 회동시키는 제1 회동력 제공 유닛과, 상기 회동 쉘을 상기 제2 회동축에 대해 회동시키는 제2 회동력 제공 유닛을 구비한다. 상기 제1 회동력 제공 유닛 및 제2 회동력 제공 유닛은 각각, 제1 이중기어, 제2 이중기어, 클러치 기어(clutch gear), 랙 기어 및 체결 돌기를 포함한다. 제1 이중기어는 회전축에 웜 기어(worm gear)가 형성된 모터; 상기 웜 기어에 치합되는 모터축 치합 기어부와, 상기 모터축 치합 기어부와 동축(同軸) 회전하는 제2 이중기어 치합 기어부를 구비한다. 제2 이중기어는 상기 제2 이중기어 치합 기어부에 치합되는 제1 이중기어 치합 기어부와, 상기 제1 이중기어 치합 기어부와 동축(同軸) 회전하는 웜(worm) 기어부를 구비한다. 클러치 기어는 상기 제2 이중기어의 웜 기어부에 치합되는 웜 기어부 치합 기어부와, 상기 웜 기어부 치합 기어부와 동축(同軸) 회전하는 랙 기어(rack gear) 치합 기어부를 구비한다. 랙 기어는 상기 랙 기어 치합 기어부에 치합되며, 상단부가 상기 하우징을 벗어나 돌출된다. 체결돌기는 상기 랙 기어의 상단에 형성되고 상기 회동 셀에 체결된다. 상기 제1 회동력 제공 유닛의 체결 돌기의 연장선은 상기 제2 회동축과 일치하고, 상기 제2 회동력 제공 유닛의 체결 돌기의 연장선은 상기 제1 회동축과 일치하도록 구성된다. The mirror actuator of the present invention is disposed inside the housing, a rotatable shell rotatable about a first and a second pivotal axis orthogonal to each other at the geometric center of the housing, and the rotatable shell. And a first rotating force providing unit for rotating the first rotating shaft, and a second rotating force providing unit for rotating the rotating shell with respect to the second rotating shaft. The first rotating force providing unit and the second rotating force providing unit each include a first double gear, a second double gear, a clutch gear, a rack gear, and a fastening protrusion. The first double gear includes a motor in which a worm gear is formed on the rotation shaft; And a motor shaft engagement gear portion engaged with the worm gear, and a second double gear engagement gear portion coaxially rotating with the motor shaft engagement gear portion. The second double gear includes a first double gear meshing gear portion engaged with the second double gear meshing gear portion, and a worm gear portion coaxially rotating with the first double gear meshing gear portion. The clutch gear includes a worm gear part engaging gear part engaged with the worm gear part of the second double gear and a rack gear engaging gear part coaxially rotating with the worm gear part engaging gear part. The rack gear is engaged with the rack gear engagement gear portion, and an upper end portion protrudes out of the housing. A fastening protrusion is formed on an upper end of the rack gear and fastened to the pivoting cell. The extension line of the fastening projection of the first rotational force providing unit coincides with the second rotational axis, and the extension line of the fastening projection of the second rotational force providing unit coincides with the first rotational shaft.
상기 모터의 회전축과 상기 클러치 기어의 회전축은 상기 제1 회동축 및 상기 제2 회동축에 의해 한정되는 평면과 평행하고, 상기 제1 이중기어의 회전축과 상기 제2 이중기어의 회전축은 상기 제1 회동축 및 상기 제2 회동축에 의해 한정되는 평면에 직교할 수 있다. The rotating shaft of the motor and the rotating shaft of the clutch gear are parallel to the plane defined by the first rotating shaft and the second rotating shaft, and the rotating shaft of the first double gear and the rotating shaft of the second double gear are the first shaft. It can be orthogonal to the plane defined by the rotating shaft and the said 2nd rotating shaft.
상기 제1 회동력 제공 유닛과 상기 제2 회동력 제공 유닛이 상기 하우징의 내부 공간을 반분하여 차지하도록 배치될 수 있다. The first rotational force providing unit and the second rotational force providing unit may be arranged to occupy half the internal space of the housing.
상기 제1 이중기어의 모터축 치합 기어부와, 상기 클러치 기어의 웜 기어부 치합 기어부는 헬리컬 기어(helical gear)일 수 있다. The motor shaft engagement gear portion of the first double gear and the worm gear portion engagement gear portion of the clutch gear may be a helical gear.
상기 모터축 치합 기어부의 기어치(gear teeth) 개수가 상기 제2 이중기어 치합 기어부의 기어치 개수보다 많고, 상기 제2 이중기어 치합 기어부의 기어치 개수와 상기 제1 이중기어 치합 기어부의 기어치 개수의 차이는 0 내지 3 일 수 있다. The number of gear teeth of the motor shaft engagement gear portion is greater than the number of gear teeth of the second double gear engagement gear portion, and the number of gear teeth of the second double gear engagement gear portion and the gear teeth of the first double gear engagement gear portion. The difference in number may be 0 to 3.
상기 웜 기어부 치합 기어부의 기어치 개수는 상기 랙 기어 치합 기어부의 기어치 개수보다 많고, 상기 랙 기어 치합 기어부의 기어치 개수는 상기 랙 기어의 기어치 개수보다 적을 수 있다.The number of gear teeth of the worm gear engaging gear unit may be greater than the number of gear teeth of the rack gear engaging gear unit, and the number of gear teeth of the rack gear engaging gear unit may be smaller than the number of gear teeth of the rack gear.
한편, 본 발명은, 모터의 동력 전달 방향을 따라 자신의 상류측 기어에 치합되는 제1 기어부를 외주면에 구비하고, 중앙에 중앙 통공이 형성된 제1 기어 부재, 상기 모터의 동력 전달 방향을 따라 자신의 하류측 기어에 치합되는 제2 기어부를 외주면에 구비하고, 상기 중앙 통공에 끼워져 일 측 단부가 상기 중앙 통공을 관통하며, 상기 일 측 단부의 외주면에 적어도 하나의 외주면 그루브(groove)가 형성된 제2 기어 부재, 및 알파벳 C자 형상으로 일 측이 개방되고, 절곡되어 주변보다 융기된 적어도 하나의 요철부를 구비하며, 상기 개방된 일 측을 통해 상기 적어도 하나의 외주면 그루브에 끼워져 상기 제1 기어 부재와 상기 제2 기어 부재가 서로 밀착되도록 탄성 가압하는 판 스프링을 구비하고, 상기 적어도 하나의 요철부의 내측 엣지(edge)가 상기 적어도 하나의 외주면 그루브에 안착되어 상기 외주면 그루브의 일 측면에 밀착되고, 상기 적어도 하나의 요철부 이외의 부분은 상기 제1 기어 부재에 밀착되도록 구성된 클러치 기어를 제공한다. On the other hand, the present invention is provided with a first gear member meshed with its upstream gear along the power transmission direction of the motor on the outer circumferential surface thereof, the first gear member having a central hole formed in the center thereof, and the power transmission direction of the motor. A second gear part engaged with the downstream gear of the outer peripheral surface, the one end being penetrated by the central through hole, the one end of which penetrates the central through hole, and at least one outer peripheral face groove formed on the outer peripheral face of the one end; And a second gear member and at least one uneven portion bent and raised from the periphery of one side of the letter C shape, and fitted into the at least one outer circumferential groove through the opened one side to form the first gear member. And a leaf spring for elastically pressing the second gear member to be in close contact with each other, wherein an inner edge of the at least one uneven portion is at least And a clutch gear seated on one outer circumferential surface groove and in close contact with one side of the outer circumferential surface groove, wherein portions other than the at least one uneven portion are in close contact with the first gear member.
상기 적어도 하나의 외주면 그루브는 한 쌍이 구비되고, 상기 한 쌍의 외주면 그루브는 상기 제2 기어 부재의 길이 방향 축선에 대해 대칭되게 반대측 외주면에 형성되고, 상기 적어도 하나의 요철부는 상기 한 쌍의 외주면 그루브에 대응되게 한 쌍이 구비되며, 상기 한 쌍의 요철부 사이의 간격이 상기 한 쌍의 외주면 그루브 사이의 간격보다 크거나 같고, 상기 한 쌍의 요철부의 내측 엣지가 상기 한 쌍의 외주면 그루브의 길이 방향과 평행한 방향으로 상기 한 쌍의 외주면 그루브에 진입하여 상기 판 스프링이 상기 한 쌍의 외주면 그루브에 끼워지도록 구성될 수 있다. The at least one outer circumferential surface groove is provided with a pair, the pair of outer circumferential surface grooves are formed on the opposite outer circumferential surface symmetrically with respect to the longitudinal axis of the second gear member, and the at least one uneven portion is the pair of outer circumferential surface grooves A pair is provided so as to correspond to, wherein the interval between the pair of uneven parts is greater than or equal to the distance between the pair of outer circumferential surface grooves, the inner edge of the pair of uneven parts is a longitudinal direction of the pair of outer circumferential surface grooves It may be configured to enter the pair of outer peripheral surface grooves in a direction parallel to the plate spring is fitted to the pair of outer peripheral surface grooves.
상기 중앙 통공의 내주면은 경사지게 연장되고, 상기 제2 기어 부재는 상기 내주면에 접촉되도록 상기 내주면의 경사와 동일한 경사각으로 경사지게 연장된 외주면을 구비하고, 상기 제2 기어 부재가 상기 하류측 기어로부터 받는 하중이 미리 정한 기준을 초과하면 상기 제1 기어 부재가 회전하더라도 상기 중앙 통공의 내주면이 상기 제2 기어 부재의 외주면에 대해 미끄러져 상기 제2 기어 부재는 회전하지 않도록 구성될 수 있다. The inner circumferential surface of the central through hole is inclinedly extended, the second gear member has an outer circumferential surface inclined at the same inclination angle as the inclination of the inner circumferential surface to contact the inner circumferential surface, and the load received by the second gear member from the downstream gear When the predetermined criterion is exceeded, even if the first gear member rotates, the inner circumferential surface of the central through hole may slide with respect to the outer circumferential surface of the second gear member so that the second gear member does not rotate.
상기 제1 기어부와 상기 제2 기어부는 기어부의 외경이 서로 다르고, 동축(同軸) 회전하도록 구성될 수 있다. The outer diameter of the first gear portion and the second gear portion are different from each other, and may be configured to coaxially rotate.
또한 본 발명은, 하우징, 상기 하우징에 대해 회동 가능한 회동 쉘(shell), 및 상기 하우징의 내부에 배치된 것으로, 상기 회동 쉘을 회동시키는 적어도 하나의 회동력 제공 유닛을 구비하고, 상기 회동력 제공 유닛은, 모터, 상기 모터의 동력이 전달되어 회전하는, 상술한 클러치 기어, 및 상기 클러치 기어의 제2 기어부에 치합되고, 상단부가 상기 하우징을 벗어나 상기 회동 쉘에 체결되는 랙 기어(rack gear)를 구비하는 미러 액추에이터를 제공한다. The present invention also includes a housing, a rotating shell rotatable with respect to the housing, and at least one rotating force providing unit for rotating the rotating shell, the rotating shell being provided inside the housing, and providing the rotating force. The unit is a rack gear that is engaged with the motor, the above-described clutch gear, to which the power of the motor is transmitted and rotates, and the second gear portion of the clutch gear, and the upper end portion is engaged with the pivoting shell outside the housing. It provides a mirror actuator having a).
상기 회동력 제공 유닛은, 상기 모터의 동력 전달 방향을 따라 상기 모터와 상기 클러치 기어 사이에 위치하고 상기 클러치 기어의 제1 기어부에 치합되는 이중기어를 더 구비할 수 있다.The rotational force providing unit may further include a double gear positioned between the motor and the clutch gear along the power transmission direction of the motor and engaged with the first gear part of the clutch gear.
본 발명에 따른 미러 액추에이터는 복수의 이중 기어를 연이어 사용하여 모터의 동력을 랙 기어에 전달하여 회동 쉘을 회동시킨다. 따라서, 모터의 동력 손실을 저감할 수 있고 저출력 모터로도 만족스러운 각도 조정 성능을 구현할 수 있다. The mirror actuator according to the present invention uses a plurality of dual gears in succession to transmit the power of the motor to the rack gears to rotate the rotating shell. Therefore, power loss of the motor can be reduced, and satisfactory angle adjustment performance can be realized even with a low output motor.
또한, 회동 쉘의 두 방향의 회동축이 서로 직교하고, 그 2개의 회동축이 교차하는 점이 하우징의 기하학적 중심과 일치하도록 구성된다. 따라서, 회동 쉘의 회동 각도를 정밀하게 조정할 수 있다. Further, the rotational axes of the rotational shells in the two directions are orthogonal to each other, and the points at which the two rotational axes intersect are coincident with the geometric center of the housing. Therefore, the rotation angle of the rotation shell can be adjusted precisely.
또한 본 발명에 따른 미러 액추에이터는, 회동 쉘을 서로 직교하는 2개의 축에 대해 독립적으로 회동시키는 구동 요소들이 하우징 내부의 공간을 반분하여 콤팩트(compact)하게 배치되므로, 조립 및 분해가 용이하다. In addition, the mirror actuator according to the present invention is easy to assemble and disassemble because the drive elements for rotating the pivoting shell independently about two axes perpendicular to each other are arranged compactly in half the space inside the housing.
또한, 알파벳 C자 형상의 판형 스프링의 개방된 일 측을 통해 제2 기어 부재에 그 스프링을 끼움으로써 클러치 기어 조립을 용이하게 끝낼 수 있고, 알파벳 C자 형상의 판 스프링은 프레스 가공 방법만으로 빠르고 쉽게 가공할 수 있다. 따라서, 클러치 기어의 생산성이 향상되고, 비용이 절감된다. In addition, the clutch gear assembly can be easily completed by fitting the spring to the second gear member through an open side of the letter C-shaped spring, and the letter C-shaped spring can be quickly and easily I can process it. Therefore, the productivity of the clutch gear is improved, and the cost is reduced.
도 1 및 도 2는 본 발명의 실시예에 따른 미러 액추에이터의 사시도 및 분해 사시도이다. 1 and 2 are a perspective view and an exploded perspective view of a mirror actuator according to an embodiment of the present invention.
도 3 및 도 4는 도 1의 하부 하우징과 그 내부에 배치된, 회동력을 제공하기 위한 요소들을 도시한 사시도 및 평면도이다.3 and 4 are a perspective view and a plan view of the lower housing of FIG. 1 and elements for providing a rotational force disposed therein.
도 5 및 도 6은 도 1의 클러치 기어를 서로 다른 방향에서 보고 도시한 사시도이다. 5 and 6 are perspective views showing the clutch gear of FIG. 1 viewed from different directions.
도 7 및 도 8은 도 1의 클러치 기어를 서로 다른 방향에서 보고 도시한 분해 사시도이다. 7 and 8 are exploded perspective views showing the clutch gear of FIG. 1 viewed from different directions.
이하, 첨부된 도면을 참조하여 본 발명의 실시예에 따른 클러치 기어 및 미러 액추에이터를 상세하게 설명한다. 본 명세서에서 사용되는 용어(terminology)들은 본 발명의 바람직한 실시예를 적절히 표현하기 위해 사용된 용어들로서, 이는 사용자 또는 운용자의 의도 또는 본 발명이 속하는 분야의 관례 등에 따라 달라질 수 있다. 따라서, 본 용어들에 대한 정의는 본 명세서 전반에 걸친 내용을 토대로 내려져야 할 것이다.Hereinafter, a clutch gear and a mirror actuator according to an embodiment of the present invention will be described in detail with reference to the accompanying drawings. Terminology used herein is a term used to properly express a preferred embodiment of the present invention, which may vary depending on the intention of a user or an operator or customs in the field to which the present invention belongs. Therefore, the definitions of the terms should be made based on the contents throughout the specification.
도 1 및 도 2는 본 발명의 실시예에 따른 미러 액추에이터의 사시도 및 분해 사시도이다. 도 1 및 도 2를 참조하면, 본 발명의 실시예에 따른 미러 액추에이터(10)는 반구형의 하우징(11)과, 하우징(11)에 대해 회동 가능한, 링(ring) 형상의 회동 쉘(shell)(20)과, 회동 쉘(20)에 고정 결합되는 미러 지지 플레이트(25)를 구비한다. 하우징(11)은 사발(bowl) 형태의 하부 하우징(12)과, 하부 하우징(12)의 상측 개구를 폐쇄하는 상부 하우징(17)을 구비한다. 1 and 2 are a perspective view and an exploded perspective view of a mirror actuator according to an embodiment of the present invention. 1 and 2, the mirror actuator 10 according to the embodiment of the present invention has a hemispherical housing 11 and a ring-shaped rotating shell which can be rotated with respect to the housing 11. 20 and a mirror support plate 25 fixedly coupled to the rotation shell 20. The housing 11 has a lower housing 12 in the form of a bowl and an upper housing 17 for closing the upper opening of the lower housing 12.
상부 하우징(17)의 중앙부와 미러 지지 플레이트(25)의 중앙부는 후크(33)에 의해 밀착된다. 구체적으로, 반구형의 스프링(30)이 사이에 개재된 채 피봇 캡(pivot cap)(28)과 후크(33)가 결합된다. 미러 지지 플레이트(25)의 중앙부는 상부 하우징(17)의 중앙부 위에 올려 지고, 상기 피봇 캡(28)과 결합된 후크(33)가 상부 하우징(17) 측으로 내려져 후크(33)의 하단부가 상부 하우징(17)의 중앙부와 체결된다. 그리고, 중심 파이프(37)가 후크(33)의 중앙 통공에 끼워지고 Z축에 평행한 중심축(CL)을 따라 내려져 그 하단이 하부 하우징(12)의 중앙 홀(13)(도 4 참조)에 끼워 고정된다. The central portion of the upper housing 17 and the central portion of the mirror support plate 25 are in close contact with the hook 33. Specifically, the pivot cap 28 and the hook 33 are coupled with the hemispherical spring 30 interposed therebetween. The central portion of the mirror support plate 25 is raised above the central portion of the upper housing 17, and the hook 33 coupled with the pivot cap 28 is lowered toward the upper housing 17 so that the lower end of the hook 33 is the upper housing. Engage with the central part of (17). The center pipe 37 is fitted into the central through hole of the hook 33 and is lowered along the central axis CL parallel to the Z axis so that the lower end thereof is the central hole 13 of the lower housing 12 (see FIG. 4). It is fixed in the
하우징(11)의 내부 공간에는 제1 회동력 제공 유닛(40)(도 4 참조)과 제2 회동력 제공 유닛(60)(도 4 참조)이 배치된다. 제1 회동력 제공 유닛(40)은 회동 쉘(20)을 X축과 평행한 제1 회동축(R1)(도 4 참조)에 대해 회동시키는 동력을 제공하고, 제2 회동력 제공 유닛(60)은 회동 쉘(20)을 Y축과 평행한 제2 회동축(R2)(도 4 참조)에 대해 회동시키는 동력을 제공한다. 제1 회동력 제공 유닛(40)의 체결 돌기(59)와 제2 회동력 제공 유닛(60)의 체결 돌기(79)가 각각 회동 쉘(20)의 체결공(22, 23)에 삽입 체결된다. The first rotational force providing unit 40 (see FIG. 4) and the second rotational force providing unit 60 (see FIG. 4) are disposed in the inner space of the housing 11. The first rotational force providing unit 40 provides power for rotating the rotational shell 20 about the first rotational shaft R1 (see FIG. 4) parallel to the X axis, and the second rotational force providing unit 60. ) Provides power to rotate the pivoting shell 20 about a second pivotal axis R2 (see FIG. 4) parallel to the Y axis. The fastening protrusion 59 of the first turning force providing unit 40 and the fastening protrusion 79 of the second turning force providing unit 60 are inserted into and fastened to the fastening holes 22 and 23 of the rotating shell 20, respectively. .
미러 지지 플레이트(25)에는 미러(미도시)가 부착 지지되고, 미러 액추에이터(10)는 하부 하우징(12)의 아래로부터 중심 파이프(37)로 삽입 체결되는 볼트(bolt)(미도시)에 의해 지지대(미도시)에 고정 장착된다. 제1 회동력 제공 유닛(40)(도 4 참조)에 전기 신호가 인가되면 회동 쉘(20)과 미러 지지 플레이트(25)가 제1 회동축(R1)(도 4 참조)에 대해 시계 방향 또는 반시계 방향으로 회동한다. 제2 회동력 제공 유닛(60)(도 4 참조)에 전기 신호가 인가되면 회동 쉘(20)과 미러 지지 플레이트(25)가 제2 회동축(R2)(도 4 참조)에 대해 시계 방향 또는 반시계 방향으로 회동한다. 제1 및 제2 회동축(R1, R2)에 대한 독립적인 회동이 가능하여 미러(mirror)의 기울어짐 각을 자유롭게 조정할 수 있다. A mirror (not shown) is attached and supported to the mirror support plate 25, and the mirror actuator 10 is bolted (not shown) inserted into and fastened from the bottom of the lower housing 12 to the center pipe 37. It is fixedly mounted on a support (not shown). When an electrical signal is applied to the first rotational force providing unit 40 (see FIG. 4), the pivoting shell 20 and the mirror support plate 25 are clockwise or relative to the first rotational axis R1 (see FIG. 4). Rotate counterclockwise. When an electrical signal is applied to the second rotational force providing unit 60 (see FIG. 4), the rotation shell 20 and the mirror support plate 25 are clockwise or relative to the second rotational axis R2 (see FIG. 4). Rotate counterclockwise. Independent rotation of the first and second rotation shafts R1 and R2 is possible, so that the inclination angle of the mirror can be freely adjusted.
도 3 및 도 4는 도 1의 하부 하우징과 그 내부에 배치된, 회동력을 제공하기 위한 요소들을 도시한 사시도 및 평면도이다. 도 2 내지 도 4를 참조하면, 제1 회동력 제공 유닛(40)과 제2 회동력 제공 유닛(60)은 중심축(CL)을 교차하여 직선으로 연장되는 가상의 분할 라인(HL)을 기준으로 일 측 및 타 측에 각각 배치된다. 상기 분할 라인(HL)은 서로 직교하며 중심축(CL)에서 교차하는 제1 회동축(R1)과 제2 회동축(R2)에 대해 등각도를 형성하는 직선으로 하부 하우징(12) 내부 공간은 반분되고, 제1 회동력 제공 유닛(40)과 제2 회동력 제공 유닛(60)은 각각 상기 반분되는 하부 하우징(12) 내부 공간의 일 측 및 타 측을 차지한다. 뿐만 아니라, 도 3 및 도 4에 도시된 실시예에서는 제1 회동력 제공 유닛(40)과 제2 회동력 제공 유닛(60)이 분할 라인(HL)을 기준으로 대칭되게 배치된다. 3 and 4 are a perspective view and a plan view of the lower housing of FIG. 1 and elements for providing a rotational force disposed therein. 2 to 4, the first rotational force providing unit 40 and the second rotational force providing unit 60 refer to an imaginary dividing line HL extending in a straight line across the central axis CL. It is disposed on one side and the other side, respectively. The dividing line HL is a straight line that is orthogonal to each other and forms an isometric angle with respect to the first and second pivoting shafts R1 and R2 that intersect at the central axis CL. The half turning, the first turning force providing unit 40 and the second turning force providing unit 60 occupy one side and the other side of the inner space of the half housing 12 which is half divided. 3 and 4, the first turning force providing unit 40 and the second turning force providing unit 60 are symmetrically arranged with respect to the dividing line HL.
제1 회동력 제공 유닛(40) 및 제2 회동력 제공 유닛(60)은 각각, 모터(41, 61), 제1 이중기어(45, 65), 제2 이중기어(50, 70), 클러치 기어(clutch gear)(100A, 100B), 랙 기어(rack gear)(58, 78), 및 체결 돌기(59, 79)를 구비한다. 모터(41, 61)는 DC 모터일 수 있고, 그 회전축에는 웜 기어(worm gear)(43, 63)가 형성된다. 모터(41, 61)의 회전축과 동일한 방향으로 연장된 가상의 축선(P11, P21)은 제1 회동축(R1) 및 제2 회동축(R2)에 의해 한정되는 가상의 평면과 평행하다. 다시 말해, XY 평면과 평행하다. The first rotational force providing unit 40 and the second rotational force providing unit 60 are respectively a motor 41, 61, a first double gear 45, 65, a second double gear 50, 70, a clutch. Clutch gears 100A and 100B, rack gears 58 and 78, and fastening protrusions 59 and 79 are provided. The motors 41 and 61 may be DC motors, and worm gears 43 and 63 are formed on the rotating shaft. The imaginary axes P11 and P21 extending in the same direction as the rotation axes of the motors 41 and 61 are parallel to the imaginary plane defined by the first rotating shaft R1 and the second rotating shaft R2. In other words, it is parallel to the XY plane.
제1 이중기어(45, 65)는 하부 하우징(12)의 중앙부에 배치되며, 분할 라인(HL)에 근접하여 서로 마주보도록 배치된다. 제1 이중기어(45, 65)는 웜 기어(43, 63)에 치합되는 모터축 치합 기어부(46, 66)과, 모터축 치합 기어부(46, 66)와 동축(同軸) 회전하는 제2 이중기어 치합 기어부(48, 68)를 구비한다. 모터축 치합 기어부(46, 66)의 직경이 제2 이중기어 치합 기어부(48, 68)의 직경보다 크다. 제1 이중기어(45, 65)의 회전축과 동일한 방향으로 연장된 가상의 축선(V11, V21)은 제1 회동축(R1) 및 제2 회동축(R2)에 의해 한정되는 가상의 평면에 직교한다. 다시 말해, Z축과 평행하다. 모터축 치합 기어부(46, 66)가 아래에 배치되고, 제2 이중기어 치합 기어부(48, 68)가 위에 배치된다. 모터축 치합 기어부(46, 66)의 외주면에는 웜 기어(43, 63)와 치합되어 손실 없이 정확하게 동력 전달 받을 수 있도록, 기울어진 기어치를 구비한 헬리컬 기어(helical gear)가 형성된다. The first double gears 45 and 65 are disposed at the center of the lower housing 12 and are disposed to face each other in proximity to the dividing line HL. The first double gears 45 and 65 rotate coaxially with the motor shaft engagement gear portions 46 and 66 engaged with the worm gears 43 and 63 and the motor shaft engagement gear portions 46 and 66. Two double gear engagement gear parts 48 and 68 are provided. The diameters of the motor shaft engagement gear portions 46 and 66 are larger than the diameters of the second double gear engagement gear portions 48 and 68. The imaginary axes V11 and V21 extending in the same direction as the rotation axes of the first double gears 45 and 65 are orthogonal to the imaginary plane defined by the first pivot shaft R1 and the second pivot shaft R2. do. In other words, it is parallel to the Z axis. Motor shaft engagement gear portions 46, 66 are disposed below, and second double gear engagement gear portions 48, 68 are disposed above. On the outer circumferential surfaces of the motor shaft engagement gear portions 46 and 66, a helical gear having inclined gear teeth is formed so as to be engaged with the worm gears 43 and 63 so as to receive power accurately without loss.
제2 이중기어(50, 70)는 제2 이중기어 치합 기어부(48, 68)에 치합되는 제1 이중기어 치합부(51, 71)와, 제1 이중기어 치합부(51, 71)와 동축(同軸) 회전하는 웜(worm) 기어부(52, 72)를 구비한다. 제2 이중기어(50, 70)의 회전축과 동일한 방향으로 연장된 가상의 축선(V12, V22)은 제1 회동축(R1) 및 제2 회동축(R2)에 의해 한정되는 가상의 평면에 직교한다. 다시 말해, Z축과 평행하다. 제1 이중기어 치합부(51, 71)가 아래에 배치되고, 웜 기어부(52, 72)가 위에 배치된다. The second double gear (50, 70) and the first double gear engagement portion (51, 71) to be engaged with the second double gear engagement gear portion (48, 68), and the first double gear engagement portion (51, 71) Coaxially rotating worm gears 52 and 72 are provided. The imaginary axes V12 and V22 extending in the same direction as the rotation axes of the second double gears 50 and 70 are orthogonal to the imaginary plane defined by the first pivot shaft R1 and the second pivot shaft R2. do. In other words, it is parallel to the Z axis. The first double gear engagement portions 51, 71 are disposed below, and the worm gear portions 52, 72 are disposed above.
클러치 기어(100A, 100B)는 제2 이중기어(50, 70)의 웜 기어부(52, 72)에 치합되는 제1 기어부(102A, 102B)와, 상기 제1 기어부(102A, 102B)와 동축(同軸) 회전하는 제2 기어부(120A, 120B)를 구비한다. 제1 기어부(102A, 102B)의 외경이 제2 기어부(120A, 120B)의 외경보다 크다. 클러치 기어(100A, 100B)의 회전축과 동일한 방향으로 연장된 가상의 축선(P12, P22)은 XY 평면과 평행하다. 제1 기어부(102A, 102B)의 외주면에는 웜 기어부(52, 72)와 치합되어 손실 없이 정확하게 동력 전달 받을 수 있도록, 기울어진 기어치를 구비한 헬리컬 기어(helical gear)가 형성된다. 제2 기어부(120A, 120B)의 외주면에는 랙 기어(58, 78)와 치합되는 스퍼 기어(spur gear)가 형성된다. Clutch gear (100A, 100B) is the first gear portion (102A, 102B) to be engaged with the worm gear portion (52, 72) of the second double gear (50, 70), the first gear portion (102A, 102B) And second gear portions 120A, 120B which coaxially rotate with each other. The outer diameters of the first gear parts 102A and 102B are larger than the outer diameters of the second gear parts 120A and 120B. Virtual axes P12 and P22 extending in the same direction as the rotational axes of the clutch gears 100A and 100B are parallel to the XY plane. A helical gear having an inclined gear tooth is formed on the outer circumferential surfaces of the first gear portions 102A and 102B so as to be engaged with the worm gear portions 52 and 72 so as to receive power accurately without loss. Spur gears meshing with the rack gears 58 and 78 are formed on the outer circumferential surfaces of the second gear portions 120A and 120B.
랙 기어(58, 78)는 하부 하우징(12) 경사진 내측벽에 고정 지지되어 경사지게 연장되며, 랙 기어 치합 기어부(57, 77)에 치합된다. 랙 기어(58, 78)의 상단부는 상부 하우징(17)(도 2 참조)을 관통하여 하우징(11) 외부로 돌출된다. 체결 돌기(59. 79)는 랙 기어(58, 78)의 상단에 랙 기어(58, 78)와 일체로 형성되고, 상술한 바와 같이 회동 쉘(20)(도 2 참조)의 체결공(22, 23)에 삽입 체결된다. The rack gears 58 and 78 are fixedly supported on the inclined inner wall of the lower housing 12 to extend inclinedly and are engaged with the rack gear engaging gear portions 57 and 77. The upper ends of the rack gears 58 and 78 penetrate the upper housing 17 (see FIG. 2) and protrude out of the housing 11. The fastening protrusions 59.79 are integrally formed with the rack gears 58 and 78 at the upper ends of the rack gears 58 and 78, and the fastening holes 22 of the rotating shell 20 (see FIG. 2) as described above. , 23) is fastened.
제1 회동력 제공 유닛(40)의 체결 돌기(59)의 돌출 방향으로 연장된 가상의 연장선은 제2 회동축(R2)과 일치하고, 제2 회동력 제공 유닛(60)의 체결 돌기(79)의 돌출 방향으로 연장된 가상의 연장선은 제1 회동축(R1)과 일치한다. 따라서, 제1 회동축(R1)과 제2 회동축(R2)에 대해 회동 쉘(20)(도 2 참조) 및 미러 지지 플레이트(25)가 독립적으로 미리 정한 각도만큼 회동할 수 있으며, 모터(41, 61)의 동력이 정확히 체결 돌기(59, 79)에 전달되어 작동 에러가 발생하지 않게 된다. 또한, 부분적인 하중의 집중으로 인한 제1 회동력 제공 유닛(40)과 제2 회동력 제공 유닛(60)의 구성하는 구성 부품들의 손상이 억제된다. The imaginary extension line extending in the protruding direction of the fastening protrusion 59 of the first turning force providing unit 40 coincides with the second turning shaft R2, and the fastening protrusion 79 of the second turning force providing unit 60. The imaginary extension line extending in the protruding direction of Ny coincides with the first rotational axis R1. Therefore, the rotating shell 20 (see FIG. 2) and the mirror support plate 25 can be independently rotated by a predetermined angle with respect to the first rotating shaft R1 and the second rotating shaft R2, and the motor ( The power of 41 and 61 is correctly transmitted to the fastening protrusions 59 and 79 so that an operation error does not occur. In addition, damage to the components constituting the first rotational force providing unit 40 and the second rotational force providing unit 60 due to the concentration of the partial load is suppressed.
미러 지지 플레이트(25)의 회동에 있어 회동력과 회동 속도의 요구 조건을 만족하기 위하여 기어치의 개수도 적절하게 선택된다. 바람직하게는, 제1 이중기어(45, 65)의 모터축 치합 기어부(46, 66)의 기어치(teeth) 개수는 제2 이중기어 치합 기어부(48, 68)의 기어치 개수보다 많다. 또한, 제2 이중기어 치합 기어부(48, 68)의 기어치 개수와 제2 이중기어(50, 70)의 제1 이중기어 치합 기어부(51, 71)의 기어치 개수의 차이는 0 내지 3개이다. 예를 들어, 모터축 치합 기어부(46, 66)의 기어치(teeth) 개수는 28개, 제2 이중기어 치합 기어부(48, 68)의 기어치 개수는 16개, 제1 이중기어 치합 기어부(51, 71)의 기어치 개수는 17개일 수 있다. The number of gear teeth is also appropriately selected in order to satisfy the requirements of the rotational force and the rotational speed in the rotation of the mirror support plate 25. Preferably, the number of teeth of the motor shaft engagement gear portions 46 and 66 of the first double gear 45 and 65 is greater than the number of gear teeth of the second double gear engagement gear portions 48 and 68. . In addition, the difference between the number of gear teeth of the second double gear engagement gear parts 48 and 68 and the number of gear teeth of the first double gear engagement gear parts 51 and 71 of the second double gear 50 and 70 are 0 to. Three. For example, the number of teeth of the motor shaft engagement gear parts 46 and 66 is 28, the number of gear teeth of the second double gear engagement gear parts 48 and 68 is 16, and the first double gear teeth is meshed. The number of gear teeth of the gear parts 51 and 71 may be 17.
또한 바람직하게는, 클러치 기어(100A, 100B)의 웜 기어부 치합 기어부(55, 75)의 기어치 개수는 랙 기어 치합 기어부(57, 77)의 기어치 개수보다 많고, 랙 기어 치합 기어부(57, 77)의 기어치 개수는 랙 기어(58, 78)의 기어치 개수보다 적다. 예를 들어, 웜 기어부 치합 기어부(55, 75)의 기어치 개수는 17개, 랙 기어 치합 기어부(57, 77)의 기어치 개수는 9개, 랙 기어(58, 78)의 기어치 개수는 13개일 수 있다. Also preferably, the number of gear teeth of the worm gear portion engagement gear portions 55 and 75 of the clutch gears 100A and 100B is greater than the number of gear teeth of the rack gear engagement gear portions 57 and 77, and the rack gear engagement gear The number of gear teeth of the portions 57 and 77 is smaller than the number of gear teeth of the rack gears 58 and 78. For example, the number of gear teeth of the worm gear engaging gears 55 and 75 is 17, the number of gear teeth of the rack gear engaging gears 57 and 77 is 9 and the gears of the rack gears 58 and 78. The number of teeth may be thirteen.
상술한 제1 및 제2 회동력 제공 유닛에서 모터(41, 61)의 동력 전달 경로는 모터 샤프트의 웜 기어(43, 63) → 제1 이중 기어(45, 65) → 제2 이중 기어(50, 70) → 클러치 기어(100A, 100B) → 랙 기어(58, 78)의 순서이다. 여기서, 랙 기어(58, 78)에 치합된 클러치 기어(100A, 100B)의 제2 기어부(120A, 120B)는, 회동 쉘(20)이 최대 각도까지 회동되면 더 이상 회전할 수 없다. 따라서 클러치 기어(100A, 100B)는, 회동 쉘(20)이 최대 각도까지 회동한 이후에도 전기 신호가 추가로 입력되어 모터(41, 61)가 회전하면 제2 기어부(120A, 120B)는 회전하지 않고 제1 기어부(102A, 102B)만 회전하도록, 제1 기어부(102A, 102B)와 제2 기어부(120A, 120B)가 분리된 구성을 갖는다. 이하에서, 클러치 기어(100A, 100B)의 구성에 대해 상술한다. In the above-described first and second rotational force providing units, the power transmission paths of the motors 41 and 61 are worm gears 43 and 63 → first double gears 45 and 65 → second double gears 50 of the motor shaft. , 70) → clutch gears 100A, 100B → rack gears 58, 78. Here, the second gear portions 120A, 120B of the clutch gears 100A, 100B meshed with the rack gears 58, 78 can no longer rotate when the rotation shell 20 is rotated to the maximum angle. Therefore, the clutch gears 100A and 100B do not rotate when the electric signals are further input even after the rotational shell 20 rotates to the maximum angle and the motors 41 and 61 rotate. The first gear portions 102A and 102B and the second gear portions 120A and 120B are separated from each other so that only the first gear portions 102A and 102B are rotated. Hereinafter, the structure of clutch gear 100A, 100B is explained in full detail.
도 5 및 도 6은 도 1의 클러치 기어를 서로 다른 방향에서 보고 도시한 사시도이고, 도 7 및 도 8은 도 1의 클러치 기어를 서로 다른 방향에서 보고 도시한 분해 사시도로서, 이 도면들을 참조하면, 클러치 기어(100A, 100B)는 제1 기어 부재(101), 제2 기어 부재(110), 및 판 스프링(130)을 구비한다. 제1 기어 부재(101)는 모터(41, 61)의 동력 전달 방향을 따라 자신의 상류측 기어, 즉 제2 이중기어(50, 70)에 치합되는 제1 기어부(102A, 102B)를 외주면에 구비하고, 중앙에 중앙 통공(104)이 형성된다. 5 and 6 are perspective views of the clutch gear of FIG. 1 viewed from different directions, and FIGS. 7 and 8 are exploded perspective views of the clutch gear of FIG. 1 viewed from different directions. The clutch gears 100A, 100B include a first gear member 101, a second gear member 110, and a leaf spring 130. The first gear member 101 has an outer circumferential surface of the first gear portion 102A, 102B meshed with its upstream gear, that is, the second double gear 50, 70 along the power transmission direction of the motors 41, 61. It is provided in, and the central through-hole 104 is formed in the center.
제2 기어 부재(110)는 모터(41, 61)의 동력 전달 방향을 따라 자신의 하류측 기어, 즉 랙 기어(58, 78)에 치합되는 제2 기어부(120A, 120B)를 외주면에 구비한다. 제2 기어 부재(110)는 제1 기어 부재(101)의 중앙 통공(104)에 끼워지며, 일 측 단부가 중앙 통공(104)을 관통한다. 제2 기어 부재(110)는 클러치 기어(100A, 100B)의 회전축이 되는 것으로, 제2 기어부(120A, 120B)측 말단의 제1 회전축(115)과 그 반대측 말단의 제2 회전축(117)이 각각, 하부 하우징(12)에 형성된 제1 회전축 홀더(145A, 145B)(도 3 참조)와 제2 회전축 홀더(148A, 148B)(도 3 참조)에 끼워져 지지된다. The second gear member 110 is provided on the outer circumferential surface of the second gear portion 120A, 120B meshed with its downstream gear, that is, the rack gears 58, 78 along the power transmission direction of the motors 41, 61. do. The second gear member 110 is fitted into the central through hole 104 of the first gear member 101, and one end thereof passes through the central through hole 104. The second gear member 110 serves as the rotation shaft of the clutch gears 100A and 100B, and the first rotation shaft 115 at the end of the second gear portion 120A and 120B and the second rotation shaft 117 at the opposite end thereof. Each of these is sandwiched and supported by the first rotary shaft holders 145A and 145B (see FIG. 3) and the second rotary shaft holders 148A and 148B (see FIG. 3) formed in the lower housing 12.
중앙 통공(104)을 관통하는 제2 기어 부재(110) 일 측 단부의 외주면에는 한 쌍의 외주면 그루브(groove)(123)가 형성된다. 한 쌍의 외주면 그루브(123)는 제2 기어 부재(110)의 길이 방향 축선(P12, P22)(도 3 참조)에 대해 대칭되게 반대측 외주면에 형성된다. 외주면 그루브(123)는 제2 기어 부재(110)의 원호를 따라 연장되고 일정한 폭(W)을 갖는다. 외주면 그루브(123)의 폭(W) 방향 양 측에 제1 및 제2 단차면(124, 125)이 형성되고, 제1 및 제2 단차면(124, 125)의 깊이는 외주면 그루브(123)의 중앙부가 가장 깊고 주변으로 갈수록 얕다. A pair of outer circumferential grooves 123 is formed on the outer circumferential surface of one end of the second gear member 110 penetrating the central through hole 104. The pair of outer circumferential surface grooves 123 is formed on the opposite outer circumferential surface symmetrically with respect to the longitudinal axes P12 and P22 (see FIG. 3) of the second gear member 110. The outer circumferential surface groove 123 extends along the arc of the second gear member 110 and has a constant width (W). First and second stepped surfaces 124 and 125 are formed at both sides of the width W direction of the outer circumferential surface groove 123, and the depths of the first and second stepped surfaces 124 and 125 are the outer circumferential surface grooves 123. The central part of is deepest and shallower toward the periphery.
판 스프링(130)은 판형의 스프링 강재를 프레스 가공 방법으로 찍어 눌러 형성한다. 판 스프링(130)은 알파벳 C자 형상으로 일 측(131)이 개방되어 있다. 판 스프링(130)은 개방된 일 측(131)으로 인해 서로 분리된 한 쌍의 말단부(133)와, 상기 개방된 일 측(131)의 반대편에 이어진 연결부(135)를 구비한다. 또한, 연결부(135)와 한 쌍의 말단부(133) 사이에는 절곡되어 주변보다 융기된 한 쌍의 요철부(137)를 구비한다. 요철부(137)의 융기된 높이(H)는 외주면 그루브(123)의 폭(W)보다 작다. The leaf spring 130 is formed by pressing a plate-shaped spring steel by pressing. The leaf spring 130 has an alphabet C shape and one side 131 is open. The leaf spring 130 has a pair of distal ends 133 separated from each other due to the open side 131, and a connecting portion 135 connected to the opposite side of the open side 131. In addition, between the connecting portion 135 and the pair of distal end portion 133 is provided with a pair of concave-convex portion 137 is bent and raised than the periphery. The raised height H of the uneven portion 137 is smaller than the width W of the outer circumferential surface groove 123.
판 스프링(130)은 상기 개방된 일 측(131)을 통해 한 쌍의 외주면 그루브(123)에 끼워져 제1 기어 부재(101)와 제2 기어 부재(110)가 서로 밀착되도록 탄성 가압한다. 구체적으로, 한 쌍의 요철부(137)의 내측 엣지(edge)(139)가 한 쌍의 외주면 그루브(123)에 안착되어 제1 단차면(124)에 밀착된다. 제1 단차면(124)은 외주면 그루브(123)의 한 쌍의 단차면(124, 125) 중에 제2 회전축(117)에 더 가까운 단차면이다. 한 쌍의 요철부(137) 이외의 부분, 즉 연결부(135) 및 한 쌍의 말단부(133)는 제1 기어 부재(101)에 밀착된다. The leaf spring 130 is fitted into the pair of outer circumferential grooves 123 through the open side 131 to elastically press the first gear member 101 and the second gear member 110 to closely contact each other. In detail, the inner edges 139 of the pair of uneven parts 137 are seated on the pair of outer circumferential surface grooves 123 to be in close contact with the first step surface 124. The first stepped surface 124 is a stepped surface closer to the second rotation shaft 117 among the pair of stepped surfaces 124 and 125 of the outer circumferential surface groove 123. Portions other than the pair of uneven portions 137, that is, the connecting portion 135 and the pair of end portions 133, are in close contact with the first gear member 101.
한 쌍의 요철부(137)가 한 쌍의 외주면 그루브(123)에 끼워질 수 있도록 판 스프링(130)의 한 쌍의 요철부(137) 사이의 간격(G2)은 한 쌍의 외주면 그루브(123) 사이의 간격(G1)보다 크거나 같다. 판 스프링(130)은 제2 기어 부재(110)의 길이 방향에 직교하는 방향, 즉 외주면 그루브(123)의 길이 방향과 평행한 방향으로 진입하여 한 쌍의 외주면 그루브(123)에 끼워진다. 이에 따라 한 쌍의 요철부(137)의 내측 엣지(139)가 한 쌍의 외주면 그루브(123)의 길이 방향과 평행한 방향으로 한 쌍의 외주면 그루브(123)에 진입하여 안착된다. The gap G2 between the pair of uneven parts 137 of the leaf spring 130 is such that the pair of uneven parts 137 fit into the pair of outer circumferential surface grooves 123. Is greater than or equal to the interval G1). The leaf spring 130 enters a direction orthogonal to the longitudinal direction of the second gear member 110, that is, a direction parallel to the longitudinal direction of the outer circumferential surface groove 123, and is fitted to the pair of outer circumferential surface grooves 123. Accordingly, the inner edge 139 of the pair of uneven parts 137 enters and rests in the pair of outer circumferential surface grooves 123 in a direction parallel to the longitudinal direction of the pair of outer circumferential surface grooves 123.
한편, 제1 기어 부재(101)의 중앙 통공(104)의 내주면(105)은 제1 회전축(115)에서 제2 회전축(117)을 향한 방향으로 갈수록 내경이 작아지도록 경사지게 연장된다. 제1 기어 부재(101)에 끼워지는 제2 기어 부재(110) 중간 부분의 외주면(112)은 상기 경사진 내주면(105)에 접촉되도록 내주면(105)의 경사와 동일한 경사각으로 경사지게 연장된다. 판 스프링(130)이 외주면 그루브(123)에 끼워져 체결됨으로 인해 제1 기어 부재(101)의 경사진 내주면(105)과 제2 기어 부재(110)의 경사진 외주면(112)이 탄성 밀착된다. On the other hand, the inner circumferential surface 105 of the central through hole 104 of the first gear member 101 extends inclined so as to decrease the inner diameter toward the direction from the first rotation shaft 115 toward the second rotation shaft 117. The outer circumferential surface 112 of the middle portion of the second gear member 110 fitted to the first gear member 101 extends inclined at the same inclination angle as that of the inner circumferential surface 105 so as to contact the inclined inner circumferential surface 105. Since the leaf spring 130 is fitted into the outer circumferential surface groove 123 and fastened, the inclined inner circumferential surface 105 of the first gear member 101 and the inclined outer circumferential surface 112 of the second gear member 110 are elastically in close contact with each other.
상술한 동력 전달 경로를 따라 모터(41, 61)(도 3 참조)의 동력이 제1 기어 부재(101)에 전달되면 제1 기어 부재(101)가 회전하고, 탄성 밀착된 내주면(105)과 외주면(112)을 통해 그 회전력이 전달되어 제2 기어 부재(110)가 회전하여 하류측의 랙 기어(58, 78)를 구동한다. 그러나, 랙 기어(58, 78)가 움직일 수 있는 한계까지 이동된 때에는 제2 기어 부재(110)는 더 이상 회전할 수 없고 모터(41, 61)의 동력이 제1 기어 부재(101)에 전달된다 하더라도 제1 기어 부재(101)만 회전하게 된다. 부연하면, 제2 기어 부재(110)가 하류측 기어, 즉 랙 기어(58, 78)로부터 받는 하중(load)이 미리 정해진 기준, 즉 최대 하중을 초과하여 제1 기어 부재(101)가 회전하더라도 중앙 통공(104)의 내주면(105)이 제2 기어 부재(110)의 외주면(112)에 대해 미끄러져 제2 기어 부재(110)는 회전하지 않게 된다. When the power of the motors 41 and 61 (see FIG. 3) is transmitted to the first gear member 101 along the above-described power transmission path, the first gear member 101 rotates and the inner circumferential surface 105 that is elastically in close contact with the power transmission path. The rotational force is transmitted through the outer circumferential surface 112 so that the second gear member 110 rotates to drive the rack gears 58 and 78 downstream. However, when the rack gears 58 and 78 are moved to the limit of their movement, the second gear member 110 can no longer rotate and the power of the motors 41 and 61 is transmitted to the first gear member 101. Even if only the first gear member 101 is rotated. In other words, even if the load received by the second gear member 110 from the downstream gear, that is, the rack gears 58 and 78 exceeds the predetermined reference, that is, the maximum load, the first gear member 101 rotates. The inner circumferential surface 105 of the central through hole 104 slides with respect to the outer circumferential surface 112 of the second gear member 110 such that the second gear member 110 does not rotate.
본 발명은 도면에 도시된 실시예를 참고로 설명되었으나 이는 예시적인 것에 불과하며, 당해 분야에서 통상의 지식을 가진 자라면 이로부터 다양한 변형 및 균등한 타 실시예가 가능함을 이해할 수 있을 것이다. 따라서 본 발명의 진정한 보호범위는 첨부된 특허청구범위에 의해서만 정해져야 할 것이다.Although the present invention has been described with reference to the embodiments shown in the drawings, this is merely exemplary, and it will be understood by those skilled in the art that various modifications and equivalent other embodiments are possible. Therefore, the true scope of protection of the present invention should be defined only by the appended claims.
본 발명은 자동차의 미러에 사용될 수 있다. The invention can be used for mirrors of automobiles.

Claims (15)

  1. 하우징; 상기 하우징의 기하학적 중심에서 서로 직교 교차하는 제1 및 제2 회동축에 대해 회동 가능한 회동 쉘(shell); 및, 상기 하우징의 내부에 배치된 것으로, 상기 회동 쉘을 상기 제1 회동축에 대해 회동시키는 제1 회동력 제공 유닛과, 상기 회동 쉘을 상기 제2 회동축에 대해 회동시키는 제2 회동력 제공 유닛;을 구비하고, 상기 제1 회동력 제공 유닛 및 제2 회동력 제공 유닛은 각각, housing; A rotatable shell rotatable about a first and a second pivotal axis orthogonal to each other at a geometric center of the housing; And a first rotational force providing unit, disposed in the housing, for rotating the pivoting shell about the first pivotal axis, and providing a second pivoting force for pivoting the pivoting shell with respect to the second pivotal shaft. And a first turning force providing unit and a second turning force providing unit, respectively.
    회전축에 웜 기어(worm gear)가 형성된 모터; 상기 웜 기어에 치합되는 모터축 치합 기어부와, 상기 모터축 치합 기어부와 동축(同軸) 회전하는 제2 이중기어 치합 기어부를 구비한 제1 이중기어; 상기 제2 이중기어 치합 기어부에 치합되는 제1 이중기어 치합 기어부와, 상기 제1 이중기어 치합 기어부와 동축(同軸) 회전하는 웜(worm) 기어부를 구비한 제2 이중기어; 상기 제2 이중기어의 웜 기어부에 치합되는 웜 기어부 치합 기어부와, 상기 웜 기어부 치합 기어부와 동축(同軸) 회전하는 랙 기어(rack gear) 치합 기어부를 구비한 클러치 기어(clutch gear); 상기 랙 기어 치합 기어부에 치합되며, 상단부가 상기 하우징을 벗어나 돌출되는 랙 기어; 및, 상기 랙 기어의 상단에 형성되고 상기 회동 셀에 체결되는 체결 돌기;를 구비하며, A motor in which a worm gear is formed on the rotating shaft; A first double gear having a motor shaft engagement gear portion meshed with the worm gear and a second double gear engagement gear portion coaxially rotating with the motor shaft engagement gear portion; A second double gear having a first double gear meshing gear portion meshed with the second double gear meshing gear portion and a worm gear portion coaxially rotating with the first double gear meshing gear portion; Clutch gear having a worm gear part engaging gear part engaged with the worm gear part of the second double gear and a rack gear engaging gear part coaxially rotating with the worm gear part engaging gear part. ); A rack gear engaged with the rack gear coupling gear and having an upper end projecting out of the housing; And a fastening protrusion formed at an upper end of the rack gear and fastened to the pivoting cell.
    상기 제1 회동력 제공 유닛의 체결 돌기의 연장선은 상기 제2 회동축과 일치하고, 상기 제2 회동력 제공 유닛의 체결 돌기의 연장선은 상기 제1 회동축과 일치하는 미러 액추에이터. The extension line of the fastening protrusion of the first rotational force providing unit coincides with the second rotational axis, and the extension line of the fastening protrusion of the second rotational force providing unit coincides with the first rotational shaft.
  2. 제1 항에 있어서,The method of claim 1,
    상기 모터의 회전축과 상기 클러치 기어의 회전축은 상기 제1 회동축 및 상기 제2 회동축에 의해 한정되는 평면과 평행하고, 상기 제1 이중기어의 회전축과 상기 제2 이중기어의 회전축은 상기 제1 회동축 및 상기 제2 회동축에 의해 한정되는 평면에 직교하는 미러 액추에이터. The rotating shaft of the motor and the rotating shaft of the clutch gear are parallel to the plane defined by the first rotating shaft and the second rotating shaft, and the rotating shaft of the first double gear and the rotating shaft of the second double gear are the first shaft. And a mirror actuator orthogonal to a plane defined by the pivot shaft and the second pivot shaft.
  3. 제1 항에 있어서,The method of claim 1,
    상기 제1 회동력 제공 유닛과 상기 제2 회동력 제공 유닛이 상기 하우징의 내부 공간을 반분하여 차지하도록 배치된 미러 액추에이터. And the first rotational force providing unit and the second rotational force providing unit are arranged to occupy half the internal space of the housing.
  4. 제1 항에 있어서,The method of claim 1,
    상기 제1 이중기어의 모터축 치합 기어부와, 상기 클러치 기어의 웜 기어부 치합 기어부는 헬리컬 기어(helical gear)인 미러 액추에이터. And the worm gear portion of the first double gear and the worm gear portion of the clutch gear are helical gears.
  5. 제1 항에 있어서,The method of claim 1,
    상기 모터축 치합 기어부의 기어치(gear teeth) 개수가 상기 제2 이중기어 치합 기어부의 기어치 개수보다 많고, 상기 제2 이중기어 치합 기어부의 기어치 개수와 상기 제1 이중기어 치합 기어부의 기어치 개수의 차이는 0 내지 3 인 미러 액추에이터. The number of gear teeth of the motor shaft engagement gear portion is greater than the number of gear teeth of the second double gear engagement gear portion, and the number of gear teeth of the second double gear engagement gear portion and the gear teeth of the first double gear engagement gear portion. The difference in the number of mirror actuators is 0 to 3.
  6. 제1 항에 있어서, The method of claim 1,
    상기 웜 기어부 치합 기어부의 기어치 개수는 상기 랙 기어 치합 기어부의 기어치 개수보다 많고, 상기 랙 기어 치합 기어부의 기어치 개수는 상기 랙 기어의 기어치 개수보다 적은 미러 액추에이터. The number of gear teeth of the worm gear engagement gear portion is greater than the number of gear teeth of the rack gear engagement gear portion, and the number of gear teeth of the rack gear engagement gear portion is less than the number of gear teeth of the rack gear.
  7. 모터의 동력 전달 방향을 따라 자신의 상류측 기어에 치합되는 제1 기어부를 외주면에 구비하고, 중앙에 중앙 통공이 형성된 제1 기어 부재;A first gear member provided on an outer circumferential surface of the first gear portion engaged with the upstream gear of the motor along a power transmission direction of the motor, and having a central through hole at its center;
    상기 모터의 동력 전달 방향을 따라 자신의 하류측 기어에 치합되는 제2 기어부를 외주면에 구비하고, 상기 중앙 통공에 끼워져 일 측 단부가 상기 중앙 통공을 관통하며, 상기 일 측 단부의 외주면에 적어도 하나의 외주면 그루브(groove)가 형성된 제2 기어 부재; 및,A second gear part engaged with the downstream gear of the motor along the power transmission direction of the motor on an outer circumferential surface thereof, and fitted into the central through hole, one end of which passes through the central through hole, and at least one on the outer circumferential surface of the one end portion A second gear member having an outer circumferential surface groove of the second gear member; And,
    알파벳 C자 형상으로 일 측이 개방되고, 절곡되어 주변보다 융기된 적어도 하나의 요철부를 구비하며, 상기 개방된 일 측을 통해 상기 적어도 하나의 외주면 그루브에 끼워져 상기 제1 기어 부재와 상기 제2 기어 부재가 서로 밀착되도록 탄성 가압하는 판 스프링;을 구비하고, One side is opened in the shape of the letter C, has at least one concave-convex portion that is bent and raised than the periphery, and is fitted to the at least one outer peripheral surface groove through the open one side to the first gear member and the second gear And a leaf spring for elastically pressing the members to be in close contact with each other.
    상기 적어도 하나의 요철부의 내측 엣지(edge)가 상기 적어도 하나의 외주면 그루브에 안착되어 상기 외주면 그루브의 일 측면에 밀착되고, 상기 적어도 하나의 요철부 이외의 부분은 상기 제1 기어 부재에 밀착되도록 구성된 클러치 기어. The inner edge of the at least one uneven portion is seated on the at least one outer circumferential groove so as to be in close contact with one side of the outer circumferential groove, and portions other than the at least one uneven portion are in close contact with the first gear member. Clutch gear.
  8. 제7 항에 있어서,The method of claim 7, wherein
    상기 적어도 하나의 외주면 그루브는 한 쌍이 구비되고, 상기 한 쌍의 외주면 그루브는 상기 제2 기어 부재의 길이 방향 축선에 대해 대칭되게 반대측 외주면에 형성되고, 상기 적어도 하나의 요철부는 상기 한 쌍의 외주면 그루브에 대응되게 한 쌍이 구비되며, The at least one outer circumferential surface groove is provided with a pair, the pair of outer circumferential surface grooves are formed on the opposite outer circumferential surface symmetrically with respect to the longitudinal axis of the second gear member, and the at least one uneven portion is the pair of outer circumferential surface grooves A pair is provided to correspond to
    상기 한 쌍의 요철부 사이의 간격이 상기 한 쌍의 외주면 그루브 사이의 간격보다 크거나 같고, 상기 한 쌍의 요철부의 내측 엣지가 상기 한 쌍의 외주면 그루브의 길이 방향과 평행한 방향으로 상기 한 쌍의 외주면 그루브에 진입하여 상기 판 스프링이 상기 한 쌍의 외주면 그루브에 끼워지도록 구성된 클러치 기어. The pair of gaps between the pair of uneven parts is greater than or equal to the gap between the pair of outer circumferential surface grooves, and the pair of inner edges of the pair of uneven parts are parallel to the longitudinal direction of the pair of outer circumferential surface grooves. A clutch gear configured to enter an outer circumferential surface groove of the leaf spring so that the leaf spring is fitted into the pair of outer circumferential surface grooves.
  9. 제7 항에 있어서,The method of claim 7, wherein
    상기 중앙 통공의 내주면은 경사지게 연장되고, The inner circumferential surface of the central aperture extends inclinedly,
    상기 제2 기어 부재는 상기 내주면에 접촉되도록 상기 내주면의 경사와 동일한 경사각으로 경사지게 연장된 외주면을 구비하고, The second gear member has an outer circumferential surface inclined at the same inclination angle as the inclination of the inner circumferential surface to contact the inner circumferential surface,
    상기 제2 기어 부재가 상기 하류측 기어로부터 받는 하중이 미리 정한 기준을 초과하면 상기 제1 기어 부재가 회전하더라도 상기 중앙 통공의 내주면이 상기 제2 기어 부재의 외주면에 대해 미끄러져 상기 제2 기어 부재는 회전하지 않도록 구성된 클러치 기어. If the load received by the second gear member from the downstream gear exceeds a predetermined criterion, even if the first gear member rotates, the inner circumferential surface of the central through hole slides with respect to the outer circumferential surface of the second gear member, so that the second gear member Clutch gear configured to not rotate.
  10. 제7 항에 있어서,The method of claim 7, wherein
    상기 제1 기어부와 상기 제2 기어부는 기어부의 외경이 서로 다르고, 동축(同軸) 회전하도록 구성된 클러치 기어. A clutch gear, wherein the first gear portion and the second gear portion have different outer diameters of the gear portion, and are configured to coaxially rotate.
  11. 하우징; 상기 하우징에 대해 회동 가능한 회동 쉘(shell); 및, 상기 하우징의 내부에 배치된 것으로, 상기 회동 쉘을 회동시키는 적어도 하나의 회동력 제공 유닛;을 구비하고, 상기 회동력 제공 유닛은, housing; A rotatable shell rotatable with respect to the housing; And at least one rotational force providing unit, disposed in the housing, for rotating the pivoting shell, wherein the rotational force providing unit includes:
    모터; 상기 모터의 동력이 전달되어 회전하는 클러치 기어; 및, 상기 클러치 기어의 제2 기어부에 치합되고, 상단부가 상기 하우징을 벗어나 상기 회동 쉘에 체결되는 랙 기어(rack gear)를 구비하며,motor; A clutch gear that rotates by transmitting power of the motor; And a rack gear meshed with the second gear portion of the clutch gear, the upper end portion of which is coupled to the pivoting shell out of the housing,
    상기 클러치 기어는:The clutch gear is:
    모터의 동력 전달 방향을 따라 자신의 상류측 기어에 치합되는 제1 기어부를 외주면에 구비하고, 중앙에 중앙 통공이 형성된 제1 기어 부재;A first gear member provided on an outer circumferential surface of the first gear portion engaged with the upstream gear of the motor along a power transmission direction of the motor, and having a central through hole at its center;
    상기 모터의 동력 전달 방향을 따라 자신의 하류측 기어에 치합되는 제2 기어부를 외주면에 구비하고, 상기 중앙 통공에 끼워져 일 측 단부가 상기 중앙 통공을 관통하며, 상기 일 측 단부의 외주면에 적어도 하나의 외주면 그루브(groove)가 형성된 제2 기어 부재; 및,A second gear part engaged with the downstream gear of the motor along the power transmission direction of the motor on an outer circumferential surface thereof, and fitted into the central through hole, one end of which passes through the central through hole, and at least one on the outer circumferential surface of the one end portion A second gear member having an outer circumferential surface groove of the second gear member; And,
    알파벳 C자 형상으로 일 측이 개방되고, 절곡되어 주변보다 융기된 적어도 하나의 요철부를 구비하며, 상기 개방된 일 측을 통해 상기 적어도 하나의 외주면 그루브에 끼워져 상기 제1 기어 부재와 상기 제2 기어 부재가 서로 밀착되도록 탄성 가압하는 판 스프링;을 구비하고, One side is opened in the shape of the letter C, has at least one concave-convex portion that is bent and raised than the periphery, and is fitted to the at least one outer peripheral surface groove through the open one side to the first gear member and the second gear And a leaf spring for elastically pressing the members to be in close contact with each other.
    상기 적어도 하나의 요철부의 내측 엣지(edge)가 상기 적어도 하나의 외주면 그루브에 안착되어 상기 외주면 그루브의 일 측면에 밀착되고, 상기 적어도 하나의 요철부 이외의 부분은 상기 제1 기어 부재에 밀착되도록 구성된 미러 액추에이터. The inner edge of the at least one uneven portion is seated on the at least one outer circumferential groove so as to be in close contact with one side of the outer circumferential groove, and portions other than the at least one uneven portion are in close contact with the first gear member. Mirror actuator.
  12. 제11 항에 있어서,The method of claim 11, wherein
    상기 적어도 하나의 외주면 그루브는 한 쌍이 구비되고, 상기 한 쌍의 외주면 그루브는 상기 제2 기어 부재의 길이 방향 축선에 대해 대칭되게 반대측 외주면에 형성되고, 상기 적어도 하나의 요철부는 상기 한 쌍의 외주면 그루브에 대응되게 한 쌍이 구비되며, The at least one outer circumferential surface groove is provided with a pair, the pair of outer circumferential surface grooves are formed on the opposite outer circumferential surface symmetrically with respect to the longitudinal axis of the second gear member, and the at least one uneven portion is the pair of outer circumferential surface grooves A pair is provided to correspond to
    상기 한 쌍의 요철부 사이의 간격이 상기 한 쌍의 외주면 그루브 사이의 간격보다 크거나 같고, 상기 한 쌍의 요철부의 내측 엣지가 상기 한 쌍의 외주면 그루브의 길이 방향과 평행한 방향으로 상기 한 쌍의 외주면 그루브에 진입하여 상기 판 스프링이 상기 한 쌍의 외주면 그루브에 끼워지도록 구성된 미러 액추에이터. The pair of gaps between the pair of uneven parts is greater than or equal to the gap between the pair of outer circumferential surface grooves, and the pair of inner edges of the pair of uneven parts are parallel to the longitudinal direction of the pair of outer circumferential surface grooves. A mirror actuator configured to enter an outer circumferential surface groove of the leaf spring so that the leaf spring is fitted into the pair of outer circumferential surface grooves.
  13. 제11 항에 있어서,The method of claim 11, wherein
    상기 중앙 통공의 내주면은 경사지게 연장되고, The inner circumferential surface of the central aperture extends inclinedly,
    상기 제2 기어 부재는 상기 내주면에 접촉되도록 상기 내주면의 경사와 동일한 경사각으로 경사지게 연장된 외주면을 구비하고, The second gear member has an outer circumferential surface inclined at the same inclination angle as the inclination of the inner circumferential surface to contact the inner circumferential surface,
    상기 제2 기어 부재가 상기 하류측 기어로부터 받는 하중이 미리 정한 기준을 초과하면 상기 제1 기어 부재가 회전하더라도 상기 중앙 통공의 내주면이 상기 제2 기어 부재의 외주면에 대해 미끄러져 상기 제2 기어 부재는 회전하지 않도록 구성된 미러 액추에이터. If the load received by the second gear member from the downstream gear exceeds a predetermined criterion, even if the first gear member rotates, the inner circumferential surface of the central through hole slides with respect to the outer circumferential surface of the second gear member, so that the second gear member Mirror actuator configured to not rotate.
  14. 제11 항에 있어서,The method of claim 11, wherein
    상기 제1 기어부와 상기 제2 기어부는 기어부의 외경이 서로 다르고, 동축(同軸) 회전하도록 구성된 미러 액추에이터. And said first gear portion and said second gear portion are different from each other in outer diameter of the gear portion, and are configured to coaxially rotate.
  15. 제11 항에 있어서,The method of claim 11, wherein
    상기 회동력 제공 유닛은, 상기 모터의 동력 전달 방향을 따라 상기 모터와 상기 클러치 기어 사이에 위치하고 상기 클러치 기어의 제1 기어부에 치합되는 이중기어를 더 구비한 미러 액추에이터. And the rotational force providing unit further comprises a double gear positioned between the motor and the clutch gear along the power transmission direction of the motor and meshed with the first gear portion of the clutch gear.
PCT/KR2012/008681 2012-09-24 2012-10-22 Clutch gear and mirror actuator WO2014046334A1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR1020120106058A KR101403034B1 (en) 2012-09-24 2012-09-24 Mirror actuator
KR10-2012-0106058 2012-09-24
KR2020120009060U KR200471924Y1 (en) 2012-10-09 2012-10-09 Clutch gear and mirror actuator with the same
KR20-2012-0009060 2012-10-09

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WO2014046334A1 true WO2014046334A1 (en) 2014-03-27

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016048140A1 (en) * 2014-09-22 2016-03-31 Mci (Mirror Controls International) Netherlands B.V. Motion mechanism, exterior mirror device and vehicle
CN105667404A (en) * 2015-03-13 2016-06-15 东莞皓永汽车配件有限公司 Automobile outside rear-view mirror adjusting device

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Publication number Priority date Publication date Assignee Title
JPS58136536A (en) * 1982-02-08 1983-08-13 Ichikoh Ind Ltd Electric motor driven remotely controlled mirror
KR960017114U (en) * 1994-11-22 1996-06-17 유기설 Electric adjusting device for car side mirror
KR200215917Y1 (en) * 2000-09-26 2001-03-15 최정곤 Automatic adjustment device of inclination angle of automobile side miller
KR20050060207A (en) * 2003-12-16 2005-06-22 한국프로큅인터내셔널(주) Mechanism for adjusting the mirror of automotive outerside mirror assembly
KR200407216Y1 (en) * 2005-11-17 2006-01-25 주식회사 액트로닉스 Apparatus adjusting the angle of inclination of side mirror for automobile
KR100787696B1 (en) * 2006-12-20 2007-12-21 주식회사 쉐프네커 풍정 Side mirror with apparatus for detecting position

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Publication number Priority date Publication date Assignee Title
JPS58136536A (en) * 1982-02-08 1983-08-13 Ichikoh Ind Ltd Electric motor driven remotely controlled mirror
KR960017114U (en) * 1994-11-22 1996-06-17 유기설 Electric adjusting device for car side mirror
KR200215917Y1 (en) * 2000-09-26 2001-03-15 최정곤 Automatic adjustment device of inclination angle of automobile side miller
KR20050060207A (en) * 2003-12-16 2005-06-22 한국프로큅인터내셔널(주) Mechanism for adjusting the mirror of automotive outerside mirror assembly
KR200407216Y1 (en) * 2005-11-17 2006-01-25 주식회사 액트로닉스 Apparatus adjusting the angle of inclination of side mirror for automobile
KR100787696B1 (en) * 2006-12-20 2007-12-21 주식회사 쉐프네커 풍정 Side mirror with apparatus for detecting position

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016048140A1 (en) * 2014-09-22 2016-03-31 Mci (Mirror Controls International) Netherlands B.V. Motion mechanism, exterior mirror device and vehicle
NL2013509B1 (en) * 2014-09-22 2016-09-29 MCI (Mirror Controls International) Netherlands B V Movement mechanism, exterior mirror device and vehicle.
CN105667404A (en) * 2015-03-13 2016-06-15 东莞皓永汽车配件有限公司 Automobile outside rear-view mirror adjusting device
CN105667404B (en) * 2015-03-13 2018-05-08 东莞皓永汽车配件有限公司 Automobile using outside rear-view mirror adjusting apparatus

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