JP2011179593A - Power transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce the overall height of a power transmission device to which power can be input from two input elements and which outputs when power is input from either of the input elements. <P>SOLUTION: The power transmission device includes: a sun gear 31 arranged rotationally around its own axial center; a ring gear 32 arranged rotationally around the axial center of the sun gear; a planetary gear which meshes with the sun gear and the ring gear respectively, can rotate around its own axial center and revolve around the axial center the sun gear, and is driven according to selective rotation of either of the sun gear and the ring gear; and a transmission mechanism 50 transmitting power generated by rotation around an axis to the sun gear or the ring gear when rotation around the axis crossing the axial center of the sun gear at right angles substantially in projection to a plane passing the axial center of the sun gear is converted into rotation around the axial center of the sun gear. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a power transmission device in which power can be input from two input elements, and output is performed when power is input from one of the input elements.

  Conventionally, as a power transmission device capable of inputting power from two input elements and outputting when power is input from either one of the input elements, automatic focus adjustment by an ultrasonic motor, A technique related to a lens barrel of a camera capable of manual focus adjustment by manual operation is known (see, for example, Patent Document 1). In this lens barrel, an intermediate gear member is interposed between a drive member that is rotated by an ultrasonic motor and an operation member that is rotated by manual operation. The intermediate gear member is a planetary gear, the drive member is a ring gear, and an operation member. The planetary gear mechanism is configured with the sun gear. The carrier of the intermediate gear member is connected to a lens driving cylinder that is a power transmission target.

  In the lens barrel configured as described above, regardless of whether the ultrasonic motor is driven or the operation member is rotated, the intermediate gear member is revolved and the lens drive cylinder is rotated via the carrier. Thus, two operations can be performed without performing a switch switching operation.

  By the way, in order to regulate the rotation of the other member while rotating the drive member or the operation member to revolve the intermediate gear member, in Patent Document 1, an ultrasonic motor is used as follows. Yes. That is, the engaging member that can be engaged with the operating member is disposed on the non-rotating member, and the ultrasonic gear is driven in a state where the engaging member is engaged with the operating member, whereby the intermediate gear is rotated by the rotation of the driving member. Revolve the member. On the other hand, when the operating member is rotated, the frictional force generated between the stator and the rotor in the non-energized ultrasonic motor is used to restrict the rotation of the driving member. However, according to such a configuration, what can be applied as an actuator is limited to an ultrasonic motor having a large rotational load torque. Even with such a configuration, when the load applied to the carrier increases, the intermediate gear member does not revolve, but rotates and the drive member rotates, making it difficult to rotate the lens drive mirror. It is also possible to become.

JP-A-10-115760

  Further, in such a power transmission device, in order to input the driving force of the ultrasonic motor to the planetary gear mechanism, both of them are adjusted so that the axis of the driving shaft of the ultrasonic motor matches the axis of the planetary gear mechanism. Since the power transmission device is disposed, the height of the entire power transmission device is increased, and there is a problem that it is difficult to mount on the small lens.

  This invention is made | formed in view of the said situation, Comprising: It aims at providing the power transmission device which can suppress the height of the whole apparatus.

  In order to achieve the above object, a power transmission device according to the present invention is provided with a first gear member rotatably disposed about its own axis, and rotatably disposed about the axis of the first gear member. The second gear member and the first and second gear members meshed with each other, and can be rotated around its own axis and revolved around the axis of the first gear member, An intermediate gear member that is driven in accordance with an alternative rotation of one of the first and second gear members, and the first gear member when projected onto a plane that passes through the axis of the first gear member. By converting the rotation about the axis substantially orthogonal to the axis to the rotation about the axis of the first gear member, the power generated by the rotation about the axis is generated by any of the first and second gear members. And transmission means for transmitting to either of them.

  In the power transmission device according to the present invention, in the above invention, the transmission means has a gear tooth inclined with respect to its own axis, and is arranged to be rotatable around the axis. The gear member has gear teeth inclined with respect to its own axis, meshes with the first inclined gear member, and is disposed so as to be rotatable about an axis parallel to the axis of the first gear member. And a second inclined gear member.

  The power transmission device according to the present invention is the worm wheel according to the above invention, wherein the first inclined gear member is a worm having screw teeth, and the second inclined gear member has inclined teeth that can mesh with the screw teeth. Or it is a bevel gear.

  In the power transmission device according to the present invention, in the above invention, the first gear member has a gear shaft, and the second inclined gear member is fixed to the gear shaft.

  In the power transmission device according to the present invention, in the above invention, the second inclined gear member has a gear shaft, the transmission means is fixed to the gear shaft of the second inclined gear member, and the second gear. A third gear member that meshes with the member is further included.

  The power transmission device according to the present invention is characterized in that, in the above-described invention, the power transmission device further includes power generation means for generating power transmitted by the transmission means.

  The power transmission device according to the present invention is characterized in that, in the above invention, the power generation means is an actuator having the shaft as a drive shaft.

  According to the present invention, the power generated around the axis substantially orthogonal to the axis of the first gear member when projected onto a plane passing through the axis of the first gear member is transmitted by the transmission means to the first gear member. The rotation is converted to rotation around the axis and then transmitted to the first or second gear member. Therefore, the actuator can be arranged in such a direction that the axis of the drive shaft coincides with such a shaft. That is, it is not necessary to dispose the actuator so that the axis of the drive shaft coincides with the axis of the first gear member, so that the height of the entire power transmission device can be suppressed.

FIG. 1 is a perspective view conceptually showing the power transmission apparatus according to Embodiment 1 of the present invention. FIG. 2A is a front view showing the power transmission device of FIG. 1. FIG. 2B is a top view showing the power transmission device of FIG. 1. FIG. 3 is a perspective view showing a main part of the power transmission device of FIG. FIG. 4 is a perspective view showing a part of the power transmission device of FIG. FIG. 5 is a cross-sectional view taken along line AA in FIG. 2A. 6 is a cross-sectional view taken along line BB in FIG. 2B. 7 is a cross-sectional view taken along the line CC of FIG. 2B. 8 is a cross-sectional view taken along the line DD of FIG. 2B. FIG. 9 is a perspective view showing a power transmission apparatus according to Embodiment 2 of the present invention. FIG. 10 is a perspective view showing a main part of the power transmission device of FIG. FIG. 11 is a top view showing a main part of the power transmission device of FIG. 12 is a partial cross-sectional view taken along the line EE of FIG. 13 is a cross-sectional view taken along line FF in FIG.

  Exemplary embodiments of a power transmission device according to the present invention will be described below in detail with reference to the accompanying drawings.

(Embodiment 1)
FIG. 1 shows a power transmission apparatus according to Embodiment 1 of the present invention. This power transmission device 1 enables automatic focus adjustment by an actuator that generates power and manual focus adjustment by a manual operation in a lens barrel having a so-called autofocus function. Any actuator that generates a rotational driving force, such as a DC (direct current) motor, a stepping motor, or an ultrasonic motor, may be applied as the actuator. In the first embodiment, a DC motor is used. .

As shown in FIGS. 2A and 2B, the power transmission device 1 includes a gear case 10 and a DC motor 20.
The gear case 10 includes a first cover member 11 and a second cover member 12. Each of the cover members 11 and 12 has a box shape having a concave portion, and a storage space such as a gear is formed by facing each other. In addition, the outer shape of the gear case 10 is molded in an arc shape in accordance with the shapes of the lens driving cylinder LD and the manual focus ring MR. Furthermore, a part of the gear case 10 is provided with an insertion hole or a notch, and a part of the gear accommodated in the gear case 10 protrudes outside the gear case 10 from the insertion hole or the like. It is arranged.

  The DC motor 20 is attached to the gear case 10 via the motor fixing plate 13. Further, the DC motor 20 includes a drive shaft 21. The drive shaft 21 is a portion that is rotationally driven when the DC motor 20 is driven, and protrudes from the center of one end face of the DC motor 20 main body portion. The drive shaft 21 passes through a through hole 13 a formed in the motor fixing plate 13. Such a DC motor 20 is arranged such that when the shaft center of the drive shaft 21 is projected onto a plane passing through the shaft center of the sun gear shaft 31b, both shaft centers are in a substantially perpendicular relationship.

  As shown in FIG. 3, the power transmission device 1 includes a planetary gear mechanism 30, an output gear unit 40, a transmission mechanism 50, a manual input unit 60, a clutch unit 70, and a brake unit 80. Yes.

  As shown in FIGS. 4 and 5, the planetary gear mechanism 30 includes a sun gear (first gear member) 31, a ring gear (second gear member) 32, and a planetary gear (intermediate gear member) 33. The sun gear 31 is a spur gear having a gear portion 31a on the outer peripheral portion. The ring gear 32 is a cylindrical gear having gear portions 32a and 32b on both the outer peripheral portion and the inner peripheral portion, and is arranged so that its axis coincides with the sun gear shaft 31b. The planetary gear 33 is a spur gear having a gear portion 33 a on the outer peripheral portion, and three planetary gears 33 are arranged inside the ring gear 31 and around the sun gear 31. Each planetary gear 33 meshes with the sun gear 31 and the ring gear 32 via a gear portion 33 a, and each planetary gear 33 can rotate around its own axis and can revolve around the axis of the sun gear 31.

  As shown in FIG. 6, the output gear unit 40 includes a support plate 41, a support portion 42 that protrudes from the support plate 41 and penetrates the inner periphery of the planetary gear 33, and rotatably supports the planetary gear 33. The output gear 43 is formed. These support board 41, the support part 42, and the output gear 43 are integrally molded. Such an output gear unit 40 is disposed so as to be rotatable around the axis of the sun gear shaft 31b, and rotates following the revolving motion of the planetary gear 33. The output gear 43 is disposed so as to protrude outward through the insertion hole 14 of the second cover member 12, and transmits the power generated by the rotation of the output gear unit 40 to the lens driving cylinder LD.

  As shown in FIGS. 3 and 6, the transmission mechanism 50 converts the driving force output from the DC motor 20 into the sun gear 31 by converting the direction of the rotation axis thereof to be parallel to the axis of the sun gear 31. It has a worm (first inclined gear member) 51 and a worm wheel (second inclined gear member) 52. The worm 51 is a screw tooth gear having a gear portion 51 a forming a screw tooth on the outer peripheral portion, and is fixed to the drive shaft 21 of the DC motor 20 and rotates around the axis of the drive shaft 21. On the other hand, the worm wheel 52 is a helical gear (an oblique gear) having a gear portion 52a that can mesh with the worm 51 on the outer peripheral portion, and is fixed to the sun gear shaft 31b and rotates about the axis of the sun gear shaft 31b. Further, the worm 51 and the worm wheel 52 are disposed so that the gear portions 51a and 52a mesh with each other.

  As shown in FIGS. 3 and 7, the manual input unit 60 includes a manual input gear 61, a manual transmission gear 62, and a protrusion 63. The manual input gear 61 and the manual transmission gear 62 are gears in which spur teeth are formed on the outer peripheral portion, and are integrally molded together with the projecting portion 63 so that the shaft centers are aligned. A concave portion 64 is formed at the center of the manual input gear 61. In such a manual input unit 60, the convex portion 15 formed in the first cover member 11 is fitted into the concave portion 64, and the protruding portion 63 is fitted into the insertion hole 16 provided in the second cover member 12. Therefore, it is positioned so as to be rotatable around the axis. Further, a part of the outer peripheral portion of the manual input gear 61 protrudes outward from a notch portion 17 provided in the first cover member 11, and this protruding portion is connected to the gear portion MRG and the tooth of the manual focus ring MR. Match. On the other hand, the manual transmission gear 62 meshes with a first clutch gear 71 described later.

  As shown in FIGS. 3, 6, and 7, the clutch unit 70 includes a first clutch gear 71 and a second clutch gear 72. The first clutch gear 71 and the second clutch gear 72 are spur gears having a gear portion on the outer peripheral portion. A clutch plate 73 is fixed to the first clutch gear 71, and a boss portion 72 a that contacts the clutch plate 73 is formed on the second clutch gear 72. The first clutch gear 71 and the second clutch gear 72 are supported by a clutch shaft 74 so as to be rotatable around an axis. Further, the first clutch gear 71 meshes with the manual transmission gear 62 and also meshes with a brake gear 81 described later. On the other hand, the second clutch gear 72 meshes with the ring gear 32.

  Both ends of the clutch shaft 74 are fitted and positioned in a recess 18a formed in the first cover member 11 and a hole 18b formed in the second cover member 12, respectively. Further, an E-ring (E-type retaining ring) 75 is attached to the clutch shaft 74. Further, a flange portion 74 a is provided in the vicinity of the longitudinal end portion of the clutch shaft 74. A washer 76 and a compressed pressure spring 77 are interposed between the flange portion 74a and the second clutch gear 72. The first clutch gear 71, the second clutch gear 72, and the clutch plate 73 are clamped by the E ring 75, the pressing spring 77, and the flange portion 74a, and are in a pressure contact state.

  As shown in FIG. 8, the brake unit 80 includes a brake gear 81 and a brake shaft 82 that supports the brake gear 81 so as to be rotatable about its axis. The brake gear 81 is a spur gear having a gear portion on the outer peripheral portion, and meshes with the first clutch gear 71. Further, both end portions of the brake shaft 82 are respectively fitted and positioned in a concave portion 19 a formed in the first cover member 11 and a hole portion 19 b formed in the second cover member 12. Further, an E ring 83 is attached to the brake shaft 82.

  A boss portion 81 a that contacts the washer 84 is formed on one end surface (the upper side in the drawing) of the brake gear 81, and a boss portion that contacts the washer 85 on the other end surface (the lower side in the drawing) of the brake gear 81. 81b is formed. Further, a flange portion 82a is provided in the vicinity of the longitudinal end portion of the brake shaft 82, and a compressed pressure spring 86 is interposed between the flange portion 82a and the washer 85. The washer 84, the brake gear 81, and the washer 85 are sandwiched between the E ring 83, the pressing spring 86, and the flange portion 82a, and are in a pressure contact state.

  In the power transmission device 1 configured as described above, for example, as shown in FIG. 1, the manual input gear 61 is engaged with a gear portion MRG provided on the inner peripheral surface of the manual focus ring MR, while the output gear 43 is driven by a lens. The lens barrel is used by being attached to a gear portion LDG provided on the inner peripheral surface of the tube LD.

  Now, when the DC motor 20 is driven in this lens barrel, the driving force is input to the sun gear 31 via the worm 51 and the worm wheel 52, and the sun gear 31 rotates in one direction. At this time, in the power transmission device 1, the boss portion 72 a of the second clutch gear 72 is in pressure contact with the clutch plate 73 by the pressing spring 77. Therefore, the relative rotation of the second clutch gear 72 with respect to the first clutch gear 71 is restricted by the frictional force acting between the second clutch gear 72 and the clutch plate 73. On the other hand, the rotation of the brake gear 81 is also restricted by frictional forces generated between the boss portion 81a and the washer 84 and between the boss portion 81b and the washer 85, respectively. Eventually, as the rotation of the first clutch gear 71 by the brake unit 80 is restricted, the rotation of the second clutch gear 72 is also restricted, so that the rotation of the ring gear 32 meshing with the second clutch gear 72 is also restricted. Thereby, all the rotational movement of the sun gear 31 is transmitted to the rotation and revolution movement of the planetary gear 33, and the lens drive cylinder LD is rotated by the rotation of the output gear unit 40 that follows the revolution movement of the planetary gear 33. Further, during this time, it is possible to avoid a situation in which the manual input unit 60 and the manual focus ring MR are rotated due to the rotation restriction on the first clutch gear 71.

  On the other hand, when performing manual focus adjustment, the manual input gear 61 is rotated by rotating the manual focus ring MR. At that time, a rotational force that overcomes the frictional force of the boss portions 81a and 81b due to the pressing force of the pressing spring 86 is applied to the manual focus ring MR from the outside. As a result, the ring gear 32 rotates via the first clutch gear 71 and the second clutch gear 72. Here, the axial center of the worm 51 and the axial center of the worm wheel 52 are orthogonal to each other on the projection plane, and the rotation of the sun gear 31 is restricted by the action of the worm 51 and the worm wheel 52. Therefore, all the rotational movement of the ring gear 32 is transmitted to the output gear 43 through the revolution movement of the planetary gear 33, and further the power is transmitted to the lens driving cylinder LD.

  Here, in a general power transmission device, a stopper mechanism is provided so that the lens driving mirror does not further rotate at both ends of the lens operating angle when the manual focus ring is rotated. For this reason, if the manual focus ring is rotated with a large force, a rotational force is generated in the gear inside the power transmission device even though the rotation of the lens drive cylinder is restricted, and there is no escape for the rotational force. The gears and peripheral mechanisms may be damaged. On the other hand, in the power transmission device 1 according to the first embodiment, in such a case, in other words, when the manual focus ring is rotated with a large force regardless of both ends of the operating angle of the lens, In this way, damage to gears and the like inside the power transmission device 1 is prevented. That is, the output gear unit 40 cannot rotate due to the rotation restriction with respect to the lens driving cylinder LD, and the sun gear 31 cannot rotate due to the action of the worm 51 and the worm wheel 52. Therefore, both the planetary gear 33 and the ring gear 32 are restricted from rotating. Yes. At this time, if the rotational force of the first clutch gear 71 meshed with the manual input unit 60 overcomes the frictional force between the boss portion 72a and the clutch plate 73, the first clutch gear 71 starts to idle. , Its rotational force can be released.

  As described above in detail, in the first embodiment, since the transmission mechanism 50 that converts the rotational axis direction of the driving force of the DC motor (actuator) 20 is provided, the shaft center of the driving shaft 21 is the center of the sun gear shaft 31b. The DC motor 20 can be arranged so that both axial centers are in a substantially perpendicular relationship when projected onto a plane passing through the axial center. As a result, the overall height of the power transmission device can be reduced as compared with a general DC motor arrangement in which the axis of the drive shaft 21 is aligned with the sun gear shaft 31b. As a result, the power transmission device can be easily mounted on the small lens.

Further, with the above configuration, since the rotation of the sun gear 31 is restricted by the transmission mechanism 50 while the DC motor 20 is not driven, the power from the manual input gear 61 is operated when the manual focus ring MR is operated. Can be reliably transmitted to the output gear 43. As described above, since the transmission mechanism 50 has the effect of restricting the rotation of the sun gear 31, an inexpensive DC motor or stepping motor with a low rotational load torque can be applied as the actuator, thereby reducing the manufacturing cost. It becomes possible.
Further, since the worm gear has a high reduction ratio, the backlash with respect to the reduction ratio can be reduced, and the power can be transmitted with high accuracy.

  In addition, in Embodiment 1, since the worm gear is used in the transmission mechanism 50, the meshing frequency can be made smaller than that of a normal spur gear, and the noise level can be made smaller than that of a general power transmission device. An effect is also obtained.

(Embodiment 2)
FIG. 9 is a diagram illustrating an appearance of the power transmission device according to the second embodiment of the present invention. The power transmission device 2 shown in FIG. 9 includes a gear case 130 including a first cover member 131 and a second cover member 132, and a DC motor 20 attached to the gear case 130 via a motor fixing plate 133.

  FIG. 10 is a diagram illustrating an internal state of the gear case 130 illustrated in FIG. 9. The power transmission device 2 includes a planetary gear mechanism 30, an output gear unit 40, a transmission mechanism 110 that transmits a driving force output from the DC motor 20 to the planetary gear mechanism 30, and a manual input unit 120. The DC motor 20 is arranged such that when the shaft center of the drive shaft 21 is projected onto a plane passing through the shaft center of the sun gear shaft 31b, both shaft centers are in a substantially perpendicular relationship.

  The planetary gear mechanism 30 includes a sun gear 31, a ring gear 32, and a planetary gear 33. Further, the output gear unit 40 rotates following the revolving motion of the planetary gear 33, and the output gear unit 40 is connected via an output gear 43 disposed so as to protrude from an insertion hole 131 a provided in the first cover member 131. Power is transmitted to the lens driving cylinder. The planetary gear mechanism 30 and the output gear unit 40 are configured in the same manner as in the first embodiment.

  As shown in FIGS. 10 to 12, the transmission mechanism 110 has a worm (first inclined gear member) 111, a worm wheel (second inclined gear member) 112, and a transmission gear (third gear member) 113. is doing. The worm 111 is a screw-tooth gear having a gear portion having screw teeth on the outer peripheral portion, and is fixed to the drive shaft 21 of the DC motor 20 and rotates around the axis of the drive shaft 21. The worm wheel 112 is a helical gear (an oblique gear) having a gear portion that can mesh with the worm 111 on the outer peripheral portion, and is disposed so as to be rotatable about its own axis. Further, the transmission gear 113 is a spur gear having a gear portion on the outer peripheral portion, and is fixed to the gear shaft 114 of the worm wheel 112 or integrally formed with the gear shaft 114 so as to be around the axis of the gear shaft 114. Rotate to. The worm 111, the worm wheel 112, and the transmission gear 113 are disposed so that the worm 111 and the worm wheel 112 mesh with each other, and the transmission gear 113 and the gear portion 32a of the ring gear 32 mesh with each other.

  As shown in FIG. 10, the manual input unit 120 includes a manual input gear 121 that is a spur gear having a gear portion on the outer peripheral portion, a first manual transmission gear 122 that meshes with the manual input gear 121, and the sun gear 31. And a second manual transmission gear 123 that meshes. As shown in FIG. 11, a part of the manual input gear 121 protrudes from the notch 132a provided in the second cover member 132 to the outside of the gear case 130, and is disposed so as to be rotatable around its own axis. Has been. Further, as shown in FIG. 13, the first manual transmission gear 122 and the second manual transmission gear 123 are integrally molded with their axes aligned, and are disposed rotatably around the axis. Yes. In order to shift the rotation input to the first manual gear 122, the outer diameter of the second manual transmission gear 123 is designed to be larger than the outer diameter of the first manual transmission gear 122.

  In the power transmission device 2 configured as described above, the manual input gear 121 meshes with the gear portion provided on the inner peripheral surface of the manual focus ring, while the output gear 43 is connected to the lens driving cylinder, as in the first embodiment. The lens barrel is used by being attached to a gear portion provided on the inner peripheral surface.

  When the DC motor 20 is driven in the lens barrel, the driving force is input to the ring gear 32 via the worm 111, the worm wheel 112, and the transmission gear 113. When a rotational force is generated in the ring gear 32, the planetary gear 33 meshed with the gear portion 32b on the inner peripheral portion of the ring gear 32 starts rotating and revolving, and the output gear unit 40 rotates following the revolving motion. . As a result, power is transmitted through the output gear 43, and the lens driving cylinder operates.

  On the other hand, when performing manual focus adjustment, the manual input gear 121 is rotated by rotating the manual focus ring. When the manual input gear 121 rotates, a rotational force is generated in the sun gear 31 via the first manual transmission gear 122 and the second manual transmission gear 123. When a rotational force is generated in the sun gear 31, the planetary gear 33 meshed with the sun gear 31 starts rotating and revolving, and the output gear unit 40 rotates following the revolving motion. At this time, the rotation of the ring gear 32 is restricted via the transmission gear 113 by the action of the worm 111 and the worm wheel 112. Therefore, all the rotational movement of the sun gear 31 is transmitted to the output gear 43 through the revolution movement of the planetary gear 33, and further the power is transmitted to the lens driving cylinder LD.

  As described above in detail, in the second embodiment, since the transmission mechanism 110 that converts the rotational axis direction of the driving force of the DC motor 20 is provided, the axis of the driving shaft 21 is changed to the axis of the sun gear shaft 31b. The DC motor 20 can be arranged so that both axial centers are positioned so as to be substantially orthogonal when projected onto a passing plane. Thereby, it becomes possible to suppress the height of the whole power transmission device. Since the rotation of the ring gear 32 is restricted by the transmission mechanism 110 while the DC motor 20 is not driven, the power from the manual input gear 121 is reliably output when the manual focus ring MR is operated. This can be transmitted to the gear 43. As described above, since the worm gear (worm 111 and worm wheel 112) of the transmission mechanism 110 has an effect of restricting the rotation of the ring gear 32, the degree of freedom in selecting a motor that can be applied as an actuator is increased, and the manufacturing cost can be reduced. Become. In addition, since the worm gear has a high reduction ratio, the backlash with respect to the reduction ratio can be reduced, and the power can be transmitted with high accuracy. Furthermore, also in the second embodiment, by using the worm gear in the transmission mechanism 110, the meshing frequency can be made smaller than that of a normal spur gear, and the noise level can be made smaller than that of a general power transmission device. can get.

  In Embodiments 1 and 2 of the present invention described above, a worm gear in which a worm and a worm wheel are combined is used as a transmission mechanism. However, as long as the gear has an inclined gear tooth with respect to its own axis. Any gear may be used in combination. For example, even if a spiral gear (screw gear) in which two helical gears having a torsion angle of 45 degrees are combined is used, the axis of the rotational power output from the actuator can be changed by approximately 90 degrees.

DESCRIPTION OF SYMBOLS 1, 2 Power transmission device 10 Gear case 11 1st cover member 12 2nd cover member 13 Motor fixed plate 20 DC (direct current) motor 21 Drive shaft 30 Planetary gear mechanism 31 Sun gear 32 Ring gear 33 Planetary gear 40 Output gear unit 41 Support board 42 Support Portion 43 Output gear 50 Transmission mechanism 51 Worm 52 Worm wheel 60 Manual input unit 61 Manual input gear 62 Manual transmission gear 63 Protrusion 70 Clutch unit 71 First clutch gear 72 Second clutch gear 73 Clutch plate 74 Clutch shaft 76 Washer 77 Press Spring 80 Brake unit 81 Brake gear 82 Brake shaft 83 E ring 84, 85 Washer 86 Pressing spring 110 Transmission mechanism 111 Worm 1 2 worm wheel 113 transmitting gear 114 gear shaft 120 manually input unit 121 manually input gear 122 first manual transmission gear 123 second manual transmission gear 130 gear case 131 first cover member 132 second cover member LD lens drive cylinder MR manual focus ring

Claims (7)

A first gear member rotatably disposed about its own axis;
A second gear member disposed rotatably about an axis of the first gear member;
The first and second gear members respectively mesh with each other, and are arranged so as to be able to rotate around their own axis and to revolve around the axis of the first gear member. An intermediate gear member that is driven by any one of the alternative rotations;
Converting rotation about an axis substantially orthogonal to the axis of the first gear member into rotation about the axis of the first gear member when projected onto a plane passing through the axis of the first gear member. Transmission means for transmitting power generated by rotation around the shaft to one of the first and second gear members;
A power transmission device comprising: The transmission means includes
A first inclined gear member having gear teeth inclined with respect to its own axis and arranged rotatably about said axis;
A gear tooth inclined with respect to its own axis, meshed with the first inclined gear member, and arranged to be rotatable about an axis parallel to the axis of the first gear member. An inclined gear member;
The power transmission device according to claim 1, comprising: The first inclined gear member is a worm having screw teeth;
The power transmission device according to claim 2, wherein the second inclined gear member is a worm wheel or an inclined gear having inclined teeth that can mesh with the screw teeth. The first gear member has a gear shaft;
The power transmission device according to claim 2 or 3, wherein the second inclined gear member is fixed to the gear shaft. The second inclined gear member has a gear shaft;
4. The power according to claim 2, wherein the transmission unit further includes a third gear member fixed to a gear shaft of the second inclined gear member and meshing with the second gear member. Transmission device.   The power transmission device according to any one of claims 1 to 5, further comprising power generation means for generating power transmitted by the transmission means.   The power transmission device according to claim 6, wherein the power generation means is an actuator having the shaft as a drive shaft.

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