JP2024068448A - Power transmission clutch structure - Google Patents

Abstract

[Problem] To provide a power transmission clutch structure capable of cutting off transmission of rotational force to a first rotating shaft according to the rotation angle of the drive shaft. [Solution] The power transmission clutch structure 100 includes a drive shaft 15 that is rotationally driven by an actuator (drive motor 11), a first rotating shaft 21 and a second rotating shaft 22 that each rotate with the rotation of the drive shaft 15, and a clutch mechanism that switches between a state in which rotational force is transmitted from the drive shaft 15 to the first rotating shaft 21 and a state in which it is not transmitted, and in the process in which the drive shaft 15 rotates in one direction, the clutch mechanism is in a drive transmission state in which the rotational force of the drive shaft 15 is transmitted to the first rotating shaft 21 when the rotation angle of the drive shaft 15 is within a specific range, and is in a drive cut-off state in which the rotational force of the drive shaft 15 is not transmitted to the first rotating shaft 21 when the rotation angle is outside the specific range, and the second rotating shaft 22 can rotate with the rotation of the drive shaft 15 both when the clutch mechanism is in the drive transmission state and when the clutch mechanism is in the drive cut-off state. [Selected Figure] Figure 2

Description

The present invention relates to a power transmission clutch structure.

Patent Document 1 describes a power transmission clutch structure (a vehicle drive device in the same document) that includes an electric motor (actuator), a clutch, and a solenoid pin that can be brought into and out of contact with the outer circumferential surface of the clutch. The outer circumferential surface of the clutch is formed with a guide groove having a guide surface that intersects with the rotational direction of the clutch, an introduction groove that introduces the solenoid pin into the guide groove, and a release groove. When the electric motor rotates, the solenoid pin moves sequentially from the introduction groove to the guide groove and the release groove, thereby moving the clutch and disengaging the clutch from the reduction mechanism.

JP 2019-138425 A

The inventors of the present application have recognized that there is a need for a structure in a mechanism that transmits the rotational force of a drive shaft driven by an actuator to a first rotating shaft and a second rotating shaft, which is capable of blocking the transmission of the rotational force to the first rotating shaft depending on the rotation angle of the drive shaft.

The present invention was made in consideration of the above problems, and provides a power transmission clutch structure that can interrupt the transmission of rotational force to the first rotating shaft depending on the rotation angle of the drive shaft.

According to the present invention, there is provided a drive shaft that is rotationally driven by an actuator;
a first rotating shaft and a second rotating shaft which rotate in association with the rotation of the drive shaft;
a clutch mechanism that switches between a state in which a rotational force is transmitted from the drive shaft to the first rotation shaft and a state in which a rotational force is not transmitted;
Equipped with
When the drive shaft rotates in one direction, the clutch mechanism is in a drive transmission state in which the rotational force of the drive shaft is transmitted to the first rotating shaft when the rotation angle of the drive shaft is within a specific range, and is in a drive interruption state in which the rotational force of the drive shaft is not transmitted to the first rotating shaft when the rotation angle of the drive shaft is outside the specific range,
A power transmission clutch structure is provided in which the second rotating shaft can rotate in conjunction with the rotation of the drive shaft both when the clutch mechanism is in the drive transmission state and when the clutch mechanism is in the drive cut-off state while the drive shaft rotates in the one direction.

According to the present invention, it is possible to cut off the transmission of rotational force to the first rotating shaft depending on the rotation angle of the drive shaft.

1 is a perspective view of a power transmission clutch structure according to an embodiment; 1 is a perspective view showing an internal structure of a power transmission clutch structure according to an embodiment of the present invention; 1 is a perspective view showing a portion of the internal structure of a power transmission clutch structure according to an embodiment of the present invention; 1 is a perspective view showing a portion of the internal structure of a power transmission clutch structure according to an embodiment of the present invention; 1 is a plan view showing a portion of the internal structure of a power transmission clutch structure according to an embodiment, illustrating an initial state before the actuator starts to operate. 1A to 1C are plan views showing a portion of the internal structure of the power transmission clutch structure according to the embodiment, illustrating intermediate states at the start and end of the operation of the actuator. 1 is a plan view showing a portion of the internal structure of the power transmission clutch structure according to the embodiment, illustrating a state at the end of the operation of the actuator. FIG. FIG. 2 is a plan view of an engaged member in the power transmission clutch structure according to the embodiment. FIG. 2 is a plan view of a guide member in the power transmission clutch structure according to the embodiment. FIG. 2 is a schematic plan view for explaining the operation of the power transmission clutch structure according to the embodiment, showing an initial state before the actuator starts to operate. 5A to 5C are schematic plan views for explaining the operation of the power transmission clutch structure according to the embodiment, showing intermediate states at the start and end of the operation of the actuator. 5 is a schematic plan view for explaining the operation of the power transmission clutch structure according to the embodiment, showing a state at the end of the operation of the actuator. FIG. 1 is a perspective view showing an example in which the power transmission clutch structure according to the embodiment is used for deploying a deployable structure, in which the deployable structure is in a folded, stored state. FIG. 1 is a perspective view showing an example in which the power transmission clutch structure according to the embodiment is used for deploying a deployable structure, in which the deployable structure is partially deployed. FIG. 1 is a perspective view showing an example in which the power transmission clutch structure according to the embodiment is used for deploying a deployable structure, in which the deployable structure is deployed. FIG. 1 is a plan view showing an example in which the power transmission clutch structure according to the embodiment is used for deploying a deployable structure, in which the deployable structure is in a folded, stored state. FIG. 1 is a plan view showing an example in which the power transmission clutch structure according to the embodiment is used for deploying a deployable structure, in which the deployable structure is partially deployed. FIG. 1 is a plan view showing an example in which the power transmission clutch structure according to the embodiment is used for deploying a deployable structure, in a deployed state. FIG.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings. In all the drawings, the same components are denoted by the same reference numerals, and the description thereof will be omitted as appropriate.
1 and 2 are perspective views of a power transmission clutch structure 100 according to an embodiment, and in FIG. 2, the housing 60 is omitted to show the internal structure of the power transmission clutch structure 100.
In the following description, for ease of explanation, the upper side in FIG. 1 and the lower side in FIG. 2 are regarded as the upper side and the lower side as the lower side.

As shown in Figures 1 and 2, the power transmission clutch structure 100 of this embodiment includes a drive shaft 15 that is rotated by an actuator (in this embodiment, a drive motor 11), a first rotating shaft 21 and a second rotating shaft 22 that each rotate in conjunction with the rotation of the drive shaft 15, and a clutch mechanism that switches between a state in which rotational force is transmitted from the drive shaft 15 to the first rotating shaft 21 and a state in which it is not transmitted.
When the drive shaft 15 rotates in one direction, the clutch mechanism enters a drive transmission state in which the rotational force of the drive shaft 15 is transmitted to the first rotating shaft 21 when the rotational angle of the drive shaft 15 is within a specific range, and enters a drive interruption state in which the rotational force of the drive shaft 15 is not transmitted to the first rotating shaft 21 when the rotational angle of the drive shaft 15 is outside the specific range.
On the other hand, while the drive shaft 15 rotates in the above-mentioned one direction, the second rotating shaft 22 can rotate in conjunction with the rotation of the drive shaft 15 both when the clutch mechanism is in the drive transmission state and when the drive interruption state.

According to this embodiment, it is possible to cut off the transmission of rotational force from the drive motor 11 to the first rotating shaft 21 depending on the rotation angle of the drive shaft 15. As described below, the power transmission clutch structure 100 can be used, for example, to deploy a deployable structure 200 such as a solar panel paddle or an antenna in outer space, but it can also be used on the ground, not limited to outer space.

In this embodiment, the second rotating shaft 22 is always rotating while the drive shaft 15 rotates in the above-mentioned direction. This makes it possible to selectively cut off the transmission of rotational force from the drive motor 11 to only the first rotating shaft 21 out of the first rotating shaft 21 and the second rotating shaft 22, depending on the rotation angle of the drive shaft 15.

In this embodiment, the clutch mechanism is in a drive-disconnecting state at the beginning and end of the process in which the drive shaft 15 rotates in one direction, and is in a drive-transmitting state at an intermediate period between the beginning and end.
For example, when the power transmission clutch structure 100 is used for deploying the deployable structure 200 as described below, the operation of the locking mechanism can be continued by the second rotating shaft 22 even after the deployment of the deployable structure 200 is completed by the first rotating shaft 21, and the operation of the locking mechanism can be continued by the second rotating shaft 22 even after the stowing of the deployable structure 200 is completed by the first rotating shaft 21. Furthermore, before the deployment of the deployable structure 200 is started by the first rotating shaft 21, the operation of the locking mechanism can be started by the second rotating shaft 22, and before the stowing of the deployable structure 200 is started by the first rotating shaft 21, the operation of the locking mechanism can be started by the second rotating shaft 22.
It should be noted that the present invention is not limited to this example, and the clutch mechanism may be in the drive cut-off state only at the beginning or end of the process in which the drive shaft 15 rotates in one direction.

This will be explained in more detail below.

As shown in Fig. 2, in this embodiment, the drive motor 11 as an actuator includes an output shaft 12 (Fig. 2, etc.). The power transmission clutch structure 100 includes a worm gear (worm 13 and worm wheel 14) that transmits the rotation of the output shaft 12 to the drive shaft 15, and a bevel gear (first bevel gear 16 and second bevel gear 17) that transmits the rotation of the drive shaft 15 to a second rotating shaft 22.
The axial direction of the output shaft 12 and the axial direction of the drive shaft 15 are perpendicular to each other.
The axial direction of the drive shaft 15 and the axial direction of the second rotating shaft 22 are perpendicular to each other.
The axial direction of the output shaft 12 and the axial direction of the second rotating shaft 22 are parallel to each other.

The worm 13 is provided integrally with the output shaft 12 around the outer periphery of the output shaft 12 , and the axial direction of the worm 13 coincides with the axial direction of the output shaft 12 .
The worm wheel 14 is provided integrally with the drive shaft 15 around the outer periphery of the drive shaft 15, and the axial direction of the worm wheel 14 coincides with the axial direction of the drive shaft 15. The worm wheel 14 is provided, for example, on the lower end of the drive shaft 15.
The first bevel gear 16 is provided integrally with the drive shaft 15 around the outer periphery of the drive shaft 15, and the axial direction of the first bevel gear 16 coincides with the axial direction of the drive shaft 15. The first bevel gear 16 is disposed, for example, above the worm wheel 14.
The second bevel gear 17 is provided integrally with the second rotating shaft 22 on the outer periphery of the second rotating shaft 22, and the axial direction of the second bevel gear 17 coincides with the axial direction of the second rotating shaft 22. The second bevel gear 17 is provided, for example, at one end of the second rotating shaft 22.

In the present embodiment, the first rotating shaft 21 is disposed on an extension of the drive shaft 15 .
Therefore, the axial direction of the first rotating shaft 21 and the axial direction of the second rotating shaft 22 intersect (more specifically, are perpendicular to) each other. Therefore, the rotational force of the drive motor 11 can be transmitted to the first rotating shaft 21 and the second rotating shaft 22, which are set in different axial directions, and the transmission of the rotational force from the drive motor 11 to the first rotating shaft 21 can be cut off depending on the rotation angle of the drive shaft 15.

As shown in FIG. 1, the power transmission clutch structure 100 includes a housing 60 that houses a clutch mechanism.
The housing 60 includes, for example, a first housing 61, a second housing 62, and a third housing 63, arranged in this order from the bottom, and the first housing 61, the second housing 62, and the third housing 63 are integrated with one another.
The first housing 61 accommodates, for example, a portion of the output shaft 12 , the worm 13 , the worm wheel 14 , and a portion (lower portion) of the drive shaft 15 .
The second housing 62 accommodates, for example, another portion of the drive shaft 15 (the middle portion in the vertical direction), the first bevel gear 16, the second bevel gear 17, and a portion of the second rotating shaft 22 (the portion on one end side).
The third housing 63 accommodates, for example, the remaining portion (upper portion) of the drive shaft 15, as well as the pin 30, the swinging member 35, the fixed member 36, the biasing portion 37, the engaged member 40, and the guide path 51, which will be described later.

The output shaft 12 is provided, for example, penetrating the first housing 61, and is supported by a pair of bearing members 64 provided on the outer surface of the first housing 61. One of the bearing members 64 supports the tip end of the output shaft 12, and the other bearing member 64 supports the middle portion of the output shaft 12. The worm 13 is disposed between the pair of bearing members 64.
Although not explained here, both ends (upper end and lower end) of the drive shaft 15 are supported by a pair of bearing members provided in the housing 60 .
The second rotating shaft 22 is arranged from the inside to the outside of the second housing 62, and is supported by a bearing member 65 provided on the outer surface of the second housing 62 and an external bearing portion 67 arranged outside the second housing 62.
The first rotating shaft 21 is supported by, for example, a bearing member 66 provided on the upper surface of the third housing 63 .

The power transmission clutch structure 100 further includes a control cable 80 for transmitting control signals and supplying power to the drive motor 11. The drive motor 11 can rotate in one direction (and stop rotating) and rotate in the opposite direction (and stop rotating) according to the control signal.

Figures 3 and 4 show the first rotating shaft 21, pin 30, swinging member 35, biasing portion 37, engaged member 40, guide member 50, etc., which are provided in the power transmission clutch structure 100. Of these, Figure 3 shows these structures as viewed from diagonally below, and Figure 4 shows these structures as viewed from diagonally above.

As shown in Figures 3 and 4, the clutch mechanism has an engaging member (in this embodiment, pin 30) provided on the first rotating shaft 21, and an engaged member 40 that is integral with the drive shaft 15 and has an engaged portion (in this embodiment, recess 41) with which the engaging member (pin 30) can engage.
When the engaging member (pin 30) engages with the engaged portion (recess 41), the clutch mechanism is in a drive transmission state and the first rotating shaft 21 rotates along with the drive shaft 15, and when the engaging member (pin 30) disengages from the engaged portion (recess 41), the clutch mechanism is in a drive interruption state and the first rotating shaft 21 stops rotating.
Therefore, the drive transmission state and the drive cut-off state can be switched by engaging the pin 30 with the recess 41 of the engaged member 40 or disengaging the pin 30 from the recess 41 during the process of rotating the drive shaft 15 by the drive motor 11.
3 and 4 show a state in which the pin 30 is engaged with the recess 41.
The engaged member 40 is provided, for example, on the upper end of the drive shaft 15 .

In this embodiment, the engaged portion is a recess 41 that is formed at an end of the engaged member 40 in the radial direction of the drive shaft 15 and has a shape that opens outward in the radial direction. The engaging member (pin 30) moves outward in the radial direction relative to the recess 41 and disengages from the recess 41, thereby causing the clutch mechanism to enter a drive-disconnected state.
In this embodiment, the engaged member 40 is a disk-shaped member arranged coaxially with the drive shaft 15, and the engaged portion (recess 41) is formed at one location in the circumferential direction of the outer circumferential surface 43 of the engaged member 40. The outer circumferential surface 43 of the engaged member 40 is formed in a cylindrical shape except for the location where the recess 41 is formed.
In this embodiment, the engagement member is a cylindrical pin extending parallel to the axial direction of the drive shaft 15. In other words, the engagement member (pin 30) extends parallel to the axial direction of the first rotating shaft 21.
A portion of the pin 30 in the axial direction constitutes an engagement portion 31 that engages with the recess 41. In this embodiment, the lower end of the pin 30 constitutes the engagement portion 31.

As shown in FIG. 8 , the dimension of the recess 41 in the radial direction of the engaged member 40 (dimension D shown in FIG. 8 ) is larger than the radius of the pin 30 .
Therefore, the pin 30 stably engages with the recess 41, and when the pin 30 is engaged with the recess 41, the first rotating shaft 21 can rotate stably in conjunction with the rotation of the drive shaft 15 and the engaged member 40.
Here, the dimension D shown in FIG. 8 is the distance from an imaginary circle VO, which is a circumscribing circle of the engaged member 40 when viewed in the axial direction of the engaged member 40, to the deepest part of the recess 41.
More specifically, the dimension D is set to, for example, a dimension equivalent to the diameter (outer diameter) of the engagement portion 31 .

The recess 41 is formed in an arc shape that follows the outer peripheral surface of the pin 30. This allows the pin 30 to be stably positioned relative to the recess 41.

As shown in FIG. 8, both ends (ends 41a, 41b) of the recess 41 in the circumferential direction of the engaged member 40 are each formed with a chamfered shape. This allows the pin 30 to smoothly enter and engage with the recess 41 and to smoothly disengage from the recess 41 as the engaged member 40 rotates.

As shown in Figures 3 and 4, the clutch mechanism includes a guide member 50 having a guide path 51 that guides a portion of the pin 30 other than the portion that engages with the recess 41 (for example, the guided portion 32, which is the upper end of the pin 30).
As the pin 30 is guided by the guide path 51 , the pin 30 switches between a drive transmission state in which the pin 30 engages with the recess 41 and a drive interruption state in which the pin 30 disengages from the recess 41 .
In other words, by guiding the pin 30 along the guide path 51, switching between the drive transmission state and the drive interruption state can be achieved.

In this embodiment, the guide member 50 is a plate-shaped member, and the guide path 51 is a guide groove formed on one surface of the guide member 50, which guides one end of the pin 30 (the guided portion 32, which is the upper end of the pin 30).
Therefore, the pin 30 can be guided with a simple structure.

More specifically, as shown in Figures 3, 4 and 9, the guide member 50 has, for example, a flat main body portion 52 and a guide path forming wall 53 standing (standing downward in this embodiment) from one side (the lower surface in this embodiment) of the main body portion 52, and the area surrounded by the guide path forming wall 53 constitutes the guide path 51.
The width of the guide path 51 is set to be equal to the outer diameter of the pin 30 or slightly larger than the outer diameter of the pin 30 .

As shown in Figure 9, the guide passage 51 includes a main portion 51a extending in an arc shape coaxial with the drive shaft 15 (i.e., coaxial with the first rotating shaft 21), and end portions 51b, 51c connected to the end of the main portion 51a and extending from the end of the main portion 51a toward the radial outside of the drive shaft 15 (i.e., the radial outside of the first rotating shaft 21).
When one end (guided portion 32) of pin 30 is guided by main portion 51a, it is in a drive transmission state (i.e., the engaging portion 31 of pin 30 is engaged with recess 41), and when one end (guided portion 32) of pin 30 is guided by ends 51b, 51c, it is in a drive interruption state (i.e., the engaging portion 31 of pin 30 is disengaged from recess 41).
In this embodiment, an example is described in which the guide passage 51 has ends 51b, 51c extending radially outward at both ends of the main portion 51a, but the present invention is not limited to this example, and only one end of the main portion 51a may have an end extending radially outward.

In this embodiment, the angle range in which the main portion 51a extends in the circumferential direction of the drive shaft 15 (the circumferential direction of the first rotating shaft 21) is smaller than 360 degrees but close to 360 degrees, for example, about 350 degrees. That is, as an example, the angle range of the specific range is about 350 degrees, and the clutch mechanism is in a drive transmission state over an angle range of about 350 degrees. In this embodiment, the clutch mechanism is in a drive interruption state at the beginning and end of the process in which the drive shaft 15 rotates in one direction. As an example, the angle range in which the drive shaft 15 rotates in the beginning of the process in which the drive shaft 15 rotates in one direction is about 25 degrees, and the angle range in which the drive shaft 15 rotates in the end of the process in which the drive shaft 15 rotates in one direction is also about 25 degrees. In other words, as an example, when the drive shaft 15 rotates approximately 390 degrees in one direction, the drive is interrupted during the first 15 degrees of rotation and during the last 15 degrees of rotation, and the drive is transmitted during the remaining 350 degrees of rotation.
The specific range is not limited to this example.

As shown in Figure 9, among the directional components in the extension direction of the guide passage 51, the radial component of the drive shaft 15 (the radial component of the first rotating shaft 21) gradually increases from the main portion 51a to the ends 51b and 51c.
That is, in the main portion 51a, the directional component of the extension direction of the guide passage 51 is only the circumferential component of the drive shaft 15 (the circumferential component of the first rotating shaft 21), whereas from the main portion 51a toward the end portion 51b, the radial component of the drive shaft 15 (the radial component of the first rotating shaft 21) of the directional components of the extension direction of the guide passage 51 gradually increases. Similarly, from the main portion 51a toward the end portion 51c, the radial component of the drive shaft 15 (the radial component of the first rotating shaft 21) of the directional components of the extension direction of the guide passage 51 gradually increases.
This allows smooth movement of the pin 30 (engagement portion 31) from the main portion 51a to the end portion 51b, movement of the pin 30 (engagement portion 31) from the main portion 51a to the end portion 51c, movement of the pin 30 (engagement portion 31) from the end portion 51b to the main portion 51a, and movement of the pin 30 (engagement portion 31) from the end portion 51c to the main portion 51a.

More specifically, at least in the portion of the end portion 51b, 51c farthest from the main portion 51a, among the directional components in the extension direction of the end portion 51b, 51c, the radial component of the drive shaft 15 (the radial component of the first rotating shaft 21) is larger than the circumferential component of the drive shaft 15 (the circumferential component of the first rotating shaft 21).
Therefore, after the pin 30 (engagement portion 31) moves from the main portion 51a to the end portion 51b or the end portion 51c, the pin 30 can be moved radially outward quickly (in a short time) and removed from the recess 41. Also, when the pin 30 (engagement portion 31) starts to move from the end portion 51b or the end portion 51c toward the main portion 51a, the pin 30 can be moved radially inward quickly (in a short time). In other words, the pin 30 can also be inserted into the recess 41 quickly.

The clutch mechanism includes a biasing portion 37 that biases the pin 30 toward the radial inside of the drive shaft 15 (the radial inside of the first rotating shaft 21).
Therefore, in the process of the engaged member 40 rotating along with the drive shaft 15, the pin 30 (the engaging portion 31) can be moved radially inward according to the bias of the biasing portion 37 and can enter the recess 41. In addition, in the process of the engaged member 40 rotating along with the drive shaft 15, the pin 30 can be moved radially outward against the bias of the biasing portion 37 and can be removed from the recess 41.
The biasing portion 37 is formed of, for example, a tension type coil spring.

The clutch mechanism further includes a swing member 35 that is supported swingably relative to the first rotating shaft 21 by a swing shaft 35 b that is parallel to the first rotating shaft 21 at a position offset from the axis of the first rotating shaft 21 .
The pin 30 is provided at a portion of the swing member 35 that is spaced apart from the swing shaft 35b. The biasing portion 37 biases a portion of the swing member 35 that is closer to the pin 30 than the swing shaft 35b toward the radial inside of the drive shaft 15 (the radial inside of the first rotating shaft 21).
Therefore, when the pin 30 moves radially outward to leave the recess 41, the swinging member 35 swings against the bias of the biasing portion 37. Conversely, when the pin 30 moves radially inward to enter the recess 41, the swinging member 35 swings in accordance with the bias of the biasing portion 37.

In Figures 5 to 7, the guide member 50 and the engaged member 40 are shown by virtual lines (two-dot chain lines), and the pin 30, the swinging member 35, the fixed member 36, and the biasing portion 37 are shown by solid lines or dotted lines (hidden lines).

The swinging member 35 is, for example, a plate-like member, and is formed into a substantially rectangular shape in plan view.
The swing member 35 includes a plate-like main body 35a having a substantially rectangular planar shape, and a swing shaft 35b provided on the main body 35a. The swing shaft 35b protrudes upward from the main body 35a.

The clutch mechanism includes a fixed member 36 provided at the lower end of the first rotating shaft 21 .
The fixing member 36 includes a main body 36a having a substantially circular planar shape and a protruding portion 36b protruding radially outward from the main body 36a. The fixing member 36, including the main body 36a and the protruding portion 36b, is formed in a disk shape.
In a plan view of the main body portion 36a, the center of the main body portion 36a and the axis of the first rotating shaft 21 coincide with each other.
A swing shaft 35b is supported by the protruding portion 36b, so that the swing member 35 can swing in a horizontal plane with the swing shaft 35b as a fulcrum.
In the main body 35a of the swing member 35, the end opposite to the swing shaft 35b side constitutes a holding portion 35c that holds the pin 30. The holding portion 35c holds a held portion 33 that is a middle portion of the pin 30 in the up-down direction.

Here, as shown in Figures 5 to 7, in a plan view, the straight line (line segment) connecting the pivot shaft 35b and the center of the pin 30 always extends generally in the tangent direction of the outline of the engaged member 40.
3 and 4, one end of the urging portion 37 is fixed to the swinging member 35, and the other end of the urging portion 37 is fixed to the fixed member 36. More specifically, one end of the urging portion 37 is held by a urging portion holder protruding downward from the main body portion 36a, and the other end of the urging portion 37 is held by a urging portion holder protruding horizontally from the main body portion 35a. In a plan view, a holder 35c that holds the pin 30 is disposed between the swinging member 35, where the other end of the urging portion 37 is fixed, and the swing shaft 35b.
The direction in which the biasing portion 37 (via the oscillating member 35) pulls the pin 30 may be completely aligned with the radial direction of the first rotating shaft 21 (the radial direction of the drive shaft 15) but in this embodiment, the direction is shifted from the radial direction of the first rotating shaft 21 (the radial direction of the drive shaft 15).

The fixing member 36 is disposed above the engaged member 40 .
Below the fixed member 36 and above the engaged member 40, the biasing portion 37 and the swinging member 35 are each disposed horizontally.
The guide member 50 is disposed above the fixed member 36 .

The power transmission clutch structure 100 is configured as described above.

Next, the operation of the power transmission clutch structure 100 will be described with reference to FIGS. 5 to 7 and 10 to 12.
10 to 12, the components of the clutch mechanism are shown as an excerpt of the pin 30, the engaged member 40 having the recess 41, and the guide path 51, and the engaged member 40 and the guide path 51 are shown by virtual lines (dash lines).
Figures 5 and 10 show the same timing, Figures 6 and 11 show the same timing, and Figures 7 and 12 show the same timing. Note that Figures 3 and 4 also show the same timing as Figures 6 and 11.

In the initial state, for example, as shown in FIG. 10, the guided portion 32 of the pin 30 is located at the end 51b, and the engaging portion 31 of the pin 30 is disengaged from the recess 41. More specifically, as shown in FIG. 10, in a plan view, for example, the recess 41 is located at a position slightly shifted clockwise from the pin 30. Also, in this state, the engaging portion 31 of the pin 30 is in contact with the outer peripheral surface 43 of the engaged member 40. Therefore, although the pin 30 is biased radially inward by the biasing portion 37, the outer peripheral surface 43 restricts the pin 30 from moving radially inward.

When the output shaft 12 of the drive motor 11 starts to rotate in one direction from this state, the drive shaft 15 starts to rotate in one direction (for example, counterclockwise in a plan view) accordingly. Then, the engaged member 40 provided on the drive shaft 15 also starts to rotate counterclockwise together with the drive shaft 15.
When the drive shaft 15 rotates, the second rotating shaft 22 always rotates.
However, when the drive shaft 15 first starts to rotate, the clutch mechanism is in a drive-disconnected state, so that the first rotating shaft 21 is in a stopped state.
In the initial drive-disconnected state, the pin 30 is in contact with the outer circumferential surface 43 of the engaged member 40 due to the biasing force of the biasing portion 37 , and the outer circumferential surface 43 slides against the outer circumferential surface of the pin 30 .
When the engaged member 40 rotates counterclockwise and the recess 41 reaches the position of the pin 30, the pin 30, which is biased radially inward by the biasing portion 37, moves radially inward in accordance with the bias of the biasing portion 37 and enters the recess 41. In other words, the guided portion 32 of the pin 30 moves from the end portion 51b of the guide path 51 to the main portion 51a, and the engaging portion 31 of the pin 30 enters the recess 41.
When the engaging portion 31 enters the recess 41, the clutch mechanism transitions from a drive-disconnected state to a drive-transmitting state.

In the drive transmission state, the pin 30 is pushed and moved by the engaged member 40 while being guided by the main portion 51a, so that the pin 30 revolves around the axis of the first rotating shaft 21. Accordingly, the first rotating shaft 21 rotates. In other words, the first rotating shaft 21 rotates integrally with the drive shaft 15 (rotating counterclockwise in a plan view).
After the engagement portion 31 enters the recess 41, that is, after the transition from the drive-cutting state to the drive-transmitting state, the first rotating shaft 21 rotates together with the drive shaft 15 until the engagement portion 31 again disengages from the recess 41 and transitions to the drive-cutting state.
6 and 11 show a state in which the engaged member 40 and the pin 30 have been rotated approximately half a turn from the state shown in FIGS.

When the engaged member 40 and the pin 30 rotate about a half turn from the state shown in Fig. 6 and Fig. 11, the guided portion 32 moves from the main portion 51a to the end portion 51c, and the engaging portion 31 disengages from the recess 41, and the clutch mechanism transitions from the drive transmission state to the drive interruption state, as shown in Fig. 7 and Fig. 12. That is, the engaged member 40 tries to rotate the engaging portion 31 of the pin 30 along with the recess 41, but the guided portion 32 of the pin 30 moves from the main portion 51a to the end portion 51c, i.e., moves radially outward, and disengages from the recess 41. At this time, the engaging portion 31 of the pin 30 is pushed in the counterclockwise direction by the inner peripheral surface of the recess 41, but the guided portion 32 is guided by the guide path 51 and moves from the main portion 51a to the end portion 51c. That is, the pin 30 moves radially outward against the bias of the biasing portion 37. That is, the pin 30 is pushed outward in the radial direction by the inner circumferential surface of the recess 41 , and is also guided by the guide passage 51 to move outward in the radial direction.
As a result of the clutch mechanism shifting from the drive transmission state to the drive interruption state, the first rotating shaft 21 is again stopped, but the drive shaft 15, the engaged member 40, and the second rotating shaft 22 continue to rotate.
After the pin 30 is pushed radially outward by the recess 41, as shown in Figure 12, the pin 30 is in contact with the outer peripheral surface 43 of the engaged member 40 due to the biasing force of the biasing portion 37, and the outer peripheral surface 43 slides against the outer peripheral surface of the pin 30.
Thereafter, the drive shaft 15, the engaged member 40 and the second rotating shaft 22 rotate until the drive motor 11 stops rotating, and when the drive motor 11 stops rotating, the drive shaft 15, the engaged member 40 and the second rotating shaft 22 also stop rotating.
When the drive motor 11 is at a stop, as shown in FIG. 12, the recess 41 is located at a position slightly shifted counterclockwise from the pin 30 in plan view.
Therefore, in the case of this embodiment, between the time when the drive motor 11 starts to rotate in one direction and the time when the drive motor 11 stops rotating, the drive shaft 15 and the engaged member 40 rotate an angle exceeding 360 degrees (for example, approximately 390 degrees).
During the process in which the drive shaft 15 and the engaged member 40 rotate approximately 390 degrees, the clutch mechanism is in a drive-disconnected state while the drive shaft 15 and the engaged member 40 rotate approximately the first 25 degrees (initial period) and while the drive shaft 15 and the engaged member 40 rotate approximately the last 25 degrees (final period).
In the process in which the drive shaft 15 and the engaged member 40 rotate by approximately 390 degrees, the clutch mechanism is in a drive transmitting state in the intermediate period excluding the initial and final periods.

Note that, although the operation in which the guided portion 32 of the pin 30 moves from the end 51b via the main portion 51a to the end 51c has been described here, the reverse operation in which the guided portion 32 of the pin 30 moves from the end 51c via the main portion 51a to the end 51b can also be performed in a similar manner. However, during this reverse operation, the rotation directions (revolution directions) of the drive motor 11, drive shaft 15, engaged member 40, pin 30, first rotating shaft 21, and second rotating shaft 22 are each reversed.

Next, an example of using the power transmission clutch structure 100 according to this embodiment to deploy and store the deployable structure 200 will be described with reference to Figures 13 to 18.

13 to 18, the deployable structure 200 has a plurality of (e.g., nine) deployable blades 70. Each deployable blade 70 is formed in a flat plate parallel to the axial direction of the first rotating shaft 21, and is supported or fixed to the first rotating shaft 21 via a pair of upper and lower arms (an upper first arm 71 and a lower second arm 72).
The first arms 71 holding the respective deployment blades 70 are disposed at positions offset vertically from each other by approximately the thickness of each first arm 71. Similarly, the second arms 72 holding the respective deployment blades 70 are disposed at positions offset vertically from each other by approximately the thickness of each second arm 72.

In the stored state shown in Figures 13 and 16, the multiple deployment wings 70 are in close proximity to each other.
The multiple deployment blades 70 include, for example, a deployment blade 70a that rotates along with the first rotation shaft 21, a deployment blade 70b whose position relative to the housing 60 is fixed, and a deployment blade 70c that is located between the deployment blade 70a and the deployment blade 70b around the axis of the first rotation shaft 21. In this embodiment, the number of deployment blades 70c is seven.
The deployment blade 70 a is fixed to the first rotating shaft 21 via, for example, a first arm 71 and a second arm 72 , and rotates integrally with the first rotating shaft 21 around the axis of the first rotating shaft 21 .
The deployment blade 70b is fixed to the third housing 63, for example, via a first arm 71 and a second arm 72, and is supported on the first rotating shaft 21, so that its position relative to the third housing 63 remains unchanged regardless of the position of the deployment blade 70a (regardless of the deployment state of the deployable structure 200).
The deployment blade 70 c is pivotally supported on the first rotating shaft 21 via a first arm 71 and a second arm 72 .
13 and 16, the angular range in which the multiple deployment blades 70 exist around the first rotating shaft 21 is about 10 degrees. In other words, the angle between the deployment blade 70a and the deployment blade 70b is about 10 degrees.
In the deployed state shown in Figures 15 and 18, the deployment blade 70a moves to a position where it is in approximate surface contact with the deployment blade 70b, and the deployment blades 70a and 70b and the other deployment blades 70c are arranged at approximately equal angular intervals (i.e., approximately 45 degree intervals).
In the deployed state, for example, the locking claws of the first arm 71 and the second arm 72 holding one deployment blade 70 are locked to the first arm 71 and the second arm 72 holding the deployment blade 70 adjacent to the one deployment blade 70, thereby restricting the rotation angle between adjacent deployment blades 70 from increasing any further. As a result, the rotation angles between the deployment blades 70 are spaced at approximately equal angles. In other words, when the deployment blade 70a rotates from the position shown in Fig. 16 to the position shown in Fig. 18, the deployment blades 70c, which are the deployment blades 70 other than the deployment blades 70a and 70b, rotate in response to the rotation of the deployment blade 70a. However, since the upper limit of the rotation angle between adjacent deployment blades 70 is about 45 degrees, in the deployed state shown in Fig. 18, the rotation angles between the deployment blades 70 are spaced at approximately equal angles.

The deployable structure 200 further includes a lock lever 75 that locks (restrains so that the position of) the multiple deployment wings 70 in both the stowed state and the deployed state.
The lock lever 75 is fixed to the second rotating shaft 22. More specifically, one end of the lock lever 75 is fixed to the second rotating shaft 22, and the extension direction of the lock lever 75 is perpendicular to the axial direction of the second rotating shaft 22. Therefore, the lock lever 75 turns in association with the rotation of the second rotating shaft 22.
In the stored state shown in Figures 13 and 16, the tip of the lock lever 75 is in close proximity to or in contact with the deployment blade 70a, preventing the deployment blade 70a from moving in the deployment direction away from the deployment blade 70b.
In the deployed state shown in Figures 15 and 18, the tip of the lock lever 75 is in close proximity to or in contact with the deployment blade 70a, preventing the deployment blade 70a from moving in the retracting direction away from the deployment blade 70b.
Of the front and back surfaces of the deployment blades 70a, the surface (one surface) with which the tip of the lock lever 75 abuts or comes close to in the stored state and the surface (the other surface) with which the tip of the lock lever 75 abuts or comes close to in the deployed state are opposite surfaces. During the process of deploying the multiple deployment blades 70, the lock lever 75 rotates along a path that avoids interference with the deployment blades 70, and moves from a rotation angle at which the tip abuts or comes close to one surface of the deployment blades 70a to a rotation angle at which the tip abuts or comes close to the other surface of the deployment blades 70a.

The deployable structure 200 includes, for example, a support membrane (not shown) that is supported by the upper edges of the multiple deployment wings 70. The support membrane is in a folded state in the stored state, and unfolds as the multiple deployment wings 70 unfold, and spreads out in a plane that includes the upper edges of the multiple deployment wings 70 in the deployed state.
The support film supports, for example, a plurality of solar cells.

Next, an operation for changing the deployable structure 200 from the stored state to the deployed state will be described.
In the stored state shown in Figures 13 and 16, the power transmission clutch structure 100 is in the state shown in Figures 5 and 10. That is, the clutch mechanism is in a drive-disconnected state. When the drive motor 11 starts to rotate in one direction from this state, the drive shaft 15 and the second rotating shaft 22 start to rotate along with the rotation of the output shaft 12. This causes the lock lever 75 to start turning. In addition, the engaged member 40 also rotates along with the drive shaft 15 (counterclockwise in Figure 10).
Thereafter, the guided portion 32 of the pin 30 moves from the end portion 51b of the guide path 51 to the main portion 51a, and the engaging portion 31 of the pin 30 enters the recess 41 of the engaged member 40, causing the clutch mechanism to transition from a drive interruption state to a drive transmission state. Then, as the engaged member 40 rotates, the pin 30 begins to revolve around the axis of the first rotating shaft 21, and the first rotating shaft 21 begins to rotate integrally with the pin 30. As a result, the deployment blade 70a begins to move around the axis of the first rotating shaft 21 (counterclockwise in FIG. 16 ) in a direction away from the deployment blade 70b.
Thereafter, the guided portion 32 of the pin 30 moves from the main portion 51a to the end portion 51c of the guiding member 50, and the engaging portion 31 of the pin 30 disengages from the recess 41, causing the clutch mechanism to transition from the drive transmission state to the drive interruption state. Then, even if the engaged member 40 continues to rotate together with the drive shaft 15, the pin 30 stops revolving around the axis of the first rotating shaft 21, and the rotation of the first rotating shaft 21 stops. Therefore, the rotation of the deployment blade 70a around the axis of the first rotating shaft 21 also stops. However, since the second rotating shaft 22 continues to rotate together with the drive shaft 15, the pivoting operation of the lock lever 75 continues.
Thereafter, as shown in Figures 15 and 18, when the lock lever 75 rotates until it abuts or approaches the other surface of the deployment blade 70a, the rotation of the drive motor 11 stops and the rotation of the lock lever 75 also stops.
In this way, the deployable structure 200 is in the deployed state.

The operation for returning the deployable structure 200 from the deployed state to the stowed state is the reverse of the operation for returning the deployable structure 200 from the stowed state to the deployed state. In other words, the deployable structure 200 can be returned to the stowed state again by rotating the drive motor 11 in the opposite direction to the one direction described above, and stopping the rotation of the drive motor 11 at the timing when the lock lever 75 has rotated until it abuts or approaches the one surface of the deployment blade 70.

As described above, when the drive shaft 15 rotates in one direction, it rotates, for example, about 390 degrees, and the engaged member 40 also rotates about 390 degrees along with the drive shaft 15. However, as can be seen from a comparison between Fig. 13 and Fig. 15, the rotation angle of the lock lever 75 is less than 360 degrees, for example, about 315 degrees. In other words, the rotation speed (the number of rotations per unit time) of the drive shaft 15 and the rotation speed of the second rotating shaft 22 rotated by the rotational force transmitted from the drive shaft 15 to the second rotating shaft 22 via the first bevel gear 16 and the second bevel gear 17 are not necessarily in a one-to-one relationship, and in this embodiment, the number of teeth of the first bevel gear 16 and the second bevel gear 17 are set so that the rotation speed of the second rotating shaft 22 is smaller than the rotation speed of the drive shaft 15.
On the other hand, in the case of this embodiment, the relationship between the rotation angle of the drive shaft 15 in the drive transmission state and the rotation angle of the first rotating shaft 21 is substantially one to one. That is, when the guided portion 32 of the pin 30 moves from the end portion 51b to the main portion 51a, when it moves from the main portion 51a to the end portion 51c, when it moves from the end portion 51c to the main portion 51a, and when it moves from the main portion 51a to the end portion 51b, the rotation speed of the first rotating shaft 21 is smaller than the rotation speed of the drive shaft 15, but when the guided portion 32 is guided by the main portion 51a, the rotation speed of the first rotating shaft 21 matches the rotation speed of the drive shaft 15.

The present invention is not limited to the above-described embodiment, but includes various modifications, improvements, and other aspects as long as the object of the present invention is achieved.

For example, in the above example, the guide member 50 has an upright guide path forming wall 53, and the area surrounded by the guide path forming wall 53 forms the guide path 51. However, the present invention is not limited to this example, and the guide path 51 may be formed by a groove carved into one surface of the plate-shaped guide member 50.

Furthermore, the various components of the power transmission clutch structure 100 do not need to be independent entities, and it is acceptable for multiple components to be formed as a single member, for one component to be formed from multiple members, for one component to be part of another component, or for part of one component to overlap with part of another component, etc.

The present embodiment encompasses the following technical ideas.
(1) a drive shaft that is rotationally driven by an actuator;
a first rotating shaft and a second rotating shaft which rotate in association with the rotation of the drive shaft;
a clutch mechanism that switches between a state in which a rotational force is transmitted from the drive shaft to the first rotation shaft and a state in which a rotational force is not transmitted;
Equipped with
When the rotation angle of the drive shaft is within a specific range, the clutch mechanism is in a drive transmission state in which the rotation force of the drive shaft is transmitted to the first rotating shaft, and when the rotation angle of the drive shaft is outside the specific range, the clutch mechanism is in a drive interruption state in which the rotation force of the drive shaft is not transmitted to the first rotating shaft,
A power transmission clutch structure in which the second rotating shaft can rotate in conjunction with the rotation of the drive shaft both when the clutch mechanism is in the drive transmission state and when the clutch mechanism is in the drive interruption state while the drive shaft rotates in the one direction.
(2) A power transmission clutch structure as described in (1), wherein the second rotating shaft always rotates during the process in which the drive shaft rotates in the one direction.
(3) At the beginning and end of the process in which the drive shaft rotates in one direction, the clutch mechanism is in the drive interruption state,
The power transmission clutch structure according to (1) or (2), wherein the clutch mechanism is in the drive transmission state in an intermediate period between the initial period and the final period.
(4) The clutch mechanism includes:
an engagement member provided on the first rotating shaft;
an engaged member that is integral with the drive shaft and has an engaged portion with which the engaging member can engage;
having
When the engaging member is engaged with the engaged portion, the clutch mechanism is in the drive transmission state, and the first rotating shaft rotates together with the drive shaft,
A power transmission clutch structure described in any one of (1) to (3), wherein when the engaging member is disengaged from the engaged portion, the clutch mechanism is in the drive interruption state and the first rotating shaft stops rotating.
(5) The engaged portion is a recess formed at an end of the engaged member in a radial direction of the drive shaft and having a shape that is open outward in the radial direction,
The power transmission clutch structure according to claim 4, wherein the clutch mechanism is brought into the drive-disconnected state by the engaging member moving radially outward relative to the recess and disengaging from the recess.
(6) The engaged member is a disk-shaped member arranged coaxially with the drive shaft,
The power transmission clutch structure according to (5), wherein the engaged portion is formed on an outer peripheral surface of the engaged member.
(7) A power transmission clutch structure according to (6), wherein the first rotating shaft is disposed on an extension of the drive shaft.
(8) The engaging member is a cylindrical pin extending parallel to the axial direction of the drive shaft,
The power transmission clutch structure according to claim 7, wherein a portion of the pin in the axial direction is engaged with the recess.
(9) A power transmission clutch structure as described in (8), wherein the dimension of the recess in the radial direction of the engaged member is larger than the radius of the pin.
(10) A power transmission clutch structure as described in (9), wherein the recess is formed in an arc shape along the outer peripheral surface of the pin.
(11) A power transmission clutch structure according to claim (10), wherein both ends of the recess in the circumferential direction of the engaged member are formed into a chamfered shape.
(12) The clutch mechanism includes a guide member having a guide path that guides a portion of the pin other than a portion that engages with the recess,
A power transmission clutch structure according to any one of (8) to (11), wherein, during the process in which the pin is guided by the guide path, the power transmission state is switched between the pin engaging with the recess and the power interruption state in which the pin disengages from the recess.
(13) The guide member is a plate-shaped member,
The guide path is a guide groove formed on one surface of the guide member, and guides one end of the pin.
(14) The guide passage includes a main portion extending in an arc shape coaxial with the drive shaft, and an end portion connected to an end of the main portion and extending from the end of the main portion toward a radially outer side of the drive shaft,
The power transmission clutch structure according to claim 13, wherein the drive transmission state is when the one end of the pin is guided by the main portion, and the drive interruption state is when the one end of the pin is guided by the end portion.
(15) A power transmission clutch structure as described in (14), in which a radial component of the drive shaft among directional components of the extension direction of the guide passage gradually increases from the main portion toward the end portion.
(16) A power transmission clutch structure as described in (15), wherein, at least in the portion of the end farthest from the main portion, the radial component of the drive shaft among the directional components of the extension direction of the end is greater than the circumferential component of the drive shaft.
(17) A power transmission clutch structure described in any one of (8) to (12), wherein the clutch mechanism includes a biasing portion that biases the pin radially inwardly of the drive shaft.
(18) A power transmission clutch structure as described in (17) above, in which the biasing portion is constituted by a tension type coil spring.
(19) The clutch mechanism includes a swing member supported by a swing shaft parallel to the first rotating shaft at a position offset from an axis of the first rotating shaft so as to be swingable with respect to the first rotating shaft,
The pin is provided at a portion of the swing member that is spaced from the swing shaft,
The power transmission clutch structure according to (17) or (18), wherein the biasing portion biases a portion of the pivot member that is closer to the pin than the pivot shaft toward a radially inward direction of the drive shaft.
(20) The actuator includes an output shaft,
The power transmission clutch structure includes:
A worm gear that transmits rotation of the output shaft to the drive shaft;
a bevel gear that transmits rotation of the drive shaft to the second rotating shaft;
Equipped with
The axial direction of the output shaft and the axial direction of the drive shaft are perpendicular to each other,
The axial direction of the drive shaft and the axial direction of the second rotation shaft are perpendicular to each other,
The power transmission clutch structure according to any one of (1) to (19), wherein the axial direction of the output shaft and the axial direction of the second rotating shaft are parallel to each other.
In the above description, the term "power transmission clutch structure" can be read as "power transmission clutch device."

11 Drive motor (actuator)
12 Output shaft 13 Worm (worm gear)
14 Worm wheel (worm gear)
15 Drive shaft 16 First bevel gear (bevel gear)
17 Second bevel gear (bevel gear)
21 First rotating shaft 22 Second rotating shaft 30 Pin (engagement member)
31 Engagement portion (part of the pin in the axial direction)
32 Guided portion 33 Retained portion (a portion other than the portion of the pin that engages with the recess)
35 Swinging member 35a Main body (plate-shaped)
35b Oscillating shaft 35c Holding portion 36 Fixed member 36a Main body portion 36b Protrusion 37 Pressing portion 40 Engaged member 41 Recess (engaged portion)
41a, 41b End 43 Outer circumferential surface 50 Guide member 51 Guide path 51a Main portion 51b End 51c End 52 Main body portion 53 Guide path forming wall 60 Housing 61 First housing 62 Second housing 63 Third housing 64, 65, 66 Bearing member 67 External bearing portion 70 Deployment blade 70a Deployment blade 70b Deployment blade 70c Deployment blade 71 First arm 72 Second arm 75 Lock lever 80 Control cable 100 Power transmission clutch structure 200 Deployment structure

Claims (20)

A drive shaft that is rotationally driven by an actuator;
a first rotating shaft and a second rotating shaft which rotate in association with the rotation of the drive shaft;
a clutch mechanism that switches between a state in which a rotational force is transmitted from the drive shaft to the first rotation shaft and a state in which a rotational force is not transmitted;
Equipped with
When the drive shaft rotates in one direction, the clutch mechanism is in a drive transmission state in which the rotational force of the drive shaft is transmitted to the first rotating shaft when the rotation angle of the drive shaft is within a specific range, and is in a drive interruption state in which the rotational force of the drive shaft is not transmitted to the first rotating shaft when the rotation angle of the drive shaft is outside the specific range,
A power transmission clutch structure in which the second rotating shaft can rotate in conjunction with the rotation of the drive shaft both when the clutch mechanism is in the drive transmission state and when the clutch mechanism is in the drive interruption state while the drive shaft rotates in the one direction. The power transmission clutch structure according to claim 1, wherein the second rotating shaft always rotates during the process in which the drive shaft rotates in the one direction. At the beginning and end of the process in which the drive shaft rotates in one direction, the clutch mechanism is in the drive cut-off state,
2. The power transmission clutch structure according to claim 1, wherein the clutch mechanism is in the drive transmission state in an intermediate period between the initial period and the final period. The clutch mechanism includes:
an engagement member provided on the first rotating shaft;
an engaged member that is integral with the drive shaft and has an engaged portion with which the engaging member can engage;
having
When the engaging member is engaged with the engaged portion, the clutch mechanism is in the drive transmission state, and the first rotating shaft rotates together with the drive shaft,
2. The power transmission clutch structure according to claim 1, wherein, when the engaging member is disengaged from the engaged portion, the clutch mechanism is in the drive interrupted state and the first rotating shaft stops rotating. the engaged portion is a recess formed at an end of the engaged member in a radial direction of the drive shaft and having a shape that opens outward in the radial direction,
5. The power transmission clutch structure according to claim 4, wherein the clutch mechanism is brought into the drive-disconnected state by the engagement member moving outward in the radial direction relative to the recess and disengaging from the recess. the engaged member is a disk-shaped member arranged coaxially with the drive shaft,
6. The power transmission clutch structure according to claim 5, wherein the engaged portion is formed on an outer circumferential surface of the engaged member. The power transmission clutch structure according to claim 6, wherein the first rotating shaft is disposed on an extension of the drive shaft. The engagement member is a cylindrical pin extending parallel to an axial direction of the drive shaft,
8. The power transmission clutch structure according to claim 7, wherein an axial portion of said pin engages with said recess. The power transmission clutch structure according to claim 8, wherein the dimension of the recess in the radial direction of the engaged member is greater than the radius of the pin. The power transmission clutch structure according to claim 9, wherein the recess is formed in an arc shape along the outer peripheral surface of the pin. The power transmission clutch structure according to claim 10, wherein both ends of the recess in the circumferential direction of the engaged member are formed into a chamfered shape. the clutch mechanism includes a guide member having a guide path that guides a portion of the pin other than a portion that engages with the recess,
12. A power transmission clutch structure according to claim 8, wherein, during the process of the pin being guided by the guide path, the pin switches between the drive transmission state in which the pin is engaged with the recess and the drive interruption state in which the pin is disengaged from the recess. The guide member is a plate-shaped member,
13. The power transmission clutch structure according to claim 12, wherein the guide path is a guide groove formed on one surface of the guide member, and guides one end of the pin. the guide passage includes a main portion extending in an arc shape coaxial with the drive shaft, and an end portion connected to an end of the main portion and extending from the end of the main portion toward a radially outer side of the drive shaft,
14. The power transmission clutch structure according to claim 13, wherein the drive transmission state is when the one end of the pin is guided by the main portion, and the drive interruption state is when the one end of the pin is guided by the end portion. The power transmission clutch structure according to claim 14, wherein the radial component of the drive shaft gradually increases from the main portion to the end portion of the guideway. The power transmission clutch structure according to claim 15, wherein, at least in the portion of the end farthest from the main portion, the radial component of the drive shaft is greater than the circumferential component of the drive shaft in the direction of extension of the end. The power transmission clutch structure according to claim 12, wherein the clutch mechanism includes a biasing portion that biases the pin radially inward of the drive shaft. The power transmission clutch structure according to claim 17, wherein the biasing portion is composed of a tension-type coil spring. the clutch mechanism includes a swing member supported by a swing shaft parallel to the first rotation shaft at a position offset from an axis of the first rotation shaft so as to be swingable relative to the first rotation shaft,
The pin is provided at a portion of the swing member that is spaced apart from the swing shaft,
18. The power transmission clutch structure according to claim 17, wherein the biasing portion biases a portion of the pivot member that is closer to the pin than the pivot shaft toward a radially inward direction of the drive shaft. The actuator includes an output shaft.
The power transmission clutch structure includes:
A worm gear that transmits rotation of the output shaft to the drive shaft;
a bevel gear that transmits rotation of the drive shaft to the second rotating shaft;
Equipped with
The axial direction of the output shaft and the axial direction of the drive shaft are perpendicular to each other,
The axial direction of the drive shaft and the axial direction of the second rotation shaft are perpendicular to each other,
12. The power transmission clutch structure according to claim 1, wherein an axial direction of the output shaft and an axial direction of the second rotating shaft are parallel to each other.

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