JP6755286B2 - Rotating body stopper - Google Patents

Description

The present invention is used for a rotating body (including a rotating shaft) such as a caster attached to a trolley for carrying luggage or a leg of furniture or the like for the purpose of facilitating movement, and holds the rotating body in a stopped state. It is about the stopper.

Small wheels, casters, are attached to trolleys, carry bags, etc. for carrying luggage to enable smooth movement. Casters are also commonly used in furniture such as cabinets, chairs, and nursing beds that move frequently.
When a caster is attached, for example, a stopper is often provided to restrain the caster in a non-rotatable state so that the attached trolley does not unexpectedly start moving when loading and unloading luggage. As such a stopper, a friction plate or the like is pressed against the caster or a rotating body fixed to the caster to prevent the rotation, or a gear-shaped hooking member having a large number of uneven portions is fixed to the caster and hooked. It is known that a fixing side member is engaged with a stopping member and fixed so as not to rotate.

As a stopper to be installed on a caster or the like, the applicant of the present application devised the stopper described in Patent Document 1. This is an application of the principle of a so-called roller-type one-way clutch that stops a rotating body by the biting action of a roller arranged in a wedge-shaped space, and this stopper will be described with reference to FIGS. 11 and 12. .. FIG. 11 is a diagram showing the overall structure of the stopper, and FIG. 12 is a cross-sectional view of each part.

Explaining with reference to FIGS. 11 and 12, the rotating body RS is installed in a state of being surrounded by the fixed ring FR. As shown in the DD cross-sectional view of FIG. 12, the fixed ring FR has a space portion S in which a cam surface CS whose distance X from the outer circumference of the rotating body RS changes in the circumferential direction is formed, that is, a wedge-shaped cross section. Six space portions are provided, and the space portions S are set so that the increasing directions of the distance X are opposite to each other in the adjacent space portions S. The adjacent space portions S form a pair of combined space portions PS, and three of these combined space portions PS are arranged on the outer periphery of the rotating body RS at intervals in the circumferential direction. In each of the space portions S, a rolling element RB pressed by the spring SP in the direction in which the distance X decreases is installed, and a pressing piece P for moving the rolling element RB in the direction in which the distance X increases is installed. All the pressing pieces P are simultaneously operated by the operating means CM. As shown in the BB sectional view and the CC sectional view of FIG. 12, the operating means CM includes a pair of operating members MM and MM'rotating around the central axis o of the rotating body RS, and a pair of operating members. A cam body CB that changes the relative angular positions of the members MM and MM'is provided, and a rotation drive member RD that changes the posture of the cam body CB is provided. All of the pressing pieces P installed in every other space S in the circumferential direction of the rotating body RS are fixed to each of the pair of operating members MM and MM'. As shown in the cross-sectional view taken along the line BB in FIG. 12, the cam body CB is arranged in the radial intermediate portion to which the driven gear PG is fixed, and the rotary drive member RD is arranged in the radial center. The drive gear AG is fixed to the vehicle, and the driven gear PG and the drive gear AG are in mesh with each other. Therefore, by operating the rotary drive member RD to rotate the drive gear AG, the passive gear PG that meshes with the drive gear AG is rotated. The rotation drive member RD can move between the one-side operation position shown in FIG. 12 (a) and the other-side operation position shown in FIG. 12 (b).

When the rotation drive member RD is in the one-sided operating position, the pressing piece P is separated from the rolling element RB, and the rolling element RB is the spring of the spring SP, as shown in the DD cross-sectional view of FIG. 12A. It is located in a state of being moved in a direction in which the distance X is reduced by a force. Then, the rolling element RB meshes between the cam surface CS and the rotating body RS, and the rotating body RS cannot rotate (bidirectionally locked state). On the other hand, when the rotation drive member RD is in the operation position on the other side, the pressing piece P resists the spring force of the spring SP against the rolling element RB as shown in the DD cross-sectional view of FIG. 12 (b). The distance X is moved in the increasing direction. Then, the biting of the rolling element RB is released, and the rotating body RS becomes a rotatable state (bidirectional free state).

Patent No. 6064067

The stopper described above can easily switch the rotating body between a rotatable state and a stopped state by operating the rotation driving member RD. However, in the above-mentioned stopper, the number of teeth of the drive gear AG fixed to the rotary drive member RD is 24, and the number of teeth of the driven gear PG fixed to the cam body CB is 16 (the teeth are missing and actually 5). Since both gears are in direct mesh with each other, the rotation from the drive gear AG to the driven gear PG is increased to 24/16 and transmitted. That is, the torque applied to the rotary drive member RD (drive gear AG) becomes 16/24 and is transmitted to the cam body CB (driven gear PG), so that the required torque for changing the posture of the cam body CB increases. Resulting in. On the other hand, since the torque from the driven gear PG to the drive gear AG is transmitted at 24/16, for example, the rotating body RS is in a rotatable state, that is, the pressing piece P resists the rolling element RB against the spring force of the spring SP. In the state of moving in the direction in which the distance X increases, the pressing piece P moves only by a slight external force caused by the vibration of the rotating body RS or the like acting on the rolling element RB, and the rolling element RB bites. There is a risk that the crowd will be released.

In order to solve such a problem, it is conceivable to set the number of teeth of the driving gear AG to be smaller than the number of teeth of the driven gear PG so that the driven gear PG decelerates with respect to the rotation of the driving gear AG. However, the reduction ratio obtained by the above-mentioned meshing type of gears is small, and the above-mentioned problems cannot be sufficiently solved. Further, by setting the number of teeth of the drive gear AG to be extremely large and the number of teeth of the driven gear PG to be extremely small, it is possible to set a large reduction ratio of the driven gear PG to the drive gear AG. If the number of teeth of both gears is set in this way, the entire device becomes large.
From the above, the subject of the present invention is to provide a compact stopper capable of operating the rotation driving member with a small force and preventing the pressing piece from unintentionally moving due to vibration of the rotating body or the like. Is to provide.

In view of the above problems, the present invention combines two so-called differential planetary gear mechanisms so that each of the pair of operating gears is rotated in opposite directions.
That is, the present invention
"A stopper that switches the rotating body between a rotatable state and a stopped state.
A fixing member installed so as to surround the outer circumference of the rotating body is provided.
The fixing member is provided with a plurality of space portions having a cam surface in which the distance from the outer periphery of the rotating body changes in the circumferential direction, and the plurality of space portions increase the distance in the adjacent space portion. The adjacent space portions form a pair of combined space portions, and a plurality of the combined space portions are arranged on the outer periphery of the rotating body, so that the directions are set to be opposite to each other.
In each of the space portions, a rolling element pressed by a spring in the direction in which the distance decreases and a pressing piece for moving the rolling element in the direction in which the distance increases are installed, and further, the pressing piece is provided. It is equipped with operating means to operate at the same time.
A fixed gear fixed to the fixing member and all of the pressing pieces installed in every other space in the circumferential direction of the rotating body are fixed to the operating means, and the center of the rotating body is fixed. A pair of operating gears that rotate around a shaft, a planetary gear that meshes in common with the fixed gear and the pair of operating gears, and a rotary drive member that rotatably supports the planetary gears are provided. ,
The fixed gear and the pair of operating gears are both internal gears, the number of teeth of one of the pair of operating gears is larger than the number of teeth of the fixed gear by a natural number n, and the number of teeth of the other is fixed. It is set to be smaller than the number of teeth of the gear by a natural number n, and each of the pair of operating gears is rotated in opposite directions by the rotation of the rotation driving member. "
It is a stopper characterized by that.

It is preferable that the fixed gear and the pair of operating gears both have the same tooth tip circle diameter and have different transfer coefficients from each other.
It is preferable that the plurality of combination space portions are arranged at equal intervals on the outer circumference of the rotating body.
The fixing member preferably has a housing and a fixing ring that is fixed to the inside of the housing.

In the stopper of the present invention, the fixing member surrounding the rotating body is provided with a plurality of space portions having a cam surface whose distance from the outer circumference of the rotating body changes in the circumferential direction. The adjacent space portions form a pair of combined space portions, and each of the space portions includes a rolling element pressed by a spring in the direction in which the distance decreases and a pressing piece for moving the rolling element in the direction in which the distance increases. And are installed, and all the pressing pieces are operated simultaneously by the operating means. As the operating means, a pair of operating members and a pair of operating members, in which all the pressing pieces installed in every other space in the circumferential direction of the rotating body are fixed and rotate around the central axis of the rotating body. It is provided with a rotation drive member for changing each posture of the above, and the rotation drive member can move between one side operation position and the other side operation position.
These points are the same as the conventional stoppers shown in FIG. 11 and the like, but in the operating means in the present invention, each of the pair of operating members is a gear (operating gear) and is fixed to the fixing member. The gear is stuck. The number of teeth of one of the pair of working gears is larger than the number of teeth of the fixed gear by a natural number n, and the number of teeth of the other is smaller than the number of teeth of the fixed gear by a natural number n. Planetary gears are in mesh in common. Further, the planetary gears are rotatably supported by a rotation driving member.

The operation of the stopper of the present invention is basically the same as that of the conventional stopper. When the position of the rotation driving member is in the one-sided operating position, that is, in the state shown in FIG. 2 (a) described later, the pressing piece is separated from the rolling element, and the rolling element is separated from the rolling element in the direction in which the distance is reduced by the spring. It is pressed and bites between the cam surface and the rotating body, and the rotating body becomes in a non-rotatable state. On the other hand, when the position of the rotation driving member is in the other side operating position, that is, in the state shown in FIG. 2B described later, the pressing piece comes into contact with the rolling element and resists the pressing force of the spring. Then, the rotating body is moved in the direction in which the distance increases, and the rotating body becomes rotatable.

Here, in the stopper of the present invention, each of the pair of working gears, the fixed gear, and the planetary gear form a so-called differential planetary gear mechanism, and the planetary gear is common to the pair of working gear and the fixed gear. The number of teeth of one of the pair of operating gears is larger than the number of teeth of the fixed gear by a natural number n, and the number of the other teeth is smaller than the number of teeth of the fixed gear by a natural number n. From this, when the planetary gear moves planetarily due to the rotation of the rotation drive member, one operating gear having a natural number n larger than the number of teeth of the fixed gear rotates in the direction opposite to the revolution direction of the planetary gear. At the same time, the other operating gear, which has a small number of teeth by a natural number n with respect to the number of teeth of the fixed gear, rotates in the same direction as the revolution direction of the planetary gear. The reduction ratio η of the operating gear at this time is calculated by the following formula.
η = (Zf-Za) / Zf
Zf: Number of teeth of fixed gear
Za: Number of teeth of the working gear Since the absolute value of the difference between the number of teeth of each pair of working gears and the number of teeth of the fixed gear is the same as the natural number n, the reduction ratio (rotation amount) of each of the pair of working gears. The absolute values of are the same. Therefore, each of the pair of pressing pieces arranged in all the combination spaces moves at the same time in the opposite directions by the same amount. Further, as shown in the above equation, the reduction ratio of the working gear can be set extremely large by setting the difference between the number of teeth of the working gear and the number of teeth of the fixed gear to be small. Further, if the difference between the number of teeth of the working gear and the number of teeth of the fixed gear is set small, the entire device becomes compact. From this, in the stopper of the present invention using the operating planetary gear mechanism, the rotation drive member can be operated with a small force without increasing the size of the entire device, and the vibration of the rotating body and the like can be operated. It is possible to prevent the pressing piece from moving unintentionally.

It is a figure which shows the whole structure of the Example of the stopper of this invention. It is a figure which shows the cross section of each part of the stopper shown in FIG. It is an assembly drawing of the part which comprises the stopper shown in FIG. It is an enlarged view of one of the combination space part in the CC cross section of FIG. 2A. It is a simple substance figure of the housing of the stopper shown in FIG. It is a simple substance figure of the fixing ring of the stopper shown in FIG. It is a simple substance figure of the rotating body of the stopper shown in FIG. It is a simple substance figure of the fixed gear of the stopper shown in FIG. It is a simple substance figure of the operating gear of the stopper shown in FIG. It is a simple substance figure of the planetary gear of the stopper shown in FIG. It is a simple substance figure of the rotation drive member of the stopper shown in FIG. It is a figure which shows the structure of the conventional stopper which the applicant devised. It is a figure which shows the cross section of each part of the stopper shown in FIG.

Hereinafter, the stopper of the present invention for switching the rotating body between the rotatable state and the stopped state will be described with reference to the drawings. 1 and 2 show an overall view of the stopper of the present invention, FIG. 4 shows an assembly view of the main components by a perspective view, and FIGS. 5 to 10 show the main components individually. Shown in each.

As shown in FIGS. 1 to 3, the stopper of this embodiment includes a fixing member 2, and inside the fixing member 2, a rotating body 4 which is an object for switching between a rotatable state and a stopped state, and a rotating body 4 A rolling element 6 for switching the operating state of the rotating body 4, a spring 7 for pressing the rolling element 6, a pressing piece 8 for operating the rolling element 6 against the pressing of the spring 7, and an operating means for operating the pressing piece 8. 10 and are arranged.

The fixing member 2 includes a housing 12 made of synthetic resin and a metal fixing ring 14 fixed inside the housing 12. Mainly with reference to FIG. 5, the housing 12 has a substantially annular plate-shaped substrate 16 and a cylindrical outer peripheral wall 18 extending perpendicularly to the outer peripheral edge of the substrate 16. .. Six pins 20 arranged at equal intervals on the virtual circle indicated by the alternate long and short dash line c1 are provided in the radial intermediate portion of the substrate 16 inside the outer peripheral wall 18. Three annular ridges 24 are also concentrically formed in the radial intermediate portion of the substrate 16. Three through-holes 26 are formed on the outer peripheral edge of the substrate 16 at equal angular intervals in the circumferential direction. Each of the through hole portions 26 has a substantially rectangular shape extending in the circumferential direction. A groove 28 is formed on the inner peripheral surface of the outer peripheral wall 18 so as to extend linearly from a side located on the outer side in the radial direction of the through hole portion 26 toward the free end edge of the outer peripheral wall 18. A claw portion 30 slightly extending inward in the radial direction is formed at the free end edge portion of the outer peripheral wall 18 in the central portion in the circumferential direction of the groove 28. The inner diameter of the free end edge portion of the outer peripheral wall 18 is slightly increased except for the portion where the groove 28 is formed, and the shoulder surface 32 is formed. A notch 34 is formed in a region at a predetermined angle in the circumferential direction of the free end edge portion of the outer peripheral wall 18. Three ears 38 are fixed to the outer peripheral surface of the base end portion of the outer peripheral wall 18 at equal angular intervals in the circumferential direction, and the stopper of the present invention is attached to the center of the ears 38. A mounting hole 40 is formed.

Continuing the description with reference to FIG. 6, the outer circumference of the fixing ring 14 is circular. On the other hand, on the inner circumference of the fixing ring 14, six recesses 42 opened inward are formed at equal angular intervals in the circumferential direction, and a cam surface 43 is formed between the recesses 42 adjacent in the circumferential direction. It is formed. The cam surface 43 will be further described later.
The rotating body 4 is made of metal, and as shown in FIG. 7, both have a disk shape and have a relatively large diameter main portion 44 fixed coaxially and a relatively small diameter shaft portion 46. .. A shaft hole 47 having a non-circular cross section extending in the axial direction is formed in the center of the rotating body 4. For example, the rotating shaft of the caster is inserted into the shaft hole 47.
The rolling element 6 is made of metal and is a cylindrical roller as can be understood by referring to FIG. If desired, the rolling element may be a spherical ball.
Here, as will be described later, since the rolling element 6 causes biting between the cam surface 43 of the fixing ring 14 and the rotating body 4, at least the portion of the fixing member 2 where the cam surface 43 is formed is made of metal. There must be. However, if the entire fixing member 2 is made of metal, the weight of the entire device will increase significantly. Therefore, in the illustrated embodiment, the fixing member 2 is composed of two parts, a housing 12 made of synthetic resin and a fixing ring 14 made of metal, in order to reduce the weight of the entire device.

Next, the operating means 10 will be described mainly with reference to FIGS. 8 to 11. The operating means 10 includes a fixed gear 48 fixed to the fixing member 2 (fixing ring 14), a pair of operating gears 50 (50a and 50b) rotating around the central axis o of the rotating body 4, and a fixed gear. A planetary gear 52 that meshes with the 48 and a pair of operating gears 50, and a rotary drive member 54 that rotatably supports the planetary gear 52 are provided.

As shown in FIG. 8, the fixed gear 48 is an internal gear and has 60 teeth. Six ear portions 56 protruding outward in the radial direction are fixed to the outer peripheral surface of the fixed gear 48 at equal angular intervals in the circumferential direction, and six ear portions 52 are fixed to the fixed gear 48 in the center of each ear portion 52. A pin 58 that protrudes vertically is provided. Two annular ridges 60 are formed on one side surface of the fixed gear 48, and one annular ridge 60 is formed on the other side surface.

As shown in FIG. 9, the working gears 50a and 50b are both internal gears, and the working gear 50a has 63 teeth and the working gear 50b has 57 teeth. That is, the number of teeth of the working gear 50a is 3 larger and the number of teeth of the working gear 50b is 3 smaller than the number of teeth of the fixed gear 48, and the difference in the number of teeth between the fixed gear and each of the pair of working gears 50a and 50b. Both absolute values are 3. Further, the operating gears 50a and 50b are appropriately transferred so that the diameter of each tooth tip circle is the same as the tooth tip circle diameter of the fixed gear 48. Six pressing pieces 8 (8a and 8b) are fixed to the outer peripheral surfaces of each of the pair of operating gears 50 (50a and 50b) at equal angular intervals in the circumferential direction. Each of the pressing pieces 8 has a rod shape extending perpendicular to the operating gear 50, and its base end is aligned with the operating gear 50. Further, the pressing piece 8a is shorter than the pressing piece 8b.

The planetary gear 52 has 20 teeth, and annular ridges 62 having a trapezoidal cross section are formed on both side surfaces thereof, as shown in FIG. As understood by referring to FIG. 1 and the like, in the illustrated embodiment, three planetary gears 52 are provided.

As shown in FIG. 11, the rotation driving member 54 includes a ring-shaped main portion 64 and a lever portion 66 extending radially outward at a predetermined angular position in the circumferential direction of the main portion 64. A ring-shaped pedestal portion 68 is formed in the center of one side surface of the main portion 64 in a plan view. The pedestal portion 68 is provided with three support shafts 70 for axially supporting the planetary gears 52 at equal angular intervals in the circumferential direction. All three support shafts 70 are arranged on the virtual circle c2 indicated by the alternate long and short dash line, and tubular reinforcing portions 72 are also provided between the support shafts 70 adjacent to each other in the circumferential direction. In a plan view, the outer peripheral edge of each reinforcing portion 72 coincides with the outer peripheral edge of the pedestal portion 68. Further, the pair of side surfaces of the two reinforcing portions 72 adjacent to each other in the circumferential direction facing each other in the circumferential direction are arranged on the virtual circle c3 indicated by the alternate long and short dash line centered on the support shaft 70 located between them. .. The diameter of the virtual circle c3 is larger than the diameter of the tooth tip circle of the planetary gear 52. An arcuate step portion 74 is formed on the outer peripheral edge portion on the other side surface of the main portion 64.

Continuing the description with reference to FIGS. 1 to 4, the above-mentioned components are combined as follows, for example.
First, the fixing ring 14 is arranged in the housing 12. At this time, the pin 20 is fitted into the recess 42, and the fixing ring 14 becomes non-rotatable with respect to the housing 12. Next, the rotating body 4 is arranged at the center inside the fixing ring 14. Then, as shown in FIG. 4, the fixing ring 14 (fixing member 2) is formed with a plurality of cam surfaces 43 in which the distance X from the outer periphery of the rotating body 4 changes in the circumferential direction (12 in the illustrated embodiment). The space portions 76 are provided, and the plurality of space portions 76 are set so that the directions in which the distance X increases in the adjacent space portions 76 are opposite to each other, and the adjacent space portions 76 are a pair of combinations. The space portions 78 are formed, and a plurality of combination space portions 78 (six in the illustrated embodiment) are arranged on the outer periphery of the rotating body 4 at equal intervals.

After that, a pair of working gears 50a and 50b are arranged inside the housing 12. The pair of working gears 50a and 50b are arranged so as to be vertically overlapped with each other so that the working gears 50a are located closer to the substrate 16 of the housing 12 than the working gears 50b. When the pair of working gears 50a and 50b are arranged inside the housing 12, the pressing pieces 8a and 8b fixed to each of the pair of working gears 50a and 50b are spatial portions in every other space in the circumferential direction of the rotating body 4. It will be arranged in each of 88. After the operating gear 50b is arranged inside the housing 12, the fixing gear 48 is fixed to the fixing member 2. In the illustrated embodiment, the fixed gear 48 is fixed to the fixed ring 14 by fitting the pin 58 of the fixed gear 48 into the recess 42 of the fixed ring 14. After the fixed gear 48 is fixed to the fixed ring 14, the rolling elements 6 and the springs 7 are arranged in each of the space 76s.

After that, a rotary drive member 54 that rotatably supports the planetary gear 52 is arranged inside the housing 12, and the planetary gear 52 is commonly meshed with the fixed gear 48 and the pair of operating gears 50a and 50b. At this time, as shown in FIG. 1, the lever portion 66 is aligned with the notch 34, one side surface of the outer peripheral edge portion of the main portion 64 faces the shoulder surface 32 of the outer peripheral wall 18, and the step of the main portion 64. By engaging the claw portion 30 of the outer peripheral wall 18 with the portion 74, the rotation driving member 54 can rotate within a predetermined angle range with respect to the portion 74 without falling off from the housing 12.

Next, the operation of the stopper of the present invention will be described mainly with reference to FIG.
When the stoppers of the present invention are combined as described above, for example, the rotary drive member 54 can move between the one-sided operation position shown by the solid line and the other-side operation position shown by the alternate long and short dash line in FIG. .. FIG. 2A shows a cross-sectional view of each part when the rotation drive member 54 is in the one-side operation position, and FIG. 2B shows a cross-sectional view of each part when the rotation drive member 54 is in the other side operation position.

When the rotary drive member 54 is in the one-sided operating position, the pressing pieces 8a and 8b fixed to each of the pair of operating gears 50a and 50b are close to each other as shown in the cross-sectional view taken along the line BB in FIG. Is located. Therefore, as shown in the CC cross-sectional view of FIG. 2A, the pressing piece 8 is separated from the rolling element 6 in all the space portions 76, and the rolling element 6 is pressed by the spring 7 in the direction in which the distance X decreases. , The rotating body 4 is engaged between the cam surface 43 and the rotating body 4, and the rotating body 4 becomes non-rotatable.

On the other hand, when the rotation drive member 54 is moved from the one-side operation position to the other side operation position, the planetary gear 52 rotatably supported by the rotation drive member 54 is clocked in the BB sectional view of FIG. 2A. It revolves in the direction and rotates counterclockwise (that is, planetary motion) due to meshing with the fixed gear 48 and the like, resulting in the state shown in the BB cross-sectional view of FIG. 2 (b). At this time, since the planetary gear 52 meshes with the pair of operating gears 50a and 50b together with the fixed gear 48, when the planetary gear 52 makes the planetary motion as described above, the number of teeth is 3 larger than the number of teeth of the fixed gear 48. The working gear 50a rotates in the direction opposite to the revolving direction of the planetary gear 52, that is, in the counterclockwise direction, and the working gear 50b, which has three smaller teeth than the fixed gear 48, is in the same direction as the revolving direction of the planetary gear 52, that is, the clock. It will rotate in the direction (that is, each of the pair of working gears 50a and 50b will rotate in opposite directions). As described above, the reduction ratio of the operating gear 50 at this time is the difference in the number of teeth between the operating gear 50 and the fixed gear 48 with respect to the number of teeth of the fixed gear 48. Since the absolute value of the difference in the number of teeth of the pair of working gears 50a and 50b with respect to the number of teeth of the fixed gear 48 is the same at 3, the absolute value of the reduction ratio of the working gears 50a and 50b is both 3/60, and the pair of working gears is operated. The gears 50a and 50b will rotate in opposite directions by the same magnitude. As a result, as shown in the cross-sectional view taken along the line BB in FIG. 2B, the pressing pieces 8a and 8b fixed to each of the pair of operating gears 50a and 50b move by the same distance in the direction of separating from each other. Become. As a result, as shown in the CC cross-sectional view of FIG. 2B, the pressing pieces 8 arranged in the respective space portions 76 come into contact with the rolling elements 6, and the pressing pieces 8 abut against the pressing force of the spring 7 for a distance. By moving in the direction in which X increases, the rotating body 4 becomes rotatable.

As described above, in the stopper of the present invention, two so-called differential planetary gear mechanisms are combined to operate each of the pair of operating gears. Therefore, by reducing the difference in the number of teeth between the fixed gear 48 and the operating gear 50, the rotary drive member can be operated with a small force without increasing the size of the entire device, and vibration of the rotating body, etc. It is possible to prevent the pressing piece from moving unintentionally.

2: Fixing member 4: Rotating body 6: Rolling body 7: Spring 8 (8a and 8b): Pressing piece 10: Operating means 12: Housing 14: Fixing ring 43: Cam surface 48: Fixed gear 50 (50a and 50b): Operating gear 52: Planetary gear 54: Rotational drive member 76: Space part 78: Combination space part

Claims (4)

A stopper that switches the rotating body between a rotatable state and a stopped state.
A fixing member installed so as to surround the outer circumference of the rotating body is provided.
The fixing member is provided with a plurality of space portions having a cam surface in which the distance from the outer periphery of the rotating body changes in the circumferential direction, and the plurality of space portions increase the distance in the adjacent space portion. The adjacent space portions form a pair of combined space portions, and a plurality of the combined space portions are arranged on the outer periphery of the rotating body, so that the directions are set to be opposite to each other.
In each of the space portions, a rolling element pressed by a spring in the direction in which the distance decreases and a pressing piece for moving the rolling element in the direction in which the distance increases are installed, and further, the pressing piece is provided. It is equipped with operating means to operate at the same time.
A fixed gear fixed to the fixing member and all of the pressing pieces installed in every other space in the circumferential direction of the rotating body are fixed to the operating means, and the center of the rotating body is fixed. A pair of operating gears that rotate around a shaft, a planetary gear that meshes in common with the fixed gear and the pair of operating gears, and a rotary drive member that rotatably supports the planetary gears are provided. ,
The fixed gear and the pair of working gears are both internal gears, the number of teeth of one of the pair of working gears is larger than the number of teeth of the fixed gear by a natural number n, and the number of teeth of the other is fixed. A stopper that is set to be smaller than the number of gear teeth by a natural number n, and that each of the pair of operating gears is rotated in opposite directions by the rotation of the rotation driving member. The stopper according to claim 1, wherein the fixed gear and the pair of operating gears both have the same tooth tip circle diameter and have different transfer coefficients from each other. The stopper according to claim 1 or 2, wherein the plurality of combination spaces are arranged on the outer periphery of the rotating body at equal intervals. The stopper according to any one of claims 1 to 3, wherein the fixing member has a housing and a fixing ring fixed to the inside of the housing.