JP5498806B2 - Interrupting device - Google Patents

Description

  The present invention relates to an interrupting device for a clutch, and more particularly to an interrupting device capable of simplifying the structure and reducing the size.

  In a transmission such as a vehicle, the members connected to the input shaft and the output shaft are brought into contact with each other, and the disks are engaged with each other by frictional force generated between the members to transmit the rotation of the input shaft to the output shaft. A friction clutch or the like (hereinafter referred to as “clutch”) is used. Since the member is brought into contact with each other using the biasing force of the spring disposed in the clutch and the clutch is engaged, a force that resists the spring biasing force is input to the clutch in order to release the clutch. There is a need. As an interrupting device for releasing such a clutch, one that uses the driving force of a motor is known.

  For example, in Patent Document 1, a follower operating end of cams 1708 and 2007 rotated by motors 1701 and 1002 is connected to a clutch, and an energy accumulator is added to cranks 1713 and 2010 that are integrally formed with cams 1708 and 2007. Actuators 1700 and 2000 (intermittent devices) in which 1714 and 2015 are disposed are disclosed. According to the intermittent device disclosed in Patent Literature 1, when the clutch is engaged, the load is accumulated in the energy accumulator disposed in the crank, while the accumulated load is released when the clutch is released. Is output toward the clutch. As a result, the load accumulated in the accumulator can be output in addition to the driving force of the motor, and the clutch can be released.

  Patent Document 2 discloses a crank arm 10 that is moved by a motor, a load accumulating means (coil spring 18) that accumulates a load as the crank arm 10 moves, and a pivotable connection to the load accumulating means. There is disclosed an automatic interrupting device (interrupting device) including a link 21 and a toggle device formed by connecting these links so as to be rotatable. According to the interrupting device disclosed in Patent Document 2, since the toggle device is configured, as shown in FIG. 3 of Patent Document 2, the load is accumulated and held in the coil spring 18 even after the friction clutch is engaged. The As a result, when releasing the friction clutch, the clutch can be released by outputting the load accumulated and held in the coil spring 18.

JP-A-9-207600 (FIGS. 23 and 24) Japanese Patent Laid-Open No. 11-201188 (FIG. 3)

  However, since the intermittent device disclosed in Patent Document 1 uses a crank, a large space is required in the device so that the crank can be swung. Also in the interrupting device disclosed in Patent Document 2, there is a problem that the link mechanism including the crank arm 10 occupies a large space and the device becomes large.

  Further, in the interrupting device disclosed in Patent Document 2, since the load is accumulated and held in the coil spring 18 even after the friction clutch is engaged, the toggle device is formed by the link mechanism, which makes the structure complicated. There was a problem.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide an interrupting device capable of simplifying the structure and reducing the size.

Means for Solving the Problems and Effects of the Invention

To achieve this object, the interrupting device according to claim 1 is provided with a cam rotated by a motor, a first follower that presses the clutch by the cam, and a position different from the first follower. And a second follower that is biased toward the cam and gives the cam a rotational force in the direction of releasing the clutch, so the cam can convert the rotational motion of the motor into a linear motion, simplifying the structure There is an effect that can be done. In the second follower, a contact constituted by a roller follower directly contacts the cam, and the shaft on which the contact is supported at one end reciprocates linearly on its own axis. The shaft is urged toward the cam by the accumulator that is compressed and extended as the shaft moves. Cams, since it like a crank is not necessary to secure a space enough to swing, there is an effect that the apparatus can be downsized.

Further, since the positions, speeds, and timings of the first follower and the second follower are arbitrarily determined from the cam shape, there is an effect that the flexibility of designing the interrupting device can be improved. Further, each camshaft torque required for displacing the first follower and the second follower can be calculated based on the load characteristics of the clutch spring, the second follower, the cam shape, and the like. Here, the first camshaft torque for rotating the cam in the direction for releasing the clutch by the urging force of the second follower and the cam for rotating in the direction for engaging the clutch by the urging force of the spring. The difference from the second camshaft torque is the camshaft torque required by the motor. The shape of the cam and the biasing force of the second follower are set so that the first camshaft torque is canceled by the second camshaft torque at the corresponding cam rotation angle. As a result, the peak torque of the cam shaft torque - can be reduced (the first cam shaft torque second cam shaft torque), Ru can reduce the peak current of the motor. As a result, the motor can be reduced in size. That is, since the first follower and the second follower are displaced using the cam, the motor can be reduced in size by taking into account the load characteristics of the clutch spring and the second follower, and adding the cam shape and the second follower. There is an effect that can be easily realized by optimizing the power.

Further , since the pressure angle of the cam with respect to the moving direction of the shaft when the clutch is engaged is set to substantially 0 °, the rotational force in the direction of releasing the clutch is the second when the clutch is engaged. Prevent the follower from giving the cam. As a result , there is an effect that it is possible to prevent the clutch engaging force from being weakened by the biasing force of the second follower and the transmission torque from being lowered.

  Further, since the biasing force of the second follower does not rotate the cam when the clutch is engaged, there is an effect that the energy consumed by the motor for maintaining the engagement of the clutch can be greatly reduced. Furthermore, since the clutch is strongly engaged simply by controlling the cam rotation angle and stopping the cam so that the pressure angle is substantially 0 °, the mechanism can be greatly simplified. There is an effect that can be miniaturized.

According to the interrupting device of claim 2, since the pressure angle of the cam with respect to the moving direction of the first follower when the clutch is released is set to substantially 0 °, the interrupting device of claim 1 In addition to the effects of the above, the energy consumed by the motor to maintain the release of the clutch can be greatly reduced, the mechanism can be greatly simplified, and the apparatus can be miniaturized.

That is, when the clutch is released, it is necessary to prevent the displacement of the first follower in order to maintain the released state. In order to prevent the displacement of the first follower, it is only necessary to prevent the cam from rotating due to the urging force of the clutch spring. According to the second aspect of the present invention, since the cam has a pressure angle with respect to the direction of movement of the first follower when the clutch is released is substantially 0 °, the cam is biased by the urging force of the clutch spring. Even if one follower moves in the direction of the cam, the cam cannot rotate. Therefore, there is an effect that the energy consumed by the motor for maintaining the released state of the clutch can be greatly reduced. Also, the clutch release state can be maintained simply by stopping the cam so that the pressure angle becomes substantially 0 ° by controlling the cam rotation angle, so that the mechanism can be greatly simplified, There is an effect that can be miniaturized.

According to the intermittent device of claim 3, wherein the biasing force of the cams of the shape and the second followers, the difference between the first cam shaft torque and the second cam shaft torque, except for the retention period, the rotation angle of the cam Therefore, the camshaft torque required by the motor can be leveled. As a result, in addition to the effect produced by the interrupting device according to claim 1 or 2, there is an effect that it is possible to eliminate cam rattling and rotation unevenness.

It is the cross-sectional schematic diagram which showed typically the intermittent device in one embodiment of this invention. It is a cross-sectional schematic diagram of the intermittent device in the II-II line of FIG. (A) is the schematic diagram which showed typically the internal structure of the interruption apparatus when a clutch is engaged, (b) is the inside of an interruption apparatus when outputting the load hold | maintained at the energy storage part to the clutch. It is the schematic diagram which showed the structure typically, (c) is the schematic diagram which showed typically the internal structure of the interruption apparatus when a clutch is released. (A) is a schematic diagram of the cam and the first follower for explaining the camshaft torque when displacing the first follower, and (b) is for explaining the camshaft torque when displacing the second follower. It is a schematic diagram of a cam and a 2nd follower. It is a figure which shows an example of the calculation result of the 1st camshaft torque when releasing a clutch, and a 2nd camshaft torque.

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, preferred embodiments of the invention will be described with reference to the accompanying drawings. FIG. 1 is a schematic cross-sectional view schematically showing an interrupting device 1 according to an embodiment of the present invention, and FIG. 2 is a schematic cross-sectional view of the interrupting device 1 taken along the line II-II in FIG.

  As shown in FIG. 1, the interrupting device 1 is arranged at a position different from the cam 6 rotated by the motor M, the first follower 9 that presses the clutch 20 by the cam 6, and the first follower 9. The second follower 10 is mainly provided.

  The cam 6 is composed of a plate cam and is fixed to the cam shaft 7. The cam shaft 7 is fixed to the housing 2 via a bearing 8 so that both ends can be rotated. On the other hand, a motor M is disposed outside the housing 2. The motor shaft 3 for outputting the rotation of the motor M extends in the housing 2 so as to intersect the cam shaft 7, and the end of the motor shaft 3 is fixed to the housing 2 so as to be rotatable via a bearing 4. Has been. A worm 5 is formed on the motor shaft 3 and is engaged with a worm wheel (not shown) formed on the end side of the cam shaft 7. Thereby, along with the rotation of the motor shaft 3, the power is transmitted to the worm 5 and the worm wheel (not shown), and the cam 6 rotates.

  As shown in FIG. 2, the second follower 10 includes a roller follower and a contact 10 a that directly contacts the contour of the cam 6. The contact 10 a is supported at one end and the other end is fixed to the housing 2. The shaft 10b is formed to be extendable and retractable, and a power storage portion 10c disposed on the shaft 10b is mainly provided. The accumulator 10c is constituted by a coil spring, and is disposed on the outer periphery of the shaft 10b. One end is fixed to the front end side of the shaft 10b and the other end is fixed to the housing 2. As the cam 6 rotates, the shaft 10b repeats contraction and extension, and the accumulator 10c also repeats compression and extension accordingly. The contact 10 a is pressed against the cam 6 by the urging force of the energy storage portion 10 c compressed by the rotation of the cam 6.

  The first follower 9 is disposed at a position different from that of the second follower 10, and is composed of a roller follower and a contact 9a that directly contacts the contour of the cam 6, and the contact 9a is supported at one end. The other end side is mainly provided with a thrust bar 9 b extending outside the housing 2. Biasing means 9c composed of a coil spring is disposed on the outer periphery of the thrust bar 9b. The biasing means 9 c has one end fixed to the tip end side of the thrust bar 9 b and the other end fixed to the housing 2. The contact 9a is pressed against the cam 6 by the urging force of the urging means 9c in the same manner as the above-described power storage unit 10c. Moreover, since the 1st follower 9 and the 2nd follower 10 are equipped with the contactors 9a and 10a comprised from a roller follower, friction with the cam 6 can be reduced and energy loss can be suppressed.

  Returning to FIG. 1, the clutch 20 linked to the interrupting device 1 will be described. The clutch 20 is spaced apart from the flywheel 21, the clutch plate 22 disposed on the disk surface of the flywheel 21, the friction pad 23 attached to the disk surface of the clutch plate 22, and the friction pad 23. A pressure plate 24 provided, a spring 25 that presses the pressure plate 24 toward the clutch plate 22 by its urging force, and generates a friction force on the friction pad 23; and the urging force of the spring 25 is released to release the pressure plate 24. A release bearing 26 and a release fork 27 that are separated from the friction pad 23 are mainly provided. The release fork 27 is operated by the output element 28, and the output element 28 is connected to the first follower 9 (the thrust bar 9 b) of the interrupting device 1.

  According to the clutch 20, when the output element 28 is displaced toward the intermittent device 1, the pressure plate 24 is pressed toward the clutch plate 22 by the urging force of the spring 25. As a result, a frictional force is generated on the friction pad 23. Thereby, the clutch 20 is engaged and power is transmitted. On the other hand, when the output element 28 is displaced to the clutch 20 side, the release fork 27 is operated and the urging force of the spring 25 is released. As a result, the clutch 20 is released and power transmission is interrupted.

  The intermittent device 1 is a device that operates the output element 28 to engage and release the clutch 20. Hereinafter, the operation of the interrupting device 1 will be described with reference to FIG. FIG. 3A is a schematic diagram schematically showing the internal structure of the interrupting device 1 when the clutch 20 is engaged, and FIG. 3B is a diagram illustrating the load held in the force accumulating portion 10c applied to the clutch 20. It is the schematic diagram which showed typically the internal structure of the interruption device 1 when outputting, FIG.3 (c) is the schematic diagram which showed typically the internal structure of the interruption device 1 when the clutch 20 is released. is there. In FIG. 3, the urging means 9c of the first follower 9 is not shown. When the clutch 20 is engaged, it is expressed as “Lock” (see FIG. 3A), and when the clutch 20 is released, it is expressed as “Free” (FIG. 3C). reference).

  As shown in FIG. 3A, when the first follower 9 of the interrupting device 1 is displaced to the cam 6 side, the output element 28 (see FIG. 1) is displaced to the interrupting device 1 side. As a result, the clutch 20 is engaged as described above. On the other hand, as the first follower 9 is displaced toward the cam 6, the force storage portion 10 c disposed in the second follower 10 is compressed and the load is accumulated. Here, the cam 6 is a pressure angle with respect to the movement direction of the second follower 10 when the clutch 20 is engaged (the contour of the cam 6 and the common normal n of the second follower 10 and the movement of the second follower 10. The angle formed with the direction m) is substantially set to 0 ° (where t is the tangent line of the cam 6 at the point where the contact 10a contacts the contour of the cam 6).

  Thereby, since the common normal line n and the movement direction m of the second follower 10 coincide, the cam 6 cannot be rotated by the urging force (the urging force of the second follower 10) due to the elastic deformation of the accumulator 10c. . Thereby, when the clutch 20 is engaged, the rotational force in the direction of releasing the clutch 20 is prevented from being applied to the cam 6 from the second follower 10. As a result, the engaging force of the clutch 20 is weakened by the urging force of the second follower 10, and the transmission torque can be prevented from decreasing.

  Further, as described above, since the urging force of the second follower 10 does not rotate the cam 6 when the clutch 20 is engaged, the energy consumed by the motor M (see FIG. 1) to maintain the engagement of the clutch 20. Can be greatly reduced. Further, since the engagement of the clutch 20 can be maintained only by stopping the cam 6 so that the rotation angle of the cam 6 is controlled so that the pressure angle becomes substantially 0 °, the mechanism can be greatly simplified. Can be miniaturized.

  Next, when releasing the clutch 20, the cam 6 is rotated around the cam shaft 7 using the motor M (see FIG. 1) as shown in FIG. 3B (arrows around the cam shaft 7). Indicates the direction of rotation of the cam 6). As a result, the cam 6 generates a pressure angle θp with respect to the second follower 10, and the accumulator 10c outputs the accumulated load to the cam 6 side. As a result, in addition to the driving force of the motor M, the cam 6 is rotated by the load and pressure angle θp output by the power storage unit 10c. As the cam 6 rotates, the first follower 9 is displaced toward the clutch 20 and presses the spring 25 (see FIG. 1) of the clutch 20.

  Next, as shown in FIG. 3C, the cam 6 is rotated until the first follower 9 displaced toward the clutch 20 stops. The accumulator 10c outputs a load until the first follower 9 stops. When the first follower 9 is displaced toward the clutch 20, the release fork 27 (see FIG. 1) is operated and the urging force of the spring 25 is released. As a result, the clutch 20 is released. Here, the cam 6 has a pressure angle with respect to the first follower 9 when the clutch 20 is released (the contour of the cam 6 and the common normal line n of the first follower and the movement direction m of the first follower 9). (The angle formed) is set to substantially 0 °.

  As a result, the common normal n and the movement direction m of the first follower 9 coincide with each other, so that the first follower 9 moves in the direction of the cam 6 by the urging force of the spring 25 (see FIG. 1) of the clutch 20. However, the cam 6 cannot rotate. Therefore, the energy consumed by the motor M (see FIG. 1) for maintaining the released state of the clutch 20 can be greatly reduced. Further, since the released state of the clutch 20 can be maintained simply by controlling the rotation angle of the cam 6 and stopping the cam 6 so that the pressure angle is substantially 0 °, the mechanism can be greatly simplified. The interrupting device 1 can be reduced in size.

  Moreover, since the intermittent device 1 can convert the rotational motion of the motor M (see FIG. 1) into a linear motion by the cam 6, the structure can be simplified. Further, when releasing and engaging the clutch using the crank, it is necessary to secure a space enough for the crank to swing, but the cam 6 displaces the first follower 9 and the second follower 10. In the interrupting device 1 to be operated, it is not necessary to secure a space necessary for swinging the crank, so that the interrupting device 1 can be reduced in size and simplified. Furthermore, since the positions, speeds, and timings of the first follower 9 and the second follower 10 are arbitrarily determined from the cam shape, the design flexibility of the interrupting device 1 can be improved.

  Note that the pressure angle is set to substantially 0 ° means that the movement direction m of the first follower 9 (or the second follower 10) substantially coincides with the common normal n of the cam 6. By doing so, the friction between the first follower 9 (or the second follower 10) and the cam 6 is reduced to a negligible level.

  Next, the cam shaft torque necessary for the rotation of the cam 6 will be described with reference to FIG. 4A is a schematic diagram of the cam 6 and the first follower 9 for explaining the cam shaft torque when the first follower 9 (the thrust bar 9b) is displaced, and FIG. 4B is a second follower. It is a schematic diagram of the cam 6 and the 2nd follower 10 explaining the cam shaft torque when displacing the joint 10 (shaft 10b). In FIG. 4A, Rn is a cam radius, dα is a rotation angle when the cam 6 is rotated from a point a to a point b on the cam track surface around the cam shaft 7, and Snc is a tangent at the point b of the cam 6. A force P acting in the direction, P, is a force generated by the spring 25 of the clutch 20 (see FIG. 1). In FIG. 4B, Sns is a force acting in the tangential direction at the point b of the cam 6, and Pns0 is an initial load output by the energy storage portion 10c (see FIG. 1) (the energy storage portion 10c is the cam base circle radius). (The load generated by being compressed).

In FIG. 4, when the rotation angle of the cam 6 is dα, db = Rn (1−cos (dα)) and da = Rn · sin (dα). If the angle between the tangent line of the cam 6 at the point a and the straight line connecting the points a and b is θn, θn = tan ⁻¹ {(dR + db) / da} −tan ⁻¹ (db / da) Represented. Here, in FIG. 4A, the displacement amount δn of the thrust bar 9b toward the clutch 20 is expressed as δn = (Rn−R ₀ ) + dR, where the cam basic circle radius is R ₀ . The force Pnc applied to the thrust bar 9b by the displacement of the thrust bar 9b toward the clutch 20 (displacement amount δn) is the force P generated by the spring 25 of the clutch 20 (see FIG. 1) and the lever ratio of the clutch 20 It is expressed by a function f (δn) taking i into account.

  As a result, the tangential force Snc at the point b of the cam 6 required when releasing the clutch 20 to be engaged is expressed as Snc = Pnc (tan θn + μ). Note that μ is a coefficient of friction between the cam 6 and the contact 9a (see FIG. 1). Here, the camshaft torque (hereinafter referred to as “first camshaft torque”) Mnc when the first follower 9 (the thrust bar 9b) is displaced in the direction in which the clutch 20 is released is Mnc = Snc (Rn + dR). Represented. The first camshaft torque Mnc can be approximated by substituting the above-described equations for this equation.

  Next, in FIG. 4B, the force Pns applied to the shaft 10b by the energy storage portion 10c (see FIG. 1) of the second follower 10 by the displacement (displacement amount δn) of the shaft 10b is the energy storage portion. From the elastic modulus k of 10c and the initial load Pns0 of the energy storage portion 10c, it is expressed as Pns = k · δn + Pns0. When the clutch 20 is engaged, a load is input to the energy storage unit 10c by the cam 6, and the tangential force Sns at the point b of the cam 6 acting at this time is Sns = Pns (tan θn−μ). Represented. Note that μ is a friction coefficient between the cam 6 and the contact 10a (see FIG. 1).

  Here, the camshaft torque (hereinafter referred to as “second camshaft torque”) Mns required to displace the second follower 10 in the direction in which the clutch 20 is engaged and accumulate the load in the accumulator 10c is as follows. , Mns = Sns (Rn + dR). The second camshaft torque Mns can be approximated by substituting the above-described equations into this equation.

  As described above, the first cam shaft torque and the second cam shaft torque are the radius and shape (contour) of the cam 6, characteristics such as the elastic modulus of the spring 25 (see FIG. 1) of the clutch 20, and the lever ratio of the clutch 20. Further, it is obtained from the characteristics such as the elastic modulus of the accumulator 10c (the urging force of the second follower 10), the friction coefficient between the cam 6 and the contacts 9a and 10a (see FIG. 1), and the like.

  Here, the characteristics and lever ratio of the spring 25 of the clutch 20 are known, and the friction coefficient between the cam 6 and the contacts 9a and 10a can also be set. Accordingly, the radius and shape (contour) of the cam 6 and the urging force of the second follower 10 can be set from the first cam shaft torque and the second cam shaft torque. As described above, since the intermittent device 1 uses the cam 6 to displace the first follower 9 and the second follower 10, the cam 1 can be set by setting the first cam shaft torque and the second cam shaft torque. The radius and shape (contour) of 6 and the urging force of the second follower 10 can be set.

  Here, FIG. 5 is a diagram illustrating an example of calculation results of the first cam shaft torque and the second cam shaft torque when the clutch 20 is released. In FIG. 5, the horizontal axis indicates the rotation angle of the cam 6, and the vertical axis indicates the torque. A and B are rotation angles of the cam 6 when the first follower 9 or the second follower 10 is in a stationary state. In FIG. 5, the second camshaft torque is 0 or less (different in direction from the first camshaft torque). This is because the load input to the second follower 10 when the clutch 20 is engaged is output from the second follower 10 to the clutch 20 side at the corresponding rotation angle when the clutch 20 is released. Assisting the release of 20 is shown. Further, the cam shaft torque curve shown in FIG. 5 is obtained by canceling the first cam shaft torque and the second cam shaft torque with each other.

  Referring to FIG. 5, it can be seen that the first camshaft torque is leveled except for the section B (the vicinity of the torque is 0). Similarly, it can be seen that the second camshaft torque is also leveled except for the sections A and B (torque is near 0). As a result, since the load accumulated in the energy storage unit 10c (see FIG. 1) is output from the energy storage unit 10c to the clutch 20 side when the clutch 20 is released, the motor M (see FIG. 1) is necessary. The load on the motor M can be reduced by leveling the cam shaft torque.

  This optimizes the shape of the cam 6 and the urging force of the second follower 10 based on the calculation method of the first cam shaft torque and the second cam shaft torque described with reference to FIG. It depends on. The shape of the cam 6 and the urging force of the second follower 10 are set so that the first camshaft torque is canceled by the second camshaft torque at the corresponding rotation angle. As a result, the peak torque of the camshaft torque (first camshaft torque−second camshaft torque) can be reduced, and the peak current can be reduced. Therefore, the motor M can be reduced in size. Further, since the camshaft torque can be leveled, the cam 6 can be prevented from rattling or uneven rotation.

  As described above, the present invention has been described based on the embodiments, but the present invention is not limited to the above embodiments, and various improvements and modifications can be made without departing from the spirit of the present invention. It can be easily guessed. For example, the numerical values (for example, the quantity of each component) given in the above embodiment are examples, and other numerical values can naturally be adopted.

  In the above-described embodiment, the case where the cam 6 of the interrupting device 1 is configured by a plate cam has been described. However, the present invention is not necessarily limited thereto, and other cams can naturally be employed. Other cams include, for example, a flat cam groove cam similar to a plate cam, a three-dimensional cam end face cam, and a cylindrical groove cam. An arbitrary cam can be appropriately selected according to the characteristics of the clutch 1 and the power storage unit 10c.

  In the above embodiment, the case where one cam 6 is disposed on the cam shaft 7 has been described. However, the present invention is not necessarily limited to this, and two or more cams are arranged in parallel on the cam shaft 7. Of course, it is also possible to arrange the first follower 9 and the second follower 10 in each cam. In this case, the cam shape of the cam in which the first follower 9 is disposed is designed according to the characteristics of the clutch 20, and the cam shape of the cam in which the second follower 10 is disposed is the accumulator 10c. Designed according to the characteristics of Each cam shape may be determined in consideration of the characteristics of the clutch 20 or the accumulator 10c, so that each cam shape can be easily designed.

  In the above embodiment, the case where the clutch 20 is configured as a single-plate friction clutch has been described. However, the present invention is not necessarily limited to this, and other clutches can naturally be employed. Examples of the other clutch include other friction clutches such as a multi-plate clutch, a disk clutch, a drum clutch, and a conical clutch.

  In the above embodiment, the case where the power transmission means from the motor M to the cam 6 is the worm 5 and the worm wheel (not shown) has been described. However, the present invention is not necessarily limited to this, and other transmission means may be used. It is also possible to adopt. Examples of other transmission means include a spur gear device, a planetary gear device, and combinations thereof.

1 Interrupting device 6 Cam 9 First follower 9a Contact (part of the first follower)
9b Stick (part of 1st follower)
10 Second follower 10a Contact (part of second follower)
10b Shaft (part of second follower)
10c Energy storage (part of second follower)
20 Clutch M Motor

Claims (3)

In the intermittent device that engages and disengages a clutch that is engaged by a biasing force of a spring and released by inputting a force that resists the biasing force.
A cam rotated by a motor;
A first follower for pressing the clutch by the cam;
A second follower disposed at a position different from the first follower and biased toward the cam to apply a rotational force in a direction to release the clutch to the cam ;
The second follower comprises a roller follower and a contact that directly contacts the cam;
A shaft that is supported at one end and linearly reciprocates on its own axis;
An accumulator that is compressed and extended with the movement of the shaft and biases the shaft toward the cam;
In the cam, a pressure angle with respect to a moving direction of the shaft when the clutch is engaged is set to substantially 0 °,
The shape of the cam and the urging force of the second follower correspond to the first cam shaft torque that attempts to rotate the cam in a direction to release the clutch by the urging force of the second follower. The intermittent device is set so as to be canceled by a second camshaft torque that attempts to rotate the cam in a direction in which the clutch is engaged by the biasing force of the spring . The cam claim 1 Symbol placement of interrupter pressure angle with respect to the direction of movement of the first follower is characterized in that it is set to substantially 0 ° at which the clutch is released. The biasing force of the shape and the second follower of the cam, the difference between the first cam shaft torque and the second cam shaft torque, except for the retention section is substantially constant with respect to the rotation angle of the cam interrupter according to claim 1 or 2, characterized in that it is set to.

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