JP2010151206A - Rotary-linear motion converting mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To make amplitude of linear reciprocating member continuously changeable without requiring troublesome disassembling and assembling work and troublesome part replacement, in a rotary-linear motion converting mechanism. <P>SOLUTION: The rotary-linear motion converting mechanism 54 includes a rotatable cylindrical cam 66 provided with a cam groove 118, a contact element 110 for guiding along the cam groove 118, an oscillation rod 112 for supporting the contact element 110, a gear shift rod 114, a rod supporting bracket 116, and a linear motion bracket 68. The gear shift rod 114 is movably/rotatably supported by the oscillation rod 112 in the longitudinal direction and can move only in a direction orthogonal to a direction in parallel with the axial direction of the cylindrical cam 66. The linear motion bracket 68 is rotatably supported by the rod supporting bracket 116 which is supported by the oscillation rod 112 to be movable in the longitudinal direction and can reciprocate only in a linear direction in parallel with the axial direction of the cylindrical cam 66. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a rotary linear motion conversion mechanism that is incorporated in, for example, a power transmission device and converts an input motion between a rotary motion and a linear reciprocating motion and outputs it as an output motion.

  Conventionally, a rotary linear motion conversion mechanism that converts an input motion between a rotary motion and a linear reciprocating motion and outputs it as an output motion has been considered. For example, Non-Patent Document 1 describes an example of a conventional structure of a rotating linear motion conversion mechanism that reciprocates a moving table in a linear direction by rotating a rotating shaft. FIG. 7 is a schematic perspective view showing an example of the rotational linear motion conversion mechanism of the conventional structure described in Non-Patent Document 1, and FIG. 8A is a plan view of FIG. (B) is an exploded perspective view of (a). The rotary linear motion conversion mechanism 10 includes a columnar member 14 to which a rotary shaft 12 is attached, a cam member 16 that fixes the columnar member 14 on the inside, and a moving table 18 that is placed on the upper side of the cam member 16. The moving table 18 is supported by a fixed leg portion 20 so as to be movable in the longitudinal direction of the moving table 18 (in the direction of arrow a in FIG. 7). The cam member 16 has a substantially cylindrical shape and is provided with a circular cam groove 22 coaxial with the outer peripheral surface of the cam member 16 on the upper surface, and a pin 24 fixed to the moving table 18 is engaged with the cam groove 22.

  The columnar member 14 is fitted and fixed to an inner portion of the cam member 16 than the cam groove 22. The cylindrical member 14 is eccentric with respect to the cam member 16. The rotating shaft 12 is fixed at a position off the center of the cylindrical member 14. With this configuration, when the cam member 16 moves eccentrically due to the rotation of the rotating shaft 12, the distance between the rotating shaft 12 and the pin 24 changes, and the moving table 18 reciprocates in the linear direction indicated by the arrow a in FIG. To do. The cylindrical member 14 can be attached to and detached from the cam member 16, and the stroke, which is the amplitude of the moving table 18, can be changed by changing the distance between the center O1 of the rotating shaft 12 and the center O2 of the cam member 16. That is, FIG. 9 shows the case where (a) increases the distance between the rotation axis center O1 and the cam member center O2, and (b) shows the distance between the rotation axis center O1 and the cam member center O2. FIG. 9 is a schematic diagram of FIG. As shown in FIG. 9A, if the distance La between the rotation shaft 12 center O1 and the cam member 16 center O2 is increased, the stroke of the moving table 18 (FIG. 7) increases, and conversely, the rotation shaft 12 center. If the distance Lb between O1 and the center O2 of the cam member 16 is reduced, the stroke is reduced.

"Mecha Idea 1454", Nikkei Mechanical, June 1, 1998, No0758

  However, in such a conventional structure, every time the stroke of the moving table 18, that is, the stroke of the pin 24 is changed, the driving of the rotary linear motion conversion mechanism 10 is stopped, and the operator manually rotates the rotary shaft 12 with respect to the cam member 16. It is necessary to change the fitting position of the cylindrical member 14 (FIGS. 7 and 8) so as to change the position. For this reason, every time the stroke of the pin 24 is changed, it is necessary to perform disassembly / assembly work or part replacement of the rotary linear motion conversion mechanism 10. Therefore, in the conventional structure, the amplitude of the member that reciprocates linearly can be changed only discretely, and a troublesome work is required.

  Further, in the conventional structure, the speed of the moving table 18, that is, the speed of the pin 24 is sinusoidal as shown in FIG. FIG. 10 is a diagram illustrating temporal changes in absolute values of pin displacement amounts in an example of a conventional structure. In FIG. 10, a solid line a represents the case of FIG. 9A, and a broken line b represents the case of FIG. 9B. Thus, with the conventional structure, the speed of the pin 24 cannot be made constant regardless of the amount of movement of the pin 24. For this reason, the conventional structure cannot output a constant velocity linear motion. On the other hand, constant velocity linear motion can be output by changing the shape of the cam groove 22 at a distance between the center of the specific rotating shaft 12 and the center of the cam member 16. When the distance from the center of the cam member 16 is changed, constant velocity linear motion cannot be output in the entire range of rotation of the rotary shaft 12.

  Among the problems of the prior art as described above, the present invention continuously changes the amplitude of a member that reciprocates linearly at least in a rotary linear motion conversion mechanism without requiring troublesome disassembly and assembly work or replacement of parts. The purpose is to make it possible.

  The rotational linear motion conversion mechanism according to the present invention is a rotational linear motion conversion mechanism that converts an input motion between a rotational motion and a linear reciprocating motion and outputs it as an output motion, and is provided with a cam groove on the outer peripheral surface, A cylindrical cam rotatable around the axial direction, a contact guided along the cam groove and movable only in a direction parallel to the axial direction of the cylindrical cam, and a rocker rotatably supporting the contact It has a moving rod and a rocking support that is supported so as to be movable and rotatable in the longitudinal direction of the rocking rod with respect to the rocking rod, and moves only in a direction perpendicular to the direction parallel to the axial direction of the cylindrical cam. Variable speed rod, a rod support bracket supported so as to be movable only in the longitudinal direction of the rocking rod with respect to the rocking rod, and a linear direction that is rotatably supported by the rod support bracket and parallel to the axial direction of the cylindrical cam Reciprocating only A conversion mechanism, characterized in that it comprises a linear motion bracket Noh, a.

  According to the rotary linear motion conversion mechanism described above, when the cylindrical cam rotates, the linear reciprocating motion is performed when the cylindrical cam rotates without requiring troublesome disassembly and assembly work such as replacement of the cylindrical cam or replacement of parts. It becomes possible to continuously change the amplitude of the linear motion bracket as a member.

  In the rotary linear motion conversion mechanism according to the present invention, preferably, the cylindrical cam is driven to rotate about the axial direction, and the linear motion bracket can output a reciprocating motion in a linear direction parallel to the axial direction of the cylindrical cam. And

  In the rotation linear motion conversion mechanism according to the present invention, preferably, the rocking rod has a linear groove portion provided in the longitudinal direction of the rocking rod, and the speed change rod has a rocking support portion in the groove portion. Is supported so as to be rotatable and movable in the longitudinal direction of the groove.

  In the rotational linear motion conversion mechanism according to the present invention, preferably, the cam groove is provided so as to be continuous over the entire outer periphery of the cylindrical cam, and the circumferential direction of the outer peripheral surface of the cylindrical cam is flat. When it is unfolded, it is formed so that at least part of the straight portion is inclined with respect to the circumferential direction.

  According to the rotational linear motion conversion mechanism described above, the linear motion can be linearly corrected within at least a part of the rotational motion of the cylindrical cam, which is a rotational member, regardless of the change in the amplitude of the linear motion bracket, which is a linear reciprocating member. It is possible to output a constant velocity linear motion of the moving bracket.

  According to the rotational linear motion conversion mechanism according to the present invention, it is possible to continuously change the amplitude of the linear motion bracket, which is a member that linearly reciprocates, without requiring troublesome disassembly and assembly work or parts replacement. . Also, by changing the shape of the cam groove, it is possible to easily set a mechanism that can output various types of linear reciprocating motion such as constant velocity linear motion, and the amplitude of the linear reciprocating motion can be set continuously. For example, it can be expanded proportionally.

  Hereinafter, an example of an embodiment according to the present invention will be described in detail with reference to the drawings. The rotational linear motion conversion mechanism of the present embodiment is used for various applications such as an apparatus using a rotational linear motion conversion mechanism that converts an input motion between a rotational motion and a linear reciprocating motion and outputs it as an output motion. For example, it is used by being incorporated in a power transmission device.

  The rotational linear motion conversion mechanism 54 of the present embodiment will be described with reference to FIGS. FIG. 1A is a schematic diagram illustrating a rotational linear motion conversion mechanism according to the present embodiment, and FIG. 1B is a diagram viewed from the bottom to the top of FIG. 2A is a view of a part of the outer peripheral surface of the cylindrical cam that constitutes the rotational linear motion conversion mechanism of FIG. 1, and FIG. 2B is a view showing the circumferential direction of the cylindrical cam in an expanded state. is there. FIG. 3 is a diagram illustrating an example of a temporal change in the displacement amount of the contact constituting the rotating linear motion conversion mechanism. FIG. 4 is a diagram illustrating three operating states at different points in time when the speed change rod is at the P1 position in FIG. FIG. 5 is a diagram showing three operating states at different points in time when the speed change rod is in the P4 position in FIG. FIG. 6 is a diagram showing temporal changes in the moving direction and the amount of displacement of the linear motion bracket when the speed change rod is at four different positions in FIG.

  As shown in FIG. 1, the rotational linear motion conversion mechanism 54 converts an input motion as a rotational motion input to a cylindrical cam 66 from an input side member (not shown) that is rotationally driven between a rotational motion and a linear reciprocating motion. And output as a linear reciprocating motion of the linear motion bracket 68. For this purpose, for example, a driven gear (not shown) is fixed to a cylindrical cam 66 constituting the rotating linear motion converting mechanism 54 on a cam shaft 106 fixed coaxially with the cylindrical cam 66. Then, the drive gear fixed to the input shaft (not shown) is engaged with the driven gear so that the cylindrical cam 66 is rotationally driven around the axial direction of the cylindrical cam 66. The driving mechanism of the cylindrical cam 66 is not limited to such a configuration. For example, a configuration in which the cylindrical cam 66 is rotationally driven directly or via another member by an input side member such as a motor is employed. You can also

  As shown in FIG. 1, the rotational linear motion conversion mechanism 54 includes a cylindrical cam 66, a contact 110, a swing rod 112, a speed change rod 114, a rod support bracket 116, and a linear motion bracket 68. The cylindrical cam 66 is supported so as to be rotatable about the axial direction of the cam shaft 106 with respect to a fixing member such as a housing (not shown). Further, a cam groove 118 is provided on the outer peripheral surface which is a cylindrical surface of the cylindrical cam 66.

  As shown in FIG. 2, the cam groove 118 is provided so as to be continuous over the entire circumference of the outer circumferential surface of the cylindrical cam 66, and as shown in FIG. When the circumferential direction is developed on a plane, it is formed so that at least a linear portion inclined with respect to the circumferential direction is provided. In the present embodiment, the cam groove 118 has a first straight portion 120 and a second straight portion 124 that are inclined with respect to the circumferential direction of the cylindrical cam 66. The second straight portion 124 is continuous via a pair of bent portions 122 that are substantially perpendicular to both ends of the first straight portion 120, and is different from the inclination direction of the first straight portion 120 with respect to the circumferential direction of the cylindrical cam 66. It is inclined. In the present embodiment, the cam groove 118 is not limited to such a shape, and when the circumferential direction of the outer circumferential surface of the cylindrical cam 66 is developed on a plane, at least a part thereof is inclined with respect to the circumferential direction. A straight line portion may be provided. The cross-sectional shape of the cam groove 118 is, for example, a shape in which a U-shaped corner is a right angle.

  As shown in FIG. 1, the contact 110 is, for example, in the form of a roller or a pin, and its base end is one end in the longitudinal direction of a long thin plate-like rocking rod 112 (FIG. 1 (a) ( It is rotatably supported at the right end part b). The tip of the contactor 110 is inserted along the cam groove 118 by being inserted into the cam groove 118, and is parallel to the axial direction of the cylindrical cam 66 (in the direction of arrow L1 in FIG. 1A). In other words, it is possible to reciprocate only, that is, translational movement is possible only in the axial direction of the cylindrical cam 66. In this case, for example, the side surface of the contact 110 rolls on the inner wall surface of the cam groove 118, so that the contact 110 is guided along the cam groove 118. In order to regulate the moving direction of the contact 110, for example, a guide portion (not shown) can be provided. For example, the end of the contact 110 opposite to the cylindrical cam 66 is protruded from one surface of the swing rod 112, and the protruding portion is a linear parallel provided in a direction parallel to the axial direction of the cylindrical cam 66. It is possible to regulate the moving direction of the contact 110 by guiding with a pair of guide portions.

  The speed change rod 114 has a rocking support portion 126 such as a pin which is supported so as to be movable and rotatable in the longitudinal direction of the rocking rod 112 with respect to the rocking rod 112. It is movable only in the direction orthogonal to the parallel direction (the direction of arrow L2 in FIG. 8A). For this purpose, the rocking rod 112 has a linear groove 128 provided in the longitudinal direction of the rocking rod 112. The swing support portion 126 provided on the speed change rod 114 is inserted and supported so as to be rotatable in the groove portion and movable in the longitudinal direction of the groove 128. For example, the speed change rod 114 is constituted by two parallel leg portions and a support pin which is a swing support portion 126 connected to one end portion in the longitudinal direction of the leg portion, and the support pin is inserted and supported in the groove 128. Further, the speed change rod 114 can be moved only in the left-right direction in FIG. 1A while maintaining the posture in the direction parallel to the camshaft 106 (vertical direction in FIG. 1A), and is attached to a fixed portion (not shown). It is supported for guidance. The speed change rod 114 is mechanically connected to an electric or hydraulic actuator (not shown), a rod connected to a shift lever, or the like, and is a driver of a power transmission device including the rotary linear motion conversion mechanism 54. It is possible to move in the L2 direction of FIG.

  Further, the rod support bracket 116 supports the swing rod 112 so as to be movable only in the longitudinal direction of the swing rod 112. For this purpose, for example, the rod support bracket 116 includes a guide portion 130, a substantially L-shaped arm portion 132 connected to the guide portion 130, and a support shaft 134 connected to an end portion of the arm portion 132. The swing rod 112 is inserted in a hole provided in the guide portion 130 so as to be slidable in the axial direction.

  Further, the linear motion bracket 68 has a hole 136, and supports the support shaft 134 in the hole 136 in a rotatable manner. For example, a bearing can be provided between the hole 136 and the support shaft 134. In FIG. 1, the linear motion bracket 68 is illustrated in such a manner that the outer shape of the linear motion bracket 68 is a cylindrical surface, but this is for simplification of the description. However, other shapes may be used.

  The linear motion bracket 68 can reciprocate only in a linear direction parallel to the axial direction of the cylindrical cam 66 (L3 direction in FIG. 1A), and can output the reciprocating motion of the linear motion bracket 68. For example, the linear motion bracket 68 is movable in the axial direction of a shaft fixed to a fixed member such as a housing in parallel with the cam shaft 106 or supported on a fixed member so as to be rotatable in parallel with the cam shaft 106. To support. According to the rotating linear motion converting mechanism 54 configured as described above, the amplitude of the linear motion bracket 68 can be continuously changed by the movement of the speed change rod 114. That is, by adjusting the position of the speed change rod 114, the amplitude of the linear reciprocating motion of the linear motion bracket 68 can be changed continuously from 0 to the maximum amplitude in a proportional manner. Further, the linear motion bracket 68 that reciprocates linearly can perform a constant speed motion in at least a part of the range.

  Next, the operation of the rotating linear motion conversion mechanism 54 will be described. That is, as described above, when rotational movement is given to the cylindrical cam 66 from the input side member such as the output shaft and the motor, the contact 110 (FIG. 1) moves along a direction parallel to the axial direction of the cylindrical cam 66. Reciprocate. As a result, as shown in FIG. 3, the contact 110 is displaced corresponding to the shape of the cam groove 118 (FIG. 2).

  As shown in FIG. 1, since the fulcrum of the swing rod 112 on which the contact 110 is supported is determined by the position of the speed change rod 114, the translation of the contact 110 relative to the axial direction of the cylindrical cam 66, that is, the reciprocation in the linear direction. Along with the movement, the linear motion bracket 68 also performs a translational movement relative to the axial direction of the cylindrical cam 66, that is, a reciprocating movement in the linear direction. The amplitude when the linear motion bracket 68 reciprocates linearly is determined by the position of the speed change rod 114. That is, the speed change rod 114 is positioned at P1 in FIG. 1A, the swing support portion 126 is positioned on the central axis of the support shaft 134 of the rod support bracket 116, and the fulcrum of the swing rod 112 is defined as the action point. In the case of matching with the linear motion bracket 68, the displacement of the linear motion bracket 68 becomes zero regardless of the rotation of the cylindrical cam 66, as shown in FIG. That is, even if a rotational motion is given, the amplitude of the linear motion bracket 68 can be made zero.

  On the other hand, when the speed change rod 114 is positioned at P4 in FIG. 1A and the speed change rod 114 is moved as close as possible to the cylindrical cam 66 side, as shown in FIG. 1 approaches the contactor 110 (FIG. 1A), the linear motion bracket 68 is greatly displaced with the rotation of the cylindrical cam 66, and the amplitude of the linear motion bracket 68 becomes Dmax. Further, when the speed change rod 114 is positioned in the middle between P1 and P4 in FIG. 1A, the amplitude of the linear motion bracket 68 has an intermediate magnitude between 0 and Dmax.

  FIG. 6 shows a temporal change in the amount of displacement of the linear motion bracket 68. In FIG. 6, a solid line T1 coinciding with the horizontal axis having a displacement amount of 0 indicates that the speed change rod 114 is positioned at P1 in FIG. 1A, and a broken line T2 indicates that the speed change rod 114 is P2 in FIG. When the speed change rod 114 is located at P3 in FIG. 1A, the alternate long and short dash line T3 indicates the case where the speed change rod 114 is located at P4 in FIG. , Respectively. Thus, the amplitude of the linear motion bracket 68 can be changed according to the position of the speed change rod 114. In addition, as shown in FIG. 2, when the circumferential direction of the outer peripheral surface of the cylindrical cam 66 is developed on a plane, the cam groove 118 has the first straight portion 120 and the second straight portion 124. The case where the speed of the moving bracket 68 (FIG. 1 (a)) is constant and the first speed and the second speed are alternately repeated. For example, in the region of time C1 in FIG. 6, the linear motion bracket 68 moves at a constant first speed, and in the region of time C2, the linear motion bracket 68 moves at a constant second speed. Therefore, when the linear motion bracket 68 constituting the rotary linear motion conversion mechanism 54 moves in one direction (for example, upward in FIG. 1A), the contact 110 moves the first linear portion 120. When the linear motion bracket 68 moves in one direction and the speed change rod 114 is at a fixed position, the linear motion bracket 68 is always moved at a constant speed within a range where the contact 110 does not fold over the bent portion 122. be able to. Further, when the linear motion bracket 68 moves in the other direction (for example, downward in FIG. 1A), if the contactor 110 moves the second linear portion 124, the linear motion bracket 68 moves in the other direction. In the case of movement, when the speed change rod 114 is at a fixed position, the linear motion bracket 68 can always be moved at a constant speed as long as the contact 110 does not fold over the bent portion 122.

  Thus, according to the rotational linear motion conversion mechanism 54, when the cylindrical cam 66 rotates without requiring troublesome disassembly and assembly work such as replacement of the cylindrical cam 66, which is a member that rotates, and parts replacement, By the movement of the speed change rod 114, it is possible to continuously change the amplitude of the linear motion bracket 68 that is a member that reciprocates linearly. That is, when a rotational motion is input to the camshaft 106, the linear reciprocating motion of the linear motion bracket 68 can be output, and the amplitude of the linear reciprocating motion that is the output can be continuously changed. Moreover, in this Embodiment, when the circumferential direction of the outer peripheral surface of the cylindrical cam 66 is expand | deployed on a plane, it has the 1st linear part 120 and the 2nd linear part 124. For this reason, it is possible to output the constant velocity linear motion of the linear motion bracket 68 within at least a part of the rotational motion of the cylindrical cam 66 regardless of the change in the amplitude of the linear motion bracket 68.

  Further, when a rotational motion is given to the cylindrical cam 66 from the input shaft as described above, the contactor 110 reciprocates along a direction parallel to the axial direction of the cylindrical cam 66, and the amplitude and speed thereof are changed to the cam groove. It can be changed according to the setting of 118. That is, by changing the shape of the cam groove 118 using the rotational linear motion conversion mechanism 54 of the present embodiment, it is possible to easily set a mechanism that can output various forms of linear reciprocating motion. The amplitude of the linear reciprocation can be increased continuously, for example proportionally. For example, it is possible to easily output a linear motion other than the constant velocity linear motion.

  In the present embodiment, the relationship between the input side and the output side can be reversed. For example, the linear motion bracket 68 is connected to the input side member, and the linear motion bracket is linearly reciprocated, whereby the cylindrical cam 66 is rotated, and the rotation of the cam shaft 106 can be taken out as an output motion.

(A) is the schematic which shows the rotation linear motion conversion mechanism of this Embodiment, (b) is the figure which looked upwards from the downward direction of (a). (A) is the figure which looked at a part of outer peripheral surface of the cylindrical cam which comprises the rotation linear motion conversion mechanism of FIG. 1, (b) is the figure which expand | deploys and shows the circumferential direction of a cylindrical cam. It is a figure which shows one example of the time change of the displacement amount of the contactor which comprises a rotation linear motion conversion mechanism. It is a figure which shows three operation states of a different time when a speed-change rod exists in the P1 position of FIG. It is a figure which shows three operation states of a different time in case a speed-change rod exists in the P4 position of FIG. It is a figure which shows the time change of the moving direction and displacement amount of a linear motion bracket when a speed-change rod exists in four different positions of FIG. It is a schematic perspective view which shows the rotational linear motion conversion mechanism of an example of the conventional structure. (A) is the figure which took out the cylindrical cam from FIG. 7, and was seen from upper direction, (b) is the exploded perspective view of (a). (A) when the distance between the rotation axis center O1 and the center O2 of the cam member is increased, and (b) when the distance between the rotation axis center O1 and the center O2 of the cam member is decreased, FIG. 9 is a schematic diagram of FIG. It is a figure which shows the time change of the absolute value of the displacement amount of a pin in one example of the conventional structure.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 Rotation linear motion conversion mechanism, 12 Rotating shaft, 14 Cylinder member, 16 Cam member, 18 Moving table, 20 Leg part, 22 Cam groove, 24 pin, 54 Rotation linear motion conversion mechanism, 66 Cylindrical cam, 68 Linear motion bracket, 106 Cam shaft, 110 Contact, 112 Oscillating rod, 114 Transmission rod, 116 Rod support bracket, 118 Cam groove, 120 First linear part, 122 Bent part, 124 Second linear part, 126 Oscillating support part, 128 groove , 130 guide part, 132 arm part, 134 support shaft, 136 hole part.

Claims (4)

A rotary linear motion conversion mechanism that converts input motion between rotational motion and linear reciprocating motion and outputs it as output motion,
A cam groove provided on the outer peripheral surface and rotatable about the axial direction;
A contactor guided along the cam groove and movable only in a direction parallel to the axial direction of the cylindrical cam;
An oscillating rod that rotatably supports the contact;
A shifting rod having a swinging support portion that is movable and rotatable in the longitudinal direction of the swinging rod with respect to the swinging rod, and is movable only in a direction perpendicular to the direction parallel to the axial direction of the cylindrical cam. When,
A rod support bracket supported so as to be movable only in the longitudinal direction of the swing rod with respect to the swing rod;
And a linear motion bracket that is rotatably supported by the rod support bracket and that can reciprocate only in a linear direction parallel to the axial direction of the cylindrical cam. In the rotation linear motion conversion mechanism according to claim 1,
The cylindrical cam is driven to rotate around the axial direction,
The linear motion bracket is a rotary linear motion conversion mechanism characterized in that it can output a reciprocating motion in a linear direction parallel to the axial direction of the cylindrical cam. In the rotation linear motion conversion mechanism according to claim 1 or 2,
The rocking rod has a linear groove provided in the longitudinal direction of the rocking rod,
The speed change rod has a rotation linear motion conversion mechanism characterized in that the swing support portion is inserted and supported in the groove portion so as to be rotatable and movable in the longitudinal direction of the groove portion. In the rotation linear motion conversion mechanism according to any one of claims 1 to 3,
The cam groove is provided so as to be continuous over the entire circumference of the outer peripheral surface of the cylindrical cam, and when the circumferential direction of the outer peripheral surface of the cylindrical cam is developed on a flat surface, the cam groove is at least partially inclined with respect to the circumferential direction. A rotary linear motion conversion mechanism, characterized in that it is formed so as to be provided with a portion.

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