JP2007211869A - Positioning mechanism of intermittent transmission system and intermittent transmission system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a positioning mechanism capable of securing a smooth entrance of a roller into an abutting engagement section in the positioning mechanism of an intermittent transmission system having a roller arrangement method for making rollers rotatably circulate through the abutting engagement section. <P>SOLUTION: A roller arrangement structure 20 for making the rollers circulate through the abutting engagement section between a driving cam 3 mounted on an input shaft 1 and a cam follower 4 mounted on an output shaft 2 is arranged in the positioning mechanism. The roller arrangement structure 20 comprises a roller circulating passage 21 arranged on the driving cam 3, rolling rollers 13, 13... moving the roller circulating passage 21, and a propelling elastic member 22 for giving propelling force to the rolling rollers 13, 13... in an advancing direction of the rolling rollers 13, 13... while being interposed between the rolling rollers 13, 13.... Thus, the propelling force is given to the rolling rollers 13, 13... by the propelling elastic member 22, and the rolling rollers 13 are smoothly forwarded into the roller circulating passage 21 formed on the abutting engagement section between the driving cam 3 and cam follower 4. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

    The present invention relates to a positioning mechanism for an intermittent transmission device and an intermittent transmission device, and more specifically, by continuously driving an input shaft by cam driving a driven body attached to an output shaft by a drive body attached to the input shaft. The present invention relates to a positioning mechanism that positions an intermittent index angle of an output shaft during a stationary period in an intermittent transmission device that converts motion to intermittent rotational motion of an output shaft.

  The intermittent transmission device is used as an indexing device that constitutes a main part of an intermittent positioning device of an automatic machine, such as an intermittent conveyor, a feeding device, or an index table, which are installed in various product manufacturing processes.

  As this type of intermittent transmission device, a cam mechanism having various configurations such as a parallel cam mechanism or a geneva mechanism is used. These cam mechanisms are appropriately selected according to the purpose, such as the positional relationship of the movement direction of the driven side with respect to the driving side. Selection is adopted.

  For example, in the parallel cam mechanism, as shown in FIG. 13, an input shaft a and an output shaft b are arranged in parallel, and a drive cam c and a cam follower d are attached to the input shaft a and the output shaft b, respectively. This is a flat cam mechanism.

  The drive cam c has a three-layer structure in which a first cam plate e, a third cam plate f, and a second cam plate g are integrally formed in a stacked manner, while the cam follower d has three of the drive cams c. It consists of a first follower roller h that engages with cam members e, f, and g constituting a layer structure, a turret i that is a cam follower body, and a second follower roller j.

  The third cam plate f of the drive cam c constitutes a positioning mechanism for positioning the intermittent index angle in the parallel cam mechanism in cooperation with the turret i of the cam follower d. That is, the third cam plate f has a fan-shaped contour shape, and a plurality of needle rollers k, k,... The arcuate array portion forms a rotation restricting cam surface. Correspondingly, arc-shaped recesses l are provided at equal intervals on the outer peripheral surface of the turret i of the cam follower d, and the third cam plate f with respect to the arc surface m of the recesses l during the stopping period. The needle rollers k, k,... Are in contact with and engaged with each other while rolling, thereby positioning and fixing the intermittent indexing rotation of the cam follower d.

  When the drive cam c is continuously rotated integrally by the input shaft a, the cam members e, f, and g of the drive cam c are respectively transferred to the cam follower members h, i, and j of the cam follower d. The cam follower d is cam-driven by abutting and engaging with each other, whereby the output shaft b is intermittently rotated at a predetermined interval (see, for example, Patent Document 1).

  However, such a conventional parallel cam mechanism has the following problems and has been demanded to be improved.

  That is, the rotation of the drive cam c of the input shaft a causes the needle rollers k, k,... Of the third cam plate f to enter the concave portion l of the turret i of the cam follower d and contact with the arcuate surface m while rolling. When engaged, as shown in FIG. 13 (b), these needle rollers k, k,... Are rollers formed by the arcuate outer peripheral surface of the third cam plate f and the arcuate surface m of the concave portion l of the turret i. In the circulation path, these arcuate surfaces are pressed into contact with each other with a predetermined preload from both sides.

  Therefore, when these needle rollers k, k,... Receive a certain amount of resistance when entering the roller circulation path formed by the two circular arc surfaces, the needle rollers k, k,. ... they are in pressure contact with each other, thereby preventing smooth rolling of the needle rollers k, k, and in the worst case, the rolling of the needle roller k is completely stopped, and thus the input shaft While the rotational resistance of a increases, the smooth rotation operation | movement of the output shaft b was inhibited, and there existed a problem that an indexing precision and a repetition precision deteriorated.

  Further, the repetition of the locked state due to the pressure contact state between the needle rollers k, k,... Causes wear of the needle roller k. This wear action is shown in FIG. 13 (c) for a right cylindrical needle roller k. Such an axial center portion is deformed into a substantially drum shape. That is, with the needle rollers k, k,... Locked and unable to rotate or revolve, the arcuate outer peripheral portion of the third cam plate f of the input shaft a enters the recess l of the turret i of the output shaft b. As a result, rubbing occurs between the needle roller k and the arcuate surface m of the recess l. As a result, the central portion in the axial direction of the needle roller k is greatly worn, and the drum as shown in FIG. It will be transformed into a shape. As a result, a gap is generated between the drive cam c of the input shaft a and the cam follower d of the output shaft b during the stationary period of the parallel cam mechanism, which spurs a decrease in the indexing accuracy and causes backlash. In addition, when the needle roller k is made of metal, there is a problem that metal powder is generated due to wear of the needle roller k, which reduces the life of parts such as a bearing and the life of the apparatus.

These problems are not limited to the parallel cam mechanism, and are common to other cam mechanisms such as a Geneva mechanism having a similar positioning mechanism.
International Publication WO00 / 57086

  The present invention has been made in view of such conventional problems, and an object of the present invention is to provide a positioning mechanism for an intermittent transmission device having a roller arrangement system that rolls and circulates a contact engagement portion. An object of the present invention is to provide a positioning mechanism having a structure that ensures a smooth approach of a rolling roller to a contact engagement portion.

  Another object of the present invention is to provide an intermittent transmission device having the positioning mechanism.

  In order to achieve the above object, the positioning mechanism of the intermittent transmission device according to the present invention performs continuous rotational motion of the input shaft by cam driving the driven body attached to the output shaft by the drive body attached to the input shaft. A positioning mechanism that is provided in an intermittent transmission device that converts and transmits an intermittent rotational motion of an output shaft, and that positions an intermittent index angle of the output shaft during a stationary period, the contact between the drive body and the driven body A roller arrangement structure that circulates through the engaging portion, and the roller arrangement structure includes a roller circulation path provided in the driving body, a plurality of rolling rollers that move while being guided by rolling in the roller circulation path, and And an elastic member for propulsion interposed between at least a part of the plurality of rolling rollers and imparting a propulsive force in the traveling direction of the rolling rollers.

  As a preferred embodiment, the following configuration can be adopted.

(1) The propulsion elastic member has elasticity in the traveling direction of the rolling roller in a state of being interposed between the rolling rollers.

(2) The propulsion elastic member provides the rolling roller with a propulsive force that can smoothly enter the roller circulation path of the contact engagement portion, and the oil film existing between the rolling rollers is cut. Has a resilience of a magnitude that is not.

(3) The elastic member for propulsion is in the form of a flat plate-like metal plate formed by bending in an arc shape with respect to the moving direction of the rolling roller, and the elastic member for propulsion is the adjacent rolling member. In the state of being interposed between the rollers, the central portion in the length direction of the elastic member for propulsion contacts and engages one of the rolling rollers, and both end edges in the length direction are on the other of the rolling rollers. Abuts and engages.

(4) Both ends of the elastic member for propulsion are guided and held in a pair of guide grooves of the roller circulation path that guides both ends of the rolling roller.

(5) The elastic member for propulsion has a rectangular outline smaller than the rectangular projection surface of the rolling roller in the extended flat plate state.

(6) The propulsion elastic member is made of a softer material than the rolling roller and is made of a metal material having a spring property.

(7) The elastic member for propulsion is disposed evenly over the entire circumference of the roller circulation path for every predetermined number of continuous rolling rollers in the rolling roller array arranged to be able to roll on the roller circulation path. Is done.

  Further, the intermittent transmission device according to the present invention is configured such that the driven body attached to the output shaft is cam-driven by the drive body attached to the input shaft, so that the continuous rotational motion of the input shaft is converted to the intermittent rotational motion of the output shaft. And a positioning means for positioning the intermittent index angle of the output shaft during the stationary period, the positioning means being the positioning mechanism.

  As a preferred embodiment, the following configuration can be adopted.

(1) A contact member in which an elastic member for preload is interposed in at least one of the fitting portions of the apparatus constituent member, and the contact engagement portion between the driving body and the driven body is given a predetermined preload. It is set as the structure kept in a joint state.

(2) A cylindrical gap corresponding to a tolerance of a machining dimension of each component member is formed in a fitting portion of the device component member in which the elastic member for preload is interposed, and the preload is formed in the cylindrical gap. An elastic member for use is interposed.

(3) The preload elastic member has radial elasticity in a state of being interposed in the cylindrical gap of the fitting portion.

(4) The preload elastic member has elasticity that keeps the contact engagement portion in a contact engagement state in which a predetermined preload is applied during the stationary period, and in an indexing period set in the apparatus. It has an elastic repulsive force that can withstand an allowable rotational load.

(5) In the intermittent transmission device, the input shaft and the output shaft are arranged in parallel, the drive body attached to the input shaft is in the form of a drive cam comprising a plurality of cam plates, and is attached to the output shaft. A parallel cam mechanism type device in which a follower roller in which the follower is in contact with and engaged with the cam surface of the cam plate is provided in the form of a cam follower provided in an upright manner in the circumferential direction. A plurality of the positioning mechanisms are provided at equal intervals on the outer peripheral surface of the turret constituting the cam follower and the roller arrangement structure provided on one outer peripheral portion of the cam plate constituting the driving cam, and the roller The rolling rollers having an array structure are provided with arcuate recesses for rolling contact.

(6) In the intermittent transmission device, the input shaft and the output shaft are arranged in parallel, the drive body attached to the input shaft is in the form of a prime mover equipped with an engaging member, and is attached to the output shaft. The driven body is in the form of a driven vehicle having an engagement groove with which the engagement member abuts and engages with the engagement member. The positioning mechanism is integrated with the driving vehicle. A plurality of the roller arrangement structure provided on the outer peripheral portion of the rotation restricting cam provided, and a plurality of arc arrangements provided at equal intervals on the outer peripheral surface of the driven vehicle, and the rolling rollers of the roller arrangement structure are in rolling contact with each other. And an engaging recess.

  According to the positioning mechanism of the intermittent transmission device of the present invention, the roller arrangement structure including the roller arrangement structure that circulates the contact engagement portion between the driving body attached to the input shaft and the driven body attached to the output shaft is provided. Is interposed between at least a part of the roller circulation path provided in the drive body, a plurality of rolling rollers that move while being guided along the roller circulation path, and the plurality of rolling rollers, And an elastic member for propulsion that applies a propulsive force in the traveling direction of the rolling roller. Therefore, the rolling roller is provided with a propulsive force by the elastic member for propulsion, so that the driving body and the driven body abut on each other. It can be smoothly fed (entered) against the resistance force when entering the roller circulation path formed in the engaging portion.

  Therefore, the rolling rollers are not brought into pressure contact with each other outside the upstream side of the roller circulation path of the contact engagement portion, and as a result, smooth rolling of the rolling rollers is ensured. In addition, the smooth rotation operation of the output shaft is ensured, and the indexing accuracy and repeatability can be improved.

  In addition, as a result of ensuring smooth rolling of the rolling roller, wear of the rolling roller is reduced. As a result, during the stationary period of the cam mechanism, between the driving body of the input shaft and the driven body of the output shaft. A pressure contact state in which a predetermined preload is constantly applied stably without a gap is ensured, and from this point, indexing accuracy and repeatability can be improved. Further, generation of metal powder due to wear of the rolling roller is prevented, so that the durability of parts such as bearings is improved and the life of the apparatus is improved.

  Further, in the intermittent transmission device according to the present invention, an elastic member is interposed in at least one of the fitting portions of the device constituent members, and the contact engagement portion between the driving body and the driven body gives a predetermined preload. As a result, the variation in machining accuracy that occurs in the constituent members of the cam mechanism does not affect the cam operation of the cam mechanism. About the contact engagement part of a follower, the press-contact state to which the appropriate preload was given can be maintained in any rotational position relationship.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

Embodiment 1
An intermittent transmission device according to the present invention is shown in FIGS. 1 to 9, and this intermittent transmission device is configured such that a driven body 4 attached to an output shaft 2 is cam-driven by a drive body 3 attached to the input shaft 1. , A device that converts the continuous rotational motion of the input shaft 1 into the intermittent rotational motion of the output shaft 2 and transmits the intermittent motion of an automatic machine such as an intermittent conveyor, a feeding device or an index table used in the manufacturing process of various products. It is suitably used as an indexing device that constitutes the main part of the positioning device.

    The intermittent transmission device has a parallel cam mechanism type configuration. Specifically, as shown in FIGS. 1 and 2, the input shaft 1 and the output shaft 2 arranged in parallel and the input shaft 1 are fixedly mounted. The driven body 3 and the driven body 4 attached and fixed to the output shaft 2 are provided as main parts, and a dwell period, which will be described later, is provided between the driven body 3 and the driven body 4. 1 is provided with a positioning mechanism 5 for positioning the intermittent index angle of the output shaft 2, and a preloading elastic member 6 is interposed in the fitting portion of the constituent members 1 to 4, so that the cam of the driving body 3 is inserted. The contact engagement portion between the surface and the driven body 4 is maintained in a contact engagement state to which a predetermined preload is applied.

  As shown in FIG. 9, the main constituent members 1 to 4 are housed inside the housing 7. Specifically, the input shaft 1 and the output shaft 2 are rotatably supported by bearings 8, 8, 9, 9 on two opposing walls 7a, 7b of the housing 7, respectively. 2, one end side of each of the two is inserted through the walls 7a and 7b and faces the outside, and the input shaft 1 is drivingly connected to a driving source such as an electric motor or a hydraulic motor, while the output shaft 2 is an object to be driven. The drive unit is connected to the input unit of the intermittent positioning device of the automatic machine.

  The driving body 3 is in the form of a driving cam composed of a plurality of cam plates. In the illustrated embodiment, the driving cam 3 is formed from three cam plates 10, 11, and 12. These cam plates 10, 11, and 12 are integrally positioned and fixed in a laminated manner by fixing pins 14, and in the drawing, the first cam plate 10 is disposed at the uppermost portion, and the second cam plate 11 is The third cam plate 12 is disposed between the two cam plates 10 and 11. As shown in FIG. 6, the third cam plate 12 is integrally formed with the input shaft 1, and the first cam plate 10 and the second cam plate 11 are viewed from above and below the third cam plate 12. In addition to being joined in a sandwiched manner, the fixing pins 14 are positioned and fixed in a laminated state in a co-tightened state.

  The outer peripheral surface of the first cam plate 10 includes an arc-shaped first arc surface 10a that operates in a dwell period, which will be described later, and a first cam surface 10b, which operates in an index period, which will be described later. It is supposed to be a cam surface. The outer peripheral contour of the third cam plate 12 as an intermediate body between the first and second cam plates 10 and 11 has a semicircular arc-shaped portion 12 a having a predetermined radius of curvature, and the outer periphery of the third cam plate 12. A plurality of rolling rollers 13, 13,... Constituting the positioning mechanism 5 together with a concave portion 17a of the follower 3 to be described later are arranged in the section so as to be capable of rolling and circulating. The outer peripheral surface of the lowermost second cam plate 11 is a cam surface composed of an arcuate second arc surface 11a that acts during the stationary period and a second cam surface 11b that acts during the indexing period. .

  The follower 4 is in the form of a cam follower that abuts and engages the cam surfaces of the cam plates 10, 11, 12 of the drive cam 3, and in the illustrated embodiment, the cam surface 10a of the first cam plate 10, The first follower roller 15 that abuts and engages with 10b, the second follower roller 16 that abuts and engages with the cam surfaces 11a and 11b of the second cam plate 11, and the rotation restriction of the third cam plate 12 It is provided with the turret 17 which contact | abuts and engages with the rolling rollers 13, 13, ... as a cam surface.

  The first follower rollers 15 are provided upright at equal intervals in the circumferential direction on the upper surface side of the turret 17 as a follower body. In the illustrated example, four first follower rollers are arranged in four equal parts. A roller 15 is provided. The second follower rollers 16 are provided upright at equal intervals in the circumferential direction on the lower surface side of the turret 17, and in the illustrated one, four second follower rollers 16 are provided in four equal parts. ing. In addition, arc-shaped concave portions 17a are provided at equal intervals on the outer peripheral surface of the turret 17, and in the illustrated one, four concave portions 17a, 17a,. These concave portions 17a, 17a,... Constitute the positioning mechanism 5 together with the rolling rollers 13, 13,. As shown in FIGS. 1 and 2, the first follower roller 15 and the second follower roller 16 are disposed corresponding to the arcuate recess 17a in plan view, and The two follower rollers 16 are arranged at an intermediate position between the counterpart follower rollers 16, 16 or 15, 15.

  The relationship between the drive cam 3 and the cam follower 4 is that when a continuous rotational driving force is input to the input shaft 1, the output shaft 2 is set to the output shaft 2 by a set rotational angle during the indexing period that is the driving period. The driving force is output (transmitted), and after that, there is a stationary period that is a non-driving period in which the driving force is not transmitted for a certain period of time, and then intermittently the driving force is output only for the set rotation angle. It is set as the structure which drives.

  In the illustrated embodiment, the cam follower 4 is configured to rotate 90 ° or ¼ while the drive cam 3 rotates 360 ° or one rotation. Specifically, referring to FIG. The shape and dimensions of the cam plates 10, 11, 12 of the drive cam 3, the first and second follower rollers 15, 16 of the cam follower 4, and the turret 17, and these components so that the cam drive described below is performed. The relative arrangement configuration is set.

  In the state shown in FIG. 8A, the first arc surface 10a of the first cam plate 10 of the drive cam 3 is in contact with the first follower roller 15 of the cam follower 4, so that the cam follower 4 is driven to rotate. The state to be started is shown (start position of indexing period).

  When the drive cam 3 rotates 45 ° in the direction of the arrow in the drawing from this starting position, the state shown in FIG. In this state, the first cam surface 10b of the first cam plate 10 of the drive cam 3 is in contact with the first follower roller 15, so that the cam follower 4 is rotated in the direction of the arrow by the drive cam 3. It has been. At this time, the second cam surface 11 b of the second cam plate 11 of the drive cam 3 is in contact with and engaged with the second follower roller 16 of the cam follower 4.

  Further, from this state, when the drive cam 3 is rotated by 45 ° in the direction of the arrow, the state shown in FIG. 8C is obtained, and the state of the first cam plate 10 of the drive cam 3 is similar to the state shown in FIG. The first cam surface 10 b engages and contacts the first follower roller 15 of the cam follower 4, and the cam follower 4 is rotated in the direction of the arrow by the drive cam 3. Similarly to the above, the second cam surface 11 b of the second cam plate 11 of the drive cam 3 is in contact with and engaged with the second follower roller 16 of the cam follower 4.

  Further, when the drive cam 3 is rotated by 45 ° in the direction of the arrow, the state shown in FIG. 8D is obtained, and further rotated by 45 ° in the direction of the arrow, and 180 degrees from the start position of the indexing period in FIG. When rotated, the state shown in FIG. 8 (e) is obtained, and the second cam surface 11 b of the second cam plate 11 of the drive cam 3 comes into contact with and engages with the second follower roller 16 of the cam follower 4. It is rotated in the direction of the arrow, whereby it is rotated by 90 ° from the index period start position (end position of the index period).

  Thereafter, while the drive cam 3 continues to rotate in the direction of the arrow, both the second cam surface 10b of the first cam plate 10 and the second cam surface 11b of the second cam plate 11 of the drive cam 3 The first follower roller 15 and the second follower roller 16 are not in contact with and engaged with each other, and the cam follower 4 does not rotate (resting period). During this time, as shown in FIG. 8 (f), the rolling roller 13, 13,... Of the third cam plate 12 abuts against the recess 17 a of the cam follower 4 by the action of the positioning mechanism 5. The first and second circular arc surfaces 10a and 11a of the first and second cam plates 10 and 11 are in contact with and engaged with the first follower roller 15 and the second follower roller 16 of the cam follower 4, respectively. As a result, the rotation of the cam follower 4 is regulated.

Next, a specific configuration of the positioning mechanism 5 will be described. As described above, the positioning mechanism 5 regulates the positioning of the rotation of the cam follower 4 during the stationary period, thereby positioning the intermittent index angle of the output shaft 2. An arrangement structure 20 and the recesses 17a, 17a,... Provided in the cam follower 4 are provided as main parts, and the roller arrangement structure 20 is an abutting engagement portion between the drive cam 3 and the cam follower 4 ( The positioning range) is circulated.

  The roller arrangement structure 20 includes a roller circulation path 21 provided in the drive cam 3, the plurality of rolling rollers 13, 13,... That circulate along the roller circulation path 21, and the rolling rollers 13, ,... Are provided with a propulsion elastic member 22 that imparts a propulsive force in the traveling direction.

  As shown in FIG. 2, the roller circulation path 21 is formed along the outer peripheral contour of the third cam plate 12. Specifically, as shown in FIGS. The outer peripheral guide surface 25 of the cam plate 12 and the guide grooves 26 and 27 of the first cam plate 10 and the second cam plate 11 are formed. These guide grooves 26 and 27 are formed so as to be along the outer peripheral contour of the third cam plate 12, that is, the outer peripheral guide surface 25, and to face each other, and the groove width W is the outer diameter dimension of the rolling roller 13. Is set to be slightly larger than that, and is allowed to travel while allowing the rolling rollers 13, 13,... To roll. The depth H of the guide grooves 26 and 27 is such that both ends of the rolling roller 13 are stably held and guided, and the guide grooves 26 and 27 are not separated from the guide grooves 26 and 27 even if the rolling roller 13 is tilted to some extent. The size is set.

  The rolling roller 13 is specifically composed of a metal needle roller, and is arranged in an aligned state with a slight interval that allows rolling over the entire circumference of the roller circulation path 21, and the roller circulation path 21 is rolled and guided. Has been made to circulate.

  The propulsion elastic member 22 gives a propulsive force for feeding (intruding) the rolling rollers 13, 13,... Into the roller circulation path 21 in the contact engagement portion between the drive cam 3 and the cam follower 4. It is interposed in at least a part between the rolling rollers 13, 13,. Specifically, the propulsion elastic member 22 is evenly distributed over the entire circumference of the roller circulation path 21 for every predetermined number of the rolling rollers 13, 13,... In the rolling roller array disposed in the roller circulation path 21. It is arranged in. In the illustrated embodiment, as shown in FIGS. 3 (b) and 4 (a), a propulsion elastic member 22 is provided for each of the three rolling rollers 13, 13,...

For this purpose, the propulsion elastic member 22 is required to satisfy the following conditions.
i) The propulsion elastic member 22 has elasticity in the traveling direction of the rolling rollers 13, 13,... in a state of being interposed between the rolling rollers 13, 13,.

ii) The propulsion elastic member 22 gives the rolling rollers 13, 13,... a propulsive force that can smoothly enter the roller circulation path 21 in the contact engagement portion between the drive cam 3 and the cam follower 4. , Having an elastic force large enough to prevent the oil film existing between the rolling rollers 13, 13,...

  The propulsive force may be a force that creates a timing at which the rolling rollers 13, 13,... Enter the roller circulation path 21 in the contact engagement portion between the drive cam 3 and the cam follower 4, and a relatively weak force. It has been proved by the inventors' experiment.

  As shown in FIG. 5, the elastic member 22 for propulsion according to the illustrated embodiment is in the form of a flat plate-like metal plate formed by bending in an arc shape with respect to the traveling direction of the rolling rollers 13, 13,. Has been. As a constituent material of the elastic member 22 for propulsion, a metal material that is softer than the rolling roller 13 and has a spring property is preferable. In the illustrated embodiment, a stainless steel material is preferably used.

  As shown in FIG. 4A, the specific configuration of the propulsion elastic member 22 is such that the propulsion elastic member 22 is interposed between the adjacent rolling rollers 13 and 13, as shown in FIG. A central portion 22a in the longitudinal direction 22 abuts and engages one of the rolling rollers 13 and 13 (the rear side in the traveling direction in the figure), and both end edges 22b and 22b in the longitudinal direction are both rolling rollers 13. , 13 (in the illustrated case, the front side in the traveling direction) is in contact with and engaged. In addition, the arrangement configuration of the elastic member 22 for propulsion may be a configuration in which the illustrated arrangement is reversed in the front-rear direction.

  Further, as shown in FIG. 4 (a), the propulsion elastic member 22 has a pair of guide grooves 26 in the roller circulation path 21 whose both ends guide both ends of the rolling rollers 13, 13,. In the same manner as the rolling roller 13, the guide grooves 26 and 27 are prevented from being detached from the guide grooves 26 and 27.

  Furthermore, the elastic member for propulsion 22 has a rectangular outline smaller than the rectangular projection surface of the rolling roller 13 as shown in FIG. The length and width are set to be smaller than the length and outer diameter of the rolling roller 13), and the presence of the propulsion elastic member 22 facilitates smooth rolling running of the rolling rollers 13, 13. It is designed not to inhibit.

  The concave portions 17a are portions where the rolling rollers 13, 13,... Of the roller arrangement structure 20 configured as described above are in rolling contact engagement, and as described above, there are four concave portions 17a on the outer peripheral surface of the turret 17 of the cam follower 4. Specifically, in the stationary period, the roller arrangement structure 20 circulates through a contact engagement portion between the concave portion 17a and the semicircular arc-shaped portion 12a of the third cam plate 12 of the drive cam 3. It is configured (see FIG. 8F).

  For this purpose, the radius of curvature of the concave portion 17a of the turret 17 is set corresponding to the radius of curvature of the semicircular arc-shaped portion 12a of the third cam plate 12 of the drive cam 3, and the roller arrangement structure 20 is rotated. As shown in FIG. 4B, the moving rollers 13, 13,... Have an outer peripheral guide surface 25 in the semicircular arc-shaped portion 12 a of the third cam plate 12, and an inner peripheral guide surface 28 of the concave portion 17 a of the turret 17. Thus, it is configured to run while rolling with a predetermined preload.

  In the positioning mechanism 5 configured as described above, the roller arrangement structure 20 is driven by the propulsion action of the propulsion elastic members 22, 22,... As shown in FIG. The rolling rollers 13, 13,... Are in rolling contact with the concave portion 17a of the turret 17 while smoothly circulating through the contact engagement portion (positioning range) between the drive cam 3 and the cam follower 4. The positioning of the rotation of the cam follower 4 is restricted.

  In other words, the contact engagement portion between the drive cam 3 and the cam follower 4 is maintained in a pressure contact state to which an appropriate preload is applied in order to ensure cam drive accuracy. The rollers 13, 13,... Are sandwiched with a predetermined preload from both sides by the outer peripheral guide surface 25 in the semicircular arc-shaped portion 12 a of the third cam plate 12 and the inner peripheral guide surface 28 of the concave portion 17 a of the turret 17. Yes (see FIG. 4B). In other words, the gap between the outer peripheral guide surface 25 of the third cam plate 12 and the inner peripheral guide surface 28 of the concave portion 17a of the turret 17 in the contact engagement portion is larger than the outer diameter of the rolling roller 13. It is set narrowly, and a preload of a predetermined magnitude is applied to the contact engagement portion via the rolling roller 13.

  Normally, when the rolling rollers 13, 13,... Enter the gap where the preload is applied (when the input shaft 1 is about to rotate), the rolling roller 13 has both the circular arc surfaces 25, 28. A phenomenon occurs in which the rolling roller 13 is kicked by receiving a certain amount of resistance when entering the roller circulation path 21 formed by the above-described structure. 13, 13, ... tend to be in pressure contact with each other.

  In this embodiment, the elastic member 22 for propulsion is disposed evenly over the entire circumference of the roller circulation path 21 for every predetermined number (three in the illustrated case) of the continuous rolling rollers 13, 13. Therefore, the rolling rollers 13, 13,... Are provided with a propulsive force by the propulsion elastic members 22, 22,..., And the roller circulation formed in the contact engagement portion between the drive cam 3 and the cam follower 4. As a result, the rolling rollers 13, 13,... Are not brought into pressure contact with each other, and smooth rolling is ensured. The rotational resistance of the input shaft 1 is greatly reduced, and the smooth rotation operation of the output shaft 2 is obtained, and predetermined indexing accuracy and repeatability are ensured.

  The preload elastic member 6 is at least one of the fitting portions of the main constituent members of the apparatus, that is, the input shaft 1 and the drive cam 3, the cam plates 10, 11 and 12, the fixing pin 14, the output shaft 2 and the cam follower 4. And the follower rollers 15 and 16 and at least one of the fitting portions of the support shaft, and in the illustrated embodiment, the fitting portion of the input shaft 1 and the drive cam 3 and the cam plate 10. , 11 and 12 and the fixing pin 14 are fitted with preload elastic members 6 respectively.

  The specific structure of the fitting portion in which the preloading elastic member 6 is interposed is the cylindrical gap S (one-dot chain line in FIG. 2) corresponding to the tolerance of the processing dimensions of the constituent members 1 to 4. In addition, the preload elastic member 6 is interposed in the cylindrical gap S.

  That is, the intermittent transmission device of the present embodiment is composed of a plurality of constituent members 1 to 4 as shown in the drawing, and these constituent members are machined individually, in particular, the drive cam 3. The first to third cam plates 10, 11, 12 and the turret 17 of the cam follower 4 are likely to vary in processing accuracy due to the special shape of the contour shape.

  Therefore, when the parallel cam mechanism, which is the main part of the apparatus, is assembled from the components having variations in processing accuracy in this way, the contact engagement portion between the drive cam 3 and the cam follower 4, that is, the first cam plate 10 and The contact engagement portion between the first follower roller 15, the contact engagement portion between the third cam plate 12 and the turret 17, and the contact engagement portion between the second cam plate 11 and the second follower roller 16 are minute. Therefore, it is difficult to avoid the occurrence of a large gap or a state of excessive pressure contact, and it is difficult to apply an appropriate preload to these contact engagement portions.

  Therefore, in this embodiment, the fitting portion between the input shaft 1 and the drive cam 3 and the fitting portion between the cam plates 10, 11, 12 and the fixing pin 14 have the finished dimensions of the constituent members 1 to 4. The cylindrical gap S is formed in consideration of a tolerance that is an allowable dimensional error (processing variation), and the preload elastic member 6 is interposed in the cylindrical gap S. The drive cam 3 and the cam follower 4 are configured to be able to maintain a pressure contact state in which an appropriate preload is always received at any rotational position.

For this purpose, the preload elastic member 6 is required to satisfy the following conditions.
i) The preload elastic member 6 has radial elasticity in a state of being interposed in the cylindrical gap S of the fitting portion.

ii) The preload elastic member 6 has elasticity that allows the abutting engagement portion to be kept in the abutting engagement state in which a predetermined preload is applied during the stationary period, and allows for the indexing period set in the apparatus. Has an elastic repulsive force that can withstand rotational loads

  The preload elastic member 6 of the illustrated embodiment is a metal plate material having a corrugated cross section as shown in FIG. 7, that is, a flat band-shaped metal formed by bending it into an uneven shape perpendicular to the longitudinal direction. In the form of a plate-making material, the width dimension is set corresponding to the axial length of the cylindrical gap S of the fitting portion to be interposed, and the length dimension is set to the cylindrical gap. It is set corresponding to the circumferential length of S. Further, as the metal plate material, that is, the metal material constituting the preload elastic member 6, a metal material having a spring property having excellent corrosion resistance is preferable, and a stainless steel material is employed in the illustrated embodiment.

  The metal plate material is wound around the cylindrical gap S and is elastically inserted in the radial direction to form a cylindrical preload elastic member 6. Specifically, as described above, since the third cam plate 12 is integrally formed with the input shaft 1 as shown in FIG. 6, the preloading elastic member 6 is connected to the input shaft 1 and the first shaft as shown in FIG. A fitting portion with one cam plate 10, a fitting portion between the input shaft 1 and the second cam plate 11, a fitting portion between the first cam plate 10 and the fixing pin 14, and the second cam plate 11 and the fixing pin 14. Are fitted in the fitting parts.

  In this way, in the state where the preload elastic member 6 is interposed in the cylindrical gap S of the fitting portion, as shown in the enlarged view of the portion within the chain line in FIG. The crests 6a, 6a,... Are uniformly applied over the entire inner diameter surface of the cylindrical hole of the outer diameter side member of the fitting portion (for example, the driving cam 3 in the fitting portion of the input shaft 1 and the driving cam 3). The valleys 6b, 6b,... Of the elastic member 6 for preload are in contact with the inner diameter side member of the fitting portion (similarly, the input shaft 1 in the fitting portion of the input shaft 1 and the drive cam 3). Abuts uniformly over the entire circumference. Although not specifically described, the preload elastic members 6, 6,... Interposed between the fitting portions of the cam plates 10, 11, 12 and the fixing pin 14 of the drive cam 3 have the same configuration. .

  As a result, conditions i) and ii) required for the preload elastic member 6 are satisfied, and variations in machining accuracy of the apparatus constituent members 1 to 4 are offset and absorbed. As a result, the cam surface (10a) of the drive cam 3 10b, 11a, 11b, 13) and the contact engagement portion between the follower rollers 15 and 16 and the recessed portion 17a of the cam follower 4 is provided with an appropriate predetermined preload in any rotational positional relationship. It will be always kept stable in the combined state (pressure contact state).

  Further, in the present embodiment, the outer peripheral contour shape dimensions of the cam plates 10, 11, 12 of the drive cam 3 are slightly larger than the normal outer peripheral contour dimensions (ideal design dimensions assuming no processing error). Is formed. The size in this case is set such that the preload elastic member 6 is not plastically deformed. By setting it as such a structure, the desired press-contact state in the said contact engagement part is obtained more reliably.

  Thus, in the automatic machine equipped with the intermittent transmission device configured as described above, when a continuous rotational driving force is input to the input shaft 1 by a drive source (not shown), the input shaft 1 rotates integrally. The cam follower 4 is rotated by the drive cam 3 during the indexing period (drive period) (in the illustrated case, the drive cam 3 rotates 180 ° during this period), and the output shaft 2 moves to the input part of the automatic machine. The rotation driving force of the set rotation angle (90 ° in the figure) is output and transmitted, and then there is a stationary period (non-driving period) during which the driving force is not transmitted for a certain period, and this cam operation is repeated intermittently. Driving is performed (see FIGS. 8A to 8E).

  According to the intermittent transmission device of this embodiment, the positioning mechanism 5 circulates through the contact engagement portion (positioning range) between the drive cam 3 attached to the input shaft 1 and the cam follower 4 attached to the output shaft 2. The roller arrangement structure 20 includes a roller circulation path 21 provided in the drive cam 3 and a plurality of rolling rollers 13, 13 moving along the roller circulation path 21 while being guided by rolling. Are provided between the plurality of rolling rollers 13, 13,... And provided with an elastic member 22 for propulsion that imparts a propulsive force in the traveling direction of the rolling rollers 13, 13,. The moving rollers 13, 13,... Are applied with a propulsive force by the elastic member 22 for propulsion, and are resisting force when entering the roller circulation path 21 formed at the contact engagement portion between the drive cam 3 and the cam follower 4. Smoothly sent against That (to enter) can be.

  Therefore, the rolling rollers 13, 13,... Are smoothly brought into contact with each other without being brought into pressure contact with each other outside the upstream side of the roller circulation path 21 of the contact engagement portion. As a result, the rotational resistance of the input shaft 1 is reduced and the smooth rotation of the output shaft 2 is ensured, so that the indexing accuracy and the repeatability can be improved.

  Further, the smooth rolling of the rolling rollers 13, 13,... Ensures the wear of the rolling rollers 13, 13,. From this point, there is no gap between the cam 3 and the cam follower 4 of the output shaft 2, and the occurrence of backlash is effectively prevented, and a pressure contact state in which a predetermined preload is constantly applied is secured. Also, the indexing accuracy and repeatability can be improved.

  Further, generation of metal powder due to wear of the rolling rollers 13, 13,... Is prevented, so that the durability of parts such as bearings is improved and the life of the apparatus is improved.

  Further, in the intermittent transmission device of the present embodiment, the preload elastic member 6 is provided at the fitting portion between the input shaft 1 and the drive cam 3 and the fitting portion between the cam plates 10, 11, 12 and the fixing pin 14. Since the contact engagement portion between the drive cam 3 and the cam follower 4 is maintained in the contact engagement state to which a predetermined preload is applied, the components 1 to 1 of the parallel mechanism are interposed. 4 does not affect the cam operation of the parallel cam mechanism, and the contact engagement portion between the drive cam 3 and the cam follower 4 can be kept in a pressure contact state where an appropriate preload is applied. it can. As a result, a minute gap is generated in the contact engagement portion between the drive cam 3 and the cam follower 4, and residual vibration is generated during the intermittent rotation drive stop period, or conversely, pressure is excessively pressed. Thus, there is no problem in the roller locking with respect to the cam follower 4 by the drive cam 3 during the stationary period of the apparatus, and the indexing accuracy and repeatability are not deteriorated.

  As a result, (a) indexing accuracy and repeatability in the parallel cam mechanism are improved, (b) residual vibration in the stationary period in the parallel cam mechanism is reduced, and (c) vibration at high speed rotation of the parallel cam mechanism. Various performances required for the parallel cam mechanism are effectively exhibited. As a result, it is possible to provide an optimal intermittent transmission device as an indexing device that constitutes the main part of an intermittent positioning device of an automatic machine, such as an intermittent conveyor, a feeding device or an index table, which is installed in the manufacturing process of various products. Become.

Embodiment 2
This embodiment is shown in FIG. 10 and is an intermittent transmission device having a Geneva mechanism type configuration.

  That is, the intermittent transmission device according to the present embodiment, as specifically shown, includes an input shaft 1 and an output shaft 2 arranged in parallel, a drive body 33 attached and fixed to the input shaft 1, and an output shaft 2. A follower 34 attached and fixed to the main body is provided as a main part. A positioning mechanism 5 for positioning the intermittent index angle of the output shaft 2 during the stationary period is provided between the driving body 33 and the driven body 34, and the constituent members 1, 2, 33, 34 are arranged. A preload elastic member 6 is interposed in the fitting portion, and the contact engagement portion between the cam surface of the driving body 33 and the driven body 34 is maintained in a contact engagement state to which a predetermined preload is applied. It is said that it is dripping. In addition, although not specifically shown in figure, the said main structural members 1, 2, 33, and 34 are internally accommodated in the housing similarly to the intermittent transmission apparatus of Embodiment 1.

  The drive body 33 is provided with an engagement member 35 at an outer peripheral portion thereof, and is in the form of a driving vehicle integrally provided with a rotation restricting cam 36 at a central portion thereof.

  The engaging member 35 engages with an engaging groove 38 of a follower 34, which will be described later. In the illustrated embodiment, the engaging member 35 has a cylindrical shape rotatably supported on a support shaft 33a of the prime mover 33. It is in the form of an engagement roller.

  The rotation restricting cam 36 is engaged with an engaging recess 39 of a follower 34, which will be described later. The rotation restricting cam 36 has a substantially fan-shaped cam plate which is coaxially laminated and integrated on one side of the prime mover 33. A plurality of rolling rollers 13, 13,... Constituting the positioning mechanism 5 together with the engaging recess 39 are arranged on the outer peripheral portion so as to be able to roll and circulate.

  The follower 34 is in the form of a follower that includes the engagement groove 38 that comes into contact with and engages with the engagement roller 35.

  In the follower wheel 24, the engagement grooves 38 and the engagement recesses 39 are alternately formed with the same number (six in the drawing) with a predetermined pitch (predetermined angle) in the rotation direction.

  The engagement groove 38 has a substantially U-shaped outline that extends outward in the radial direction, and the groove width is set to be slightly larger than the outer diameter of the engagement roller 35 of the prime mover 33. In addition, the engagement recess 39 has an arc-shaped contour that opens radially outward, and the curvature of the arc-shaped contour is the curvature of the circumscribed circle contour of the rolling rollers 13, 13,. It is set almost the same.

  The relational structure between the driving vehicle 33 and the driven vehicle 34 is such that when a continuous rotational driving force is input to the input shaft 1, the output shaft 2 is rotated by a set rotational angle during an indexing period that is a driving period. The driving force is output (transmitted) at a certain time, and after that, there is a stationary period that is a non-driving period during which the driving force is not transmitted for a certain period, and then the driving force is output again for the set rotation angle. It is set as the structure which performs intermittent drive.

  In the illustrated embodiment, the driven vehicle 34 is configured to rotate 60 °, that is, 1/6, while the driving vehicle 33 rotates 360 °, that is, one rotation.

  That is, although not specifically shown, when the input shaft 1 is driven to rotate, the driving vehicle 33 rotates integrally, and the engaging roller 35 is engaged with the engaging groove 38 of the driven vehicle 34 during one rotation of the driving vehicle 33. Engage one of the two. Due to the engagement between the engagement roller 35 and the engagement groove 38, the driven vehicle 34 is rotated by 60 ° with the rotation of the prime mover 33 in the direction of the arrow (indexing period). In this case, friction caused by the engagement between the engagement roller 35 and the engagement groove 38 is reduced by the rotation of the engagement roller 35.

  After that, while the prime mover 33 continues to rotate in the direction of the arrow, the engagement roller 35 of the prime mover 33 does not engage with any of the engagement grooves 38 of the follower vehicle 34, and the follower vehicle 34 does not rotate (resting period). ). During this time, the rolling rollers 13, 13,... (Rotation regulating cam surface) of the rotation regulating cam 36 are in contact with and engaged with the engaging recess 39 of the driven vehicle 34. Rotation is regulated for positioning.

  The positioning mechanism 5 has substantially the same configuration as that in the first embodiment. That is, the positioning mechanism 5 includes the roller arrangement structure 20 provided on the outer peripheral portion of the rotation restricting cam 36 provided integrally with the prime mover 33 and the engagement recess provided on the outer peripheral surface of the driven vehicle 34. 39, and the specific configurations of these components 20 and 39 are the same as those of the first embodiment.

  Similar to the first embodiment, the preload elastic member 6 is at least one of the fitting portions of the main constituent members of the apparatus, that is, the input shaft 1 and the driving vehicle 33, and the engagement roller 35 and the support shaft 33 a of the driving vehicle 33. In the illustrated embodiment, the input shaft 1 and the driving vehicle 33, the engagement roller 35, and the support shaft 33a are interposed in at least one of the fitting portions of the output shaft 2 and the driven vehicle 34. It is inserted in the fitting part. .. (Rotation restricting cam surface) and engagement recess 39 of the follower wheel 34. The engagement roller 35 of the prime mover 33, the engagement groove 38 of the follower wheel 34, the rolling rollers 13, 13,. The contact engagement portion is maintained in the contact engagement state to which a predetermined preload is applied.

  The other configurations and operations of the preload elastic member 6 are the same as those in the first embodiment.

  The above-described embodiment is merely a preferred embodiment of the present invention, and the present invention is not limited thereto, and various design changes can be made within the scope.

  For example, the specific configuration of the roller arrangement structure 20 can be variously modified within a range that satisfies the above-mentioned various conditions. As an example, the arrangement configuration of the elastic member for propulsion 22 is as shown in FIG. The elastic member 22 for propulsion is interposed between the two rolling rollers 13, 13, or as shown in FIG. 11B, the elastic member 22 for propulsion is provided for each of the six rolling rollers 13, 13,. It can be appropriately selected and designed according to the purpose, such as being interposed between the two.

  Similarly, the specific configuration of the preload elastic member 6 can be variously modified within a range that satisfies the above-mentioned various conditions. As an example, the configuration shown in FIGS. 12A and 12B can also be adopted. is there.

  That is, the preload elastic member 6 shown in FIG. 10A is in the form of a cylindrical metal ring. Although this cylindrical metal ring is not specifically shown, it has an inner and outer diameter corresponding to the cylindrical gap S of the fitting portion of the device constituent member to be interposed, and a radial engagement convex portion. 5c, 5c,... Are formed uniformly over the entire circumference. Moreover, as a metal material which comprises the said cylindrical metal ring, the metal material which has the spring property which is excellent in corrosion resistance similarly to Embodiment 1, for example, a stainless steel material is employ | adopted.

  Further, the preload elastic member 6 shown in FIG. 10B is in the form of an elastic cylinder. This elastic cylinder is optimally employed when the allowable rotational load during the indexing period set for the intermittent transmission is relatively small, and is preferably a rubber cylinder, for example.

It is a perspective view which shows the principal part of the intermittent transmission which is Embodiment 1 of this invention. It is a top view which similarly shows the principal part of the intermittent transmission. FIG. 3 (a) is a plan view, and FIG. 3 (b) is a partially incised part of a circle with a dot-dash line in FIG. 3 (a). It is an enlarged view. 4 shows a roller arrangement structure of a positioning mechanism in the intermittent transmission device, FIG. 4 (a) is a side sectional view, FIG. 4 (b) is a sectional view taken along the line BB in FIG. 4 (a), and FIG. ) Is a cross-sectional view taken along line CC in FIG. FIG. 5A is a perspective view, FIG. 5B is a front view, and FIG. 5C is a side view showing a propulsion elastic member having a roller arrangement structure in the positioning mechanism. It is sectional drawing along the VI-VI line in FIG. 2 of the intermittent transmission. FIG. 7A is a side view, and FIG. 7B is a plan view, illustrating an elastic member for propulsion of the intermittent transmission device. It is explanatory drawing which shows the cam operation stroke of the intermittent drive of the intermittent transmission device. FIG. 9A is a plan view showing the internal configuration of the casing, and FIG. 9B is a cross-sectional view taken along line BB in FIG. 9A. It is a top view which shows the principal part of the intermittent transmission which is Embodiment 2 of this invention. FIG. 11A is a side sectional view showing a first modified example, and FIG. 11B is a side sectional view showing a second modified example, showing a modified example of the roller arrangement structure of the positioning mechanism in the intermittent transmission device. It is. FIG. 12A is a perspective view showing a first modification example, and FIG. 12B is a perspective view showing a second modification example, showing a modification example of the preload elastic member of the intermittent transmission device. FIG. 13A shows an example of a main part of a conventional intermittent transmission device, FIG. 13A is a plan view showing the start of the positioning mechanism operation, and FIG. 13B is a part of the portion within a one-dot chain line in FIG. FIG. 13C is a front view showing a shape after the needle roller is worn.

Explanation of symbols

1 Input shaft 2 Output shaft 3 Drive cam (Drive body)
4 Cam followers
5 Positioning mechanism 6 Preloading elastic member 10 First cam plate 11 Second cam plate 12 Third cam plate 12a Semi-arc shaped portion 13 of third cam plate Rolling roller 14 Fixing pin 15 First follower roller 16 Second follower Node roller 17 Turret 17a Concave portion 20 Roller arrangement structure 21 Roller circulation path 22 Elastic member 22a for longitudinal direction Both end edges 25 in the longitudinal direction Outer guide surface 26, 27 Guide groove 28 Inner guide surface 33 of the recess (Driver)
34 Driven vehicle (driven body)
35 Engagement roller (engagement member)
36 Rotation restricting cam 38 Engaging groove 39 Engaging recess W Guide groove width H Guide groove depth

Claims (15)

Provided in an intermittent transmission device that converts the continuous rotation motion of the input shaft into intermittent rotation motion of the output shaft by cam driving the driven body attached to the output shaft by the drive body attached to the input shaft. A positioning mechanism for positioning an intermittent index angle of the output shaft during a stationary period,
Comprising a roller arrangement structure that circulates through a contact engagement portion between the driving body and the driven body;
The roller arrangement structure includes a roller circulation path provided in the driving body, a plurality of rolling rollers that move while being guided by rolling in the roller circulation path, and at least a part between the plurality of rolling rollers. A positioning mechanism for an intermittent transmission, comprising: an elastic member for propulsion that is mounted and applies a propulsive force in the traveling direction of the rolling roller. 2. The intermittent transmission device positioning mechanism according to claim 1, wherein the propulsion elastic member has elasticity in a traveling direction of the rolling roller in a state of being interposed between the rolling rollers. The elastic member for propulsion provides the rolling roller with a propulsive force that can smoothly enter the roller circulation path of the contact engagement portion, and the oil film existing between the rolling rollers is not broken. The intermittent transmission device positioning mechanism according to claim 1, wherein the positioning mechanism has an elastic force. The elastic member for propulsion is in the form of a flat plate-like metal plate formed by bending in an arc shape with respect to the traveling direction of the rolling roller,
In a state where the elastic member for propulsion is interposed between the adjacent rolling rollers, the central portion in the length direction of the elastic member abuts and engages one of the two rolling rollers, and both end edges in the length direction The positioning mechanism of the intermittent transmission device according to any one of claims 1 to 3, characterized in that abuts and engages the other of the rolling rollers. 5. The intermittent transmission device according to claim 4, wherein both ends of the elastic member for propulsion are guided and held in a pair of guide grooves of the roller circulation path that guides both ends of the rolling roller. Positioning mechanism. 6. The positioning mechanism for an intermittent transmission device according to claim 5, wherein the elastic member for propulsion has a rectangular outline smaller than a rectangular projection surface of the rolling roller in the extended flat plate state.   The positioning mechanism of the intermittent transmission device according to any one of claims 4 to 6, wherein the elastic member for propulsion is made of a metal material that is softer than the rolling roller and has a spring property. . The elastic member for propulsion is disposed evenly over the entire circumference of the roller circulation path for every predetermined number of continuous rolling rollers in a rolling roller array arranged to be capable of rolling in the roller circulation path. The positioning mechanism for an intermittent transmission device according to any one of claims 1 to 7. A device that converts the continuous rotational motion of the input shaft into intermittent rotational motion of the output shaft by cam driving the driven body attached to the output shaft by a drive body attached to the input shaft,
Positioning means for positioning the intermittent index angle of the output shaft in the stationary period;
The intermittent transmission device according to any one of claims 1 to 8, wherein the positioning means is the positioning mechanism according to any one of claims 1 to 8. An elastic member is interposed in at least one of the fitting portions of the apparatus constituent member, and the contact engagement portion between the driving body and the driven body is kept in the contact engagement state to which a predetermined preload is applied. The intermittent transmission device according to claim 9, wherein the intermittent transmission device is configured as described above. A cylindrical gap corresponding to the tolerance of the processing dimension of each component member is formed in the fitting portion of the device component member in which the elastic member is interposed, and the elastic member is interposed in the cylindrical gap. The intermittent transmission device according to claim 9. The intermittent transmission device according to claim 9 or 10, wherein the elastic member has radial elasticity in a state where the elastic member is interposed in a cylindrical gap of the fitting portion. The elastic member has elasticity that allows the contact engagement portion to be maintained in a contact engagement state to which a predetermined preload is applied during a stationary period, and withstands an allowable rotational load during an indexing period set in the apparatus. The intermittent transmission device according to claim 9, wherein the intermittent transmission device has an elastic repulsive force to be obtained. The input shaft and the output shaft are arranged in parallel, the drive body attached to the input shaft is in the form of a drive cam comprising a plurality of cam plates, and the follower attached to the output shaft is the cam plate A follower roller that comes into contact with and engages with the cam surface is provided in a cam follower configuration in which the follower roller is provided upright at equal intervals in the circumferential direction.
A plurality of the positioning mechanisms are provided at equal intervals on the outer peripheral surface of the turret constituting the cam follower and the roller arrangement structure provided on one outer peripheral portion of the cam plate constituting the driving cam. The intermittent transmission device according to any one of claims 9 to 13, wherein the rolling roller includes an arcuate recess that is in rolling contact with the rolling roller. The input shaft and the output shaft are arranged in parallel, the drive body attached to the input shaft is in the form of a driving vehicle provided with an engagement member, and the follower attached to the output shaft is engaged. It is a Geneva mechanism-type device in the form of a driven vehicle having an engagement groove for abutting engagement with a member,
The positioning mechanism includes a plurality of roller arrangement structures provided on an outer peripheral portion of a rotation restricting cam provided integrally with the driving vehicle, and a plurality of positioning mechanisms provided at equal intervals on the outer peripheral surface of the driven vehicle. The intermittent transmission device according to any one of claims 9 to 13, wherein the rolling roller includes an arcuate engagement concave portion with which the rolling roller is engaged in rolling contact.

Images