JPH08105502A - Intermittence dividing device - Google Patents

Abstract

PURPOSE: To provide an intermittence dividing device in which an intermittence dividing motion can be obtained from a rotational motion in its reasonable structure by the use of a cam mechanism and a clutch means under the working principle of a pick and place unit, and besides, in which highly accurate dividing performance can be secured. CONSTITUTION: An intermittence dividing device is provided with an output shaft 40 to which compound movement to individually generate rotational motion and axial reciprocating motion from a cam mechanism 32, is transmitted, a cylindrical body 47 provided at the output shaft 40, and a disc 48 which can be relatively rotated against this cylindrical body 47. The intermittence dividing device is also provided with a clutch device 46 which is intermittently operated according to a rotational load generated between these cylindrical body 47 and disc 48, and a stopper 38 with/from which the engagement body 39 of a table 55 attached to the disc 48 of the clutch device 46 moved accompanying the axial reciprocating motion of the output shaft 40, is engaged to be freely engaged/disengaged so that the clutch device 46 is intermittently operated.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an intermittent indexing device, and in particular, by using a cam mechanism and a clutch means, it is possible to obtain an intermittent indexing motion from a rotary motion with a rational structure, and moreover, a highly accurate indexing performance. The present invention relates to an intermittent indexing device that can secure the.

[0002]

2. Description of the Related Art Conventionally, as a mechanism for generating intermittent rotary motion from rotary motion in securing intermittent indexing motion, a technique adopted for roll feed is known. This roll feed basically converts rotary motion into oscillating motion (repetitive oscillating rotary motion), and further converts this oscillating motion into intermittent rotary motion, as shown in FIGS. Among the pair of rolls 1 and 2 arranged in parallel facing each other, one of the rolls 1 is driven to rotate intermittently, so that the sheet material 3 is formed between the other roll 2.
It is designed to obtain the action of intermittently sending out in one direction.

More specifically, a pair of rolls 1 and 2
Are formed in a cylindrical shape, and their outer peripheral cylindrical surfaces are juxtaposed so as to face each other with a slight gap. In particular, one of the first rolls 1 is disposed outside and has a hollow cylindrical outer sleeve 4 facing the other second roll 2, and is disposed inside the outer sleeve 4 coaxially therewith. The inner sleeve 5 and the outer sleeve 4 are disposed between the inner sleeve 5 and the outer sleeve 4, and are arranged on both end sides of the inner sleeve 5 to transmit only one direction rotational movement of the inner sleeve 5. A pair of one-way clutches 6 for interrupting the return rotational movement of 1 are provided. Further inner sleeve 5
Is provided with a pair of shaft portions 7 extending from both axial ends thereof to the outside of the outer sleeve 4, and these shaft portions 7 are rotatably supported by bearings 8. The other end of a swing arm 9 described later is integrally connected to the shaft end of the one shaft 7. On the other hand, a brake device 12 including a brake drum 10 and a shoe 11 for braking the brake drum 10 is provided at one axial end of the outer sleeve 4. The second roll 2 has a pair of shaft portions 13 extending from both axial end portions thereof, and the pair of shaft portions 13 are both rotatably supported by a bearing 14 and elastically supported by a suspension mechanism 15. By
The first roll 1 is rotatably and elastically supported with a gap therebetween.

The transmission mechanism for inputting a motion to the rolls 1 and 2 constructed as described above is constructed as follows. Reference numeral 16 denotes an input rotary shaft that is rotationally driven in one direction. The input rotary shaft 16 is provided with a crank 17 that is integrally coupled at one end thereof and that pivots in synchronization with the input rotary shaft 16. One end of a connecting rod 18 is rotatably connected to the other end of the crank 17, and one end of a swing arm 9 is rotatably connected to the other end of the connecting rod 18. The other end of the swing arm 9 is integrally connected to one shaft portion 7 of the first roll 1 including the one-way clutch 6 and the brake device 12 described above.

To explain the operation of the roll feed as described above, as is well known, the rotational movement of the input rotary shaft 16 causes the swing arm 9 to swing to a certain degree by the link configuration of the crank 17, the connecting rod 18 and the swing arm 9. It is converted into an oscillating motion that reciprocally swings and rotates in an angular range.
By the continuous oscillating motion of the swing arm 9,
The inner sleeve 5 of the first roll 1 connected to this is continuously oscillated in a rotation angle range corresponding to the swing angle range of the swing arm 9. In response to such oscillating movement of the inner sleeve 5, the one-way clutch 6 repeats transmission / interruption of the movement, that is, while transmitting one direction rotation of the inner sleeve 5 to the outer sleeve 4, the one-way clutch 6 returns to the outer sleeve 4. The transmission is interrupted, and as a result, the outer sleeve 4 performs an intermittent rotation movement in one direction, that is, the inner sleeve 5 rotates in one direction during one rotation period and stops during the return rotation period. It will be. At this time, the sheet material 3 that is sandwiched between the outer sleeve 4 of the first roll 1 and the second roll 2 and fed out is the amount of the sheet material 3 that is fed once. It will be governed by the angle.

By the way, the action of the one-way clutch 6 on the outer sleeve 4 is to transmit only the one-way rotational movement of the inner sleeve 5, and the outer sleeve 4 is free to rotate during the returning rotational movement. If the free rotation of the outer sleeve 4 is not prevented during the return rotation period, the sheet material 3 may be returned or delivered by the free rotation of the outer sleeve 4, and the delivery amount of the sheet material 3 may fluctuate. . Therefore, the outer sleeve 4 is constantly braked by the brake device 12. That is, the brake device 12 is controlled so as to always generate a braking force, and the inner sleeve 5 is connected via the one-way clutch 6.
When the rotational movement of the outer sleeve 4 is transmitted to the outer sleeve 4, the inner sleeve 5 brakes the outer sleeve 4.
To overcome this and rotate it, while the inner sleeve 5
When the inner sleeve 5 and the outer sleeve 4 are separated by the one-way clutch 6 by returning and rotating, the brake device 12 prevents the outer sleeve 4 from freely rotating. The delivery amount is kept constant.

[0007]

However, the conventional mechanism having the above-described motion conversion structure to obtain intermittent rotary motion from rotary motion has the following problems.

First, regarding the mechanism for converting the oscillating motion of the inner sleeve 5 into the intermittent rotary motion of the outer sleeve 4 in the first roll 1, in order to realize this, free rotation of the outer sleeve 4 is prevented by the brake device 12. However, the brake device 12 is adapted to brake the inner sleeve 5 even when the one-way rotational movement of the inner sleeve 5 is transmitted to the outer sleeve 4 to rotate the outer sleeve 4, and in this state, In order to rotate the sleeve 5, the outer sleeve 4 must be rotationally driven against the braking force. Therefore, there is a problem that the life of the brake device 12 is short and maintenance is required within a short period of time. Further, the brake device 12 inevitably undergoes a secular change in braking ability due to wear and the like even before its life is reached. Therefore, from this aspect as well, the inner sleeve 5 to the outer sleeve 4 are
There is also a problem that an operation error is apt to occur in the motion transmission path to, and as a result, intermittent rotation motion of the outer sleeve 4 in a constant angle range cannot be guaranteed, and it is difficult to obtain a positive motion.

In order to deal with such problems as durability, the brake device 12 is operated only during the period when the outer sleeve 4 is free to rotate in synchronization with the return rotation of the inner sleeve 5. It is also possible to brake No. 4. However, the outer sleeve 4 has a rotational inertia, and during the braking operation and the releasing operation of the brake device 12, the outer sleeve 4 may be slightly rotated or rotated due to a frictional action or the like. In the way of operating the brake device 12 as described above, it is difficult to obtain the intermittent rotation motion of the outer sleeve 4 within a certain certain rotation angle range due to the unavoidable rotation angle error of the outer sleeve 4 caused by the operation. Become. Further, such an error becomes larger as the outer diameter of the first roll 1 becomes larger, that is, as the scale on the output side becomes larger, and it becomes difficult to put it into practical use.

Further, in order to prevent the rotation of the first roll 1 around the braking / releasing operation of the brake device 12, it is conceivable to increase the mass of the first roll 1. There is also a problem that the size and weight of the entire device will be increased.

Further, as is well known, the motion transmitting mechanism composed of the crank 17, the connecting rod 18 and the swing arm 9 can obtain only the oscillating motion within an angle range of 180 ° from the maximum dead center to the maximum dead center. Therefore, it is impossible to obtain an oscillating motion in a larger angular range and transmit the oscillating motion to the first roll 1, and it is not possible to secure an arbitrary sufficient sheet delivery amount.

In order to cope with this, when it is desired to secure a large sheet feeding amount, the above-mentioned mechanism inevitably increases the outer diameter of the first roll 1, resulting in a large-sized apparatus. It will be forced to increase in weight and weight.

Here, the inventor of the present application attaches an arm to an output shaft which performs a combined motion of an oscillating motion and a reciprocating motion in the axial direction, and causes the arm to reciprocally swing and move along the axial direction of the output shaft. A pick-and-place unit designed to be moved in parallel has already been proposed (for example, Japanese Utility Model Laid-Open No. 2-110487), but the pick-and-place unit basically moves in one direction in a mechanical structure for moving an arm. Focusing on the fact that it has an action to obtain an oscillating motion from the rotational motion to the arm and an action to reciprocate the arm during the dwell period of the oscillating motion, a mechanism for obtaining an intermittent rotary motion from the rotary motion based on these actions is proposed. It is something that has come out.

The present invention has been made in view of the above-mentioned conventional problems, and its object is to rotate by using a cam mechanism and clutch means based on the operation principle of the pick and place unit. It is an object of the present invention to provide an intermittent indexing device that can obtain an intermittent indexing motion from a motion with a rational configuration and can also ensure highly accurate indexing performance.

[0015]

An intermittent indexing device according to the present invention is provided with an output shaft to which a composite motion independently producing a rotary motion and an axial reciprocating motion is transmitted from a cam mechanism, and the output shaft. An input member and an output member capable of rotating relative to the input member, the clutch means being interrupted according to the rotational load generated between the input and output members, and the axial reciprocating motion of the output shaft. A clutch actuating means for engaging and disengaging the output member of the clutch means that moves with it to intermittently actuate the clutch means.

Further, the rotary motion is an intermittent oscillating motion having a dwell period, and the axial reciprocating motion is alternated with respect to the dwell period which is generated intermittently in sequence, and the axial movement of the clutch means is alternately performed. It is characterized in that the output member is caused to undergo either one of an advancing motion to be engaged with the clutch actuating means and a retreating motion to be disengaged.

Further, it is characterized in that the rotational movement is output from the output shaft, and at the same time, the output member is intermittently rotated.

[0018]

The operation of the invention according to claim 1 will be described. The output shaft is moved so as to independently and independently perform the rotational movement transmitted from the cam mechanism and the reciprocating movement along the axial direction thereof. Specifically, the output shaft is rotated at a certain rotation angle by the rotational movement transmitted from the cam mechanism,
Intermittent rotational movement is repeated, in which the motor is stopped for a certain period of time, then rotated at a certain rotation angle, and then stopped for another certain period of time. On the other hand, the output shaft is further stopped for a certain period after performing an axial reciprocating motion advancing in at least one direction in any one of the stationary periods in such intermittent rotary motion, and then any one of the stationary periods thereafter. In, the reciprocating motion is repeated, in which the axial reciprocating motion receding at least in the opposite direction is performed and then the motion is stopped for a certain period of time. That is, the output shaft rotates, and during any stationary period in the meantime, performs reciprocating motion that advances or retracts in at least one direction.

The output shaft which performs such a movement is provided with clutch means which is controlled to be intermittent. The clutch means includes an input member provided on the output shaft and an output member that is rotatable relative to the input member. The clutch means rotates in accordance with the rotational load generated between the input and output members. When the load is small, connect the input and output members together,
On the other hand, when the rotational load is large, the two are separated to allow relative rotation of the output member with respect to the input member. Therefore, this clutch means causes both the input member and the output member to rotate in accordance with the rotation of the output shaft when the rotational load is small, and on the other hand, when the rotational load is large, outputs the output member to the input member that rotates in accordance with the output shaft. Rotate relatively.

The clutch actuating means controls the rotational load between the input and output members so that the clutch means actuated in this way can perform the intermittent operation. That is, during the stationary period of the rotary motion, the clutch means is also moved as the output shaft reciprocates in the axial direction, and the output member is engaged with the clutch actuating means by the movement of the clutch means. Or it is supposed to be separated. Specifically, the output member is engaged with the clutch actuating means by the reciprocating motion in one direction of the output shaft for advancing the output member toward the clutch actuating means during one stop period of the rotational movement and the stop thereof. While the output member is trying to rotate together with the output shaft by restarting the rotational motion of the output shaft, the rotational motion is stopped by the clutch operating means. Due to this restraining action, a large rotational load can be generated between the input member and the output member, and the clutch means is disengaged. Due to the disconnection of the clutch means, the input member rotates together with the output shaft, while the output member is allowed to rotate relative to the input member and remains stopped. On the other hand, in the case where the output member is disengaged from the clutch actuating means due to reciprocating motion in the opposite direction of the output shaft for retracting the output member from the clutch actuating means and its stop during any one of the subsequent rotational motion stop periods. No rotational load is generated by the clutch actuating means between the output member and the input member, so that the clutch means is in the connected state. In the connected state of the clutch means, the restart of the rotational movement of the output shaft causes the output member to rotate at the rotation angle of the output shaft together with the input member.

Thus, while the output shaft continues the rotational movement transmitted from the cam mechanism, the output member is controlled by the clutch actuating means to control the on / off of the clutch means based on the reciprocating movement of the output shaft by the cam mechanism. The stopping operation and the rotating operation are repeated, which causes the intermittent rotating motion. Then, the position indexing during the intermittent rotation motion is properly ensured by the cam curve of the cam mechanism and the clutch actuating means for engaging and stopping the output member of the vertically moving clutch means, This makes it possible to obtain a positive intermittent indexing motion.

That is, the intermittent indexing device of the present invention basically uses a mechanical element called a cam mechanism that can create a reliable stop state by the dwell and can easily and reliably obtain a positive motion of the entire motion. The intermittent rotary motion is extracted from the rotary motion obtained by this cam mechanism by the intermittent operation of the clutch means controlled by the clutch operating means in association with the reciprocating motion of the output shaft. The indexing position is held by the engaging operation of the means with the output member, and the intermittent positive indexing motion can be reasonably obtained with high accuracy. Particularly, in the present invention, while applying the operation principle of the existing pick-and-place unit, an intermittent indexing motion which requires a completely different motion is rationalized by using the cam mechanism and the clutch means. Can be obtained in configurations.

Further, it is possible to eliminate the mechanical elements such as the conventional brake device having a short operation guarantee period and configure the mechanism, and it is possible to obtain a maintenance-free device.

Further, the position indexing accuracy of the output member is essentially ensured with high accuracy by the cam curve provided in the cam mechanism, and the unnecessary rotation of the output member indexed by the cam mechanism causes the clutch operation. It can be completely blocked by means. Therefore, the influence of secular change in the braking device used to ensure the indexing operation in the conventional mechanism is eliminated,
It is possible to guarantee semi-permanently a highly accurate and stable positive motion.

The operation of the invention according to claim 2 will be described. On the premise of the composite motion of the output shaft in the invention according to claim 1, the rotational motion of the output shaft is performed by the axial reciprocating motion. In the axial reciprocating motion of the output shaft, one of the advancing and retreating motions of the output member of the clutch means with respect to the clutch actuating means is sequentially generated intermittently. Against each other. In short, in contrast to the oscillating motion of rotating in one direction and returning, the output shaft always advances the output member of the clutch means toward the clutch actuating means during the stop period after the forward movement and stops after the returning movement. Perform a reciprocating exercise that always retracts during the period.

Specifically, the output shaft first rotates in one direction. At this time, the clutch means is connected,
The output member is rotated with the input member by the output shaft. After that, it stops for a certain period of time. During this stop period,
The output shaft moves in one direction so as to advance the output member of the clutch means toward the clutch actuating means to engage the output member with the clutch actuating means, and stop in that state for a certain period. In this engaged state, the output shaft will then undergo a rotational movement that returns in the next opposite direction. At the time of this return rotation, the clutch means is disengaged due to the generation of a rotational load by the clutch actuating means, and the input member rotates back together with the output shaft, while the output member is stopped. During the stationary period after the subsequent return rotation, the output shaft moves in the opposite direction so as to retract the output member from the clutch actuating means, contrary to the previous time, and the output member is disengaged from the clutch actuating means. Stop for a certain period. As a result, the clutch means is brought into the connected state, and the output member rotates together with the output shaft during the subsequent rotational movement of the output shaft in one direction.
And this exercise will be repeated repeatedly.

That is, during the rotational movement of the output shaft in one direction, the output member rotates integrally with the output shaft at a constant oscillating rotation angle due to the connection of the clutch means. Intermittent rotary motion in one direction, which is stopped by the dwell period of the rotary motion and disconnection of the clutch means, is performed, whereby the intermittent indexing motion is obtained. At this time, the output shaft is rotationally moved according to the oscillating motion from the cam mechanism, separately from the motion of the output member.

With respect to the oscillating motion, there is no limitation on the swinging rotation angle range of the oscillating motion obtained by the cam curve in the cam mechanism, and therefore, the oscillating motion in the angular range of 180 ° or more can be created.

The operation of the invention of claim 3 will be further described. As described above, the output shaft always performs the rotational movement according to the movement transmitted from the cam mechanism, and at the same time, the output member controls the on / off control of the clutch means. According to the above, intermittent rotation motion is performed, and these two types of motion can be output coaxially from a single output shaft.

[0030]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT A preferred embodiment of the present invention will be described below in detail with reference to the accompanying drawings. 1 to 3 show an intermittent indexing device according to this embodiment. Reference numeral 30 denotes a hollow box-shaped housing, and an input rotation shaft 31 is provided in the housing 30 so as to extend horizontally from one side wall 30a to the other side wall 30b facing each other. This input rotary shaft 3
1 is rotatably supported on the side walls 30a and 30b of the housing 30 via bearings 71 and the like, and is rotatably driven in one direction by a drive source such as a motor.

A housing 30 is attached to the input rotary shaft 31.
A cam mechanism 32 is provided inside. The cam mechanism 32 includes a swing rotary cam 3 fixed to the input rotary shaft 31.
3 and a vertical movement cam 36 integrally provided as a composite cam 35
And a turret 34 that serves as a follower of the swing rotation cam 33 and a lift arm 37 that serves as a follower of the vertical movement cam 36.

First, the turret 34 as a follower and its mounting support structure will be described.
Is formed in the shape of a hollow cylinder whose lower end bulges outward in the radial direction and is arranged along the vertical direction of the housing 30. On the other hand, the ceiling surface 30c of the housing 30
An opening 30d is formed at the bottom of the opening 30d, and a ring-shaped flange 30e is formed at the lower edge of the opening 30d so as to project radially inward along the circumferential direction. A hollow cylindrical sleeve 41 for supporting the turret 34 is attached to the opening 30d. A flange portion 41a is formed on the outer peripheral edge of the upper end portion of the cylindrical sleeve 41 so as to project radially outward along the circumferential direction thereof, and the flange portion 41a is located above the flange portion 30e in the opening 30d. And the flange portion 41a and the flange portion 30e are fastened together with bolts 42, and the sleeve 41 is fixed to the housing 30. In the hollow cylindrical sleeve 41, a pair of ring-shaped bearings 44 is mounted between the upper end opening and the lower end flange portion at an interval in the axial direction of the sleeve 41 by a ring-shaped spacer 43. It And
The turret 34 is inserted into the sleeve 41, rotatably supported by the bearings 44, and attached. A ring-shaped seal member 45 is attached between the spacer 43 and the turret 34, which are located at the upper end opening of the sleeve 41. The hollow cylindrical turret 34 rotatably supported by the housing 30 in this manner swings and rotates via a pair of rollers 34a provided so as to project outward in the horizontal direction from the bulged lower end. The movement of the cam 33 is transmitted to drive the rotation.

In this embodiment, a so-called roller gear cam 3 is used as the swinging rotary cam provided in the composite cam 35.
3 has been adopted. As shown in FIGS. 2 and 4, the roller gear cam 33 has one taper rib 33a along the circumferential direction on the outer peripheral surface around the input rotary shaft 31.
Are formed, and a pair of rib surfaces 33b are formed on both side walls of the tapered rib 33a, and these rib surfaces 33b are configured as sliding contact surfaces of the roller 34a.

On the other hand, the pair of rollers 34a of the turret 34 described above includes the taper rib 3 of the roller gear cam 33.
It projects toward the 3a side. These rollers 34a are rotatably attached to the turret 34, and are slidably and slidably brought into contact with the pair of rib surfaces 33b formed on the roller gear cam 33, respectively. The rollers 34a are provided with the taper rib 33.
The turret 34 is guided while being constrained by a and is moved along the cam curve created in the roller gear cam 33 by the taper rib 33a, and the turret 34 is oscillated according to this movement.

More specifically, as shown in FIG. 5, the roller gear cam 33 serving as a swinging rotary cam includes an input rotary shaft 3
The turret 34 is rotated according to the increase of the rotation angle of the turret 34 according to the rotational movement of 1 to rotate to an arbitrary rotation angle α, and then the turret 34 is stopped by the dwell for a certain period of time.
Thereafter, a cam curve is formed in which the turret 34 is further swung in the return direction and returned to the swivel angle of 0 ° in accordance with an increase in the rotation angle of the input rotation shaft 31, and then rotated again by the dwell to stop the turret 34 for a certain period. In the present embodiment, during one rotation of 360 ° of the input rotary shaft 31, the turret 34 is rotated to the turning angle α in the first 90 ° range, and then in the 180 ° range.
The turret 34 in the 270 ° range thereafter.
Back to 0 ° and then 360 °
The cam curve is set so that the operation of stopping the turret 34 in the range of ° and repeating the rotation of the input rotary shaft 31 to rotate the turret 34 to the turning angle α again is repeated. That is, the swinging rotary cam 33 is connected to the input rotary shaft 3.
It is configured to convert a rotary motion of 1 into an intermittent oscillating motion with a dwell period.

In particular, the structure of the roller gear cam 33, which comprises the taper rib 33a and the roller 34a of the present embodiment, is of a restraining type and has a preloading structure, so that it has no backlash, high rigidity and high speed driving. Suitable and
It is particularly preferable as a driving cam for the indexing device. However, the swinging rotary cam 33 is not limited to the above-mentioned roller gear cam, but other flat cams or three-dimensional cams such as plate cams, groove cams, end face cams, cylindrical rib cams,
Cylindrical groove cam, conical end face cam, conical groove cam, barrel groove cam,
Of course, any cam such as an hourglass groove cam may be applied.

On the other hand, as shown in FIGS. 1 and 2, the composite cam 35 is further provided with a vertical movement cam 36 integrally with the roller gear cam 33. In this embodiment, a so-called plane groove cam 36 is used as the vertical movement cam. The plane groove cam 36 is provided on the roller gear cam 33.
A groove 36a is formed in a predetermined cam profile along the circumference of the input rotation shaft 31 on the side wall surface of the.

The lift arm 37, which is a follower of the plane groove cam 36, is disposed substantially horizontally inside the housing 30 at a position below the input arm 31 where it does not interfere with the input rotary shaft 31. The lift arm 37 has a rotation center 37a at one end rotatably supported on the housing 30 by a support pin 72, and a lift end 37b at the other end engaged with a lower end of an output shaft 40, which will be described later. It is mounted so that it can be lifted within 30. Further, a roller 37c is rotatably provided at an intermediate portion of the lift arm 37 so as to project toward the groove 36a of the plane groove cam 36.
Is engaged with the groove 36a of the plane groove cam 36 so as to be slidably rotatable. The roller 37c is moved along the cam curve created in the flat grooved cam 36 while being guided by the groove 36a, and the lift arm 37 is moved up and down around its rotation center 37a in accordance with this movement. To be done.

Specifically, as shown in FIG. 5, in the plane groove cam 36 as the vertically moving cam, the lift arm 37 is first stopped for a certain period of time by a dwell with the rotational movement of the input rotary shaft 31. After that, the lift arm 37 is moved downward with a predetermined displacement β in accordance with the increase in the rotation angle,
After that, lift the dwelling arm 37 for a certain period by dwell
Is stopped, and then a cam curve is formed which causes the lift arm 37 to retreat upward to the position where the displacement amount is 0 as the rotation angle increases. In the present embodiment, the lift arm 37 is stopped in the first 90 ° range during one 360 ° rotation of the input rotary shaft 31, and the subsequent 90 ° to 1 °.
In the range of 80 °, the lift arm 37 is moved downward to the displacement amount β, then the lift arm 37 is stopped in the range of 270 °, and then 270 ° to 3 °.
The cam curve is set to repeat the operation of moving the lift arm 37 upward to the displacement amount 0 in the range of 60 ° and then stopping the lift arm 37 until the range of 90 ° of the next rotation.

Lift arm 3 having such a cam curve
As is clear from the cam diagram of FIG. 5, the motion of No. 7 is one of the ascending motion and the descending motion of the lift arm 37 for each dwell period of the rocking rotary cam 33 that is sequentially and intermittently generated. The movements of will occur alternately.

The vertical movement cam 36 is not limited to the above-mentioned plane groove cam, but other plane cams or three-dimensional cams,
For example, groove cam, end face cam, cylindrical rib cam, cylindrical groove cam,
Conical end face cam, conical groove cam, barrel groove cam, drum groove cam,
Of course, any cam such as a roller gear cam may be applied.

From the cam mechanism 32 thus constructed,
A description will be given of the output shaft 40 to which the composite motion that independently generates the rotational motion and the axial reciprocating motion, specifically, the intermittent oscillating motion and the axial reciprocating motion during the dwell period of the oscillating motion are transmitted. As shown in FIG. 1, the output shaft 40 extends from the inside of the housing 30 to its ceiling portion 30c.
Is formed in a shaft-like shape that extends outwardly through and has an engaging portion 40a at its lower end with which the lift end 37b of the lift arm 37 is engaged. Further, as shown in FIGS. 2 and 4, the output shaft 40 is attached so that the upper portion of the engaging portion 40a is spline-fitted in the hollow portion of the turret 34 along the axial direction. By this spline fitting, the output shaft 40 is axially slidable with respect to the turret 34 and is integrally mounted in the rotational direction. Further, the engaging portion 40a at the lower end of the output shaft 40 is constituted by an annular guide sliding groove 40c defined around the output shaft 40 by a pair of upper and lower engaging flanges 40b.
The roller 37d rotatably provided at the lift end 37b of the lift arm 37 is provided with the engagement flange 40b.
It is engaged with the guide slide groove 40c so as to be rotatable and slidable while being restrained from above and below. Then, the movement of the lift arm 37 moving up and down around the rotation center 37a by the plane groove cam 36 is input to the output shaft 40 via the roller 37d,
As a result, the output shaft 40 slides along the axial direction with respect to the turret 34, and reciprocates vertically.

In this way, the output shaft 40 mounted on the housing 30 so as to be rotatable and vertically reciprocally movable.
A clutch device 46 is provided on the end side of the housing 30 extending outward. This clutch device 46 is shown in FIG.
As shown in FIG. 3, the output shaft 40 has a cylindrical body 47 as an input member and a disc 48 as an output member rotatable relative to the cylindrical body 47. The cylindrical body 47 and the disc 48 are provided. It is configured to be intermittent according to the rotational load generated between the and.

More specifically, as shown in FIGS. 1 and 6, in the portion of the output shaft 40 extending to the outside of the housing 30, a reduced diameter portion 40a having a stepwise reduced diameter is formed. A cylindrical member 49 surrounding the output shaft 40 is integrally fixed to the diameter portion 40a by a key member 50.
A cylindrical body 47 as an input member is integrally mounted on the outside of the cylindrical member 49. An outer flange portion 47a is formed on the upper end portion side of the cylindrical body 47 so as to protrude outward from the upper end portion side thereof, and
A ring-shaped lower retainer 52 that supports the lower end of a coil spring 51 described later is attached to the lower end.
On the other hand, around the outer flange portion 47a of the cylindrical body 47, there is formed an inner flange portion 53a which is formed in a drum shape surrounding the lower surface side to the side surface side, and further has an inner peripheral edge side to which the upper end of the coil spring 51 is locked. An upper retainer 53 is provided. The retainer 5 is surrounded by the output shaft 40.
The coil spring 51 mounted between the two and 53 is configured to apply a reaction force to the lower retainer 52 to constantly urge the upper retainer 53 upward.

On the other hand, on the upper part of the cylindrical body 47, there is provided a disk 48 which is an output member by being superposed on the outer flange portion 47a from above. The disc 48 is arranged so as to be sandwiched by the cylindrical member 49 and the cylindrical body 47 from above and below,
Further, it is provided so as to surround the cylindrical member 49, and bearings 54 are respectively provided between the disk 48 and the cylindrical member 49 and the cylindrical body 47. Therefore, the disk 48 is attached so as to be rotatable relative to the output shaft 40 with respect to the cylindrical member 49 and the cylindrical body 48 which are integrally provided on the output shaft 40 and rotate together with the output shaft 40. And on the disk 48 thus configured,
A large-diameter table 55 is provided so as to overlap with this, and both are fastened with bolts 56. The table 55 has a hole 55a formed in the center thereof so as to project the output shaft 40 including the cylindrical member 49.

The disk 48 thus constructed and the cylindrical body 4
7 between the outer flange portion 47a and the upper retainer 53, the outer flange portion 47a is formed with a plurality of cutout portions 47b at intervals along the circumferential direction around the output shaft 40. A cylindrical rolling element 57 is rotatably attached to each of the portions 47b. Also, this notch 4
Corresponding to 7b, a pocket 48a is formed on the lower surface of the disk 48, which is in sliding contact with the upper cylindrical surface of the rolling element 57. In particular, the pocket 48a is formed by a taper surface inclined along the relative rotation direction of the cylindrical body 47 and the disk 48 around the output shaft 40, and holds the rolling element 57 in a detachable manner. . The upper retainer 53 also includes an outer flange portion 4
A rolling groove portion 53b is formed below the cutout portion 47b of 7a in an annular shape along the relative rotation direction of the cylindrical body 47 and the disk 48. The rolling element 57 is formed to have an outer diameter dimension that can be accommodated in the pocket 48a and the cutout portion 47b. When the rolling element 57 is separated from the pocket 48a, the rolling element 57 projects downward from the cutout portion 47b to allow the upper retainer 53 to move. The rolling groove 53b is adapted to roll along the groove.

By the way, the formation positions of the notch portion 47b and the pocket 48a corresponding thereto are set so as to match the turning angle α given by the swing rotation cam 33 described above. Rotating period (360
(°) is divided by the number of times of indexing S to set the turning angle α. In this embodiment, as shown in FIG. 6 (A), the turning angle α is 90 °, and accordingly, the turning angle α is set at four positions at 90 ° intervals.

Explaining the operation of the clutch device 46, the connection state of the clutch device 46 is shown as a torque transmission state in FIG. 6 (B). The load generated between the cylindrical body 47 and the disk 48 is small, so that the coil spring 5
The elastic urging force of 1 brings the upper retainer 53 into contact with the lower surface of the outer flange portion 47a of the cylindrical body 47, and the rolling element 57 causes the notch portion 47b of the outer flange portion 47a and the pocket 4 of the disk 48 to move.
In the state shown in the figure, which is housed in and held by 8a, the cylindrical body 47, which is an input member, and the disk 48, which is an output member, are integrally connected via the rolling elements 57. Therefore, the clutch device 46 is in the connected state, and the disc 48 has the output shaft 4
The rotational torque of 0 is transmitted through the cylindrical body 47, and the disc 4
8, by extension, the table 55 rotates integrally with the output shaft 40.

Next, the disengaged state of the clutch device 46 is shown as a torque cut-off state in FIG. 6 (C).
When a large load is generated between the disk 48 and the cylinder 47,
For example, when a load such that the disc 48 is restrained is applied, the pocket 48 a of the disc 48 and the outer flange portion 4 of the tubular body 47.
The rolling element 57 housed between the notch portion 47b of 7a
Is pushed by the cylindrical body 47 which tries to continue the rotation by receiving the rotation torque from the output shaft 40 against the stopped disk 48, and pushes down the upper retainer 53 against the elastic biasing force of the coil spring 51. At the same time, it is separated from the pocket 48a along the tapered surface of the pocket 48a. As a result, the clutch device 46 is disengaged. And rolling element 57
Is the disk 48 due to the elastic force of the coil spring 51.
While being sandwiched between the upper retainer 53 and the upper retainer 53, the rolling groove portion 5 of the upper retainer 53 while rolling in the notch 47b.
It rolls in 3b, and as a result, the cylindrical body 47 will rotate relative to the disc 48 that is stopped. During this period, the clutch device 46 is in the disengaged state, the cylinder 47 rotates together with the output shaft 40, and the transmission of the rotational torque of the output shaft 40 to the disk 48 is interrupted.
The table 55 stops. That is, when a load exceeding the set load set in the coil spring 51 is generated between the disk 48 and the cylindrical body 47, the rolling element 57 disengages from the pocket 48 a against the biasing force of the coil spring 51, and the clutch device 46. Is cut off and the rolling element 57
In the turning angle α, which is the range of rotation angle that
Relative rotation between the cylindrical body 47 and the disk 48 will occur.

Thereafter, as shown in FIG. 6 (D), when the rolling element 57 fits in the next pocket 48a, it is confirmed that the load between the disk 48 and the cylinder 47 is less than the set load of the coil spring 51. The clutch device 46 is connected to the condition, the torque transmission state is obtained again, and the disc 48 and the table 55 are rotated together with the output shaft 40. In the present embodiment, as described above, the turning angle α is 90 °.
Therefore, as shown in FIG. 6, the single torque interruption state (clutch disengagement state) occurs within the rotation angle range of 90 °.

The clutch actuating means is an operation for controlling the rotational load between the cylinder 47, which is the input / output member, and the disk 48 in order to cause the clutch device 46 thus constructed to perform the intermittent operation. This is done by the stopper 38. As shown in FIGS. 1 and 3, the stopper 38 is provided on the ceiling surface 30c of the housing 30 so as to face the lower surface of the table 55 integrally attached to the disk 48, which is an output member, from below. . This stopper 38
Is a reverse T-shaped block composed of a base portion 38a and a vertical wall 38b provided upright from the center of the base portion 38a, and is arranged at the outer peripheral edge position of the table 55. This stopper 38
On the lower surface of the upper table 55, a plurality of engaging bodies 39 which are removably engaged with the stopper 38 are provided at intervals of a turning angle α along the circumferential direction. These engaging bodies 3
Reference numeral 9 denotes a support block 39a fixed to the lower surface of the table 55 with bolts 58, and a support block 39a that is rotatably provided by horizontally projecting outward from the support block 39a toward the outer peripheral edge of the table 55, and a vertical wall 38b of the stopper 38. And a pair of rollers 39b slidably engaged with the vertical wall 38b so as to be sandwiched from both sides. Then, the engaging body 39 is adapted to enter and disengage from the stopper 38 so as to advance and retract with respect to the stopper 38 in accordance with the vertical movement of the table 55 by the output shaft 40.

In the stopper 38 provided in the housing 30, the table 55 is displaced by the output shaft 40 by an amount β.
The movement of the table 55 is stopped by moving the table 55 forward and the engaging body 39 is engaged, thereby increasing the rotational load on the side of the disk 48, which is an output member, and disengaging the clutch device 46. Clutch operation In addition to functioning as a means, it also functions as a positioning means for accurately holding the position of the engaged table 55. On the other hand, the engagement body 39 is disengaged from the stopper 38 when the table 55 is maintained at the position of the displacement amount 0 by the output shaft 40, so that the table 55 and the disk 48 are not rotated by the stopper 38. The load is not generated, and the clutch device 46 can be controlled to be in the connected state.

The operation of the above configuration will be described. As shown in the cam diagram of FIG. 5, the input rotary shaft 31 rotates up to 90 ° in one rotation 360 ° of the rotary motion of the input rotary shaft 31. Between the swinging rotary cam 3 of the cam mechanism 32
3 is a turning angle α on the output shaft 40 via the turret 34.
The rotation in one direction (indexing angle) is output. At this time, the vertical movement cam 36 moves the lift arm 3 by the dwell.
7 is stopped, and the output shaft 40 is stopped at the position where the displacement amount is 0. As a result, a large rotational load is not generated in the clutch device 46. Therefore, in the connected state of the clutch device 46, the cylinder body 47 and the disk 48 are integrally driven to rotate,
The table 55 is rotated in one direction with the output shaft 40 at a turning angle α.

Next, the input rotary shaft 31 moves from 90 ° to 180 °.
During the period of rotating up to, the swinging rotary cam 33 does not output rotation by the dwell, and the output shaft 40 enters the stationary period while maintaining the turning angle α. At this time, the table 55 also stops. At this stop position, the table 55 is arranged above the stopper 38 in accordance with the cam curve of the swing rotation cam 33.
The engaging body 39 is positioned at the turning angle α, and in this state, the up-and-down moving cam 36 moves the lift arm 3
The output shaft 40 is moved downward by a displacement amount β via 7, and the engaging body 39 enters the stopper 38 and engages with it, thereby fixing the table 55 to the housing 30 side. Then, this engagement state is maintained because the vertical movement cam 36 then stops the lift arm 37 by the dwell, and the output shaft 40 is stopped while maintaining the displacement amount β thereof.

Next, the input rotary shaft 31 moves from 180 ° to 270 °.
During the period of rotating up to °, the oscillating rotation cam 33 outputs the rotation in the opposite return direction at the turning angle α, and the turning angle becomes 0.
Let be °. At this time, the vertical movement cam 36 stops the output shaft 40 at the position of the displacement amount β by the dwell. As a result, a large rotational load is generated in the clutch device 46,
Therefore, the clutch device 46 is disengaged, and the cylinder 4
Relative rotation will occur between 7 and the disk 48.
That is, while the output shaft 40 is returned and rotated, the table 55 is stopped at the position of the turning angle α together with the engaging action of the engaging body 39 and the stopper 38.

Next, the input rotary shaft 31 moves from 270 ° to 360 °.
During the period of rotating up to °, the swinging rotary cam 33 does not output rotation by the dwell, and the swing angle of the output shaft 40 is 0 °.
Enter the stop period while maintaining. In this stop period,
The vertical movement cam 36 drives the lift arm 37 to drive the output shaft 4
0 is moved backward by the displacement amount β, the engaging body 39 of the table 55 is released from the stopper 38, returned to the position of the displacement amount 0, and the clutch device 46 is connected. In this disengaged state, the vertical movement cam 36 then stops the lift arm 37 by the dwell, and the output shaft 40
Is maintained while its displacement amount is maintained at 0, and is therefore maintained. Even during this stop period, since the swinging rotary cam 33 does not output rotation, no rotary torque is transmitted to the table 55 and the stopped state is maintained.

In this way, the output shaft 40 is the swinging rotary cam 3
While continuing the oscillating motion transmitted from No. 3, the table 55 repeats the stopping operation and the rotating operation by the intermittent control of the clutch device 46 by the stopper 38, thereby performing the intermittent rotating motion.
The position indexing during the intermittent rotary motion is performed by the stopper 38 that engages with the cam curve of the swinging rotary cam 33 and the engaging body 39 of the table 55 that is driven by the vertical moving cam 36 to move up and down to stop it. By means of and, it is possible to ensure the accuracy, and by this, it is possible to obtain the intermittent intermittent indexing motion. Further, in the present embodiment, the cutout portion 47b and the disk 48 of the cylindrical body 47 that constitutes the clutch device 46.
Since the pocket 48a of the clutch device is matched with the turning angle α, the intermittent operation of the clutch device 46 itself is performed at the indexing position. Therefore, the clutch device 46 also appropriately holds the indexing position. You can That is, in this embodiment, the swing rotation cam 3
3, the turning angle α of the clutch device 46, the arrangement angle α of the notch 47b and the pocket 48a of the clutch device 46, and the engagement body 3 of the table 55.
The arrangement angles α of 9 are all matched so that extremely high position indexing accuracy can be obtained.

In this embodiment, the output shaft 40 makes one reciprocating oscillation motion in one revolution of the input rotary shaft 31, while the table 55 makes a rotary motion which is sent out in one direction by the turning angle α. Will be done. The up-and-down moving cam 36 is provided with the stopper 3 during each of the two stop periods of the swinging rotary cam 33 in one rotation of the input rotary shaft 31.
Either the advancing movement for engaging the engaging body 39 of the table 55 with respect to 8 or the retreating movement for disengaging is alternately transmitted to the output shaft 40. And
In the present embodiment in which the turning angle α is 90 °, the table 55 is intermittently rotated by 90 ° and the input rotary shaft 31 is rotated.
It is designed to rotate once every four rotations.

By the way, in the intermittent indexing device of the present embodiment described above, basically, a cam which can create a reliable stop state by a dwell and can easily and surely obtain a positive motion of the whole motion. The intermittent rotary motion is extracted from the intermittent oscillating motion obtained by the oscillating rotary cam 33 by using the mechanical element called the mechanism 32 by the intermittent operation of the clutch device 46 controlled by the stopper 38. In addition, the indexing position is held by the engaging operation of the table 55 with respect to the stopper 38, and the positive intermittent indexing motion can be reasonably highly accurately obtained. In particular, in the present embodiment, while applying the operation principle of the existing pick-and-place unit, the intermittent indexing motion, which requires a completely different motion, is rationalized by using the cam mechanism 32 and the clutch device 46. Can be obtained in configurations.

Further, it is possible to eliminate the mechanical element such as the conventional brake device, which has a short operation guarantee period, to construct the mechanism, and it is possible to obtain a maintenance-free device.

The position indexing accuracy of the table 55 is essentially ensured with high accuracy by the cam curve provided in the swinging rotary cam 33.
The unnecessary rotation of the table 55, which has been indexed by the position, can be completely blocked by the stopper 38. Therefore, it is possible to semi-permanently ensure a highly accurate and stable positive motion by eliminating the influence of secular change in the braking device used to ensure the indexing motion in the conventional mechanism.

Further, since the up-and-down moving cam 36 alternately moves the output shaft 40 in either one of the advancing and retreating directions with respect to each stop period of the swinging rotary cam 33, the swinging motion is performed. When the rotary cam 33 rotates in one direction,
By connecting the clutch device 46, the table 55 rotates integrally with the output shaft 40 at a constant swing rotation angle, and during the other period, the table 55 is stopped by the dwell period of the swing rotation cam 33 and the disconnection of the clutch device 46. That is, it is possible to obtain an intermittent rotary motion in one direction, which allows the intermittent indexing motion to be performed.

Further, the cam curve of the oscillating rotary cam 33 does not limit the oscillating rotational angle range of the oscillating motion, so that the oscillating motion in the angular range of 180 ° or more can be created.

Further, as described above, the output shaft 40
Always performs an oscillating motion according to the motion of the oscillating rotary cam 33, and at the same time, the table 55 performs an intermittent rotary motion according to the intermittent control of the clutch device 46.
These two types of movements can be output coaxially from a single output shaft 40.

In the above embodiment, the output shaft 40 is alternately moved only in one of the advancing and retracting directions with respect to each stop period of the swinging rotary cam 33. The control of the output shaft 40 for the stay period of 33 is not limited to this. Regarding the setting of the intermittent indexing motion, with respect to the reciprocating drive of the output shaft 40 by the vertical movement cam 36, a motion for advancing in at least one direction is generated in any one of the stationary periods created by the swinging rotary cam 33 and stopped for a certain period, A cam curve may be created that causes a backward motion in at least the opposite direction during any one of the subsequent stopping periods to stop for a certain period. As a result, the output shaft 40 is rotated by the swing rotation cam 33.
During any one of the stay periods, the reciprocating motion that advances and retreats in at least one direction is generated, and the intermittent indexing motion obtained thereby becomes various.

[0066]

As described in detail above, according to the first aspect of the invention, in addition to the rotational movement, the independent axial reciprocating movement is transmitted from the cam mechanism to the output shaft, and the clutch actuating means operates. Since the clutch means is controlled to be intermittently operated, the output member can be repeatedly caused to perform the stopping operation and the rotating operation, and the intermittent rotating motion can be obtained from the rotating motion of the cam mechanism. Positioning during this intermittent rotary motion is accurately performed by the cam curve of the cam mechanism and the clutch actuating means that engages with and stops the output member of the clutch means that is driven by the cam mechanism and that undergoes reciprocating motion. It can be ensured, whereby a positive intermittent indexing movement can be obtained.

In particular, since the dwell is used to create a reliable stop state, and the cam mechanism is used as a mechanical element that can easily and reliably obtain a positive motion of the entire motion, it is possible to obtain by this cam mechanism. From the rotating motion
Intermittent rotation motion can be taken out by the on / off of the clutch means controlled by the clutch actuation means, and in this intermittent rotation motion, the indexing position can be held by the engaging operation of the clutch actuation means with the output member, and the positive movement can be performed. Intermittent indexing movement can be reasonably obtained with high accuracy.

Further, it is possible to eliminate the mechanical elements such as the conventional brake device having a short operation guarantee period and configure the mechanism, and it is possible to obtain a maintenance-free device.

The position indexing accuracy of the output member is essentially ensured with high accuracy by the cam curve provided in the cam mechanism, and the unnecessary rotation of the output member indexed by the cam mechanism is actuated by the clutch operation. It can be completely blocked by means. Therefore, the influence of secular change in the braking device used to ensure the indexing operation in the conventional mechanism is eliminated,
It is possible to guarantee semi-permanently a highly accurate and stable positive motion.

According to the second aspect of the present invention, when the output shaft rotates in one direction, the clutch member is connected to rotate the output member integrally with the output shaft at a fixed swing rotation angle. During the other period, the output member can be stopped by the dwell period of the rotational movement of the output shaft and the disconnection of the clutch means, and the intermittent rotational movement of the output member in one direction can be obtained. This allows the intermittent indexing movement to be obtained.

In addition, the cam curve of the cam mechanism does not limit the swinging rotation angle range of the oscillating motion, so that the oscillating motion in the angular range of 180 ° or more can be created.

Further, according to the third aspect of the invention, the output shaft can always be made to perform the rotary motion according to the rotary motion of the cam mechanism, and at the same time, the output member is intermittently rotated according to the intermittent control of the clutch means. The movements can be carried out, and in particular these two types of movements can be output coaxially from a single output shaft.

[Brief description of drawings]

FIG. 1 is a side sectional view showing a preferred embodiment of an intermittent indexing device according to the present invention.

FIG. 2 is a plan sectional view of the above embodiment.

FIG. 3 is a plan view of the above embodiment.

FIG. 4 is an enlarged view of a main part of a first cam mechanism adopted in the above embodiment.

FIG. 5 is a diagram for explaining an intermittent indexing operation of the above embodiment.

FIG. 6 is an explanatory view showing the structure and operation of the clutch device adopted in the above embodiment.

FIG. 7 is an overall configuration diagram of a roll feed for explaining a conventional example.

FIG. 8 is a partially cutaway front view of a roll portion of the roll feed.

[Explanation of symbols]

 32 Cam Mechanism 38 Stopper 40 Output Shaft 46 Clutch Device 47 Cylindrical Body 48 Disc

Claims (3)

[Claims] 1. An output shaft to which a composite motion that independently generates a rotational motion and an axial reciprocating motion is transmitted from a cam mechanism, an input member provided on the output shaft, and a relative rotation with respect to the input member. And an output member of the clutch means, which is engaged and disengaged according to the rotational load generated between the input and output members, and the output member of the clutch means that moves along with the axial reciprocating motion of the output shaft. An intermittent indexing device comprising: a clutch actuating means that is detachably engaged to intermittently actuate the clutch means. 2. The rotary motion is an intermittent oscillating motion having a dwell period, and the axial reciprocating motion is alternated with respect to the dwell period sequentially generated intermittently. 2. The output member is caused to undergo either one of an advancing movement to be engaged with the clutch actuating means and a retreating movement to be disengaged from the clutch operating means.
The intermittent indexing device described in. 3. The intermittent indexing device according to claim 1, wherein the output member is intermittently rotated at the same time when the rotary motion is output from the output shaft.