JPH01120472A - Motion converter - Google Patents

Abstract

PURPOSE:To reduce vibration and operational error without increasing the size of converter and power consumption by cancelling variable torque functioning onto an input shaft when motion of the input shaft is converted into motion of an output shaft and variable torque functioning onto the input shaft through a torque compensation cam and a pneumatic cylinder. CONSTITUTION:Continuous rotary motion of an input shaft 1 is converted through a transmission cam device 3 into intermittent rotary motion of an output shaft 2 which transmits its motion to a driven body. Torque functioning onto the output shaft 2 due to frictional resistance and inertia of the driven body varies continuously, and the reaction thereof is applied as variable torque onto the input shaft 1. But it is cancelled by variable torque functioning onto the input shaft 1 when a torque compensation can device 4 functions to reciprocate a piston 10 and compress/expand air in a cylinder 14, thereby scarcely applying variation torque onto the input shaft 1. Consequently, vibration and operational error can be reduced without increasing the size of converter or power consumption.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention is applicable to continuous rotary motion, intermittent rotary motion, special rotary motion such as oscillating rotary motion, or combinations of these rotary motions.
Alternatively, it is connected to a motion converting device for converting these rotational motions and linear motions into a predetermined type of motion such as a combination of motions.

Problems to be Solved by the Prior Art and the Invention Generally, the above-mentioned motion converting device includes an input shaft connected to a drive device such as a motor, and an output shaft connected to a driven body such as a turntable or a conveyor. The continuous rotational movement of the input shaft is converted into a predetermined type of movement as described above by means of a transmission cam device!
In turn, the converted motion is transmitted to the driven body via the output shaft. However, in the motion converting device that converts the continuous rotational motion of the input shaft into a predetermined type of motion of the output shaft as described above, the torque acting on the output shaft constantly fluctuates during operation, and the reaction of that torque The force acts on the input shaft as a fluctuating torque. The above-mentioned fluctuating torque acting on the input shaft becomes large especially during high-speed operation, which prevents uniform rotation of the input shaft and causes @ motion and accompanying work during operation, and compensates for the fluctuating torque. Therefore, there is a problem in that it is necessary to use a large drive device that generates a large amount of power or to enlarge the transmission cam device.

Japanese Patent Publication No. 60-32058 discloses a motion conversion device that solves the above problems. That is, this device is configured such that a torque compensating cam device separate from the transmission cam device is attached to the input shaft and the inertial mass body is rotated by the torque compensating cam device, and the fluctuating torque acting on the input shaft is
The structure is such that the variable torque applied to the input shaft when rotating the inertial mass body is offset by the torque compensating cam device. However, this motion conversion device had the problem that when a large fluctuating torque acts on the input shaft, the inertial mass body must be made large to accommodate this, resulting in an increase in the size of the device. .

SUMMARY OF THE INVENTION An object of the present invention is to provide a motion conversion device that solves the problems of the prior art described above.

SUMMARY OF THE INVENTION The present invention provides a motion converting device for converting continuous rotational motion of an input shaft into a predetermined type of motion of an output shaft via a transmission cam device, which includes a cam and a cam follower, and the cam is connected to an input shaft. A torque compensating cam device connected to the shaft, and a pneumatic cylinder device constituting a load body for applying a load to the torque compensating cam device, the pneumatic cylinder device being a cylinder into which gas pressure is introduced. , which is housed in the cylinder and connected to the cam follower marked -F, is pressed in the direction of bringing the cam follower into contact with the cam surface of the cam by the pressure of the gas introduced into the cylinder, and compresses the gas.
It has a piston that can reciprocate within the cylinder while being expanded, and a variable torque that acts on the input shaft when converting the motion of the input shaft into the motion of the output shaft via the transmission cam device. The above-mentioned problems of the prior art are solved by canceling out the fluctuation torque applied to the input shaft by the operation of the torque compensating cam device and the associated reciprocating movement of the piston within the cylinder.

Example Embodiments of the present invention will be described below with reference to the accompanying drawings.

1 and 2 show a first embodiment of the present invention. The motion conversion device ffA of the first embodiment is an intermittent drive for converting continuous rotational motion of the input shaft 1 driven by a drive device, that is, a motor 17, into an intermittent rotational motion of an output lNl2 via a transmission cam device δ3. It is configured as a device. The motor 17 and the input shaft 1 include a pulley 19 fitted to the rotation shaft 17a of the motor 17, and a fastening member 18.
The pulley 20 is fitted onto the input shaft 1 via the pulley 20 and the belt 21 is wound between the pulleys 19 and 20. The motor 17 continuously drives the input shaft 1 to rotate. It is supposed to be done.

The main driving member of the transmission cam device 3 is a three-dimensional cam 7 (a roller gear cam in the illustrated embodiment) connected to the input shaft 1.
On the other hand, the driven member is composed of a turret 6 having a plurality of cam followers 5 protruding from the periphery that sequentially engage with the three-dimensional cam 7, and the output shaft 2 is fitted into the center of the turret 6. ing.

The motion conversion device A also includes a torque compensation cam device 4 and a pneumatic cylinder device 9 that constitutes a load body for applying a load to the torque compensation cam device 4. The driving member and the driven member of the torque compensating cam device 4 each include a cam 15 connected to the input shaft 1 via a fastening member 8, and a cam follower 16 that engages with a cam surface 15a of the cam 15. There is. The pneumatic cylinder device 9 includes a cylinder 14 which has an action chamber 14a into which compressed air is introduced through an air intake 12 and a vibrator 13, and which is arranged adjacent to the right side of the outer peripheral surface of a cam 15; It has a piston 10 that is housed in an action chamber 14a and is capable of reciprocating within the action chamber 14a in a direction orthogonal to the axis of the cam 15.
A pressure regulating device 22 is provided for regulating the air pressure in the working chamber 14a and thereby the load applied to the torque compensating cam device 4.

In the illustrated embodiment, the cam 15 of the torque compensating cam device 4 is a disk-shaped cam whose center portion is attached to the input shaft 1, and the outer surface 15c of the cam 15 is attached to the outer surface 15c of the cam 15. A recess 15b extending outward (downward in FIG. 1) is formed. This recess 15b has an outer circumferential surface and an inner circumferential surface 15d whose contours are continuous in the circumferential direction of the cam 15, and the outer circumferential surface is the cam surface 15a. On the other hand, the cam follower 16 is composed of a single roller follower having a roller portion 16a that rolls into contact with the cam surface 15a, and a center shaft 16b that rotatably supports the roller portion 16a. , connected to the rod 10a of the piston 10 of the pneumatic cylinder device 9 and supported by the rod 1oa. The piston 10 is constantly pressed to the right by the pressure of the air introduced into the action chamber 14a of the cylinder 14, thereby bringing the cam follower into contact with the cam surface 15a of the cam 15.

J), the piston 10 is prevented from rotating within the cylinder 14 by a bolt 23, and the piston 10 is prevented from rotating within the cylinder 14.
is fixed to the housing 26 with bolts 25. In addition, in the figure, 24 is a nipple, and 26 is a cylinder 14.
A plug is shown that closes off the outer end of an air vent 27 drilled in the.

The above-mentioned motion conversion device continuously rotates the input shaft 1 and the three-dimensional cam 7 of the transmission cam device 3 integrally connected to the input shaft 1 by the motor 17, and the rotation is caused by the engagement of the three-dimensional cam 4 and the cam follower 5. This is converted into an intermittent rotational motion of the turret 6 and the output shaft 2 connected thereto, and transmitted to a driven body (not shown) such as a turntable or a conveyor. Further, as the input shaft 1 rotates, the cam 15 of the torque compensating cam device 4 integrally connected to the input shaft 1 rotates continuously, and the rotation is caused by the engagement between the cam 15 and the cam follower 16. , cylinder 1
This is converted into a reciprocating motion of the piston 10 within the piston 4. This reciprocating movement of the piston causes the action chamber 14 of the cylinder 14 to
This is carried out while compressing and expanding the air introduced into the chamber a and confined within the working chamber. By operating the torque compensating cam device 4 in this way to cause the piston 10 to move back and forth, almost no fluctuating torque acts on the input shaft 1 when the motion conversion device A is operated.

That is, as described above, the input shaft 1 is
When converting the continuous rotational motion of the output shaft 2 into intermittent rotational motion of the output shaft 2 and transmitting the motion of the output shaft 2 to the driven body,
I when activated! i! The load or torque acting on the output shaft 2 constantly fluctuates due to the resistance and especially the inertia of the driven body, and the reaction force of that torque acts on the input @1 as a variable at~r. When fluctuating torque acts on the input shaft 1 in this way, the uniform rotation of the input shaft 1 is hindered, and this becomes a cause of vibration of the motion conversion device and operational vJ errors. It is necessary to use a large drive device that generates a large amount of power or to enlarge the transmission cam device 3. However, in the illustrated embodiment, the fluctuating torque applied to the input shaft 1 as described above is caused by the actuation of the torque compensating cam device 4 and the piston 10.
This is offset by the fluctuating torque applied to the input shaft 1 when it moves back and forth while compressing and expanding the air in the action chamber 14a, so that almost no fluctuating torque acts on the input shaft 1.

When designing the above-mentioned motion converting device A, the variable torque Q1 applied to the input shaft 1 when the driven body is intermittently driven via the transmission cam device 3, and the reciprocating torque of the piston 10 via the torque compensation cam device 4 are used. The configuration of each part of the motion converting device should be determined so that the sum of the variable torque Q2 applied to the input @1 when moving becomes O. Conventionally, it has been widely practiced to calculate h1 the fluctuating torque that acts on the input shaft during the operation of a device that uses a cam such as an intermittent drive, and the condition is that the sum of fluctuating torque Q and 02 should be O as described above. It is easy for those skilled in the art to determine the configuration of each part of the device given the following. To briefly describe the determination method, first of all, the above-mentioned fluctuating torque Q1 is calculated as follows:
Torque due to one inertial load, I! Torque due to a friction,
The torque is a combination of torque due to viscosity and the like, and assuming that the fluctuating torque Q2 is a torque due to compression and expansion of air by the pneumatic cylinder device 9, it is expressed by the following equations (1) and (δ).

Equations (2) and (2) above are similar to the well-known formula for calculating the fluctuating torque acting on the input shaft during operation of the intermittent drive. Therefore, a detailed explanation of equations (1) and (2) will be omitted, and the physical meaning of each parameter used in the equations will be briefly explained as follows.

A, V and Sl: Output shaft 2 of transmission cam device 3
Acceleration, velocity and displacement ml: fA of the driven body C1: viscous resistance coefficient 1: Spring constant Fol: initial tension F of the spring, 1: frictional force F, 1: force due to gravity θ and θ2: division The attached angle is the angle (rotation angle of the input shaft 1 required for the output @2 to perform one indexing, that is, one intermittent rotation) K2: Spring constant due to air pressure ■ and S2: Piston 10 of the pneumatic cylinder device 9
Speed and displacement r ''-r5: Rotation to the point of action When designing the radial motion conversion device A, first determine the rotation speed of the input shaft 1, the motion type of the output shaft 2, the configuration of the transmission cam device 3, etc. The decision is made in the same manner as in the case of conventional intermittent drive devices, depending on the type of the driven body to be connected to the drive body and its load mass, etc. When the above decision is made, the above formula (1) is used. It is possible to obtain numerical values for each parameter used.

Next, in the above equations (1) and (2), the configuration of the torque compensation cam device 4 and the pneumatic cylinder device 9 is determined so as to minimize the difference Q3 between the fluctuating torques Q1 and Q (non-conservative torque). . That is, Ql.

The relationship between Q and Q' is set as shown in equations (3) and (4) below.

Ql-02=Q3Q3(Ql(3)) Here, the three-dimensional cam 7 of the transmission cam device 3 and the cam 15 of the torque compensation cam device @4 are fitted onto the same input shaft 1 and are integrated with the input shaft. When rotating and canceling the fluctuating torque applied to the input shaft 1, C1 and 0□ become equal.Therefore, the above equation (4) can be simplified as the following equation (5).

ml(A1+■1)r1+C1v1r2+1(S1×
■1) r3+ (Fo1+Ff1+Fg1) ■1・C4-
2(S2×v2)r5=03(9) Therefore, equation (5)
In A, Vl, 81°ml, C1, 1. F
Since ol, Ffl, and Fgl are already known, for example, by setting the value of 2 to an appropriate value so that C3 (Ql, that is, Q) is minimized, The configurations of the torque compensating cam device 4 and the pneumatic cylinder device 9 can be designed based on N2, V2, and S2 determined in this way.

The fluctuating torque that acts on the input shaft 1 when the transmission cam device 3 operates is a combination of inertial load torque, torque due to friction, torque due to viscosity, etc., but the inertial load torque is significantly increased during high-speed operation. It can be said that the variation 1-lux is substantially determined by the inertial load torque. The torque compensating cam device 4 and the pneumatic cylinder device 9 are configured to apply torque to the input horn shaft 1 in order to offset this inertial load torque. That is,
The operational relationship between the torque compensation cam device 4 and the pneumatic cylinder device 9 is such that the kinetic energy of the piston 10, which is caused to reciprocate by the torque compensation cam device 4, is converted into energy that compresses and expands air within the action chamber 14a due to the movement. You can say that you are doing it. The compression and expansion energy of air has the same dimensions and is equivalent to potential energy, and therefore the torque compensation cam device @4 and the pneumatic cylinder device 9 comply with the law of conservation of energy. It is clear from the viewpoint of mechanics that the dynamical system in which

Therefore, while the inertial load torque belonging to the conservative system can be compensated for by this operation, the torque due to friction and viscosity, etc., which is succumbed to the non-conservative system cannot be canceled out.

As already mentioned, the pneumatic cylinder device 9 in the illustrated embodiment
is provided with a pressure adjustment device 22 for adjusting the air pressure in the action chamber 14a, but this configuration is such that the magnitude of the fluctuating torque applied to the input shaft 1 changes due to the operation of the transmission cam device 3. Sometimes, depending on the change, the action chamber 1
By changing the air pressure in 4a, the fluctuating torque, that is, the inertial load torque, is changed to
4 and the actuation of the air cylinder device 9 offer advantages that make it possible to suitably compensate. That is, for example, if the rotational speed of the input @1 increases, the load torque applied to the input shaft by the operation of the transmission cam device will increase, but in such a case, the pressure regulating device is adjusted to reduce the pressure in the action chamber 14a.
By increasing the air pressure inside, the increased inertial load torque can be effectively offset.

3 and 4 show a second embodiment of the invention.

This second embodiment is a modification of the structure of the torque compensating cam device and the pneumatic cylinder device in the first embodiment. That is, in the second embodiment, the cam 15A of the torque compensating cam device 4A is a disc-shaped cam connected to the input shaft 1 by the bolt 3o with its center aligned with the central axis of the input shaft 1. The outer surface 1 of the cam 15A
5C' is formed with a recess 15b' extending outward (toward the dot in FIG. 3) on its outer surface. This recess 15b' is
It has an outer peripheral surface that is continuous in the circumferential direction of the cam 15A and has a curved profile vertically (FIG. 4) symmetrically with respect to a plane X that includes the axis of input @1, and the outer peripheral surface is 15A
cam surface 15a'. On the other hand, the cam follower 16A of the torque compensating cam device 15A has the above-mentioned cam surface 15
It consists of two roller followers that roll into contact with each other at positions 180 degrees apart from each other at a'. Each of these cam followers 16A has a roller portion 16a' that rolls into contact with the cam surface 15a', and a central shaft 16b' that supports the roller portion 16a' in a rotatable manner.

The pneumatic cylinder device 9A also includes a cylinder 14Δ provided on the outside of the cam 15A so as to face the cam 15A, and a cylinder 14Δ provided inside the cylinder in directions opposite to each other from the axis of the input shaft 1 (as shown in FIG. 1.2). Two pistons 10A and 10[3 are housed at positions equidistantly apart from each other in the left-right direction), and these pistons 10A and 10B are located at the center Il*16b' of each cam follower 16A, respectively.
The cam follower 16A is supported by the cam follower 16A. Two pistons 10A, 10 of the cylinder 14A
The portion between B is a working chamber 14a', and compressed air is introduced into this working chamber 14a' through the air vent 12 and the vibrator 13.

And each screw 1-1o△, 10B is an action chamber 14a'
The compressed air inside the cam followers 16A pushes them apart from each other, and the pressure causes each cam follower 16A to contact the cam surface 15a'.

The torque compensating cam device 4AJ and the pneumatic cylinder device 9A in the second embodiment also operate on the same principle as that in the first embodiment, so that the continuous rotational movement of the input shaft 1 is intermittently transferred to the output shaft 2 via the transmission cam device 3. A variable torque is applied to the input shaft 1 so as to offset the variable torque applied to the input shaft 1 when converting into rotational motion. In the second embodiment, pistons 10A and 10B are arranged on both the left and right sides of the input shaft 1, so that these pistons move symmetrically. That is, cam 15
When each piston moves in response to the rotation of A, each piston moves by the same amount in opposite directions (that is, either farther apart or closer to each other). Therefore, there is an advantage that dynamic balance can be obtained during operation, and operation can be performed smoothly. In this second embodiment, the cam surface 15a' is
Since it is symmetrical with respect to the plane 4X, the pattern of variable torque applied to the input shaft 1 by the operation of the transmission cam device 2!3 repeats the same pattern every 180 degrees of rotation of the input shaft. It can be suitably used in such cases.

The configuration of the second embodiment other than the above points is substantially the same as that of the first embodiment, and in FIGS. 3 and 4, the same elements as in FIGS. 1 and 2 are the same. Indicated by reference numerals.

Effects of the Invention As is clear from the above, according to the present invention, the fluctuating torque that acts on the input shaft when converting the motion of the input shaft into the movement of the output shaft through the transmission cam device is reduced to torque. This can be offset by the fluctuating torque applied to the input shaft by the operation of the compensation cam device and the pneumatic cylinder device, and vibrations and operational errors during operation can be canceled out without unreasonably increasing the size of the device or unreasonably increasing power consumption. This has the effect of being able to suitably reduce the

[Brief explanation of the drawing]

FIG. 1 is a partially sectional plan view showing a motion conversion device according to a first embodiment of the present invention, FIG. 2 is a partially sectional front view of the motion conversion device, and FIG. 3 is a motion conversion device according to a second embodiment of the present invention. FIG. 4 is a partially sectional front view of the motion conversion device of FIG. 3; DESCRIPTION OF SYMBOLS 1... Input shaft, 2... Output shaft, 3... Transmission cam device, 4.4A... Torque compensation cam device, 5... Cam follower, 6... Turret, 7... Three-dimensional Cam, 9
, 9A... pneumatic cylinder device, 10. IOA, 10
B...Piston, 14.14A...Cylinder, 15
．． 15A...Cam, 16.16A...Cam follower, 17...Motor, 22...Pressure adjustment device.

Claims (5)

[Claims] (1) In a motion conversion device that converts continuous rotational motion of an input shaft into a predetermined type of motion of an output shaft via a transmission cam device, a torque compensating cam having a cam and a cam follower, the cam being connected to the input shaft. and a pneumatic cylinder device constituting a load body for applying a load to the torque compensating cam device; The cam follower is connected to the cam follower, and the cam follower is pressed in the direction of contacting the cam surface of the cam by the pressure of the gas introduced into the cylinder, and can move back and forth within the cylinder while compressing and expanding the gas. and a piston that acts on the input shaft when converting the motion of the input shaft into the motion of the output shaft via the transmission cam device, the fluctuating torque acting on the input shaft is transferred to the operation of the torque compensating cam device and the accompanying piston. 1. A motion conversion device characterized in that the motion conversion device is configured to offset by fluctuating torque applied to an input shaft due to reciprocating movement of a piston within a cylinder. (2) The motion conversion device according to claim 1, wherein the pneumatic cylinder device includes a pressure adjustment device that adjusts the gas pressure within the cylinder. (3) In the motion converting device according to claim 1 or 2, the cam is a disc-shaped cam, and the outer surface of the cam has an outer circumferential surface that is continuous in the circumferential direction of the cam. a recess having an outward opening on the outer surface of the cam, the outer peripheral surface of the recess being the cam surface, and the cam follower rollingly contacting the cam surface. A motion conversion device comprising a roller follower, and the piston comprising a single piston connected to a central axis of the roller follower. (4) In the motion converting device according to claim 1 or 2, the cam is a disc-shaped cam, and the cam has a recess that opens outward on the outer surface of the cam. The recess is continuous in the circumferential direction of the cam and has an outer circumferential surface curved so as to be symmetrical with respect to a plane including the axis of the input shaft, and the outer circumferential surface is The cam surface is the cam surface, and the cam follower is composed of two roller followers that roll into contact with each of two positions separated by 180 degrees from each other on the outer peripheral surface, and
A motion converting device comprising two pistons, each of which is connected to a central axis of each roller follower and is reciprocated by these roller followers so as to move toward and away from each other. (5) In the motion converting device according to any one of claims 1 to 4, the transmission cam device sequentially engages a three-dimensional cam connected to an input shaft and the three-dimensional cam. A plurality of cam followers projecting from the periphery thereof and a turret connected to the output shaft are provided, and the continuous rotational movement of the input shaft is converted into intermittent rotational movement of the turret via the three-dimensional cam. A motion conversion device configured to be taken out from the output shaft.