JPS583861B2 - Trolley drive device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention is characterized in that the outer circumferential surface of a drive shaft disposed along the running track of a bogie is slightly inclined with respect to a plane perpendicular to the axis of the drive shaft provided on the bogie. The present invention relates to a truck drive device that causes a truck to travel by pressing friction discs into contact with each other.

Generally, positioning control in each process such as an assembly line, which requires almost no human effort, requires a high level of accuracy within several millimeters.

For this reason, methods such as endless chains or the like are arranged along the running track of the assembly line and are constantly driven to lock each running vehicle and transport it between each process. There is.

However, in the above-mentioned method, in an automobile assembly line, etc., which requires a huge number of steps, the control of the traveling vehicle between each step becomes extremely complicated, and the cost is inevitably high.

Therefore, in the above-mentioned assembly line, etc., there is a need for vehicles that can freely control each vehicle and that have reliable positioning control in each process.

The present invention is based on the above points, and provides a traveling vehicle that can freely control each traveling vehicle and has advanced positioning control.

Hereinafter, the present invention will be explained in detail based on the drawings.

In FIGS. 1 and 2, a truck T is supported on a track 1 via wheels 2, and a drive shaft 3 is disposed along the track 1.

A frame 4 is fixed to the lower surface of the trolley T, and side plates 5a and 5b of a bracket 5 are fixedly suspended from the frame 4.
In between, a rod 6 is fixed perpendicular to the axis of the drive shaft 3.

A support guide 7 is fitted to the rod 6 in a slidable and rotatable manner, and a rotating shaft 9 is rotatably supported by a bearing housing 8 (not shown) in a bearing housing 8 integrated with the supporting guide 7. A ring-shaped friction disk 11 is fixed to the lower surface of a disk body 10 formed at the lower end of the rotary shaft 9 so as to be perpendicular to the axis of the rotating shaft 9 .

The material of the friction disk 11 is preferably urethane rubber, neoprene rubber, synthetic rubber, etc., which are the best in terms of wear, elasticity, transmission ability, etc.

Furthermore, the axis of the rotating shaft 9 is inclined at a slight angle α with respect to the plane perpendicular to the axis of the drive shaft 3, and the friction disk 11 is configured to contact the outer peripheral surface of the drive shaft 3 at one point. Ru.

At this time, the contact surface 11a of the friction disk 11 is formed in a conical shape inclined at the same angle as the inclination angle α of the rotating shaft 9 with respect to the plane perpendicular to the axis of the rotating shaft 9, and A support arm 15 having a rotatable roller 14 at its tip is supported 13 on a support block 12 protruding from the upper surface of the guide 7, and a support arm 15 is screwed onto a bracket 16 protruding from the front side of the bearing housing 8. Contact surface 1 of friction disk 11 at spring 18 biased between adjustable plates 17
1a is configured to press against the outer circumferential surface of the first drive shaft 3.

Furthermore, a spring 21 is biased between a fixing pin 19 protruding from the side of the bearing housing 8 and a fixing pin 20 protruding from the bottom of the trolley T, so that the side surface of the support guide 7 that indirectly supports the friction disc 11 is biased. , is always in contact with the side plate 5b of the bracket 5 and its position is controlled.

At this time, as the trolley T travels, the rotatable cam roller 23 provided at the tip of the L-shaped arm 22 protruding from the lower surface of the support guide 7 comes into contact with the cam plate K provided on the ground side and having a predetermined slope, thereby supporting the support guide 7. The guide 7 moves along the rod 6 in a direction approaching the axis of the drive shaft 3 against the spring 21.

Incidentally, in conjunction with the movement of the support guide 7, the roller 14 provided at the tip of the support arm 15 also moves to the guide frame 24.
run on top.

That is, the side surface of the support guide 7 is the side plate 5 of the bracket.
The state in which the trolley T is in contact with b is the normal running state of the trolley T, and the support guide 7 indirectly supports the friction disc 11 by the cam roller 23 contacting the cam plate K while the trolley T is running. Resisting the spring 21, the cam plate K moves toward the axis of the drive shaft 3 according to the inclination angle of the cam plate K, and the drive shaft 3
When the center of the friction disk 11 coincides with the axis of , that is, at the position indicated by the chain line, the vehicle completely stops running.

In addition, 25 is an adjustment block 2 protruding from the support guide 7.
The adjustment bolt screwed onto the rod 6 prevents the friction disk 11 from unnecessarily pivoting around the rod 6 at joints, cuts, etc. of the drive shaft 3.

FIG. 3 shows the positional relationship of the contact points when the center of the friction disk 11 coincides with the axis of the drive shaft 3, that is, in the stopped state.
Located on the axis of the drive shaft 3, as described above, the friction disk 1
When the center 0 moves 1 in a direction orthogonal to the axis of the drive shaft 3 and reaches the chain line position O1, the contact point P also moves on the axis of the drive shaft 3 and reaches the contact point P1 position from the contact point P.

At this time, a line connecting the friction disk center O1 and the contact point P1 has a displacement angle θ with respect to the axis of the drive shaft 3.

The displacement angle θ is theoretically possible in the range of 0 degrees to 90 degrees, but in reality, it is set in the range of approximately 45 degrees from 0 degrees, taking into account the output of the drive motor that is the drive source, etc. .

That is, when the displacement angle θ is approximately 45 degrees, the normal running state is reached, and the moving distance L of the contact aP during this time is calculated as follows: If the distance between the friction disk center O and the contact point P is A, or L =
It is expressed as A −A cosθ.

In reality, as the friction disk 11 moves, the position of the contact point P itself changes on the axis of the drive shaft 3 and in the direction of the outer circumference of the disk 11, so the value is the sum of this change value. .

In this embodiment, as described above, a cart drive device that moves the friction disk 11 in a direction perpendicular to the axis of the drive shaft 3 has been described, but as shown in FIG. It is also possible to rotate the center O of the disk 11 to cause the displacement θ.

In this case, the contact point P basically does not change its position.

5 and 6 show partial cross-sectional views of the contact surface 11a in a running stopped state and a normal running state, that is, in an approximately 45-degree displaced state, and show the disk body 10 and the contact surface 11a formed at the tip of the rotating shaft 9. , a friction disk 11 fixed to the disk body 10
is inclined at a slight angle α with respect to the axis of the drive shaft 3.

Basically, it is possible if the inclination angle α is equal to or greater than zero degrees.

In reality, the best angle of inclination α is determined in consideration of elastic deformation, wear, etc. of the friction disk 11.

Further, the drive shaft contact surface 11a of the friction disk 11 is connected to the drive shaft 3.
It is formed to be inclined at an angle α with respect to a plane parallel to the axis of the rotary shaft 9, that is, perpendicular to the axis of the rotating shaft 9.

Therefore, the friction disk contact surface 11a basically becomes a line contact, and in reality it becomes a surface contact because it has elasticity.
The braking distance is reliable, and there is no risk of errors in positioning control due to inertia, etc.

Another advantage of the present invention is that by changing the inclination angle of the cam plate K, the running speed and braking distance can be controlled regardless of the rotation speed of the drive shaft 30, thereby preventing the effects of inertia, etc.

As described above, FIG. 6 shows the contact surface 11b in the normal running condition, and the cross-sectional shape of the contact surface 11b of the friction disk 11 is a gently curved surface, and is basically a little close to the tip.

In reality, since it is an elastic body, there is surface contact and almost no effect occurs.

Therefore, the state of the contact point from the actual running state to a complete stop state, that is, from a displacement of about 45 degrees to a displacement angle of 0 degrees, is to move from slightly near the tip to the center of the contact surface, and to completely stop in the stopped state. The entire surface hits, and at this time, the speed gradually decreases from the normal running speed, and the speed also reaches zero when the entire surface hits.

As described above, in the present invention, the contact area of the contact surface increases as the displacement angle approaches 0 degrees from approximately 45 degrees, so the braking distance is reliable and positioning based on inertia etc. There is no risk of control errors.

Furthermore, by adjusting the slope angle of the cam plate, braking distance and speed can be controlled regardless of the rotation speed of the drive shaft.

Therefore, highly accurate positioning control is possible.

Furthermore, since the mechanism is relatively simple, costs are reduced.

[Brief explanation of the drawing]

Figures 1 and 2 are schematic front and side views of the cart drive device, Figures 3 and 4 are diagrams explaining the movement state of the friction disk contact point, and Figures 5 and 6 are FIG. 3 is a partial cross-sectional view of the contact surface in a running stopped state and a running state. 1... Orbit, 3... Drive shaft, 9...
...Rotating shaft, 11...Friction disk, T...
...Dolly.

Claims (1)

[Claims] 1. A drive shaft is arranged along the running track of the bogie, and a friction disk is provided on the bogie so as to be rotatable around a rotation axis that is slightly inclined with respect to a plane perpendicular to the axis of the drive shaft. Further, the contact surface of the friction disk with the drive shaft is formed to be inclined at the same angle as the above-mentioned inclination angle with respect to the plane perpendicular to the rotation axis, and the friction disk is pressed against the outer circumferential surface of the drive shaft. A bogie drive device characterized in that the bogie travels by touching the bogie.