JPS583860B2 - Trolley drive device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a bogie drive device that causes a bogie to travel by pressing a friction disk provided on the bogie against the outer peripheral surface of a drive shaft disposed along a running track of the bogie, and further relates to To be more specific, a friction disk is attached to the lower surface of the drive shaft at the lower surface of the disk body formed at the tip of the rotating shaft that is slightly inclined with respect to the plane perpendicular to the axis of the drive shaft. The trolley travels by pressing against each other.

The above-mentioned propulsion force and speed during bogie running change depending on the positional relationship between the center of the friction disk and the contact point of the drive shaft of the friction disk.Theoretically, the line connecting the above two positions is the axis of the drive shaft. On the other hand, as the distance approaches the 90-degree change, the propulsive force becomes infinitely small, and conversely, the speed becomes infinitely large.

Therefore, at the time of 90 degree displacement, the propulsive force becomes completely zero, and it becomes impossible to obtain a speed that is inseparable from the propulsive force.

Also, as the displacement approaches zero, the propulsive force becomes infinitely large.
On the other hand, the speed becomes infinitely small.

Therefore, at the point when the axis line of the drive shaft is completely aligned,
Since the speed is zero, it is impossible to obtain propulsion.

That is, in the diagrams of the principle of propulsion shown in FIGS. 1 and 2, when the line connecting the drive shaft contact point P of the friction disk and the friction disk center O forms an angle θ with the axis of the drive shaft, When rotational torque T is applied to the drive shaft, tension F acts in the direction between the contact point P and the disk center O, and as a reaction force, the tension F acts on the extension line connecting the disk center O and the contact point P. A force R equal to is applied.

Therefore, the component force Ra in the axial direction of the drive shaft serves as a propulsive force to cause the bogie to travel.

That is, Because it is becomes.

Furthermore, as shown in the second figure, when the cam roller interlocking with the friction disk provided on the bogie comes into contact with the cam plate K provided on the ground side while the bogie is running, friction is generated along the profile of the cam plate K. The disk moves toward the drive axis, and with this movement, the propulsive force increases and, conversely, the speed decreases.

Incidentally, when the disk center O coincides with the drive axis, the speed becomes zero and the disk stops completely.

Also, in the speed principle diagrams shown in Figures 3 and 4,
Under the same conditions as the propulsive force described above, if the drive shaft rotation speed is N and the drive shaft diameter is D, a velocity V acts in a direction perpendicular to the line connecting the disk center O and the contact point P, The bogie travels at a speed V in the drive axis direction, which is the component force.

That is, Because it is, becomes.

Furthermore, when the cam roller on the truck comes into contact with the cam plate K as shown in the fourth figure, the friction disk moves toward the drive axis along the direction of the cam plate K, and the speed gradually decreases as described above. death,
When the center O of the friction disk coincides with the drive axis, the speed becomes zero and comes to a complete stop.

From the above, it can be seen that the propulsive force and speed change as the displacement angle θ changes within the range of 0 degrees to 90 degrees.

In reality, the displacement angle θ is set to approximately 45 degrees from 0 degrees due to the output of the drive motor serving as the drive source.

Therefore, the above displacement angle, which is the normal running state of the truck, is approximately 45
At a displacement angle of 45 degrees, the speed is maximum and the propulsive force is minimum, so it is important to maximize the transmission capacity of the friction disk at a displacement angle of 45 degrees.

The present invention is based on the above point, and the displacement angle is approximately 45
The object of the present invention is to provide a bogie drive device that has the best power transmission capability under normal running conditions.

Hereinafter, the present invention will be explained in detail with reference to the drawings.

In FIGS. 5 and 6, 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 truck T, and a rod 6 is fixed perpendicularly to the axis of the drive shaft 3 between side plates 5a and 5b of a bracket 5 which is fixedly suspended from the frame 4.

A support guide 7 is fitted into 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 for the friction disk 11 is preferably urethane rubber, neoprene rubber, synthetic rubber, etc., which are most excellent 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 into a conical shape that is somewhat gentler than the inclination angle α of the rotary shaft 9 with respect to the plane orthogonal to the axis of the rotary shaft 9, and a support arm 15 having a rotatable roller 14 at its tip, which is pivotally supported 13 on a support block 12 protruding from the bearing housing 8; and an adjustable plate screwed onto a bracket 16 protruding from the front side of the bearing housing 8. The flexural surface 11a of the friction disk 11 is caused by the spring 18 biased between the
is configured to press against the outer peripheral surface of the 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 lower surface of the truck T, so that the side surface of the support guide 7 that indirectly supports the friction disc 11 is The position is always controlled by being in contact with the side plate 5b of the bracket 5.

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 1 toward the axis of the drive shaft 3 in accordance with 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
Traveling stops completely at the chain line position.

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. 7 shows a partially enlarged view of the point when the center of the friction disk 11 coincides with the axis of the drive shaft 3, that is, when the running is stopped. , with respect to the axis of the drive shaft 3, and the contact surface 11a of the friction disk 11 is formed with an angle β with respect to the axis of the drive shaft 3.

FIG. 8 shows a partially enlarged sectional view of the transmission section in a state where the center of the friction disc 11 is displaced by approximately 45 degrees with respect to the axis of the drive shaft 3, that is, in a normal running state. The surface 11b has a curved shape and is configured to make point contact with the outer peripheral surface of the drive shaft 3 at approximately the center point P of the curved surface.

Note that during actual running, the friction disk 11 formed of an elastic body is pressed, so the entire surface of the contact surface 11b comes into contact with the outer peripheral surface of the drive shaft 3.

The above-mentioned contact point P of the curved surface contact portion 11b changes depending on the inclination angle β of the contact surface of the friction disk 11 shown in FIG.

The inclination angle β at the contact point P will be described in detail below.

In FIG. 9, A shows a plan view of the friction disk 11, B shows a view taken along the line C-C in FIG. 9, and C shows a view taken along the line B-B in FIG. The radius is R, from the center of the disk 11 0,
The distance between the axes of the drive shaft 3 is A, the inclination angle of the contact surface of the disc 11 is θ1, 1/n when the cross-sectional width of the disc 11 is divided into n equal parts is a, and each inclination displacement in the thickness direction at this time is If b is the distance between the contact point Q on the disk outer periphery from the center line of the disk 11 perpendicular to the axis of the drive shaft 3, and the distance between the contact point P from the disk center O, that is, a divided into n equal parts from the disk center O. The distance between the Pth points of contact, r=A+P·a, and therefore the distance between the contact points P from the center line of the disk 11 perpendicular to the axis of the drive shaft 3, l1-l2=y, then the following equation is obtained.

At this time, Because it is, Expressed as a general formula, if P・b=x, then Become.

That is, the shape of the disc contact surface in the B-B arrow view is It is expressed as

Furthermore, in FIG. 10, the slope T of the tangent at the contact point P
Then, since t=(A+X)2-A2, furthermore, since , the general formula for the graph of the tangent T is

Therefore, the slope at the Pth point is Then, Letting the tilt angle be λ, becomes.

At this time, the tangential inclination angle of the point P in FIG. The best transmission force is applied when the line connecting the center O of the friction disk 11 and the contact point P is displaced by approximately 45 degrees, that is, under normal running conditions.

Therefore, basically, when the center O of the friction disk 11 coincides with the axis of the drive shaft 3, that is, when the running is stopped, the inner circumference of the friction disk 11 is at a point P-1, and when the drive shaft 3 is running normally, it is at the middle point P. Become.

In reality, as described above, since the vehicle travels by pressing against the friction disk 11 formed of an elastic body, the contact portion 11b is in contact with the entire surface when the vehicle is traveling, and when the vehicle is stopped, the contact portion 11b touches the entire surface. It hits the inside surface.

The angle of inclination β is a value that corrects the slight displacement angle caused by the rotation, since the friction disk 11 rotates slightly clockwise around the rod 6 when it is displaced from the stopped state to the running state. It is said that

As described above, in the present invention, when the trolley T is in the normal running state, the drive shaft contact portion of the friction disk is brought into contact with the entire surface, so that the transmission capacity of the trolley is maximized, and the carrying capacity is maximized. Can be done.

[Brief explanation of drawings]

Figures 1 to 4 are explanatory diagrams of the principle of running the truck, Figures 5 and 6 are front and side views schematically showing the truck drive device, and Figure 7 is the friction circle when the truck is stopped running. FIG. 8 is a partial enlarged cross-sectional view of the friction disk contact portion when the bogie is running, FIG. 9 is a diagram illustrating the contact portion when the friction disk is running and stopped, and FIG. 10 is a partial enlarged view of the plate. FIG. 3 is a graph showing a cross section of a contact portion when a friction disk is running. 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. , furthermore, with respect to the axis of the drive shaft, an angle smaller than at least the above-mentioned inclination angle is made toward the outer circumference from the inner circumferential surface of the contact surface with the drive shaft passing through the center of the friction disk parallel to the axis of the drive shaft as a starting point. A bogie drive device, characterized in that the bogie is moved by forming an inclined friction disk and pressing the friction disk against the outer peripheral surface of a drive shaft.