JPS583859B2 - Friction disc sliding device in bogie 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.

The propulsion force during the above-mentioned bogie travel changes depending on the positional relationship between the center of the friction disk and the contact point of the drive shaft of the friction disk, and theoretically, the line connecting these two positions is the axis of the drive shaft. For,
As the displacement approaches 90 degrees, the propulsive force approaches zero infinitely, and at the time of 90 degree displacement, the propulsive force becomes completely zero.

Conversely, as the displacement approaches 0 degrees, the propulsive force increases to infinity.

However, at the point when the axis of the drive shaft completely coincides with the axis of the drive shaft, it becomes impossible to obtain the propulsive force of the truck from the rotational force of the drive shaft.

In other words, it becomes a stopped state. However, in reality, due to the output of the drive motor that is the drive source, the displacement angle varies from zero to about 4
It is said to be 5 degrees.

The propulsion force is transmitted by pressing one point of the friction disk against the outer peripheral surface of the drive shaft, and is generated by the frictional resistance at the contact point, but the transmission force due to the frictional resistance is equal to the pressing force of the friction disk. It changes accordingly.

Therefore, it is most ideal to always set the pressing force to a constant pressure.

However, since the contact point is displaced in the vertical direction according to the displacement angle of the friction disk, it is difficult to press the friction disk with a constant pressure at all times when using means that moves the friction disk horizontally to change the displacement angle. It becomes complicated and very difficult.

The present invention is based on the above points, and has a simple mechanism.
Moreover, the present invention provides a device that can maintain a constant pressing force at all times.

The details will be explained below based on the drawings.

FIG. 1 shows a schematic diagram of the bogie drive device of the present invention.
The truck T is supported on a track 1 via wheels 2, and a drive shaft 3 is disposed along the track.

A frame 4 is fixed to the lower surface of the truck T, and an inclined 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 so as to be slidable and rotatable, and a rotating shaft 10 is rotatably supported by a bearing 9 in a bearing housing 8 that is integrated with the support guide 7, as shown in the second figure. A ring-shaped friction disk 12 is fixed to the lower surface of a disk body 11 formed at the lower end of the rotating shaft 10, perpendicular to the axis of the rotating shaft 10.

The axis of the rotating shaft 10 is inclined at a slight angle α with respect to a plane perpendicular to the axis of the drive shaft 3, so that the friction disk 11 contacts the outer peripheral surface of the drive shaft 3 at one point.

Furthermore, the contact surface 12a of the friction disk 12 is formed in the shape of a cone inclined at the same angle α as the inclination angle α of the rotating shaft 10 with respect to a plane perpendicular to the axis of the rotating shaft 10, and is biased by a spring 14 to be described later. The contact surface 12a of the friction disk 12 having elasticity makes line contact to surface contact with the outer peripheral surface of the drive shaft.

The other end of the support guide 7 is connected to the side plate 5a of the bracket.
5b and extends to the position of two guide plates 13 fixedly suspended from the frame 4, and is slidably fitted into a guide rod 15 with springs 14 stretched near both ends as shown in FIG. , the guide rod 15 is slidably supported by the guide plate 13.

Furthermore, a fixing pin 16 is provided protruding near the middle part of the support guide 7.
Spring 1 is inserted between
8 is stretched, and the end surface 7a of the support guide 7 that indirectly supports the friction disk 12 is always in contact with the side plate 5b of the bracket 5 to control its position.

At this time, as the trolley T travels, the cam roller 20 rotatably provided at the tip of the L-shaped arm 19 fixed to the lower surface of the support guide 7 comes into contact with the cam plate 21 provided on the ground side and having an inclination angle θ. The guide 7 moves along the inclined rod 6 in a direction approaching the axis of the drive shaft 3 against the force of the spring 18.

That is, as shown in the fourth figure, the state P where the side surface 7a of the support guide 7 is in contact with the side plate 5b of the bracket is the normal traveling state of the truck T, and the cam roller 20 is in contact with the cam plate 21 while the truck T is traveling. The support guide 7, which is integral with the bearing housing 8 which indirectly supports the friction disc 12 through contact with the rotating shaft 10 integral with the disc body 11 and the bearing 9, resists the spring 18, and the cam plate It moves toward the drive shaft 3 according to the slope angle θ of 21, and completely stops running at the time Q when the center of the friction disk 12 coincides with the axial position of the drive shaft 3.

During the movement distance 1 of the friction disk 12, the friction disk 1
Since the two contact points are displaced, the friction disk 12 is vertically displaced H at the distance l between the normal running position P and the stop position Q.

Therefore, the inclined rod 6 is inclined at an angle β corresponding to the displacement H so that the pressing pressure of the friction disk 12 does not vary due to the displacement H.

That is, the inclination angle β of the above-mentioned inclined rod 6 is tanβ=H/l
It is derived from the relational expression.

Theoretically, the displacement does not occur in a straight line, but since it approximates the displacement in a straight line, it can be sufficiently covered.

Even if it were provided to be theoretically displaceable, the mechanism would only become complicated and would have almost no practical meaning.

The operation will be explained in detail below.

In FIGS. 1 to 4, while the bogie is running on the track 1 via the wheels 2, the support guide 7 that indirectly supports the friction disk 12 by the biasing of the spring 18 comes into contact with the side surface 5b of the bracket 5. Drive normally with the vehicle in contact.

At this time, the line connecting the center of the friction disk 12 and the point of contact of the drive shaft 3 on the friction disk 12 is approximately 44 degrees with respect to the axis of the drive shaft 3.
It is located at an angle displaced by 5 degrees.

During the above-mentioned traveling, the bogie T is attached to the cam plate 21 provided on the ground side.
When the side cam roller 20 makes contact, the support guide 7, which supports the friction disk 12 against the spring 18, is displaced along the inclined rod 6 in accordance with the inclination angle θ of the cam plate 21.

At this time, the speed gradually decreases according to the inclination angle θ of the cam plate 21, and it completely stops when the center of the friction disk 12 coincides with the axis of the drive shaft 3.

Further, the pressure of the friction disk 12 against the outer circumferential surface of the drive shaft 3 is applied by the spring 14 when the bogie is running.

That is, by the spring 14 stretched between the locking pin 22 on the lower surface of the truck T and the guide rod 15, the support guide 7 pivots clockwise around the inclined rod 6, and the friction coffin 12 is attached to the drive shaft 3. Pressed.

At this time, a stopper 23 is provided at the joint or cut portion of the drive shaft 3 to prevent unnecessary rotation of the friction disk 12.

Furthermore, when the friction disk 12 moves to the stop position, an angle β corresponding to the vertical displacement amount H of the contact point of the friction disk 12,
Since the inclined rod 6 is provided in an inclined manner, the above-mentioned pressing pressure always remains at a constant value.

At this time, since the guide rod 15 is provided with the same inclination as the inclined rod 6, it moves parallel to the axis of the drive shaft 3.

As described above, in the present invention, the friction disk can be moved in accordance with the amount of vertical displacement of the contact point of the friction disk while the cart is stopped from the normal running state, so that the pressing pressure due to the vertical displacement can be reduced. There is no risk of fluctuation.

[Brief explanation of the drawing]

FIG. 1 is a schematic front view of the structure of the bogie drive device, FIGS. 2 and 3 are partially enlarged side views and a plan view of the drive section of the bogie drive device, and FIG. 4 is a friction disc sliding section of the present invention. It is an enlarged view of. 1... Orbit, 3... Drive shaft, 6...
... Inclined rod, 10 ... Rotating shaft, 12 ...
...Friction disk, T...Dolly.

Claims (1)

[Claims] 1. A friction disk rotatably supported around a rotating shaft that is slightly inclined with respect to a plane perpendicular to the axis of the drive shaft disposed along the running track of the bogie is mounted on a horizontal plane passing through the axis of the drive shaft. A friction disk sliding device for a bogie drive device, characterized in that it is movable along an inclined rod provided at a slight inclination.