JPS583862B2 - 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. In other words, a friction disk is provided on the lower surface of a disk body formed at the tip of a rotating shaft that is slightly inclined with respect to a plane perpendicular to the axis of the drive shaft at the bottom of the truck, and is pressed against the drive shaft. This invention relates to a bogie drive device that moves a bogie.

The propulsive force and speed of the bogie during the above-mentioned traveling of the bogie change depending on the position of the center point of the friction disk and the contact point of the drive shaft of the friction disk, and at this time, the relationship between the above-mentioned propulsive force and speed shows a correlation with each other. Theoretically, the closer the line connecting the above two positions is to the 90 degree displacement with respect to the axis of the drive shaft, the smaller the propulsive force of the truck becomes, and conversely, the faster the speed becomes.

Further, the closer the displacement is to zero, the greater the propulsive force of the truck becomes, and conversely, the smaller the speed becomes.

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

Therefore, the axial component force R of the drive shaft which is the component force of the above force R
A becomes the driving force and causes the trolley to travel.

That is, Therefore, from ■ and ■ becomes.

Furthermore, as shown in the second figure, when the cam roller r interlocked with the friction disk provided on the truck while the truck is running comes into contact with the cam plate K provided on the ground side, the friction circle moves along the slope of the cam plate K. The plate moves toward the drive axis, and as can be seen from the above relational expression,
Along with this movement, the angle θ becomes smaller and the propulsive force Ra
will increase.

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

Therefore, the truck will travel at the speed Va.

That is, since Va=Vsinθ...■, furthermore than ■ and ■, the cam roller r on the truck is connected to the cam plate K as shown in Figure 4.
When it comes into contact with , the friction disk moves toward the drive axis along the slope of the cam plate K, as described above, and as can be seen from the above relational expression, the angle θ decreases as a result of this movement, and the speed Va
will also gradually decrease.

Incidentally, when the friction disk stop point O coincides with the drive axis, that is, when the angle θ becomes zero degrees, the speed Va becomes zero and the motor stops completely.

From the above, theoretically the displacement angle θ is 90 degrees from 0 degrees.
The propulsive force and speed of the bogie show a correlation with each other by displacing within a range of 0 degrees, but in reality, the displacement angle θ is approximately 45 degrees from 0 degrees due to the output of the drive motor that is the drive source. It is considered preferable.

Therefore, the above displacement angle θ, which is the normal running state of the truck, is approximately 4.
At 5 degrees, the propulsive force is at a minimum and the speed is at a maximum. Therefore, it is important to maximize the transmission capacity of the friction disk contact point P when the displacement angle θ is 45 degrees.

The present invention is based on the above point, and the displacement angle is approximately 4
The present invention provides a bogie drive device having the best transmission capability at 5 degrees, that is, under normal running conditions.

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

In FIGS. 5 and 6, a truck T1 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 T1, and side plates 5a, 5 of the bracket 5 are fixedly suspended from the frame 4.
A rod 6 is fixed perpendicularly to the axis of the drive shaft 3 between the drive shafts 3 and 3b.

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 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 a 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. .

The contact surface 11a of the friction disk 11, which will be described later, is inclined with respect to a plane orthogonal to the axis of the rotating shaft 9 at an angle somewhat gentler than the inclination angle α of the rotating shaft 9, and is formed in a curved shape. A shaft support 1 is attached to a support block 12 protruding from the upper surface of the support guide 7.
3 and a support arm 15 having a rotatable roller 14 at its tip, and a spring 18 biased between an adjustable plate 17 screwed onto a bracket 16 protruding from the front side of the bearing housing 8. The contact surface 11a of the friction disk 11 is configured to press against the outer peripheral surface of the drive shaft 3.

Further, 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 trolley T1, so that the side surface of the support guide 7 that indirectly supports the friction disc 11, The position is always controlled by being in contact with the side plate 5b of the bracket 5.

At this time, as the trolley T1 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 a cam plate K having a predetermined slope provided on the ground side, and the support 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 T1 is in contact with b is the normal running state of the trolley T1,
While the trolley is running, the support guide 7, which indirectly supports the friction disk 11 by contacting the cam roller 23 with the cam plate K, resists the spring 21 and moves according to the inclination angle of the cam plate K. , move 1 to the axis side of the drive shaft 3 and move 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.

Others 25 are adjustment blocks 26 protruding from the support guide 7;
The adjustment bolt screwed on prevents the friction disk 11 from unnecessarily pivoting about the rod 6 at joints, cuts, etc. of the drive shaft 3.

FIG. 7 shows a partial sectional view when the center of the friction disk 11 coincides with the axis of the drive shaft 3, that is, when the running is stopped.
The disc body 10 and the friction disc 11 that are integrally fixed with the rotating shaft 9 are inclined α with respect to the axis of the drive shaft 3, and the contact surface 11a of the friction disc 11 is a friction circle parallel to the axis of the drive shaft 3. Board 1
Passes through the center of 1.

The outer peripheral surface 11c starts from the inner peripheral surface 11b of the contact surface 11a.
A line connecting the two is inclined at least at an angle β smaller than the above-mentioned inclination angle α, and the inner peripheral surface 11b and the outer peripheral surface 11c are continuously formed in a curved shape.

In actual running, the friction disk 11 made of an elastic body is pressed against the friction disk 11, so that almost the entire surface of the contact surface 11a comes into contact with the outer circumferential surface of the drive shaft 3.

FIG. 8 shows a partial sectional view of the contact surface of the friction disk 11 in a state where the center of the friction disk 11 is displaced by approximately 45 degrees with respect to the axis of the drive shaft 3, that is, in a normal running condition. 11d is in line contact with the outer peripheral surface of the drive shaft 3.

That is, when the contact surface 11a of the friction disk 11 in the stopped state shown in FIG. The surface is in line contact with the outer peripheral surface of the drive shaft 3.

Therefore, in the normal running state of the trolley T1, the best line contact is achieved and the maximum transmission capacity is exhibited.

Note that during actual running, the friction disk 11 is pressed against the vehicle, resulting in surface contact.

Hereinafter, the contact surface 11a of the friction disk 11 and the inclination angle β will be described in detail.

In Fig. 9, A is a plan view of the friction disk 11, and C is a view taken along the line C-C in Fig. A, and C is an oblique view taken along B-B in Fig. A.
Now, the outer circumferential radius of the friction disk 11 is R, the inner circumferential radius is r, the distance between the axes of the drive shaft 3 from the center point O of the disk is A, and the drive shaft 3
The inclination angle of the rotating shaft 9 is α with respect to the plane perpendicular to the axis of
If n is a, and the oblique displacement in the thickness direction at this time is b, then the distance from the center point O of the friction disk 11 to the friction disk contact point P, where P・a is divided into n equal parts in the diagram C. This is the distance between the Pth a.

If R-lp=Y, Tona Ru.

At this time Because it is, Expressed in a general formula, if P·b=x, then

That is, the shape of the disk contact surface in the direction of the arrow C-C shown in FIG.

Further, FIG. 10 is a graph showing the contact surface 11a, where the inclination of the line T2 connecting the outer circumferential surface 11b and the inner circumferential surface 11C of the friction disk 11 with respect to the x-axis, λ, is the outer circumferential surface 11 of the friction disk 11.
If the coordinates of C and the inner circumferential surface 11b are O, Yo, Xo, and O, respectively, then the inclination is as follows.

The inclination of T2 with respect to the Y axis is, therefore, the friction disk 1
The inclination angle β of 1 is denoted by .

As described above, when the rotating shaft 9 is installed with an inclination α to the plane perpendicular to the axis of the drive shaft 3, the friction disk 11
The cross section of the friction disk 1 is further inclined at β with respect to the plane orthogonal to the axis of the drive shaft 3, and is formed into a curved shape as shown by .
1 is displaced by approximately 45 degrees, that is, in normal driving conditions, the best transmission force is applied.

Therefore, basically, the center point O of the friction disk 11 is aligned with the axis of the drive shaft 3, that is, the center point O of the friction disk 11 is displaced by about 45 degrees against the inner circumferential surface 11b of the friction disk 11 when the vehicle is stopped. , which corresponds to the entire surface l1d connecting the inner circumference 11b and outer circumference 11c of the friction disk 11 in the normal running state.

Incidentally, in actual running, as described above, the friction disk 11 made of an elastic body is pressed against the friction disc 11 while the vehicle is running, so even when the vehicle is stopped, it touches almost the entire surface 11a.

In addition, when the friction disk 11 is displaced from a running stopped state to a running state, the angle of inclination β is a value that corrects the minute displacement angle caused by the turning, since it turns somewhat clockwise around the rod 6 as a fulcrum. Ru.

As described above, in the present invention, the contact surface of the friction disk is in full contact with the outer circumferential surface of the drive shaft when the truck is in normal running condition, so the transmission force of the truck is the best and the carrying capacity is maximized. can do.

[Brief explanation of the drawing]

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 driving device, and Figure 7 is when the truck is in a stopped state. FIG. 8 is a partial cross-sectional view of the friction disk contact surface in the normal running state of the truck. FIG. 9 is a drawing of the contact surface shape when the friction disk is running and when it is stopped. FIG. 10 is a graph showing the shape of the contact surface of the friction disk when it is running. 1... Orbit, 3... Drive shaft, 9...
...Rotating shaft, 11...Friction disk, T1...
...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, a line passing through the center of the parallel friction disk and connecting the inner circumferential surface of the friction disk contact surface to the outer circumferential surface is inclined at least at an angle less than the above-mentioned inclination angle with respect to the axis of the drive shaft; A bogie drive characterized in that a friction disk is formed in a continuous curved manner between the inner circumferential surface and the outer circumferential surface, and the friction disk is pressed against the outer circumferential surface of the drive shaft so that the bogie travels. Device.