JPS583863B2 - Trolley drive device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a structure in which the outer peripheral surface of a drive shaft disposed along a running track of a bogie is slightly inclined with respect to a plane orthogonal 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 against each other.

The propulsive force and running speed of the cart in the above-mentioned cart drive device are as follows:
It changes depending on the positional relationship between the center point of the friction disk and the contact point of the drive shaft of the friction disk, and the propulsion force and traveling speed are correlated with each other, and theoretically, the line connecting the two positions is the driving force. The closer the displacement is to 90 degrees with respect to the axis of the shaft, the smaller the propulsive force of the cart becomes, and conversely, the faster the speed becomes.

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

That is, in the diagrams of the principle of propulsion shown in FIGS. 1 and 2, when the plane passing through the drive shaft contact point P of the friction disk and the friction disk center point O is displaced by an angle θ with respect to the axis of the drive shaft, When a rotational torque T is applied to the drive shaft, a force R acts between the contact point P and the disk center point O, and a resultant force F of the force R and torque T acts on the drive shaft.

At this time, a force F1 equal to the resultant force F acts on the drive shaft in a direction opposite to the traveling direction of the truck, that is, the direction of arrow A, but since the drive shaft is fixed in position, a force F1 equal to the resultant force F is applied to the truck. acts in the direction of travel of the trolley.

Therefore, the above-mentioned force F acts as a propulsive force to cause the bogie to travel.

That is, Therefore, from ■ and ■ above, becomes.

Further, as shown in the second figure, when the cam roller r interlocked with the friction disk provided on the truck comes into contact with the cam plate K provided on the ground side while the truck is running, the friction disk moves along the slope of the cam plate K. moves toward the drive shaft, and as can be seen from the above relational expression, as the friction disk moves, the displacement angle θ becomes smaller and the propulsive force F increases.

Figures 3 and 4 show principle diagrams of the running speed of the bogie. Under the same conditions as the above-mentioned propulsion force, when the number of revolutions of the drive shaft is N and the diameter of the drive shaft is D, the disk A velocity V acts in a direction perpendicular to the plane passing through the center point O and the contact point P, and a velocity Va, which is a component force of the velocity V, acts in the drive axis direction.

Therefore, the bogie travels in the direction of arrow B at the speed Va.

That is, if the circumferential speed on the outer circumferential surface of the drive shaft is Vb, then V
Since b=π・D・N (π is pi), and from ■ and ■, or Va=π・D・Ntanθ.

Therefore, the traveling speed Va becomes faster as the displacement angle θ becomes larger, and conversely becomes slower as the displacement angle θ becomes smaller.

Furthermore, as shown in the fourth figure, when the cam roller r on the truck comes into contact with the cam plate K, the friction disk moves toward the drive shaft along the slope of the cam plate K, as described above, and from the above relational expression, As can be seen, as the friction disk moves, the displacement angle θ becomes smaller and the traveling speed Va also gradually decreases.

Incidentally, when the center point O of the friction disk completely coincides with the drive axis, that is, when the displacement angle θ becomes 0 degrees, the truck completely stops running.

The present invention provides a traveling bogie drive device based on the above-described principle.

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

FIG. 5 shows a schematic diagram of the trolley drive device, and shows the trolley T.
1 is supported on a track 1 via wheels 2 and 3, and a drive shaft 4 rotated by a drive motor (not shown) is disposed along the track 1.

At this time, the trolley T1 travels on the track guided by the wheels 3.

A frame 5 is fixed to the lower surface of the trolley T1, and side plates 6a and 6b of a bracket 6 are fixedly suspended from the frame 5.
A sliding rod 7 is fixed therebetween at an angle to a plane perpendicular to the axis of the drive shaft 4.

Details of the inclination of the rod 7 are shown in FIG. 6, and the rod 7 is fixed at an angle β relative to a plane orthogonal to the drive shaft 4.

The inclination angle β is approximately 1/2 of the displacement angle θ of the friction disk described above.
is said to be the most preferable.

That is, in FIGS. 8 and 9, FIG. 8 shows an embodiment in which the friction disk is moved in a direction perpendicular to the drive shaft 4 to displace the displacement angle θ, and the friction circle at the displacement angle θ is The plate contact point P becomes smaller as the displacement angle θ becomes smaller.
Move from to P1.

That is, the distance between the drive axis and the friction disk center O is 1, and the distance between the friction disk center O and the contact point P on the drive axis is L1.
, if the distance between the friction disk center O and the contact point P is L2, or L1=L2cosθ.

At this time, the displacement angle θ is, so becomes.

Therefore, when the displacement angle θ is in the range of 0° to θ°, the moving distance Φ of the contact points P to P1 is L2−L2co
sθ, or.

Incidentally, as mentioned above, the above displacement angle θ is theoretically in the range of 0° to
It is said that displacement is possible within a range of 90 degrees, but in reality, the most preferable range is from 0 degrees to about 45 degrees, taking into consideration the efficiency of the drive motor serving as the drive source.

In the friction disk displacement means described above, the contact point P moves by the displacement angle θ, causing wear on the friction disk, or if the contact point P does not move, the friction disk center O, In other words, the cart itself moves Φ.

However, in the present invention, the movement of the contact point P described above is basically zero.

That is, in FIG. 9, when the displacement angle θ is displaced, the disk center O moves O1 using the distance L2 between the friction disk centers O as the radius of curvature from the contact point P.

At this time, it is said that it is most preferable to move the disk along the trajectory of the disk centers O to O1, but since the device would be very complicated, a straight line passing through the disk centers O to O1 that most approximates the above trajectory Configured to be mobile.

Therefore, the sliding rod 7 is slidably tilted counterclockwise at an angle β with the friction disk center O as a fulcrum with respect to a plane in which a straight line passing through the disk centers O to O1 is orthogonal to the drive axis. Fixed.

The inclination angle β is most preferably 1/2 of the displacement angle θ.

That is, if the intersection of the straight line passing through the disk centers O to O1 and the perpendicular to the contact point P is M, and the intersection on the friction disk centers O and O1 is Q, then ΔOPM and ΔOQ1Q are similar to each other.

At this time, since ∠OPM is θ/2, β=θ/2.

Incidentally, in reality, the above-mentioned inclination angle β may be increased or decreased depending on the relationship with the cam plate K.

Furthermore, in FIG. 7, a support guide 8 is fitted to the sliding rod 7 in a slidable and rotatable manner.
A rotating shaft 10 is rotatably supported by a bearing (not shown) in a bearing housing 9 integral with the rotating shaft 10, and a ring-shaped ring is provided on the lower surface of an integrally fixed disk body 11 formed at the lower end of the rotating shaft 10, perpendicular to the axis of the rotating shaft 10. A friction disk 12 is fixedly attached.

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

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 4, and the friction disk 12 is configured to always contact the outer peripheral surface of the drive shaft 4 at one location. .

Note that the above-mentioned slight inclination angle α is basically possible as long as it is equal to or greater than zero degrees, but in reality, the elastic deformation of the friction disk 12,
Considering the deflection and the like, it is sufficient that both ends of the friction disk 120 have an angle that allows rotation without contacting the drive shaft 4.

The contact surface 12a of the friction disk 12 is supported by a support arm 16 which is pivoted 14 on a support block 13 projecting from the upper surface of the support guide 8 and has a rotatable roller 5 at its tip.
A spring 19 biased between an adjustable plate 18 screwed onto a bracket 17 protruding from the front side of the bearing housing 9 causes the contact surface 12a of the friction disk 12 to align with the outer peripheral surface of the drive shaft 4. It is configured so that it comes into contact with the

Further, in FIG. 5, a spring 23 is biased between a pin 21 fixed to a bracket 20 protruding from the side of the bearing housing 9 and a fixing pin 22 protruding from the lower surface of the truck T1, and the friction disc 12 is indirectly Support guide 8
The side surface of the friction disk 12 is always in contact with the side plate 6b of the bracket 6, and the position of the friction disk 12 is controlled.

Note that as the trolley T1 travels, when the rotatable cam roller 25 provided at the tip of the L-shaped arm 24 protruding from the lower surface of the support guide 8 comes into contact with the cam plate K having a predetermined slope installed on the ground side, the support The guide 8 moves along the rod 7 in a direction approaching the axis of the drive shaft 4 against the force of the spring 23.

At this time, in conjunction with the movement of the support guide 8, the roller 15 at the tip of the support arm 16 shown in FIGS. 6 and 7 also moves guided by the guide frame 26 fixed to the lower surface of the truck T1.

That is, the side surface of the support guide 8 is the side plate 6b of the bracket.
The bogie T1 normally runs while in contact with the cam plate K, and as the cam roller 25 comes into contact with the cam plate K, the friction disc 12 resists the spring 23 and rotates against the drive shaft 4.
When the center of the friction disk coincides with the axis of the drive shaft 4 (as shown in FIG. 5), that is, at the position shown by the chain line, the vehicle completely stops running.

In addition, an adjustment bolt 28 is screwed onto a bracket 27 protruding from the side of the support guide 8 in FIGS. 6 and 7.
This prevents the friction disk 12 from unnecessary turning around the rod 7 at joints, cuts, etc. of the drive shaft 3 while the bogie is running.

The operation will be explained in detail below.

In FIGS. 5 to 7, a truck T1 is supported by wheels 2 and 3 and travels on a running track 1.

At this time, the friction disk 12 is biased by the spring 23,
It is in contact with the outer circumferential surface of the drive shaft 4 at a position farthest away from the axis of the drive shaft 4 disposed along the traveling track 1.

That is, the above-mentioned state is a normal running state of the truck T1, and the drive shaft 4 is driven and stopped by a drive motor (not shown), and as the drive shaft 4 is driven and stopped, the truck T1 runs and stops.

Furthermore, in the normal running state, the cam roller 25 that is interlocked with the friction disk 12 comes into contact with the cam plate K installed on the ground side, so that the friction disk 12 resists the spring 23 and moves toward the axis of the drive shaft 4. Move to.

At this time, the friction disk 12 moves along the sliding rod 7 that is inclined β with respect to the plane perpendicular to the axis of the drive shaft 4, so the contact point of the friction disk 12 hardly changes its position and the When the contact point in the state and the center of the friction disk are aligned on the axis of the drive shaft, that is, the contact point in the stopped state, the position does not change at all.

Therefore, since the cam roller 25 of the truck T1 comes into contact with the cam plate K, the truck T1 will not travel beyond the control distance and can be reliably stopped at the set position.

At this time, since the drive shaft 4 is in the driving state, by removing the cam plate K from the cam roller 25, the friction disc 12 is returned to its original position by the spring 23, that is, to the normal running state, and the trolley T1 runs. become.

As described above, in the present invention, when the friction disk of the trolley T1 is brought into alignment with the axis of the drive shaft from a displaced state with respect to the axis of the drive shaft, it is possible to Since the friction disk is moved along a sliding rod inclined counterclockwise with the center of the friction disk as a fulcrum, the contact point of the friction disk hardly changes in position, and therefore the braking of the truck is improved. The distance is reliable, and wear of the friction disk can be further reduced.

[Brief explanation of the drawing]

Figures 1 to 4 are explanatory diagrams showing the running principle of the truck drive device, Figure 5 is a schematic diagram of the truck drive device, Figure 6 is a plan view of the same, and Figure 7 is a view taken along the line C-C in Figure 6. Figures 8 and 9 are diagrams showing means for moving the friction disk. 1... Orbit, 4... Drive shaft, 7...
...Sliding rod, 10...Rotating shaft, 12...
・・・Friction disk, T1 ・・・Dolly.

Claims (1)

[Claims] 1. A drive shaft is arranged along the running track of the bogie, and a rotating shaft slightly inclined with respect to a plane perpendicular to the axis of the drive shaft is rotatably supported on the bogie, and is provided at the tip of the rotating shaft. The friction disk is configured to move along a sliding rod tilted counterclockwise with the center of the friction disk as a fulcrum, with respect to a plane perpendicular to the axis of the drive shaft. A trolley drive device.