JPS5858483B2 - Tamba striking force adjustment device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a tamper that continuously compacts the ground by rotating a prime mover.

Sites where compaction work is carried out using this type of tamper have different soil types, and in recent years there have been a wide variety of asphalt mixtures, so it is necessary to obtain a degree of compaction that is appropriate for the soil type or asphalt mixture. will need to adjust Tampa's hitting power.

However, in the conventional tamper of this type, a wire is connected to a speed regulating lever fixed to the operating bundle, the tip of which is connected to the governor shaft of the engine's carburetor, and the engine speed can be varied by changing the position of the governor's butterfly valve. However, changing the position of this butterfly valve requires extremely delicate means, and must be based on the results of rotation measurement using a tachometer.

Since it is not possible to change the position of the butterfly valve during operation of a machine such as a tamper that is subjected to severe shocks and vibrations, the position of the butterfly valve is set at a constant rotation speed position when it is attached to the engine body.

Therefore, the engine speed is limited to the range from no-load to the speed at which the butterfly valve is set, and the engine speed cannot be changed beyond that, so there is a certain limit to the striking force of this machine. However, there was a drawback that the desired striking force could not be obtained.

SUMMARY OF THE INVENTION An object of the present invention is to eliminate the above-mentioned drawbacks and to provide a bumper that allows the impact force of the machine to be adjusted by a simple operation without changing the rotational speed of the prime mover.

The present invention will be explained based on the illustrated embodiment. A prime mover 1 is fixed to a side surface of a head casing 14 and drives a pinion shaft T via a centrifugal clutch 4 and a centrifugal clutch drum 5.

A pinion gear 6 of the pinion shaft 1 is meshed with a crank gear 8 fixed to a crankshaft 12.

A crank head 9 having a plurality of holes at eccentric positions of the crank gear 8 has bolts 1o, io', io'<1
0'', the crank head 9 is movably mounted.
A crank pin 11 is provided at an eccentric position.

Then, by rotating the crank head 9 with respect to the crank gear 8, moving it to an arbitrary position, and attaching it,
The distance A between the axial center P of the crank gear shaft 12 and the axial center Q of the crank pin 11 can be changed as appropriate by a combination of two eccentricities.

For example, when the crank pin 11 is located at 11', the distance between the axes P and Q is B, when it is located at 11", the distance is c, and when it is located at l l ///, the distance is B. Let it be D.

The crank pin 11 is connected via a crank rod 13 to a connecting rod 18 having an intermediate spring receiver 23 at its lower end, and the crank mechanism causes the connecting rod 18 and the intermediate spring receiver 23 to reciprocate in the vertical direction.

%, the crank rod 13 has an annular shape, and the pinion gear shaft 7 is located within this annular shape.

The intermediate connecting portion 22 is slidably provided on the connecting rod 18 having a diameter of 180 mm, and its upper arms are fixed to the upper end of the guide shaft 21.21, and the guide @21.21 is slidably provided on the middle casing JT. , its lower end is fixed to the bottom casing 20 via the continuation plate 26 by bolts 33.

An upper coil spring 24 is disposed between the intermediate spring receiver 23 and the intermediate connecting portion 220, a lower coil spring 25 is disposed between the intermediate spring receiver 23 and the bottom casing 20, and a striking plate 32 is disposed on the continuation plate 26. It is installed by

In addition, in the figure, 2 is the output shaft of engine 1, 3 is the bellows, 1
5 is a head casing 7 lange, and 16 is a head casing cover.

The present invention is constructed as described above, and the rotation of the output shaft 2 of the prime mover 1 is transmitted to the pinion shaft 7 via the centrifugal clutch 4 and the centrifugal clutch drum 5, and is further transmitted to the pinion gear 6
is transmitted to the crank gear 8 through the rotation of the crank pin 11 of the flank head 9.
It can be changed to 3 up or down luck @.

The connecting rod 18 moves up and down as the crank rod 13 moves up and down, and the intermediate spring receiver 23 alternately compresses and repulses the upper and lower coil springs 24 and 25 provided above and below, thereby causing the striking plate 32 to move up and down.

That is, when the intermediate spring receiver 23 is moved upward by the crank rod 13 via the connecting rod 18, the upper coil spring 24 is compressed and the upper end of the coil spring 24 pushes up the intermediate connecting portion 22, and the striking plate 32 is guided. Axis 21.2
Rising through 1.

As the striking plate 32 rises, the bottom casing 20 or the lower end of the lower coil spring 25 is pushed up, so that the intermediate spring receiver 23 receives a repulsive force from below due to the elasticity of the lower coil spring 25.

When the middle spring holder 23 is lowered, the lower coil spring 2
5 is compressed and passes through the bottom casing 20 to the striking plate 3
2 is lowered, but at this time, the repulsive force of the upper coil spring 24 acts on the intermediate spring receiver 23 via the guide shaft 2L21 as the intermediate connecting portion 22 moves downward.

Such vertical movement of the intermediate spring receiver 23 applies compression and repulsion to both coil springs 24 and 25.

The striking plate 32, which receives the inertia of these elements and the load of the entire machine, moves up and down and strikes the ground.

When it is desired to adjust the striking force of the striking plate 32, the cover 16 is removed and the position of the crank head 9 attached to the crank gear 8 with bolts 10 is rotated to change the position of the crank pin 11.

For example, by changing from 11' to 11〃, the distance B between the axis P of the crank gear shaft 12 and the axis Q of the crank pin 11 is changed to C (C<B).

If the distance between the axial center P of the crank gear shaft 12 and the axial center Q of the crank pin 11 is reduced in this way, the vertical movement of the crank rod 13 will be reduced, so the intermediate spring bearing 2
3, the compression and repulsion forces of the upper and lower coil springs 24, 25 are reduced, and therefore the striking force of the striking plate 32 can be reduced.

It is also possible to increase the striking force by performing the opposite operation.

As described above, this invention meshes the crank gear 8 with the pinion gear 6 of the pinion gear shaft 7 that is transmitted from the prime mover 1, and moves the crank head 9 with the crank pin 11 at an eccentric position to the eccentric position of the crank gear 8. Since the crank pin 11 is freely attached and the crank rod 13 is connected to the crank pin 11, the position of the crank gear shaft 1 depends on the attachment position of the crank head 9 with respect to the crank gear 8.
The distance between the axial center P of 2 and the axial center Q of the crank pin 11 is A and B.
, C, and D. Therefore, by adjusting the stroke of the connecting rod 18 that moves up and down via the crank rod 13, the coil springs 24 disposed above and below the intermediate spring receiver 23 The compression and repulsion forces of 25 are adjusted and the impact plate 32 is affected by the compression and repulsion forces.
At the same time, it is possible to adjust the height of expansion and contraction when the entire machine jumps and then immediately falls, making it possible to easily adjust the required impact force according to the soil quality or asphalt mixture at the site where compaction work is performed. This is possible.

[Brief explanation of drawings]

The drawings show an embodiment of the present invention; FIG. 1 is a longitudinal side view, FIG. 2 is a longitudinal front view, and FIGS. 3 and 4 show how the crank gear and crank head are attached. FIG. 3 is a side view, and FIG. 4 is a front view. 1... Internal combustion engine, 2... Internal combustion engine shaft, 4.
... Centrifugal clutch, 5 ... Centrifugal clutch drum, 6 ... Pinion gear 7 ...
Pinion shaft, 8... Crank gear 9...
... Crank head, 10 ... Bolt, 11
......Crank pin, 12...Crank gear shaft, 13...Crank gear, 18...
... Connecting pin, 19... Connecting pin.

Claims (1)

[Claims] 1. A crank gear 8 is meshed with the pinion gear 6 of the pinion gear shaft 1 transmitted from the internal combustion engine 1, and a crank head 9 with a crank pin 11 provided at an eccentric position is movably attached to the eccentric position of the crank gear 8 by bolts 10. , a tamper impact force adjusting device in which a crank rod 13 is loosely fitted to the crank pin 11.