JPS6268288A - Striking generator - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention is applicable to rock and concrete impact crushing equipment 1, -41
This is a book about percussion generators used in pressure hammers, press machines, etc.

Prior Art 7: The applicant previously proposed an impact generating device manufactured by Japanese Patent Application No. 60-28391.

A tubular spring used in the impact generating device of -2, 1, and 1 is formed of a plurality of arcuate elements as shown in Figure 117.

Problems to be Solved by the Invention In order to form the structure of the tubular spring actuator 1 as described above, for example, a flat raw pipe can be bent using a bending machine, but it is not a circular arc! ! If there are a plurality of elements, processing is labor-intensive, and it is also difficult to ensure bending accuracy.

The present invention has been made in view of the above-mentioned circumstances, and its purpose is to form a tube spring actuator with one circular arc element, facilitate its processing, and ensure processing accuracy.

Means and Function for Solving the Problems The present invention provides a movable piston 3 facing the chisel 4 on the stationary side, and a
The tube spring actuator 10 is provided with a tube spring actuator formed of two circular arc elements, and is configured to supply and discharge pressure oil to the tube spring actuator 10. By supplying pressure oil to the tube spring actuator IO, elastic energy is stored and discharged. By doing so, the elastic energy is converted into energy for striking the piston 3 and striking the chisel 4.

Embodiments Hereinafter, embodiments of the present invention will be described with reference to FIGS. 1 to 16.

1 in the drawing is a mounting bracket, and a cylinder 2 is fixed to the mounting bracket 1. The lower part of the piston 3 is movably inserted into the upper part of the cylinder 2, and the upper part of a chisel 4 is movably inserted into the lower part of the cylinder 2. A bottle ε is inserted into the hole 7 formed by the groove 6 of the cylinder 2.A mounting seat 9 is formed on the outer circumference of the cylinder 2. Bracket part 11
is swingably mounted with a pin 12, and a bracket portion 11' at the upper end of the tube spring actuator 10 is swingably mounted on the top of the piston 3 with a pin 12'.

The tubular spring actuator 10 is composed of one arc element, and has a flat cross-sectional shape.

Oil is supplied to the lower end of the tube spring actuator 10 9i1
3 is a provision.

If the pressure acting on the tube spring actuator (0 is P and the absorbed oil volume is V, then the energy stored in this system is E
p is given by Ep PV. On the other hand, this energy is converted into the elastic energy Kk=k of the tube spring actuator δ2. Here, K is the spring constant of the entire system of the tubular spring actuator 10, and δ is the total amount of deflection.

Considering the configuration of multiple arcuate elements as in the past, the energy storage amount of one element is expressed as E g −-Rδ/2 (R: spring constant of one element, δ' = deflection of one element) In order to store a predetermined amount of energy Et- in the entire system by hydraulic pressure, it is sufficient to connect a plurality of these elements.

However, even with one element, a predetermined amount of energy E can be stored if the slit width B, arc radius R1 and arc angle θ are selected to be large as shown in FIGS. 3 and 6.

When a switching valve (not shown) connected to the supply pipe 13 is operated to connect the inside of the tube spring actuator 10 to the low pressure side, the oil inside the tube spring actuator 10 is removed and the spring of the tube spring actuator 10 is removed. The force causes the piston 3 to descend and strike the chisel 4.

When the chisel 4 is released from the object 14 to be crushed, a compressive force is applied to the tube spring actuator 10 so that the piston 3 rests on the contact surface 15 of the cylinder 2.

Furthermore, the switching valve is operated to supply pressure oil into the tube spring actuator 10, thereby extending the tube spring actuator 10 and raising the piston 3.

The tubular spring actuator 10 may have the cross-sectional shape shown in Figure @7.

The tube main body 10' of the tube spring actuator 10 has a thickness t' in the direction of the minor axis that is smaller than the thickness p#t of the major axis end portion, and has a width across flats shape.

As shown in FIG. 9, a tube body 10' of a tube spring actuator 10 having a flat cross section with equal wall thickness will be considered.

When hydraulic pressure P acts within the tube body 10', the tube body 10' swells by a deflection δr, and the tip of the tube spring actuator 10 is displaced by J.

At this time, δr! are in a proportional relationship. During this behavior, the maximum stress in the cross section of the tube body 10' of the tube spring actuator 10 occurs inside the end of the major axis.

This stress is a tensile stress δαt.

The next largest location is the compressive stress σbc on the inner side in the minor axis direction, and the stress load on the minor axis y is always smaller than that on the major axis X. That is, as shown in FIG. 7, it is possible to reduce the wall thickness in the y direction of the minor axis.

By reducing this wall thickness, the deflection δr of the tube body 10'
can be increased, and the deflection S can also be increased.

Alternatively, the tube bodies 10' may be stacked to form a multi-chamber structure (see FIG. 10).

Conventionally, the structure of the tube spring actuator and the pressure introduction part applied to the impact device is as shown in FIG.
Either brazing as shown in Figure 9 or welding as shown in Figure 20.

However, due to the repetitive load of the impact force generated during impact, the mounting portions of the tube spring actuator's control α and pressure introduction portion were damaged, causing oil leakage and a decline in the function of the tube spring actuator.

In order to solve this problem, joining means as shown in FIGS. 11 to 16 have been taken.

That is, by inserting the management 13 of the tubular spring actuator 10 into the split 7 flange 16.16' and fixing it with the bolt 17, the management 1B and the sugerite 7 mount/ji 16.
16'.

The split flange 16,16' and the end face of the management 18 of the tube spring actuator 10 are then in the same plane.

The bracket 19 has a passage 20 for introducing pressure into the tube spring actuator 1°, a pin hole 21 for fixing to the cylinder 2, and an oval O-ring 22.

The O-ring 23 was fitted onto the O-ring $22 of this bracket 19, and the split 7 lunge 16 was fixed to the bracket 19 and the management 18. +6' butt together and fix both with bolt 23.

Therefore, the oil is kept in a sealed state by the O-ring 23, and if the torque with 23'OM is managed so that a tensile force greater than the load is applied, the result will be pol) 17.2.
3' does not come loose.

That is, since oil leakage does not occur, there is no concern that the impact performance of the tubular spring actuator 10 will decrease.

Effects of the Invention As detailed above, the impact generating device t according to the present invention has the following effects:
A piston 3 is movably provided on the stationary side facing the chisel 4, and a tube spring actuator 1o formed of one circular arc element is provided between the piston 3 and the stationary side, and pressure oil is supplied to the tube spring actuator 10. It is characterized by being configured to supply and discharge.

Therefore, since the tube spring actuator 10 is formed of one arcuate element, it is easier to process a plurality of arcuate elements than in the case of a conventional harpoon tube spring, and it is also easier to ensure processing accuracy.

[Brief explanation of drawings]

Fig. 1 is a front view of one embodiment of the present invention, Fig. 2 is a side view of the same, Fig. 3 is a longitudinal sectional view of the same mourning part, and Fig. 4 is Fig. 3 - tv.
A sectional view taken along the line, Figure 5 is a view taken from the arrow direction in Figure 3 ■,
Figure 6 is a sectional view taken along the line ■-■ in Figure 3, Figure 7 is an explanatory diagram of the cross-sectional shape of the tube spring actuator, Figure 6 is a side view of the same, and Figure 9 is taken along the line A-A in Figure 8. Figure 10 is a cross-sectional view of a pipe spring actuator with a multi-N Sakaki construction oil chamber.
The figure is a longitudinal sectional view of another embodiment of the present invention, and FIG.
13 is a sectional view taken along the line C-C in FIG. 12, FIG. 14 is a sectional view taken along the line C-C in FIG. 12, and FIG. 15 is a sectional view taken along the line C-C in FIG. 12. 16 is a sectional view taken along line C, FIG. 16 is a view taken from the direction of arrow F in FIG. 13, FIG. 17 is an explanatory diagram of the configuration of a conventional impact generating device, and FIGS. It is an explanatory view of the attachment structure of management and a pressure introduction part. 3 is a piston, 4 is a chisel, and 1o is a tube spring actuator.

Claims (1)

[Claims] A piston 3 is provided on the fixed side so as to be movable with respect to the chisel 4, and a tube spring actuator 10 formed of one circular arc element is provided between the piston 3 and the fixed side, and pressure oil is supplied to the tube spring actuator 10. A blow generating device characterized in that it is configured to supply and discharge.