JPS5835718Y2 - fluid pressure hammer - Google Patents

Description

[Detailed description of the invention] The present invention relates to a hydraulic hammer used in construction machinery or pile driving machines, etc., to eliminate pollution such as exhaust gas and noise caused by explosions, improve horsepower efficiency, and facilitate handling control.
This was done with the aim of simplifying the structure and reducing weight.

Conventional drop hammers are mainly diesel hammers and pneumatic hammers, but these are
There are many problems with pollution such as noise, and there are restrictions on where it can be used.

Although there are few examples, as shown in FIG. 1, a hydraulic hammer is equipped with a hydraulic cylinder C attached to the upper part of a hammer outer cylinder body having a ram a inside, and a rod d of the hydraulic cylinder C and the ram a. There is a system in which the ram a is connected by a joint e, and the hydraulic cylinder C is operated by pressure oil sent from a hydraulic system g via a pipe f to lift or drop the ram a.

However, in such a hammer, the speed at which the ram falls is very fast, and the flow speed of the oil is also fast, so the greatest requirement is to minimize the pressure loss caused by this, but in the conventional method, the piping f is There is a large pressure loss due to the oil flowing through it, and in order to bring something that was moving at high speed to a sudden stop, a very large impact hole acts on the joint e, easily causing the joint e to malfunction. It became necessary to provide a shock absorber, etc., which resulted in the problem of making the device larger and more complicated.

Furthermore, as another example of a hydraulic hammer, as shown in Fig. 2,
A rod with a piston i in a hydraulic cylinder h is connected to a ram j
A chamber communication hole k is provided in the ram j, and a valve l is installed.
There is a system in which the ram j is lifted or dropped by switching the valve l against a spring p using a back pressure O applied from a hydraulic device m via a back pressure loading device n.

This method can solve the problems of the conventional method, but since it does not operate unless back pressure is applied, this extra back pressure not only reduces horsepower efficiency and requires a large amount of power, but also Since the loss turns into heat, a large roller is required to prevent the temperature from rising, which means that the equipment becomes larger and larger.Furthermore, since the valve l is built into the ram j, it has been my experience that failures can occur. It has problems such as being easy to repair and difficult to repair.

The present invention can solve the problems of the prior art described above, and includes a cylinder ram, a piston in the middle part so as to form an upper chamber and a lower chamber in the cylinder ram, and a hollow part inside. a rod that is movable up and down relative to a cylinder ram that is equipped with a guide hole that can connect the upper chamber and the lower chamber; A control piston having a switching piston, and having an oil passage communicating with each of the upper chamber and the lower chamber separately when the guide hole is shut off, and forming a lower chamber between the inner wall of the rod at the upper end and the control piston. a control rod which is provided so as to be movable up and down, and an upper end of the rod is formed to communicate with each of the oil passages and each of the control upper and lower chambers, and to connect piping from a fluid pressure device, respectively. The present invention relates to a fluid pressure hammer characterized in that it is provided with a piping hole.

Embodiments of the present invention will be described below with reference to the drawings.

3 and 4 show an example of the present invention, in which a piston 4 is provided in the middle part of the cylinder ram 1 so as to form an upper chamber 2 and a lower chamber 3 inside the cylinder ram 1. and a rod 5 having a length that projects downward.

A hollow part 6 is formed inside the rod 5 from the screw 1 flange 4 position to the upper end, and guide holes 7 and 8 are provided above and below the piston 4 to guide the upper chamber 2 and lower chamber 3. communication via the holes 7, 8 and the hollow part 6;
Furthermore, a stepped hollow part 9 is formed above the hollow part 6.

Inside the hollow part 6 of the rod 5, the guide (L7,
A control rod 14 is provided, which has a switching piston 10 for switching 8 and a control piston 13 that fits into the stepped hollow part 9 to form an upper control chamber 11 and a lower control chamber 12.

Furthermore, a control rod 14 between a suitable lower position of the control piston 13 and the switching piston 10
An oil passage 15 is formed on the outer periphery of the control rod 14, and a return oil passage 16 is formed at the center of the control rod 14, passing vertically through the rod 14.

Furthermore, on the upper outer periphery of the control rod 14,
Piping holes 17 and 18 communicating with each of the upper control chamber 11 and lower chamber 12 are provided separately, and the piping holes 17
．． 18 to the fluid pressure device 37 via piping 19.20.
A piping hole 22 is provided which is connected to the valve 21 of the fluid pressure device 37 through the piping 23, and is connected to the valve 24 of the fluid pressure device 37 through the upper hollow portion 6'. A piping hole 25 is provided which communicates with the return oil passage 16, and the piping hole 25 communicates with a tank 27 via a piping 26.

In the figure, 28 is a pump, 29 is a safety valve, 30 is a lifting fitting provided at the upper end of the rod 5, 31 is a piston ring, 32 is a seal, and 32' is a seal holder.

As shown in FIG. 3, the hydraulic hammer with the above configuration is supported so as to be able to move up and down along a leader 34 via a guide jaw 33, and is supported via a pile cap 36 placed on the upper end of a pile 35. A pipe 35 is to be driven into it.

The fluid pressure device 37 may be a hydraulic device, and the pipes 19, 2
0,23,26 are connected to the rod 5 by a piping hose 38 that brings together the pipes.

FIG. 4 shows that the control rod 14 moves upward and the upper chamber 2 and lower chamber 3 are connected through the guide holes 7 and 8 and the hollow part 6, and the cylinder ram 1 falls at a high speed due to its own weight. It shows that the lower end is about to collide with the pile cap 36.

A case will be described in which, after the cylinder ram 1 has finished falling in this way, the cylinder ram 1 is lifted again to perform the drop driving.

First, the valve 21 is switched from the state shown in FIG. 4 to the state shown in FIG.

Then, the pressure oil from the pump 28 is guided to the upper control chamber 11 via the valve 21 piping 19 and the piping hole 17, and the oil in the lower control chamber 12 is introduced to the piping hole 18, the piping 23, and the valve 2.
1 to the tank 27, the control rod 14 moves downward, and the switching piston 1 at the lower end
0 comes between the guide holes 7 and 8 to cut off their communication, and at the same time, the upper chamber 2 and the oil passage 15 come to communicate via the guide hole 7.

Subsequently, the valve 24 is switched from the state shown in FIG. 4 to the state shown in FIG.

Then, pressure oil from the pump 28 is supplied to the upper chamber 2 via the valve 24, piping 23, piping hole 22, oil passage 15, and guide hole 7, and the upper chamber 2 is pushed open, causing the cylinder ram 1 to rise. do.

At the same time, the oil in the lower chamber 3 flows through the guide hole 8, the hollow part 6,
Return oil passage 16, upper hollow part 6', piping hole 25 and piping 2
6 and returned to the tank 27.

Further, the reaction force when lifting the cylinder ram 1 is transmitted to the pile cap 36 via the rod 5.

When the cylinder ram 1 rises to a predetermined height, the valve 24 is switched from FIG. 5 to FIG. 4.

Then, the flow paths of the upper chamber 2, oil passage 15, and piping 23 are closed, and therefore the cylinder ram 1 is held lifted upward.

Subsequently, the valve 21 is switched from FIG. 5 to FIG. 4.

Then, the pressure oil from the pump 28 is introduced into the lower control chamber 12 and the oil in the upper control chamber 11 is returned to the tank 27, so that the control rod 14 immediately rises, and due to the rise of the switching piston 10 in the control rod 14. , the guide holes 7 and 8 communicate with each other, and the cylinder ram 1 falls at a high speed due to its own weight, and the pile cap 3
By colliding with 6, the pile 35 is driven.

Note that the upper chamber 2 and lower chamber 3 are drained with just the right amount of oil.
The mutual areas are determined to allow for suction, and the guide holes 7, 8, etc. that communicate them are all fixed holes, so the cross section of the flow can be maximized and the distance can be shortened. Therefore, there is less pressure loss and there is less impact on oil volume due to sudden stops.

In addition, since back pressure is not used to operate the valve, excess back pressure does not deteriorate horsepower efficiency, and only causes pressure loss in the piping. Therefore, by appropriately selecting the piping diameter, efficiency can be increased can be obtained.

Furthermore, since each chamber formed between the control rod 14 and the hollow portion 6 is designed to be balanced in terms of oil quantity, it is possible to operate efficiently and without difficulty.

In addition, since the cylinder ram 1 has a one-piece structure, it is unlikely to break down, and since the oil is sent to the upper chamber 2, lower chamber 3, etc. through the rod 5, the piping etc. are connected to the operation of the cylinder ram 1. There is no such thing as getting in the way.

Further, in the above operation, the cylinder ram 1 can be stopped intermediately by operating the valve 24 as shown in FIG. 4 and the valve 21 as shown in FIG. 5.

FIG. 6 shows another embodiment of the fluid pressure device 37, which consists of two pumps 39, 40, two safety valves 41, 42 and one valve 43, similar to the previous embodiment. The parts with the same reference numerals in the drawings indicate the same action parts.

Furthermore, the switching of each of the sections 21, 24, 43 may be performed electrically using a solenoid, or may be performed by other means.

It should be noted that the present invention is not limited to the above-mentioned embodiments, but can be applied in various ways other than driving pipes, and the shapes of the constituent parts may be changed in various ways without departing from the gist of the present invention. Of course, various changes may be made within the scope.

According to the fluid pressure hammer of the present invention described above, the following various excellent effects can be exhibited.

(i) The distance traveled by oil when the cylinder drum falls can be shortened to reduce pressure loss due to flow velocity;
Smooth operation can be achieved.

(ii) The oil flow phenomenon that occurs when the cylinder drum suddenly stops has a small effect because the distance through which the oil flows is short, and machine damage can be prevented.

(iii) By making the cylinder ram an integral structure and having no joints, etc., it has extremely high strength, has a simple structure, and can significantly reduce weight.

(iv) Since the oil discharged from one pressure oil chamber when the cylinder ram falls is guided to the other pressure oil chamber in just the right amount, there is no need to provide a separate replenishment device.

(v) Since no extra back pressure is applied, horsepower efficiency is high and hydraulic power generation devices such as coolers for motive power and cooling can be downsized.

(vi) By controlling the operation of the cylinder ram and the operation of the control rod by separate valves, the cylinder ram can be stopped mid-rise;
Operational safety is increased and equipment inspection becomes easier.

[Brief explanation of the drawing]

Figures 1 and 2 are explanatory diagrams showing a conventional hydraulic hammer, respectively. Figure 3 is a partial explanatory diagram of a pile driver equipped with the hammer of the present invention. Figure 4 is a cutaway diagram showing an embodiment of the present invention. A side view, FIG. 5 is a cutaway side view showing its operation, and FIG. 6 is a circuit diagram showing another embodiment of the fluid pressure device. 1 is a cylinder ram, 2 is an upper chamber, 3 is a lower chamber, 4 is a piston, 5 is a rod, 6 is a hollow part, 7 and 8 are guide holes, 9 is a stepped hollow part, 10 is a switching piston, 11 is a control Upper chamber, 12 is a control lower chamber, 13 is a control piston, 14 is a control rod, 15 is an oil passage, 16 is a return oil passage, 17, 18, 22.25 are piping holes, 21, 2
4.43 indicates a valve, and 28 and 39.40 indicate a pump.

Claims (1)

[Scope of utility model registration request] A cylinder ram, a piston in the middle part so as to form an upper chamber and a lower chamber in the cylinder ram, a hollow part inside, and a guide hole that can communicate the upper chamber and the lower chamber. It has a rod that can move up and down relative to the cylinder ram, and a switching piston that connects and shuts off communication with the guide hole by moving up and down in the hollow part of the rod. A control rod that is movable up and down and is provided with a control piston that has oil passages communicating with each other and that forms a lower chamber between the inner wall of the rod at the upper end, and an upper end of the rod. A fluid pressure hammer, characterized in that piping holes are provided which are formed to communicate with each of the oil passages and the control and lower chambers, and to connect piping from the fluid pressure device, respectively.