JPH10309678A - Hydraulic hammer - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve working environment and to reduce exhaust sound by furnishing a reciprocating pilot pressure supply mechanism to supply hydraulic oil to a reciprocating pilot pressure chamber when a stroking piston reaches reciprocating ends. SOLUTION: An inward moving pilot pressure supply route 20 constituting an inward moving pilot supply mechanism by being communicated to a cylinder chamber 2 is connected to an inward moving pilot pressure chamber 17. The inward moving pilot pressure supply route 20 supplies hydraulic oil in the cylinder chamber 2 to the inward moving pilot pressure chamber 17 when a stroking piston 3 reaches an outward moving end. An outward moving pilot pressure supply route 21 communicated to a first pressure oil supply route 10a is connected to an outward moving pilot pressure chamber 18. A spool valve 22 to open and close the route 21 is set in the outward moving pilot pressure supply route 21. The spool valve 22 opens when the stroking piston 3 reaches an inward moving end against energizing force of a spring 23 and supplies hydraulic oil in the first hydraulic oil supply route 10a to the outward moving pilot pressure chamber 18.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic hammer, which is a type of power tool used in a manufacturing factory or the like.

[0002]

2. Description of the Related Art It has been proposed and practiced to assemble positioning pins and nails by using a pneumatic hammer (air hammer) using pneumatic pressure as a driving force. The technology related to the air hammer is disclosed in Japanese Patent Application Laid-Open No. Hei 7-266257. This publication discloses a hammer body having an air cylinder chamber therein, a snap mounted in a snap mounting hole of the hammer body, a piston housed in the air cylinder chamber, and a source for supplying compressed air to the air cylinder chamber. An air hammer provided with the air supply means is described.

[0003]

In the above-described air hammer, the compressed air after driving the piston is discharged to the outside. At this time, there is a problem in that the discharge sound is loud and gives an uncomfortable feeling to the operator. Also, the compressed air that drives the piston contains a small amount of oil to prevent rust and lubricate the air hammer, so when discharging the compressed air, the oil in the compressed air becomes an oil mist and is discharged to the outside. And the working environment is degraded.

Accordingly, it is an object of the present invention to provide a hydraulic hammer that can improve the working environment.

[0005]

According to a first aspect of the present invention, there is provided a hammer body for transmitting a striking force to a member to be struck, a cylinder chamber formed at a rear end of the hammer body, and a cylinder chamber which moves into the cylinder chamber. It is housed freely and separates the cylinder chamber into a backward pressure chamber and a forward pressure chamber, and moves from the backward end to the forward end inside the cylinder chamber to generate a hitting output, and the hammer body Striking piston for transmitting the striking force to the hydraulic pressure source, a hydraulic oil supply path for supplying hydraulic oil from the hydraulic pressure source to the return pressure chamber or the forward pressure chamber, and a return position and pressure for supplying hydraulic oil to the return pressure chamber. A directional switching valve that can be switched to a forward position where oil is supplied to the forward pressure chamber, and that performs a switching operation by receiving pilot pressure, and a directional switching valve that moves backward and forward when pressure oil is supplied The return / forward pilot pressure chamber that switches to the position and the striking piston
When it reaches the rearward end, it is provided with a backward / forward pilot pressure supply mechanism for supplying pressure oil to the backward / forward pilot pressure chamber.

With this configuration, when the impact piston is at the backward movement end, pressure oil is supplied to the backward movement pilot pressure chamber by the backward movement movement pilot pressure supply mechanism, and the direction switching valve is set to the forward movement position. In this state, the pressure oil from the hydraulic source is supplied to the forward movement pressure chamber, and the striking piston is moved in the forward movement direction, collides with the hammer body, and transmits the striking force to the hammer body. At the same time, when the striking piston has reached the forward end, pressure oil is supplied to the backward pilot pressure chamber by the backward pilot pressure supply mechanism, and the direction switching valve is switched to the backward position. In this state, the pressure oil from the hydraulic pressure source is supplied to the return pressure chamber, and the striking piston is moved to the return position to reach the return end. By repeating the above operation, a pulsed striking force is output from the hammer body.

According to a second aspect of the present invention, in the hydraulic hammer according to the first aspect, the directional control valve is constituted by a spool valve and is disposed substantially parallel to the cylinder chamber. With this configuration, the size of the hydraulic hammer is reduced.

[0008]

An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 shows a schematic configuration diagram of a hydraulic hammer. In the figure, reference numeral 1 denotes a hydraulic hammer. The hydraulic hammer 1 has a cylinder chamber 2 at a substantially central portion thereof. A striking piston 3 for generating a striking force is movably accommodated in the cylinder chamber 2. In the cylinder chamber 2, a rebound pressure chamber 2 a for moving the impact piston 3 in the direction of arrow R (reverse direction) in the figure by the impact piston 3 and the impact piston 3 in the direction of arrow F (forward) (Moving direction) in a forward movement pressure chamber 2b. In other words, the return pressure chamber 2a is formed between the hammer body 5 and the striking piston 3 which will be described later, and the forward movement pressure chamber 2b is opposite to the striking piston 3 in the cylinder chamber 2 with respect to the returning pressure chamber 2a. Formed on the side.

The vicinity of the front end of the impact piston 3 in the F direction has an outer diameter smaller than the outer diameter of the impact piston 3, and forms a chamber 3 a with the inner wall of the cylinder chamber 2.

In front of the cylinder chamber 2 (left side in the figure),
A hammer main body 5 that transmits a striking force to a striking parallel pin 4 as a struck member is provided. The center line of the hammer body 5 is on the same line as the center line of the cylinder chamber 2, and the hammer body 5 is supported by the support member 6 so as to be movable along the center line.
The rear end of the hammer body 5 faces into the cylinder chamber 2,
That is, it projects into the cylinder chamber 2 and faces the front end of the striking piston 3. The driving parallel pin 4 is supported at the front end of the hydraulic hammer 1 in front of the hammer main body 5 so that the rear end of the driving parallel pin 4 contacts the front end of the hammer main body 5.

Here, the movement of the striking piston 3 will be briefly described. When the striking piston 3 moves from the reference position shown in FIG. 1 in the direction of arrow F, as shown in FIG. 2, it moves to the forward end where it contacts the rear end of the hammer body 5. Conversely, when the striking piston 3 moves from the forward end in the direction of arrow R, it passes through the reference position shown in FIG.
As shown in (b), the cylinder moves to the reciprocating end in contact with the end face of the cylinder chamber 2.

Below the cylinder chamber 2, a pressure oil supply path 10 for supplying pressure oil to the backward pressure chamber 2a or the forward pressure chamber 2b of the cylinder chamber 2 is provided. The pressure oil supply path 10 is
The pump P is connected to the drain tank 11, and a pump P as a hydraulic pressure source for generating hydraulic pressure is interposed in the middle part. The pressure oil supply path 10 is connected to the first
Pressure oil supply path 10a and the second communication path with the return pressure chamber 2a.
Pressure oil supply path 10b and the third fluid communication path 10b communicating with the forward movement pressure chamber 2b.
And a pressure oil supply path 10c. The first pressure oil supply path 10a is switchably connected to one of the second pressure oil supply path 10b and the third pressure oil supply path 10c by a spool valve 15 described later. here,
The pressurized oil refers to oil pressurized by the pump P.

The first pressure oil supply path 10a controls the supply of pressure oil to the backward pressure chamber 2a or the forward pressure chamber 2b of the cylinder chamber 2, in other words, the first pressure oil supply path 10a A trigger 12 that opens and closes is provided. The trigger 12 is always moved by the spring 13 to the first pressure oil supply path 10.
a is urged in a direction to close a, and its operation (opening / closing) is controlled by an operator.

Above the cylinder chamber 2, a direction switching valve for switching the connection of the first pressure oil supply path 10a to one of the second pressure oil supply path 10b and the third pressure oil supply path 10c. Is disposed substantially parallel to the cylinder chamber 2. The spool valve 15 includes a cylinder 16
And a return position where the first pressure oil supply path 10a is connected to the second pressure oil supply path 10b, and the first pressure oil supply path 10a is connected to the third pressure oil supply path 10c. To the forward movement position. In FIG. 1, the spool valve 15 is at the forward movement position.

In the middle part of the spool valve 15, three small diameter portions having an outer diameter smaller than the outer diameter of the spool valve 15 are formed. The small diameter portion is defined by the inner wall of the cylinder 16 and the chambers 15a, 15b, 15b. 15c. When the spool valve 15 is at the forward movement position (the position shown in FIG. 1), the second pressure oil supply path 10b communicates with the discharge path D3 via the chamber 15a, and the third pressure oil supply path 10c
b and communicates with the first pressure oil supply path 10a. When the spool valve 15 is at the return position (the position shown in FIG. 3A), the second pressure oil supply path 10b communicates with the first pressure oil supply path 10a via the chamber 15a, and The pressure oil supply path 10c communicates with the discharge path D4 via the chamber 15b.

A return pilot pressure chamber 17 and a forward pilot pressure chamber 18 for moving the spool valve 15 to the reverse position or the forward position are formed at both ends of the cylinder 16, respectively.

A return pilot pressure supply path 20 which is connected to the cylinder chamber 2 and constitutes a return pilot supply mechanism is connected to the return pilot pressure chamber 17. The return pilot pressure supply path 20 supplies the pressure oil in the cylinder chamber 2 to the return pilot pressure chamber 17 when the impact piston 3 reaches the forward movement end (see FIG. 2). In the vicinity of the opening 20a communicating with the cylinder chamber 2 of the return pilot pressure supply path 20,
A discharge path D1 is provided for discharging the oil in the return pilot pressure chamber 17 to the drain tank 11 when the impact piston 3 reaches the return end.

The forward pilot pressure supply passage 2 communicates with the first pressure oil supply passage 10a.
1 is connected. The forward-moving pilot pressure supply path 21 is provided with a spool valve 22 that opens and closes the path 21. One end 22a of the spool valve 22 is connected to the cylinder chamber 2
And the other end 22b is
Thus, the forward movement pilot pressure supply path 21 is urged to close. The spool valve 22 includes the striking piston 3
When the valve reaches the return end against the urging force of the spring 23 (see FIG. 3B), the first pressure oil supply path 1 is opened.
The pressure oil in Oa is supplied to the forward movement pilot pressure chamber 18. The forward pilot pressure supply path 21, the spool valve 22, and the spring 23 constitute a forward pilot pressure supply mechanism.

In the cylinder 24 accommodating the spool valve 22, when the spool valve 22 closes the forward pilot pressure supply path 21, the oil in the forward pilot pressure chamber 18 is discharged to the drain tank 11. A road D2 is provided. In FIG. 1, the middle of the discharge paths D <b> 1 to D <b> 4 is not shown, but each of the discharge paths D <b> 1 to D <b> 4 is connected to the drain tank 11.

The pressure oil supply paths 10a, 10b, 10
c, pilot pressure supply paths 20, 21, discharge paths D1 to D
The inner surface of 4 is mirror-finished to improve oil flow, and the corners (corners) of each path are formed to be smoothly curved. By doing so, the flow of oil can be improved, and the hydraulic control speed can be improved.

Next, the operation of the above-mentioned hydraulic hammer 1 will be described. First, as shown in FIG.
Attach the driving parallel pin 4 to the tip of the. In the state shown in FIG. 1, the striking piston 3 is in the reference position and the spool valve 1 is
Numerals 5 are in the return position.

After mounting the driving parallel pin 4, the driving parallel pin 4
The trigger 12 is pulled against the biasing force of the spring 13 by aligning the tip of the target with the desired driving position of the target member. FIG.
, The oil pressurized by the pump P is supplied to the first pressure oil supply path 10a, the chamber 15b,
It passes through the third pressure oil supply path 10c and flows into the forward movement pressure chamber 2b. The pressure oil in the forward movement pressure chamber 2b causes the impact piston 3
Moves to the forward end, that is, the striking piston 3 is moved in the direction of arrow F, and the front end of the striking piston 3 strikes the rear end of the hammer body 5. The impact piston 3 is in the cylinder chamber 2
By moving inside, the hydraulic pressure is converted to a striking force to generate a striking force. The striking piston 3 strikes the hammer body 5, and the striking force is transmitted to the hammer body 5. At this time, as shown by an arrow B1 in FIG. 2, the pressure oil in the return pressure chamber 2a is supplied to the second pressure oil supply path 10
b, the chamber 15a, the discharge passage D3, and the drain tank 11
Is discharged.

Further, as shown in FIG. 2, when the striking piston 3 moves to the forward movement end, as shown by the arrow A2, the pressure oil in the forward movement pressure chamber 2b is displaced by the backward movement pilot pressure supply path 20.
, And flows into the return pilot pressure chamber 17.

Thereafter, as shown in FIG. 3 (a), when the pressure oil flows into the backward movement pilot pressure chamber 17, the spool valve 15 moves from the forward movement position to the backward movement position (from left to right in the figure). Go to The movement of the spool valve 15 causes the first
The pressure oil supply path 10a communicates with the second pressure oil supply path 10b via the chamber 15a, and the third pressure oil supply path 10c communicates with the discharge path D4 via the chamber 15b. Therefore, FIG.
In (a), as indicated by an arrow A3, the pressure oil from the pump P is supplied to the first pressure oil supply path 10a, the chamber 15a, and the second pressure oil supply path 10a.
And flows into the return pressure chamber 2a through the pressure oil supply path 10b. The striking piston 3 is returned to the reference position by the pressure oil in the return pressure chamber 2a, that is, the striking piston 3 is moved in the direction of arrow R, and the rear end of the striking piston 3 abuts one end 22a of the spool valve 22. . At this time, FIG.
As shown by an arrow B2, the pressure oil in the forward pressure chamber 2b is supplied to the third pressure oil supply path 10c, the chamber 15b, and the discharge path D.
4 and is discharged to the drain tank 11. Further, as indicated by an arrow B3, the pressure oil in the forward-moving pilot pressure chamber 18 is discharged to the drain tank 11 through the forward-moving pilot pressure supply path 21 and the discharge path D2.

Further, as shown in FIG. 3B, the striking piston 3 finally moves to the return end, and the spool valve 2
2 moves against the urging force of the spring 23, and communicates with the forward movement pilot pressure supply path 21. As shown by the arrow A4, the communication of the forward movement pilot pressure supply path 21 causes the first
Flows into the forward pilot pressure chamber 18 via the spool valve 22 from the pressure oil supply path 10a. At this time, the returning pilot pressure chamber 17 is
The pressure oil in the return pilot pressure chamber 17 is discharged to the drain tank 11 through the chamber 3a discharge path D1 and the drain tank 11 (see arrow B4).

When the pressure oil flows into the forward pilot pressure chamber 18, the spool valve 15 moves from the backward position to the forward position (from right to left in the figure). Spool valve 15
The state shown in FIG. 2 returns to the state shown in FIG. 2, and the first pressure oil supply path 10a is connected to the third pressure oil supply path 10 via the chamber 15b.
c, the second pressure oil supply path 10b communicates with the discharge path D1 via the chamber 15a. Thereby, the striking piston 3 moves in the forward movement direction, reaches the forward movement end shown in FIG. 2 again through the state shown in FIG. 1, and transmits the striking force to the hammer main body 5.

Therefore, in the state where the trigger 12 is pulled, the above-described operation is repeatedly performed, and a pulsed striking force is output via the hammer body 5. The driving parallel pin 4 is driven into the target member by the continuous (pulsed) impact force.

In the present invention, a striking force is generated by moving the striking piston 3 in the cylinder chamber 2 by hydraulic pressure and striking the hammer body 5 with the striking piston 3. The pressurized oil is supplied from the drain tank 11 to the pressurized oil hammer 1 by the pump P, generates a striking force in the pressurized oil hammer 1, and is then discharged to the drain tank 11.
It only circulates in a closed path. In other words, the driving fluid that generates the impact force, that is, the pressure oil, is not discharged to the outside. Therefore, it is possible to prevent impurities such as oil mist from being discharged into the atmosphere, to maintain a favorable working environment, and to reduce discharge noise during discharge. Also,
Since the impact at the time of the impact is absorbed by the oil, the noise at the time of the impact can also be reduced.

[0029]

As described above, according to the first aspect of the present invention,
According to the invention, a hammer using hydraulic pressure can be realized, so that a driving fluid (compressed air) is used like a conventional pneumatic hammer.
Since it is not necessary to discharge the oil to the outside, the hermeticity of the driving fluid (pressure oil) is improved, impurities such as oil mist are prevented from being discharged into the atmosphere, and a favorable working environment can be maintained. Also, the discharge noise at the time of discharge can be reduced.

According to the second aspect of the present invention, the directional control valve comprises:
Since it is constituted by a spool valve and arranged substantially parallel to the cylinder chamber, the size of the hydraulic hammer can be reduced, and processing and assembly at the time of manufacture can be easily performed.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram of a hydraulic hammer of the present invention.

FIG. 2 is a schematic configuration diagram of a hydraulic hammer for explaining the flow of oil in the hydraulic hammer, showing a state in which a striking piston has moved to a forward end.

3A and 3B are schematic configuration diagrams of a hydraulic hammer for explaining oil flow in the hydraulic hammer, where FIG. 3A illustrates a state in which a striking piston returns from a forward end to a reference position, and FIG. It shows a state in which the striking piston has moved to the return end.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Hydraulic hammer 2 Cylinder chamber 2a Return pressure chamber 2b Forward pressure chamber 3 Impact piston 5 Hammer main body 10 Pressure oil supply path 11 Drain tank 12 Trigger 15 Spool valve (direction switching valve) 17 Return pilot pressure chamber 18 Forward Pilot pressure chamber 20 Reverse pilot pressure supply path (reverse pilot pressure supply mechanism) 21 Forward pilot pressure supply path (forward pilot pressure supply mechanism) 22 Spool valve (forward pilot pressure supply mechanism) P pump

Claims (2)

[Claims] 1. A hydraulic hammer for striking a member to be struck, a hammer body transmitting a striking force to the struck member, a cylinder chamber formed at a rear end of the hammer body, and a cylinder. While being movably accommodated inside the chamber, the cylinder chamber is separated into a backward pressure chamber located on the hammer body side and a forward pressure chamber located on the opposite side of the backward pressure chamber, A striking piston that moves from the reversing end to the forward end within the cylinder chamber to generate a striking output and transmits a striking force to the hammer body, and pressurized oil from a hydraulic pressure source to the returning pressure chamber or A pressure oil supply path to be supplied to the forward movement pressure chamber; a return position provided in the pressure oil supply path to supply the pressure oil to the backward movement pressure chamber; and a pressure oil to the forward movement pressure chamber. It can be switched to the forward position to supply, and it switches when it receives pilot pressure A direction switching valve, a return pilot pressure chamber that switches the direction switching valve to the return position by supplying the pressure oil, and a direction switching valve that is supplied with the pressure oil. A forward-moving pilot pressure chamber that switches to a forward-moving position, a returning pilot pressure supply mechanism that supplies the pressure oil to the returning pilot pressure chamber when the striking piston reaches the forward-moving end, And a forward-moving pilot pressure supply mechanism that supplies the pressure oil to the forward-moving pilot pressure chamber when reaching the backward movement end. 2. The hydraulic hammer according to claim 1, wherein said direction switching valve is constituted by a spool valve, and is disposed substantially parallel to said cylinder chamber.