WO1998003312A1

WO1998003312A1 - Vibration generation apparatus

Info

Publication number: WO1998003312A1
Application number: PCT/JP1997/002492
Authority: WO
Inventors: Naoki Ishizaki; Shigeru Shinohara; Takayuki Muto; Mitsuru Arai
Original assignee: Komatsu Ltd.
Priority date: 1996-07-18
Filing date: 1997-07-17
Publication date: 1998-01-29
Also published as: KR980009761A; JP3729428B2; JPH1034562A

Abstract

The invention relates to a vibration generation apparatus used for brakers used in crushing and for roller compactors used in roller compaction. According to the invention, the vibration generation apparatus is suitable for braking work because a piston (3) reciprocates at high speed when a second switching means (30) is in a braker position (C). The vibration generation apparatus is suitable for roller compaction because the thrust of the piston is great and the number of reciprocal vibration of the piston per unit time, i.e., the frequency is high when the second switching means is in a roller compaction position (D).

Description

Description Vibration generator Technical field

The present invention relates to a vibration generator used for a breaker used for crushing work, a rolling machine used for rolling work, and the like. Background art

As this type of vibration generating device, a piston is inserted into a cylinder hole of a main body to form a first chamber and a second chamber at both ends of the piston, and a pressure receiving area of the first chamber is formed. Is smaller than the pressure receiving area of the second chamber, the first chamber is always connected to the hydraulic pressure source, and the second chamber alternately communicates with the hydraulic pressure source and the tank based on the reciprocation of the piston. It is known to reciprocate the ton in the working direction and the return direction.

The piston operating speed of the above-mentioned vibration generator is increased by reducing the difference in pressure receiving area between the first and second chambers and increasing the moving speed per flow rate, and the thrust of the piston is increased. Is increased by increasing the pressure receiving area difference between the first and second chambers and increasing the area on which hydraulic pressure acts to generate thrust.

In the case of a breaker for crushing work, the higher the reciprocating speed of the chisel, the more efficient the crushing work.Therefore, as the vibration generator for the breaker, the pressure receiving area of the first and second chambers The smaller the difference, the better.

In the case of a compacting machine for performing compaction work, it is more efficient to press the compaction plate against the compaction surface with a strong force. It is better that the pressure receiving area difference between the first chamber and the second chamber is large as a vibration generator for use.

In view of this, the applicant has previously proposed a vibration generator capable of changing the pressure receiving area difference between the first chamber and the second chamber, but this apparatus is composed of the first chamber and the second chamber. There is a limit to changing the pressure receiving area difference with the chamber, and large thrust cannot be obtained.

When the piston moving speed is increased by reducing the pressure receiving area difference between the first chamber and the second chamber, the thrust of the piston becomes smaller, so that the return stroke position When the movement of the Boston in the working direction starts, it takes time for the Boston to start moving due to the inertia and weight of the Boston, and eventually the reciprocating speed of the Boston Will be delayed.

Therefore, an object of the present invention is to provide a vibration generator capable of solving the above-mentioned problem. Disclosure of the invention

One mode of the vibration generator according to the present invention for achieving the above object is as follows.

A first chamber in which a piston having a rod is inserted into a cylinder hole of the main body to move the piston in a returning direction, and a first chamber for moving the piston in a working direction. A cylinder section defining a second chamber and an auxiliary chamber having a larger pressure receiving area than the first chamber; and

A main switching valve for switching between a second position communicating the second chamber with a tank and a second position communicating the second chamber with a hydraulic pressure source;

In conjunction with the movement of the piston, the auxiliary chamber is connected to a hydraulic source and a tank. A first switching means for switching and communicating the main switching valve between a first position and a second position.

A breaker position which is operated by an external signal to communicate the first chamber to a hydraulic pressure source and to cut off the operating pressure for the main switching valve from the first switching valve, and to communicate the first chamber to the tank and Second switching means for switching to a rolling position for communicating the operating pressure for the main switching valve from the first switching valve,

When the second switching means is at the breaker position, the first switching means communicates the auxiliary chamber to a hydraulic pressure source when the piston returns to the stroke end position and connects the main switching valve to the second switching valve. When the piston moves in the working direction, the auxiliary chamber communicates with the tank, and when the piston comes to the working direction stroke position, the main switching valve is directly operated. Is the first position,

When the second switching means is at the tilling pressure position, the first switching means communicates the auxiliary chamber to a hydraulic pressure source and sets the main switching valve to the second position when the piston reaches the return stroke position. When the piston moves in the working direction, the auxiliary chamber communicates with the tank and the main switching valve is set to the first position via the second switching means. Things.

According to this configuration,

When the second switching means is set to the breaker position, the pressure from the hydraulic pressure source is constantly supplied to the first chamber 4, so the piston is (the pressure receiving area of the second chamber + the pressure receiving area of the auxiliary chamber minus the first When the piston moves a certain distance, the auxiliary chamber communicates with the tank and the piston 3 moves to the second chamber (pressure receiving area of the second chamber). 5 of (Pressure receiving area-pressure receiving area of first chamber 4) Moves to the work stroke position by hydraulic pressure acting on the pressure receiving area difference.

As a result, the piston in the return stroke stroke position has a large thrust at the start of the movement in the working direction, so that the piston starts to move quickly, and after the piston starts moving. Moves at high speed to the working direction stroke end position.

Therefore, since the piston reciprocates at a high speed, the present invention is a vibration generator suitable for a breaker operation.

In addition, when the second switching means is at the rolling position D, the piston is always in communication with the tank, so the piston receives (pressure receiving area of the second chamber + pressure receiving area of the auxiliary chamber) It moves in the working direction by hydraulic pressure acting on the sum of the areas, and its thrust is large.

In addition, when the piston moves a certain distance in the working direction, the main switching valve moves to the second position and the auxiliary chamber communicates with the tank, so that the reciprocating stroke of the piston is short. It becomes like this.

As a result, the thrust of the piston is large, and the number of reciprocating movements of the piston per unit time, that is, the frequency is increased.

Therefore, the present invention is a vibration generator suitable for the rolling work. BRIEF DESCRIPTION OF THE FIGURES

The invention will be better understood from the following detailed description and the accompanying drawings illustrating an embodiment of the invention. The embodiments shown in the accompanying drawings are not intended to specify the invention, but merely to facilitate explanation and understanding.

In the figure, FIG. 1 is a configuration explanatory view showing one embodiment of the vibration generator according to the present invention.

FIG. 2 is an explanatory diagram of a state where the switching valve is switched in the above embodiment.

FIG. 3 is an explanatory diagram of a case where the above embodiment is attached to the tip of an arm of a hydraulic shovel to perform a rolling operation. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, a vibration generator according to a preferred embodiment of the present invention will be described with reference to the accompanying drawings.

As shown in Fig. 1, a piston 3 is inserted into a cylinder hole 2 of the main body 1, a large-diameter rod 3a is inserted on one side of the piston 3, and an intermediate-diameter rod is inserted on the other side. The first chamber 4 is provided with a rod 3b and a small-diameter rod 3c connected to the rod 3b. One side of the piston 3 is provided with a first chamber 4 for pushing the piston 3 in the return direction. A second chamber 5 that has a larger pressure receiving area than the first chamber 4 that pushes 3 in the working direction and an auxiliary chamber 6 that pushes the piston 3 in the working direction are defined, and these constitute the cylinder section 7. are doing.

The valve mechanism 10 includes the first pump port 11, the second pump port 12 -tank port 13, the i-th auxiliary port 14, the second auxiliary port 15 .The main port 16, the auxiliary inlet It has a port 17 and an auxiliary outlet port 18 so that it can be switched to the first position a, the second position b, the third position c, and the fourth position d in conjunction with the movement of the piston 3. ing.

The main switching valve 20 has first, second, third, and fourth ports 21, 22, 23, and 24, and the first position A is determined by the pressure applied to the first pressure receiving portion 25. And the pressure on the second pressure receiving part 26 comes to the second position B. The first port 21 communicates with the discharge path 27 a of the hydraulic pump 27, the second port 22 communicates with the second auxiliary port 15 of the valve mechanism 10, and the third port 2 3 communicates with the tank 28, and the fourth port 24 communicates with the second chamber 5 of the cylinder part 7 and the auxiliary inlet port 17 of the valve mechanism 10.

The switching valve 30 is held at the breaker position C by the spring 31 and becomes the rolling position D when the pressure oil is supplied to the pressure receiving portion 32. The pressure receiving section 32 is supplied with and stopped by the hydraulic pressure pilot valve 33 from the hydraulic pressure discharge from the auxiliary hydraulic pump 34.

When the switching valve 30 is at the breaker position C, the first port 35 and the third port 37 are in communication, the second port 36 and the fifth port 39 are in communication, The fourth port 38 is shut off. When the switching valve 30 is at the rolling position D, the first port 35 communicates with the fourth port 38, and the fourth port 38 communicates with the fourth port 38. The third port 37 and the fifth port 39 communicate with each other, and the second port 36 is shut off.

The first port 35 is connected to one inlet side of a shuttle valve 40, and the other inlet side of the shuttle valve 40 is connected to a main port 16 of a valve mechanism 10. The outlet side of the shuttle valve 40 is connected to the first pressure receiving portion 25 of the main switching valve 20.

The second port 36 is connected to a discharge path 27 a of a hydraulic pump 27, the third port 37 is connected to a tank 28, and the fourth port 38 is a valve mechanism 1. 0 is connected to the first auxiliary port 14, and the fifth port 39 is connected to the first chamber 4.

The discharge path 27 a of the hydraulic pump 27 is connected to both the first and second pump ports 11 1 and 12 of the valve mechanism 10, and the main switching valve 20 is connected to the second pressure receiving section 26. The pressure receiving area of the first pressure receiving chamber 25 of the main switching valve 20 is larger than the pressure receiving area of the second pressure receiving chamber 26.

Next, the operation of the present embodiment will be described.

In FIG. 1, consider a state where piston 3 is at the right (return direction) stroke position and switching valve 30 is at breaker position C.

The valve mechanism 10 (first switching means) is in the fourth position d, at which time the auxiliary inlet port 17 and the auxiliary outlet port 18 communicate, and the main port 16 is connected to the tank port 13 Since the first port 35 of the switching valve 30 (the second switching means) communicates with the tank 28 through the third port 37, the main switching is performed. No pressure oil is supplied to the first pressure receiving chamber 25 of the valve 20, and the first pressure receiving chamber 25 is in communication with the tank 28, so that the main switching valve 20 is connected to the second pressure receiving section. The second position B is set by the discharge pressure of the hydraulic pump 27 acting on 26.

Thereby, the discharge pressure oil of the hydraulic pump 27 is supplied to the second chamber 5, the auxiliary chamber 6, and the first chamber 4 of the cylinder section 7 through the fourth port 24, so that (the second The piston 3 moves to the left (working direction) due to the hydraulic pressure acting on the pressure receiving area difference that is the pressure receiving area of the chamber 5 + the pressure receiving area of the auxiliary chamber 6-the pressure receiving area of the first chamber 4). Since the pressure receiving area difference at this time is large, the thrust to push the piston 3 in the working direction is large.

As the piston 3 moves to the left, the valve mechanism 10 is sequentially switched to the third position c and the second position b. When the valve mechanism 10 is in the second position b, the auxiliary inlet port 17 is shut off, the auxiliary outlet port 18 communicates with the tank port 13 and the auxiliary chamber 6 communicates with the tank 28 So The piston 3 moves to the left by the hydraulic pressure acting on the pressure receiving area difference of (pressure receiving area of the second chamber 5-pressure receiving area of the first chamber 4).

Since the pressure receiving area difference at this time is small, the speed at which the piston 3 moves in the working direction increases.

Then, when the piston 3 reaches the left stroke position, the valve mechanism 10 becomes the first position a, and the discharge pressure oil of the hydraulic pump 27 becomes the second pump port 12, It flows into the shuttle valve 40 from the port 16 and is supplied from the outlet side of the shuttle valve 40 to the first pressure receiving section 25 of the main switching valve 20.

As a result, the main switching valve 20 is switched to the first position A, so that the pressure oil in the second chamber 5 of the cylinder 7 is discharged from the fourth port 24 and the third port 23. The oil in the auxiliary chamber 6 flows out to the tank 28, and the hydraulic oil in the auxiliary chamber 6 flows out of the auxiliary outlet port 18 and the tank port 13 to the tank 28. Therefore, the piston 2 moves to the right due to the pressure in the first chamber 4. At the same time, the valve mechanism 10 moves to the second position b, the third position c, and the fourth position d, and the state described above is reached.

As described above, when the switching valve 30 is set at the breaker position C, the thrust is a dog at the initial stage of moving the piston 3 in the working direction, and therefore the inertia when the piston 3 moves in the returning direction is determined. The piston 3 can start moving in the working direction against the force (proportional to the mass of the piston 3 and the rod), and the piston 3 starts moving in the working direction after the piston 3 starts moving in the working direction. The piston 3 can move at high speed, so that the piston 3 moves quickly in the working direction and also moves quickly in the returning direction. Therefore, the present embodiment is preferable as a vibration generating device for a breaker operation.

Next, the operation when the switching valve 30 is at the rolling position D as shown in FIG. explain.

When the switching valve 30 is in the rolling position D, the first chamber 4 of the cylinder 7 is connected to the tank 28 from the fifth port 39 and the third port 37 of the switching valve 30. The first auxiliary port 14 of the valve mechanism 10 communicates with the fourth port 38 and the first port 35 to one inlet side of the shuttle valve 40.

When the piston 3 is in the right-stroke position, the valve mechanism 10 is in the fourth position d and the main switching valve 20 is in the second position B as described above. As a result, the discharge pressure of the hydraulic pump 27 is supplied to the second chamber 5 and the auxiliary chamber 6 of the cylinder section 7, and the piston 3 moves in the working direction.

At this time, since the first chamber 4 has the tank pressure, the piston 3 is pushed in the working direction by the hydraulic pressure acting on the sum of the pressure receiving areas of (the pressure receiving area of the second chamber 5 + the pressure receiving area of the auxiliary chamber 6), Since the sum of the pressure receiving areas is larger by the pressure receiving area of the first chamber 4 than the area when the switching valve 30 is set to the breaker position C, the thrust for pushing the piston 3 in the working direction is large. Therefore, the present embodiment is preferable as a vibration generator for a rolling machine.

When the piston 3 moves in the working direction and the valve mechanism 10 moves to the second position b, the first pump port 11 communicates with the first auxiliary port 14 so that the hydraulic pump 27 The discharge pressure flows into one inlet of the shuttle valve 40 via the valve mechanism 10 and the switching valve 30 and acts on the first pressure receiving portion 25 of the main switching valve 20 to cause the main switching valve 20 to operate. Let it be the first position A. Accordingly, the second chamber 5 of the cylinder section 7 communicates with the tank 28 by the main switching valve 20 _{c. At the} same time, the auxiliary chamber 6 of the cylinder section 7 communicates with the tank 28 via the valve mechanism 10. I do. Thus, the piston 3 moves to the right by an external force, and when it reaches the right stroke end position, the piston 3 moves in the working direction again as described above.

As described above, when the switching valve 30 is set at the rolling position D, the thrust of the piston 3 is large, and the reciprocating stroke of the piston 3 is short, and the unit is used even if the pump flow rate is the same. Since the number of reciprocating movements per time, that is, the frequency is increased, this embodiment is suitable as a vibration generator for a rolling machine.

For example, as shown in FIG. 3, an upper vehicle body 51 is pivotally mounted on a lower traveling body 50, and a boom 52 is mounted on the upper vehicle body 51 so that the boom can be vertically swung by a boom cylinder 53. The arm 54 is mounted on the boom 52 such that the arm 54 can be swung up and down by the arm cylinder 55.In this case, the main body 1 is attached to the tip of the arm 54. Attach the work machine cylinder 56 and the link 57 so that it can swing freely, leave the bom cylinder 53 floating and load the rod 3a with the boom weight and arm weight. By pressing against the rolling plate 58 to perform the rolling operation, when the pressurized oil is supplied to the second chamber 5 and the auxiliary chamber 6, the other part of the cylinder part 7 moves against the piston 3. It moves relatively upward, and when the second chamber 5 and the auxiliary chamber 6 communicate with the tank, that of the cylinder section 7 The other parts move downward relative to Boston 3.

Although the present invention has been described with reference to exemplary embodiments, it is understood that various changes, omissions, and additions can be made to the disclosed embodiments without departing from the spirit and scope of the present invention. It is obvious to those skilled in the art. Therefore, the present invention is limited to the above embodiment. And should be understood as encompassing the range defined by the elements recited in the claims and their equivalents.

Claims

The scope of the claims

1. A first chamber in which a piston having a rod is inserted into a cylinder hole of the main body to move the piston in a return direction, and to move the piston in a working direction. A cylinder section defining a second chamber and an auxiliary chamber having a larger pressure receiving area than the first chamber,

A main switching valve operable to switch between a first position communicating the second chamber with a tank and a second position communicating the second chamber with a hydraulic pressure source;

In conjunction with the movement of the piston, the auxiliary chamber is switched to communicate with one of a hydraulic source and a tank, and the first switching valve is operated to switch between a first position and a second position. Switching means;

Activated by an external signal, the first chamber communicates with a hydraulic pressure source and a breaker position for interrupting the operating pressure for the main switching valve from the first switching valve, and the first chamber communicates with a tank, and Second switching means for switching to a rolling position for communicating the operating pressure for the main switching valve from the first switching valve,

When the second switching means is at the breaker position, the first switching means communicates the auxiliary chamber to a hydraulic pressure source when the piston returns to the stroke position and sets the main switching valve at the second stroke position. When the piston moves in the working direction, the auxiliary chamber communicates with the tank, and when the piston comes to the working direction stroke end position, the main switching valve is directly operated. The first position,

When the second switching means is at the rolling position, the first switching means communicates the auxiliary chamber with a hydraulic pressure source when the piston comes to the return stroke position and connects the main switching valve to the second switching means. When the piston moves in the working direction, the auxiliary chamber communicates with the tank and A vibration generator, wherein the main switching valve is set to a first position via the second switching means.

2. One oil passage for supplying a main valve switching operating pressure from the first switching means to the pressure receiving portion of the main switching valve and a main switching valve from the second switching means to the pressure receiving portion of the main switching valve. The vibration generator according to claim 1, wherein a shuttle valve is arranged at a junction with another oil path that supplies an operating pressure.