WO1997013925A1

WO1997013925A1 - Roller-crusher

Info

Publication number: WO1997013925A1
Application number: PCT/JP1996/002958
Authority: WO
Inventors: Shigeru Shinohara; Takayuki Mutou; Tadao Karakama; Mitsuru Arai; Koichi Morita
Original assignee: Komatsu Ltd.
Priority date: 1995-10-13
Filing date: 1996-10-11
Publication date: 1997-04-17
Also published as: EP0855468A1; EP0855468A4; JPH09111810A; KR970021536A

Abstract

A roller-crusher comprising a boom (6) mounted on a vehicle body (3) and capable of rocking in a vertical direction, and an arm (8) mounted on the boom and capable of rocking in the vertical direction, wherein the boom and the arm are driven by a boom cylinder (7) and an arm cylinder (9), respectively. A hydraulic vibration generator (12) is fitted to the arm, and a breaker chisel (15) and a rolling member (16) are exchangeably fitted to the vibration generator. Further, a switch is disposed so as to bring the boom cylinder into the floating state during the rolling work.

Description

Description Rolling and crushing work machine Technical field

The present invention relates to a rolling and crushing work machine that performs a rolling and crushing operation using a power shovel or the like. Background art

As a compacting work machine using a power shovel, there is known a compacting work machine that performs a compact reciprocating operation of a bucket cylinder of a power shovel to vibrate a bucket.

In addition, as a crushing machine using a power shovel, there is known a crushing machine in which a vibration generator is attached to an arm of the power shovel and the breaker chisel is struck by the vibration generator. ing.

As mentioned above, the conventional rolling machine and crushing machine were each dedicated machines, so two work machines would be required to perform the compacting and crushing work. .

Therefore, an object of the present invention is to provide a compaction and crushing work machine capable of performing both a compaction work and a crushing work with one unit. Disclosure of the invention

As an aspect of the present invention, It is preferable that the timer relay switches the floating switching valve to set the floating valve to the floating position only when the detection signal is not input from the switch.

According to this configuration, even if the boom hydraulic pilot valve is set to the neutral position during the rolling operation, the boom cylinder does not float unless the floating switch is set to 〇N, so that the safety is high. .

In the above aspect,

The floating state switching means includes a boom valve for supplying pressure oil to the boom cylinder having a floating position, and a boom valve hydraulic pilot valve for controlling the boom valve is provided with a detent mechanism. It is preferable that the boom valve is switched to a floating position when a full-stroke operation is performed on the boom valve hydraulic pilot valve. According to this configuration, the boom cylinder can be floated only by operating the hydraulic pilot valve for the boom valve.

Further, in each of the above configurations,

It is preferable that a work hole is formed in the main body of the vibration generator so that a cap provided with a hook can be detachably attached to the work tool hole.

According to this configuration, it is possible to prevent foreign matter from entering the cylinder hole by the cap when the crushing operation or the rolling operation is not performed, and the hanging operation can be performed by the hook. 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 are merely examples. It is preferable that the pressure switch be a pressure switch that detects the pressure of the service valve pilot circuit that connects the service valve and the service valve hydraulic pilot valve.

In the above aspect,

A circuit for connecting the floating state switching means to a selector switch for outputting a crushing signal or a compaction signal, a boom valve for supplying pressurized oil to the boom cylinder, and the boom cylinder; A floating switching valve for switching the position of the floating valve; a second operation detecting means for detecting that the boom cylinder is in an operating state; and a second operation detecting means. Only when the detection signal is not input and the rolling pressure signal is input from the selector switch, the floating switching valve is switched to set the floating valve to the floating position. It is better to configure it.

According to this configuration, when the hydraulic pilot valve for the boom valve is operated during the rolling operation, the floating valve switches to a position other than the floating position, so that the boom cylinder is quickly extended and retracted to swing the boom up and down. It can be done. In the above configuration,

The second operation detecting means detects, from a boom hydraulic pilot valve that controls the boom valve, the higher pressure of the hydraulic oil that acts on the first and second pressure receiving portions of the boom valve. And a pressure switch for detecting the pressure on the output side of the shuttle valve.

Further, in the above configuration,

A floating switch, wherein a 0 N signal from the floating switch and a rolling signal from the selector switch are input, and the pressure switch is A vibration generator 12 is mounted in the arm 8. This vibration generator 12 is provided with a piston 14 slidably in a main body 13 and alternately supplies pressure oil to pressure receiving chambers at both ends of the piston 14 by piston. The tongue 14 is made to reciprocate, and the breaker chisel 15 and the pressurizing tool 16 can be exchangeably mounted on the main body 13.

An engine 17 provided on the upper body 3 drives a hydraulic pump 18. The discharge side of the hydraulic pump 18 is connected to the inlet ports of the boom valve 19, the arm valve 20, the packet valve 21, and the service valve 22. The first 'second actuating ports 23, 24 of the boom valve 19 are connected to the extension chamber 7a of the boom cylinder 7 in the first and second circuits 25, 26. It is connected to the compression side 7b. The function port 27 of the service valve 22 is connected to the vibration generator 12 by a circuit 28.

A floating valve 29 is provided in the middle of the first circuit 25 and the middle of the second circuit 26. The floating valve 29 is held at the communication position a by spring, and is switched to the floating position b when pressurized oil is supplied to the pressure receiving portion 30 and contracts with the extension chamber 7 a of the boom cylinder 7. Connect chamber 7 b to tank 31.

The upper vehicle body 3 is provided with a hydraulic pilot valve 32 for a boom valve. By operating the lever 32a of the hydraulic pilot valve 32 for the boom valve to switch from the neutral position c to the extended position d or the contracted position e, the first boom valve 19 Supply pressure oil to the pressure receiving part 19a or the second pressure receiving part 19b, and switch the boom valve 19 from the neutral position to the extended position or the contracted position. To facilitate explanation and understanding.

In the figure,

FIG. 1 is a configuration explanatory view showing a first embodiment of a rolling and crushing work machine according to the present invention.

FIG. 2 is an explanatory diagram of a specific structure of the vibration generator of the first embodiment.

FIG. 3 is an enlarged sectional view of a part of the main body of the vibration generator. FIG. 4 is a configuration explanatory view showing a second embodiment of the rolling and crushing work machine according to the present invention.

FIG. 5 is a configuration explanatory view showing a third embodiment of the rolling and crushing work machine according to the present invention. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, a rolling and crushing work machine according to a preferred embodiment of the present invention will be described with reference to the accompanying drawings.

First, a first embodiment will be described.

As shown in FIG. 1, an upper body 3 is rotatably mounted on a lower body 2 provided with a traveling body 1, and the upper body 3 is provided with a seat 4 and a plurality of control members 5. A boom 6 is attached to the upper body 3 so as to be vertically swingable, and is driven by a boom cylinder 7. An arm 8 is attached to the boom 6 so as to be able to swing up and down, and is driven by an arm cylinder 9. Further, a bucket 10 is attached to the arm 8 so as to be vertically rotatable, and is driven by a bucket cylinder 11. These constitute a power shovel. By providing the chamber 51, the cylinder section 52 is constituted.

The servo valve 53 has a pump port 54, a main port 55, a tank port 56, and an auxiliary port 57, and the pump port 54 is the third port of the cylinder section 52. It communicates with the first room 49 and can be switched to the neutral position A, the first position B, and the second position C by the movement of the stone 14.

The main switching valve 58 has first, second, third, and fourth ports 59, 60, 61, and 62, and the first port 59 has a circuit 28 shown in FIG. The second port 60 communicates with the auxiliary port 57 of the servo valve 53. The third port 61 communicates with the tank 31 and the fourth port 62 communicates with the servo valve 53. The first pressure receiving portion 63 communicates with the main port 55 of the servo valve 53, and the second pressure receiving portion 64 communicates with the circuit 28. The circuit 28 communicates with the first chamber 49 of the cylinder section 52 and the pump port 54 of the servo valve 53. Then, the main switching valve 58 can be switched to the first position D by the pressure to the first pressure receiving portion 63 and to the second position E by the pressure to the second pressure receiving portion 64. I have.

The auxiliary chamber 51 of the cylinder section 52 is connected to the tank 31 or the second chamber 50 by a switching valve 70. The switching valve 70 is of a pilot switching type in which the drain position F is set to the drain position F by spring force and the communication position G is set to the communication position G by the pressure oil of the pressure receiving portion 71. Is connected to the floating pilot circuit 41. The switching valve 70 may be of a manual switching type with a mechanism.

Next, the basic operation of the vibration generator will be described.

In the state shown in FIG. 2, the piston 14 is in the intermediate position, the servo valve 53 is in the neutral position A, and the first pressure receiving portion 63 and the second pressure receiving portion 63 are in the neutral position A. The upper vehicle body 3 is provided with a hydraulic pilot valve 33 for a service valve. When the pedal 34 is depressed, pressurized oil is supplied to the pressure receiving portion 22a of the service valve 22 from the service valve pilot circuit 35, and the service valve 22 is actuated. It can be switched to the supply position where pressure oil is output from the gate 27. A pressure switch 36 is connected to the service valve pilot circuit 35.

For example, a selector switch 37 is provided on a lever 32 a of a hydraulic pilot valve 32 for a boom valve of the upper body 3, and a selector switch 37 is provided. By switching 7 to the rolling position f or crushing position g, a rolling signal or crushing signal is output.

The pressure signal from the pressure switch 36 and the rolling signal from the selector switch 37 are input to a timer relay 38. The timer relay 38 energizes the solenoid 40 of the floating switching valve 39 a predetermined time after both signals are input.

The floating switching valve 39 is provided in a floating pilot circuit 41 connected to the pressure receiving portion 30 of the floating valve 29, and the floating switching valve 39 is spring-drained. And is switched to the supply position i when the solenoid 40 is energized.

Next, a specific structure of the vibration generator 12 will be described.

As shown in FIG. 2, a cylinder hole 43 formed of a large-diameter cylinder hole 41 and a small-diameter cylinder hole 42 is formed in the main body 13, and the cylinder hole 43 is formed in the cylinder hole 43. Piston 14 is slidably fitted. The piston 14 includes a large diameter part 45, a large diameter rod part 46, an intermediate diameter rod part 47, and a small diameter rod part 48. The first chamber 49 with a small pressure receiving area and the second chamber 50 with a large pressure receiving area are provided on both sides of the large-diameter portion 45. The pressure receiving area of the chamber for moving the piston 14 to the left is the pressure receiving area (A 1 -A 2) of the second chamber 50. Here, A 1 is the cross-sectional area of the large-diameter portion 45, and A 2 is the cross-sectional area of the intermediate-diameter rod portion 47.

When pressurized oil is supplied to the pressure receiving portion 71 of the switching valve 70, the switching valve 70 becomes the communication position G and the second chamber 50 communicates with the auxiliary chamber 51, so the piston 14 is moved to the left. The pressure receiving area of the chamber to be moved is the pressure receiving area of the second chamber 50 (Al-A2) + the pressure receiving area of the auxiliary chamber 51 (A2-A3). Here, A 3 is the cross-sectional area of the small diameter rod portion 8.

As described above, if the switching valve 70 is set to the drain position F, the pressure receiving area of the chamber for moving the piston 14 to the left is reduced, and the reciprocating speed of the piston 4 is reduced. This is suitable when the vibration generator is used as a drive source of a breaker.

Further, if the switching valve 70 is set to the communication position G, the pressure receiving area of the chamber for moving the piston 14 to the left increases, and the moving force of the piston 14 increases. This is suitable when the present vibration generator is used as a drive source of a rolling machine.

In the main body 13 of the vibration generating device 12, as shown in FIG. 3, a working tool insertion hole 72 is formed continuously with the cylinder hole 43. Insert the breaker chisel 15 or the pressing tool 16 into the shaft, and penetrate the pin 73 into the longitudinally long recess provided on the shaft of the breaker chisel 15 or the pressing tool 16 so that the breaker chisel 15 Alternatively, the pressing tool 16 is held so as to be able to reciprocate with a predetermined stroke.

In FIG. 3, a cap 74 is detachably inserted into the work tool insertion hole 73, and the cap 74 is retained by the pin 73. Pump discharge pressure is supplied to 64. Since the pressure receiving area of the first pressure receiving portion 63 is larger than the pressure receiving area of the second pressure receiving portion 64, the main switching valve 58 is at the first position D, and therefore, the cylinder. Since the second chamber 50 of the section 52 communicates with the tank 31, the piston 14 moves to the right with the pressurized oil in the first chamber 49.

Servo valve when piston 14 takes the right-stroke position.

53 becomes the second position C, the main port 55 communicates with the tank port 56, and the connection between the pump port 54 and the auxiliary port 57 is cut off. Therefore, the pressure oil of the first pressure receiving portion 63 of the main switching valve 58 flows out to the tank 31, and the main switching valve 58 is moved to the second position E by the pressure of the second pressure receiving portion 64. The first port 59 and the fourth port 62 communicate with each other, and the second port 59

60 communicates with the third port 61. As a result, pressurized oil is supplied to the second chamber 50 of the cylinder section 52 and the pressure difference caused by the area difference between the first chamber 49 and the second chamber 50 causes the pressure of the piston 14 to decrease. Moves to the left.

When piston 14 assumes the left stroke end position, servo valve 53 is in first position B and pump port 54 communicates with main port 55. Therefore, the connection between the tank port 56 and the auxiliary port 57 is shut off. As a result, the pressurized oil is supplied to the first pressure receiving portion 63 of the main switching valve 58, and the main switching valve 58 becomes the first position D. As described above, the piston 14 is moved to the first position D. Move to the right.

The above operation is repeated, and piston 14 reciprocates.

Next, the operation of changing the reciprocating speed and the moving force of the piston 4 will be described.

If the switching valve 70 is set to the drain position F, the connection between the second chamber 50 and the auxiliary chamber 51 is shut off, and the auxiliary chamber 51 communicates with the tank 31. (Rolling work)

Attach the pressure roller 16 to the body 13 of the vibration generator 12 and set the selector switch 37 to the rolling position f.

When the pedal 34 is depressed in this state, the service valve 22 becomes the supply position and the piston 14 of the vibration generator 12 reciprocates and the piston 14 rolls as in the crushing operation. Since the pressure tool 16 is vibrated, the rolling operation can be performed.

At this time, since the pressure signal from the pressure switch 36 and the rolling signal from the selector switch 37 are input to the timer 38, a floating switching valve is provided after a predetermined time. The solenoid 40 of 39 is energized to reach the line-in position i.

As a result, pressure oil is supplied to the pressure receiving portion 30 of the floating valve 29, and the floating valve 29 becomes the force drain position b. Since the shrinkage chamber 7b communicates with the tank 31, the boom cylinder 7 freely expands and contracts by an external force, that is, the boom cylinder 7 floats. When the beam cylinder 7 is in a floating state, the boom 6 swings up and down by an external force, so that the rolling operation can be performed efficiently.

When the pressurized oil is supplied to the floating pilot circuit 41, the switching valve 70 shown in FIG. 2 is in the supply position G, so that the piston 14 moves as described above. The greater the force, the greater the compaction effect.

Next, a second embodiment will be described.

As shown in FIG. 4, the floating switch 80 is attached to the lever 32a of the hydraulic pilot valve 32 for the boom, and the first and second pressure receiving portions 19a of the boom valve 19 are provided. , 19b is provided with a shut-off valve 81 for detecting the higher pressure of the hydraulic oil acting on the pressure oil. And have a hook 75. Therefore, when crushing work and compaction work are not performed, a cap 74 is attached to the work tool insertion hole 73 to prevent foreign matter from entering the cylinder hole 43. The hanging work can be performed by the hook 75 provided on the cap 74.

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

(Crushing work)

Attach the breaker chisel 15 to the body 13 of the vibration generator 12 and set the selector switch 37 to the crushing position g.

Depress the pedal 34 to operate the service valve hydraulic pilot valve 33 to output pressure oil to the service valve pilot circuit 35. As a result, the pressure oil is supplied to the pressure receiving portion 22 a of the service valve 22, the service valve 22 becomes the supply position, and the discharge pressure oil of the hydraulic pump 18 is supplied to the vibration generating device. The piston 14 is reciprocated by being supplied into the main body 13 of 1 2, and the piston 14 strikes the breaker chisel 15 to perform crushing work.

At this time, the pressure switch 36 outputs a pressure signal, but the pressure switch signal is not input from the selector switch 37, so that the timer relay 38 does not operate. As a result, pressure oil is not supplied to the floating pilot circuit 41 until the floating switching valve 39 remains at the drain position h, so that the switching valve 70 shown in FIG. As F, the reciprocating speed of the piston 14 increases as described above.

Also, during the crushing operation, by operating the lever 32a of the hydraulic pilot valve 32 for the boom valve, the boom cylinder 7 is extended and contracted, and the boom 6 is swung up and down. Move. Therefore, safety is high.

Next, a third embodiment will be described.

As shown in FIG. 5, the boom valve 19 has a floating position X, the boom hydraulic pilot valve 32 has a detent mechanism, and the boom valve has a detent mechanism. When the hydraulic pilot valve 32 is operated at full stroke, the boom valve 19 is switched to the floating position X.

By doing so, the hydraulic pressure is applied to the second pressure receiving portion 19 b of the boom valve 19 by performing the full stroke operation of the lever 32 a of the boom hydraulic pilot valve 32. When the boom valve 19 is supplied, the boom valve 19 is set to the floating position X and the lever 32a is maintained in the full stroke operation state, so that the boom cylinder 7 is set to the floating state. Rolling work can be performed.

Although the present invention has been described with reference to exemplary embodiments, various modifications, omissions, and additions can be made to the disclosed embodiments without departing from the spirit and scope of the present invention. This is obvious to those skilled in the art. Therefore, the present invention should not be construed as being limited to the above-described embodiments, but as encompassing the scope defined by the elements recited in the claims, and equivalents thereof. Must.

Switch 82 will be provided.

The ON signal of the floating switch 80 and the pressure signal of the pressure switch 82 are input to the timer relay 38, and the timer relay 38 is connected to the floating switch 80. Only when the ON signal and the pressure signal from the selector switch 37 are input and the pressure signal from the pressure switch 82 is not input, the solenoid 4 of the floating switching valve 39 is provided only when the pressure signal of the pressure switch 82 is not input. Turn on 0.

With this configuration, when the boom valve 19 is operated by operating the lever 32a of the boom hydraulic pilot valve 32 during the rolling operation, the pressure switch 82 is pressed. Since the signal is output, the timer 38 does not energize the solenoid 40, and the floating switching valve 39 becomes the drain position h. The communication position is a.

Therefore, during the rolling operation with the boom cylinder 7 in the floating state, the floating state is released by operating the boom hydraulic pilot valve 32 to expand and contract the boom cylinder 7. Therefore, the boom cylinder 7 can be extended and retracted to swing the boom 6 up and down, and when the extension and retraction of the boom cylinder 7 is stopped, the boom cylinder 7 automatically returns to the floating state. I do.

Note that the floating switch 80 is omitted, and the timer relay 38 is replaced with the pressure switch signal from the selector switch 37 and the pressure switch 8. The same effect as described above can be obtained by energizing the solenoid 40 of the floating switching valve 39 only when the pressure signal of No. 2 is not input.

However, those who have the floating switch 80 can move the floating switch 80 even if the lever 32 a of the boom hydraulic pilot valve 32 is set to the neutral position during the rolling work. Boom cylinder 7 floats unless set to 0 N A selector switch, a floating valve for supplying pressure oil to the boom cylinder, and a floating valve provided in a circuit connecting the boom cylinder, and a floating switch for switching a position of the floating valve. A valve, a second operation detecting means for detecting that the beam cylinder is in an operating state, a detection signal from the second operation detecting means not being input, and the selector switch 2. The rolling compressor according to claim 1, wherein the floating switching valve is switched only when a rolling pressure signal is input from a switch to set the floating valve to a floating position. Crushing work machine. 5. The second operation detecting means increases the pressure of the hydraulic oil acting on the first and second pressure receiving portions of the boom valve from the boom hydraulic pilot valve for controlling the boom valve. 5. The rolling and crushing work machine according to claim 4, further comprising a shuttle valve for detecting the pressure and a pressure switch for detecting an output pressure of the shuttle valve. .

6. A floating switch is further provided, and a 0 N signal from the floating switch and a rolling signal from the selector switch are input thereto, and a detection signal is output from the pressure switch. 6. The compacting and crushing work machine according to claim 5, wherein the timer relay switches the floating switching valve to the floating position only when no input is made.

7. The floating state switching means, wherein a boom valve for supplying pressure oil to the boom cylinder has a floating position, and a hydraulic pilot valve for a boom valve for controlling the boom valve. When the hydraulic pilot valve for the boom valve is operated at full stroke,

Claims

The scope of the claims

1. A boom is attached to the vehicle body so that it can swing up and down, an arm is attached to the boom so that it can swing up and down, and the boom and the arm are driven by a boom cylinder and an arm cylinder, respectively.

A vibration generating device driven by pressurized oil is mounted on the arm, a breaker chisel or a rolling tool is replaceably mounted on the vibration generating device, and a floating state switching hand for lifting the boom cylinder during the rolling operation. Rolling and crushing work machine with steps. 2. The floating state switching means includes: a first operation detecting means for detecting that the vibration generator is in an operating state; a select switch for outputting a crushing signal or a tilling signal; and the boom. A boom valve for supplying pressurized oil to the cylinder and a floating valve provided in a circuit connecting the boom cylinder, a floating switching valve for switching a position of the floating valve, and the first operation detecting means And a timer relay that switches the floating switching valve when the pressure signal from the selector switch is input to set the floating valve to the floating position. The rolling and crushing work machine according to claim 1. 3. The first operation detecting means includes a service valve pilot circuit for connecting a service valve for supplying pressure oil to the vibration generator and a service valve hydraulic pilot valve. The rolling and crushing work machine according to claim 2, wherein the machine is a pressure switch for detecting pressure. 4. The floating state switching means outputs a crushing signal or a compaction signal. The rolling and crushing work machine according to claim 1, wherein the boom valve is configured to be switched to a floating position.

8. The working tool insertion hole according to claim 1, wherein a working tool insertion hole is formed in the main body of the vibration generator, and a cap provided with a hook can be detachably attached to the working tool insertion hole. The rolling and crushing work machine according to any one of the above.