KR20130032533A - Hydraulic breaker - Google Patents

Abstract

PURPOSE: A hydraulic breaker is provided to activate a no-load strikes preventing function by selectively supplying oil drawn through a high pressure line to a no-load strike preventing chamber due to the operation of an adjust. CONSTITUTION: A hydraulic breaker(100) comprises a cylinder, an adjust unit, a back head(130), a front head(140), a piston(150), a chisel(160), and a front cover(170). A mounting hole is formed inside of the cylinder and comprises a high pressure line and a low pressure line on one side of the mounting hole. The mounting hole comprises a no-load strikes preventing chamber(112e) in which oil is filled. The no-load strikes preventing chamber is connected to the high pressure line through a connection port and a fluid path. A first fluid path and a second fluid path are formed in the inside of the cylinder, and the adjust unit is installed in the inside of the cylinder to selectively connect the cylinder to the first fluid path and the second fluid path.

Description

Hydraulic Breaker {HYDRAULIC BREAKER}

The present invention relates to a hydraulic breaker, and more particularly, to a hydraulic breaker that can selectively activate the anti-static function according to the working environment to improve the work efficiency.

Hydraulic breaker is a device that is installed in construction equipment such as excavators, loaders, etc. to crush rock or concrete, and when the cylinder is operated, the piston lifts and strikes the chisel, which is a crushing tool, and the chisel is the object of crushing concrete and rock. Apply impact force to crush.

In the conventional hydraulic breaker, when a crushing object is completely crushed, the crushing tool, the chisel, is lowered to the lower portion of the front head by a distance allowed by the chisel pin by its own weight so that the piston and the chisel are separated from each other. In this state, when the cylinder operates to raise and lower the piston, the piston and the cylinder (more specifically, the front head) are hit, causing excessive stress on the piston and the cylinder. These phenomena are called 'no-load strikes', and the shocks that occur when the piston strikes the cylinder directly damage the parts installed inside the cylinder (stop pins, thrust rings, front covers, etc.). This causes problems such as reduced service life of the hydraulic breaker.

In order to solve the above problems, a hydraulic breaker having an anti-spin function has recently been developed. FIG. 12 shows an example of a hydraulic breaker having an anti-sitting function, which is installed in an excavator including a hydraulic pump 92, an operation valve 94, and an oil tank 95, and the operation valve 94 is operated at operation O. FIG. When it is switched to, the oil compressed by the hydraulic pump 92 is supplied to the hydraulic breaker to operate the hydraulic breaker, and when the operation valve 94 is switched to the stop position (S), the supply of oil is cut off and the operation of the hydraulic breaker stops. .

If the shredding object is completely broken in the process of shredding the shredding object through the above-described process, the chisel 30 is lowered by the position (ie, the free position D) allowed by the chisel pin 19. In this state, when the piston 20 moves up and down, it does not hit the chisel 30 and goes down to the struck position E through the normal hitting position B. Thus, when the piston 20 descends to the vacant position E, the annular groove 23 formed between the 1st large diameter part 22 and the 2nd large diameter part 24 of the piston 20 is an anti-ballout port 80 And the switching port 62 are connected to each other, and the oil introduced through the supply line 46 is supplied to the second valve hydraulic pressure surface 54 via the anti-ballout prevention line 82 and the second pilot line 64.

Since the first valve hydraulic pressure surface 52 at which constant high pressure is applied through the first pilot line 46a is smaller than the second valve hydraulic pressure surface 54, the force acting on the second valve hydraulic pressure surface 54 is the first. It is larger than the force acting on the valve hydraulic pressure surface 52. Therefore, since the control valve 50 is switched to the second position Y and the second hydraulic line 48 is connected to the cylinder upper chamber 13a, high pressure is applied to the piston upper hydraulic pressure surface 24a.

On the other hand, although the high pressure is always applied to the cylinder chamber 13b through the first hydraulic line 47, the piston lower pressure receiving surface 22a is smaller than the piston upper pressure receiving surface 24a. Therefore, when the control valve 50 is switched to the second position (Y) and high pressure is applied to both the piston lower hydraulic pressure surface 22a and the piston upper hydraulic pressure surface 24a, the force acting on the piston upper hydraulic pressure surface 24a is reduced. Since the piston acts greater than the force acting on the lower pressure receiving surface 22a, the piston 20 does not rise again due to the downward force, and thus the lifting and lowering of the piston 20 is stopped, thereby preventing struck.

However, the hydraulic breaker having the above-described structure has an anti-ballast function in which the control valve 50 is switched to the second position (Y) when the chisel 30 is lowered to the free position (D) to suppress the rise of the piston 20. Since it is automatically activated, there is a problem that is automatically activated even when the anti-tagging function is not necessary according to the working environment. For example, in the case of tunnel or building crushing work, the hydraulic breaker is often operated in the upward or horizontal direction. When the anti-taking function is activated during the crushing work in the upward or horizontal direction, the operation of the hydraulic breaker is automatically performed. Will stop. Therefore, in order to restart the hydraulic breaker, the inconvenience of having to wait for a predetermined time by switching the hydraulic breaker back to the crushing posture.

The present invention is to solve the problems of the prior art described above is to provide a hydraulic breaker that can selectively activate the anti-static function according to the working environment to improve the work efficiency.

Hydraulic breaker according to the present invention for achieving the above object, the high pressure line and the low pressure line formed in the cylinder and connected to the external hydraulic pump, the mounting hole formed inside the cylinder, and the movable hole is movable An upper chamber and a lower chamber formed at upper and lower ends of the mounting hole and filled with oil for moving the piston, a low pressure chamber, a switching chamber, and an anti-ballout chamber formed at the middle of the mounting hole; And a back head and a front head respectively coupled to both ends of the cylinder, and chisels installed on the front head and hit by the piston.

In this case, a first flow path, one end of which is connected to the high pressure line and a second flow path, of which one end is connected to the anti-ballout chamber, is formed in the cylinder, and the first flow path and the second flow path are formed between the first flow path and the second flow path. An adjust is provided to connect or disconnect the second flow path.

The present invention configured as described above, by selectively supplying the oil introduced through the high-pressure line by the operation of the high pressure line to the anti-ballast prevention chamber can selectively activate the anti-ballout function. Therefore, depending on the working environment, it is possible to selectively activate the anti-static function, thereby improving work efficiency.

1 is a cross-sectional view of a hydraulic breaker according to an embodiment of the present invention.
Figure 2 is a perspective view of a cylinder of the hydraulic breaker according to an embodiment of the present invention.
3 is a plan view of a cylinder of the hydraulic breaker according to an embodiment of the present invention.
4 is a cross-sectional view taken along AA of FIG. 3.
5 is an enlarged view of a portion “B” of FIG. 3.
6 and 7 are a longitudinal cross-sectional view and a cross-sectional view of the cylinder of the hydraulic breaker according to another embodiment of the present invention.
8 and 9 are views showing a blow process of the hydraulic breaker according to an embodiment of the present invention.
10 and 11 are views showing a process of activating and deactivating the anti-ballout function of the hydraulic breaker according to an embodiment of the present invention.
12 is a schematic view of a hydraulic breaker with a general anti-seat function.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to the accompanying drawings, embodiments of the present invention will be described in detail. In the following description of embodiments according to the present invention, and in adding reference numerals to the components of each drawing, the same reference numerals are added to the same components as much as possible even though they are shown in different drawings.

1 is a cross-sectional view of a hydraulic breaker according to an embodiment of the present invention.

As shown in FIG. 1, the hydraulic breaker 100 according to the present embodiment includes a cylinder 110 provided with an anti-ballout function and an adjuster installed on the cylinder 110 to control the anti-ballout function (see FIG. 3). 120, the back head 130 coupled to the top of the cylinder 110, the front head 140 coupled to the bottom of the cylinder 110, and move inside the cylinder 110. It includes a piston 150 that can be installed, a chisel 160 that is movable in the front head 140, and a front cover 170 that is coupled to the lower end of the front head 140.

This embodiment configured as described above can be prevented by using the anti-ballet function provided in the cylinder (110). In particular, when operating the adjust 120, by selectively activating the anti-taking function can be allowed to allow or prevent the hit according to the working environment.

Looking at each component (110 ~ 170) of the hydraulic breaker 100 according to the present embodiment for selectively activating the anti-hit function as follows.

First, the cylinder 110 and the adjust 120 installed in the cylinder 110 will be described with reference to FIGS. 2 to 5.

2 is a perspective view of a cylinder of the hydraulic breaker according to an embodiment of the present invention, Figure 3 is a plan view of the cylinder of the hydraulic breaker according to an embodiment of the present invention, Figures 4 and 5 are AA cross-sectional view of FIG. It is an enlarged view of "B" part.

2 to 5, the cylinder 110 is a rectangular parallelepiped block having a predetermined length, and a mounting hole 112 is formed therein to allow the piston 150 to be movable. Around the mounting hole 112, a coupling hole 118 through which a fixing bolt (not shown) for coupling the back head (130 of FIG. 1) and the front head (140 of FIG. 1) to the cylinder 110 is formed. do. One side of the mounting hole 112 is formed with a high pressure line 114a through which high pressure oil is supplied and a low pressure line 114b through which oil is returned.

The upper inner wall of the mounting hole 112 is formed with an upper chamber 112a filled with oil to lower the piston 150, and the lower inner wall of the mounting hole 112 has oil to raise the piston 150. The lower chamber 112b to be filled is formed. In addition, a low pressure chamber 112c for supplying oil of low pressure, a switching chamber 112d for switching oil supply direction, and an anti-ball chamber 112e filled with oil for preventing an attack on the inner wall of the mounting hole 112. ) Are sequentially formed spaced apart from the upper portion of the mounting hole 112 by a predetermined interval. At this time, the upper chamber 112a, the lower chamber 112b and the anti-ballout chamber 112e of the chambers 112a to 112d formed on the inner wall of the mounting hole 112 are connected to the high pressure line 114a, and the low pressure chamber ( 112e is connected to the low pressure line 114b, and the switching chamber 112d is connected to the low pressure chamber 112e as the piston 150 moves.

In the above-described configuration, the anti-ballout chamber 112e is connected to the high pressure line 114a through the flow paths 116a and 116b and the connection port 116c formed in the cylinder 110, as shown in FIG. That is, the inside of the cylinder 110, the first end is connected to the first passage 116a connected to the high-pressure line (114a), the first end is connected to the anti-ballast chamber (112e) and arranged to cross the first passage (116a) Two flow paths 116b are formed. In addition, a connection port 116c is formed at a point where the first flow path 116a and the second flow path 116b cross each other, and the first flow path 116a and the second flow path 116a are formed inside the other end of the first flow path 116a. Manual adjust 120 is installed to selectively connect 116b. At this time, the thread is formed in the other end of the first passage 116a so that the manual adjust 120 can be screwed. In addition, the connection port 116c is formed in a tapered shape so as to prevent the internal pressure from changing rapidly during the process of connecting the first passage 116a and the second passage 116b.

The manual adjust 120 is formed in a spool shape having a plurality of stages so that one end thereof may be positioned at the connection port 116c while being inserted through the other end of the first flow passage 116a. One end of the manual adjust 120 is formed in a tapered shape corresponding to the shape of the connection port 116c, and a thread is formed on the outer peripheral surface of the other end so that the manual adjust 120 is screwed to the other end of the first flow passage 116a. To be possible. In addition, the other end of the manual adjust 120 is exposed to the outside of the cylinder 110 to enable the operator to operate from the outside of the hydraulic breaker (100).

According to the above structure, the operator can selectively activate the anti-rat function according to the working environment. In more detail, when the operator opens the connection port 116c by manipulating the manual adjust 120 exposed to the outside of the cylinder 110, the first flow path 116a and the second flow path 116b are formed. Since the high pressure oil connected through the high pressure line 114a is connected to the anti-ballout chamber 112e, the anti-ballout function can be activated. On the other hand, when the operator operates the manual adjust 120 to close the connection port 116c, the connection of the first flow path 116a and the second flow path 116b is blocked, so that it is supplied through the high pressure line 114a. Since the high pressure oil does not flow into the anti-ballout chamber 112e, the anti-ballout function may be deactivated, that is, the ball may be enabled.

6 and 7 are longitudinal cross-sectional views and cross-sectional views of a cylinder in the hydraulic breaker according to another embodiment of the present invention, with reference to FIGS. 6 and 7 of the adjuster 210 installed in the cylinder 210 and the cylinder 210. Looking at the embodiment as follows.

A mounting hole 212 is formed inside the cylinder 210, which is a cuboid block, to allow the piston 150 to be movable. A back head (130 of FIG. 1) and a front head are formed around the mounting hole 212. A coupling hole 218 for coupling with (140 in FIG. 1) is formed. One side of the mounting hole 212 is formed with a high pressure line 214a for supplying high pressure oil and a low pressure line 214b for returning oil.

An upper chamber 212a is formed on the upper inner wall of the mounting hole 212, a lower chamber 212b is formed on the lower inner wall of the mounting hole 212, and a low pressure chamber 212c and a switching chamber 212d are disposed on the middle wall of the mounting hole 212. And the anti-ballout chamber 212e is sequentially formed to be spaced apart from the upper portion of the mounting hole 212 by a predetermined interval. At this time, the upper chamber 212a, the lower chamber 212b and the anti-ballast chamber 212e are connected to the high pressure line 214a, the low pressure chamber 212e is connected to the low pressure line 214b, the switching chamber 212d Is connected to the low pressure chamber 212e according to the movement of the piston 150.

In the above-described configuration, the anti-ballout chamber 212e is connected to the high-pressure line 216a connected to the high-pressure line 214a and the second flow path 216b connected to the anti-ballout chamber 212e as shown in FIG. 6. 214a). At the point where the first passage 216a and the second passage 216b cross each other, an automatic adjust 220 for selectively connecting the first passage 216a and the second passage 216b is installed.

The automatic adjust 220 includes the flow path block 222 connected to the other end of the first flow path 216a and the other end of the second flow path 216b, and the first flow path 216a by opening or closing the flow path block 222. And a solenoid valve 224 for connecting or disconnecting the second flow path 216b and a switch (not shown) for remotely controlling the solenoid valve 224. Since the automatic adjust 220 of this configuration is operated by an electrical signal applied from the switch, when the switch is installed in the driver's seat, the operator can easily activate or deactivate the anti-taking function.

According to the above structure, the operator can selectively activate the anti-rat function according to the working environment. That is, when the operator operates the switch (not shown) installed in the driver's seat and the automatic adjuster 220 is turned on, the first passage 216a and the second passage 216b are connected to each other so that the high pressure line 214a is connected. The high pressure oil supplied through) is filled in the anti-ballout chamber 212e, so that the anti-ball function can be activated. On the other hand, when the operator operates the switch (not shown) and the automatic adjust 220 is turned off, the connection between the first flow path 216a and the second flow path 216b is cut off, and thus the high pressure line 214a Since the high pressure oil supplied through) does not flow into the anti-ballout chamber 212e, the anti-ball protection function can be deactivated.

Meanwhile, referring to FIG. 1, other components 130 to 170 of the hydraulic breaker 100 are as follows.

The back head 130 is a portion filled with a working gas for moving the piston 150. The back head 130 has a gas chamber 132 formed therein so that the working gas can be filled, so that the upper portion of the piston 150 can be inserted into the gas chamber 132 in a state coupled to the cylinder 110. The lower surface is formed to be open.

The front head 140 is a portion in which the piston 150 and the chisel 160 directly contact each other. An impact chamber 142 is formed inside the front head 140, and a ring bush 144 is provided on an inner wall of the impact chamber 142. In addition, the chisel pin 148 is provided at the lower portion of the impact chamber 142, the chisel pin 148 is to prevent the chisel 160 from protruding a predetermined length or more to the lower portion of the front head 140.

Piston 150 is a round rod having a constant length, the upper end is inserted into the gas chamber 132 of the back head 130, the suspension is located inside the cylinder 110, the lower end hitting the front head 140 It is inserted into the thread 142. At this time, the interruption of the piston 150 is formed with an annular groove 152 connecting the switching chamber 112d and the low pressure chamber 112c to be described later.

8 and 9 are views showing a blow process of the hydraulic breaker according to an embodiment of the present invention, Figures 10 and 11 are the activation and deactivation process of the anti-ballast function of the hydraulic breaker according to an embodiment of the present invention Figure is a diagram.

The high pressure oil compressed by the hydraulic pump (not shown) of the construction equipment is supplied into the hydraulic breaker 100 through the high pressure line 114a. When the valve 170 provided at the upper portion of the high pressure line 114a switches the supply direction, the high pressure oil filled on the high pressure line 114a is supplied to the lower chamber 112b, and the high pressure oil is supplied to the lower chamber 112b. When this is filled, the piston 150 is raised to compress the working gas charged in the gas chamber 132 (see FIG. 8).

When the piston 150 rises by a predetermined height or more through the above-described process, the direction of the valve 170 is switched to supply the high pressure oil supplied to the lower chamber 112b to the upper chamber 112a. Therefore, the piston 150 descends at a high speed and strikes the chisel 160 by the pressure of the working gas compressed in the gas chamber 132 and the pressure of the oil supplied to the upper chamber 112a (see FIG. 9).

On the other hand, in the hydraulic breaker 100 according to the present embodiment, the worker can selectively activate the anti-ballout function according to the working environment.

First, referring to FIG. 10, the process of activating and deactivating the anti-taking function using the manual adjust 120 is as follows.

Manual operator screwed to the other end of the first flow path (116a) when the operator rotates the manual adjust 120 exposed to the outside of the cylinder 110 in the arrow direction (c) shown in Figure 10 (a) Just 120 is released and opens the connection port 116c. When the connection port 116c is opened, the first flow path 116a and the second flow path 116b are connected, so that the high pressure oil supplied through the first flow path 116a passes through the second flow path 116b. It is charged to 112e. Therefore, the piston 150 is prevented from rising again due to the high pressure oil filled in the anti-air chamber 112e, thereby preventing the rising of the piston 150 (see FIG. 9).

On the other hand, when the operator rotates the manual adjust 120 exposed to the outside of the cylinder 110 in the arrow direction (d) shown in Figure 10 (b) is screwed to the other end of the first flow path (116a) The manual adjust 120 is tightened and closes the connection port 116c. When the connection port 116c is closed, the connection between the first flow path 116a and the second flow path 116b is blocked, so that the high pressure oil supplied through the first flow path 116a does not flow into the anti-ballout chamber 112e. I can't. Therefore, since the oil is not filled in the anti-ballout chamber 112e, the piston 150 may not be suppressed from rising so that the piston 150 may rise again to allow the ball to be hit (see FIG. 9).

Referring to FIG. 11, the process of activating and deactivating the anti-taking function using the automatic adjust 220 is as follows.

When the operator operates the switch (not shown) installed in the driver's seat, the automatic adjuster 220 is turned on, and the first flow path 216a and the second flow path 216b are connected to each other. Accordingly, since the high pressure oil supplied through the first passage 216a is filled in the anti-ballast chamber 212e via the second passage 216b, the piston (Fig. 2) is formed by the high pressure oil filled in the anti-ball chamber 112e. 8 of 150 is prevented from rising because the upward movement of the piston 150 is stopped by the upward downward force.

On the other hand, when the operator operates the switch (not shown) installed in the driver's seat, the automatic adjuster 220 is turned off, so that the connection between the first flow path 216a and the second flow path 216b is cut off. The high pressure oil supplied through the flow path 216a does not flow into the anti-ballout chamber 212e. Therefore, since the oil is not filled in the anti-ballout chamber 212e, the piston 150 may not be suppressed from rising, so that the piston 150 may rise again to allow the ball to be hit.

While the present invention has been particularly shown and described with reference to preferred embodiments thereof, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims. Those skilled in the art will understand. Therefore, the scope of protection of the present invention should be construed not only in the specific embodiments but also in the scope of claims, and all technical ideas within the scope of the same shall be construed as being included in the scope of the present invention.

100: hydraulic breaker 110: cylinder
112: space 112a: upper chamber
112b: lower chamber 112c: low pressure chamber
112d: switching chamber 112e: anti-ball chamber
114a: high pressure line 114b: low pressure line
116a: first euro 116b: second euro
116c: connection port 118: coupling hole
120: Adjust 130: Backhead
132: gas chamber 140: front head
142: batting chamber 144: ring bush
148: chisel pin 150: piston
152: fantasy groove 160: chisel
170: front cover 180: valve

Claims (6)

A high pressure line and a low pressure line formed in the cylinder and connected to an external hydraulic pump, a mounting hole formed in the cylinder, a piston movably installed in the mounting hole, and formed at upper and lower ends of the mounting hole. And an upper chamber and a lower chamber filled with oil for moving the piston, a low pressure chamber, a switching chamber and an anti-ball chamber formed at an interruption of the mounting hole, and a back head and a front head respectively coupled to both ends of the cylinder; In the hydraulic breaker comprising a chisel installed on the front head hit by the piston,
Inside the cylinder, a first flow path having one end connected to the high pressure line and a second flow path having one end connected to the anti-ballout chamber are formed.
An adjust is provided between the first channel and the second channel to connect or block the first channel and the second channel,
The hydraulic breaker, characterized in that to selectively activate the anti-ballast function by selectively supplying the oil introduced through the high pressure line by the operation of the anti-chamber chamber. The method according to claim 1,
The first flow path and the second flow path are arranged to cross each other, and a connection port is formed at a point where the first flow path and the second flow path cross each other.
And wherein the adjust connects or blocks the first flow path and the second flow path by opening or closing the connection port. The method according to claim 2,
The connection port is formed on the first flow path, and is formed in a tapered shape that the diameter increases toward the other end of the first flow path,
One end of the adjust is a hydraulic breaker, characterized in that formed in a tapered shape corresponding to the shape of the connection port. The method according to claim 2,
The adjuster is a hydraulic breaker, characterized in that screwed to the other end of the first passage. The method according to claim 1,
The adjust includes a flow path block connected to the other end of the first flow path and the other end of the second flow path, and a solenoid valve that connects or blocks the first flow path and the second flow path by opening or closing the flow path block. Hydraulic breaker, characterized in that. The method according to claim 5,
And a switch for remotely controlling the solenoid valve.

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