KR20160009216A - 3 step variable auto stroke hydraulic breaker - Google Patents

Abstract

The present invention relates to a three-step variable automatic stroke hydraulic breaker, which can reduce hitting energy reflected in case of an idle blow by subdividing a function of a stroke into a long stroke, a middle stroke, and a short stroke. The three-step variable automatic stroke hydraulic breaker comprises: a cylinder (201); a piston (202) accommodated in the cylinder (201); a pressure pipe (212) to provide operating pressure through an outlet connected to the cylinder (201); a decompression return pipe (217) to decompress pressure through the outlet connected to the cylinder (201); a control valve (209) wherein a control plunger (209a) is placed; a stroke valve (219) having a long stroke pipe (213), a middle stroke pipe (224), a short stroke pipe (216), and a preliminary control pressure pipe (225); and a spring (228) to change a position of the stroke valve (219).

Description

STEP VARIABLE AUTO STROKE HYDRAULIC BREAKER 3 STEP VARIABLE AUTO STROKE HYDRAULIC BREAKER

[0001] The present invention relates to a three-stage variable automatic stroke hydraulic breaker in which a stroke distance is automatically changed, and more particularly, to a hydraulic stroke breaker having a long stroke, , A middle stroke (S1), and a short stroke (S2), thereby reducing the striking energy reflected at the time of striking.

Generally, a hydraulic breaker is used to break the rock. Wherein the hydraulic breaker includes a housing and an accumulator having a reciprocating piston and a cylinder bore controlled by a dispense valve and wherein during operation of the hydraulic breaker the accumulator causes the hydraulic breaker to be damaged by the fluid cavity and pressure gradient Pressure to a pre-load pressure to increase the performance of the hydraulic breaker, and the stroke of the piston is transmitted to the chisel, whereby the chisel tip breaks the rock by the kinetic energy of the piston.

These hydraulic breakers are crushed in the case of a rock material with a weak material to be crushed and the remaining energy is applied to the hydraulic breaker part.

Thus, a process in which the applied kinetic energy is greater than the energy required for crushing is undesirable, because the crushing and residual energy causes high stresses in the hydraulic breaker. Therefore, rapid application of kinetic energy to all operating conditions is an important condition for optimal material crushing while extending the life of hydraulic breakers.

However, in the hydraulic breaker of the related art,

- continues to operate after it has been driven before reaching a level equal to or higher than the load pressure or when the hydraulic pressure has dropped below the pre-load pressure inside the accumulator. That is, the accumulator can not operate as desired, i. E. Can not absorb undesired pressure gradients, can not prevent cavities in the hydraulic fluid, and can not increase fluid flow during the operating stroke of the hammer piston. Thus, there is a serious risk that certain parts of the impact mechanism may be damaged.

To solve these problems, Korean Patent No. 10-1285062 has been proposed.

This prior art patent discloses a hydraulic pump comprising a housing 10 having a cylinder bore 11, a front operating chamber 23 and a rear operating chamber 18, a hydraulic fluid supply passage 26 continuously connected to the front operating chamber 23, A drain passage 33 connected to the chamber 18 and a hammer piston 12 reciprocally guided in the cylinder bore 11 for conveying the hammer blow to the operating mechanism 14 associated with the housing 10 , The rear operating chamber 18 is alternately connected to the drain passage 33 and the supply passage 26 so as to reciprocate the accumulator 27 and the hammer piston 12 preliminarily loaded to a certain pressure level By including the dispensing valve 30, the continuous valve 34 is provided in the drain passage 33 to maintain the pressure in the rear operating chamber 18 at a certain level, and the forward applied force is transmitted to the accumulator 27, Under a pressure less than the pre-loaded pressure level of the supply passage 26, The piston 12 is prevented from moving backward in the piston 11 and the striking energy caused by the striking action is reduced.

However, the prior art has a problem that it is still insufficient to lower the reflected striking energy due to the striking.

1. Korean Patent No. 10-1285062 "Hydraulic Shock Mechanism" (registered on Feb. 2013. 07. 04)

Accordingly, an object of the present invention is to solve the above-mentioned problems, and it is an object of the present invention to provide a three-stage variable automatic stroke in which the stroke distance is automatically variable and the crushing operation of the chisel is switched to three kinds of strokes The present invention is intended to provide a three-stage variable automatic stroke hydraulic breaker to be operated.

A three-stage variable automatic stroke hydraulic breaker according to the present invention comprises: a cylinder; A first piston surface received in the cylinder and axially reciprocated therein and oriented such that an applied pressure acts in a return stroke direction, a second piston surface oriented so that the applied pressure acts in the actuation stroke direction, A piston having a circumferential groove positioned between the first piston surface and the second piston surface; A pressure conduit for providing an operating pressure through an outlet connected to the cylinder; A reduced pressure return conduit for reducing pressure through an outlet connected to the cylinder; A control valve having a control plunger located therein and having a small control plunger face for delivering said control plunger to a return stroke position and a large control plunger face for delivering said control plunger to an actuation stroke position and a return stroke position; And a large stroke plunger surface connected to the control valve and located within the stroke plunger and connected to the cylinder via a first reserve control conduit by a first preliminary control reset conduit, 2 a small stroke plunger face connected to the cylinder through a spare control conduit, a long stroke conduit for operating the piston with a long stroke, a middle stroke conduit for operating the piston with a middle stroke, And a spring for converting the position of the valve of the stroke valve, wherein the stroke control valve is connected to the pressure conduit and has a preliminary control pressure conduit for applying pressure to the stroke conduit.

As described above, according to the three-stage variable automatic stroke hydraulic breaker of the present invention, since the crushing operation of the chisel is switched to three kinds of strokes according to the characteristics of the rock, the stroke range is widened, There is an advantage.

In addition, there is an advantage that the life of the hydraulic breaker is extended in order to lower the striking energy remaining by shortening the stroke at the time of blanking.

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a diagrammatic representation of a conventional hydraulic impact mechanism.
2 is a schematic view of a hydraulic impact mechanism of a normally three-stage variable-stroke hydraulic breaker according to the present invention.
3 is a hydraulic shock mechanism view of a three-stage variable automatic stroke hydraulic breaker during a long stroke.
Fig. 4 is a hydraulic shock mechanism diagram of a three-stage variable-stroke hydraulic breaker at the middle stroke. Fig.
5 is a hydraulic shock mechanism view of a three-stage variable-stroke hydraulic breaker in a short stroke.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS [0028] Hereinafter, a three-stage variable-stroke hydraulic breaker according to the present invention will be described in detail with reference to the accompanying drawings. In the following description of the present invention, a detailed description of known functions and configurations incorporated herein will be omitted when it may make the subject matter of the present invention rather unclear. The following terms are defined in consideration of the functions of the present invention, and they may vary depending on the intentions or customs of the client, the operator, the user, and the like. Therefore, the definition should be based on the contents throughout this specification.

Like numbers refer to like elements throughout the drawings.

Fig. 2 is a diagram showing a hydraulic impact mechanism of a normally three-stage variable automatic stroke hydraulic breaker according to the present invention, Fig. 3 is a hydraulic shock mechanism of a three-stage variable automatic stroke hydraulic breaker at a long stroke, FIG. 5 is a hydraulic shock mechanism view of a three-stage variable-stroke automatic hydraulic breaker during a short stroke; FIG. 5 is a hydraulic shock mechanism view of a three-stage variable automatic stroke hydraulic breaker during a short stroke;

3-stage Variable Auto Stroke Hydraulic Shock Mechanism of Hydraulic Breaker (see FIG. 2)

A normal three-stage variable-stroke hydraulic breaker 200 according to the present invention includes a cylinder 201 and a piston 202 received in the cylinder 201 and axially reciprocated therein. The piston 202 is provided with a rear guide portion and a front guide portion 204, 205 separated from each other by a circumferential groove 203. First and second piston surfaces 202a and 202b directed outwardly of the circumferential groove 203 define the rear and front cylinder chamber sections 206 and 207, respectively. Here, the area of the first piston surface 202a is smaller than the area of the second piston surface 202b. Further, the operation of the piston 202 in the direction of the front stroke is as indicated by a thick arrow.

An operating mechanism such as a chisel 208 is attached to an end of the piston 202. When a normal operation is performed, that is, when the chisel 208 does not penetrate the rock mass to be crushed, The piston 202 assumes the normal impact position.

The control device for switching the operation of the piston (202) includes a control plunger (209a) movable within the control valve (209). The control plunger 209a has a small control plunger surface 209b and a large control plunger surface 209c that are continuously exposed to the operating pressure by the reset conduit 210. The control plunger surface 209a is shown in FIG. The operating pressure is generated by the hydraulic pump 211. The first piston surface 202a is also continuously exposed to operating pressure by the pressure conduit 212 in communication with the reset conduit 210. [ The outlet 212a of the pressure conduit 212 is always disposed with respect to the cylinder 201 so as to be located in the front cylinder chamber portion 207. [

The large control plunger surface 209c of the control plunger 209a is connected to the cylinder 201 by the long stroke conduit 213 through the circumferential groove 203 in the normal operating state.

The control valve 209 is connected to the pressure conduit 212 on the one hand by a control conduit 214 and to the tank 216 on the other hand via a return conduit 215, And the outlet 217a is connected to the cylinder 201 by the reduced pressure return conduit 217 through the circumferential groove 203. [ The outlet 217a of the reduced pressure return conduit 217 and the outlet 213a of the long stroke conduit 213 are spaced apart from each other by a distance smaller than the axial length of the circumferential groove 203. [

The control valve 209 is also connected to the rear cylinder chamber portion 206 by an alternating pressure conduit 218. The second piston surface 202b is adapted to be exposed to an operating pressure that can be supplied to the rear cylinder chamber portion 206 by the alternate pressure conduit 218. [

The control valve 209 can take two valve positions. That is, the return stroke position (lower) where the second piston surface 202b is depressurized through the alternating pressure conduit 218 and the return conduit 215 and the rear cylinder chamber portion 206 are connected to the pressure conduit 212, (Upper side) in which the operating pressure is applied by the control conduit 214 connected to the control valve 212 and the alternate pressure conduit 218. As a result of this operating condition, the piston 202 actuates the actuation stroke in the direction of the thick arrow against the reset force exerted on the first piston surface 202a.

On the other hand, the hydraulic breaker 200 according to the present invention includes a stroke valve 219 capable of taking a position of a long stroke, a position of a middle stroke, and a short stroke position.

The stroke valve 219 includes a stroke plunger 219a that can move within the stroke valve 219. [ The stroke plunger 219a has a large stroke plunger surface 219b and a small stroke plunger surface 219c.

The position of the stroke valve 219 is determined by the pressure applied to the large stroke plunger surface 219b and the small stroke plunger surface 219c. The large stroke plunger surface 219b is connected to the cylinder 201 via a first preliminary control conduit 221 by a first preliminary control reset conduit 220. The outlet 221a of the first preliminary control conduit 221 is positioned behind the outlet 213a of the long stroke conduit 213 in the direction of the operating stroke (bold arrow). The first preliminary control conduit 221 is connected to the output side of the stroke valve 219 by a first preliminary control branch conduit 221b.

The small stroke plunger surface 219c of the stroke plunger 219a is connected to the cylinder 201 via the second reserve control conduit 223 by the second preliminary control reset conduit 222. [ The outlet 223a of the second reserve control conduit 223 is located behind the outlet 224a of the middle stroke conduit 224 in the direction of the operating stroke (bold arrow). The second preliminary control conduit 223 is connected to the output side of the stroke valve 219 by a second preliminary control branch conduit 223b.

The stroke plunger 219a is connected to the pressure conduit 212 through a preliminary control pressure conduit 225. [ Accordingly, the stroke plunger 219a is continuously exposed to the operating pressure, and the stroke valve 219 tries to assume the open position under the influence of the resetting pressure applied to the stroke plunger 219a.

On the input side of the stroke valve 219 is connected to the cylinder 201 by means of a short stroke conduit 226 with a middle stroke conduit 224 having an outlet 224a and an outlet 226a on the one hand, Is connected to the pressure conduit 212 through the preliminary control pressure conduit 225. [ The outlet 226a of the short stroke conduit 226 is located behind the outlet 223a of the second preliminary control conduit 223 in the direction of the operating stroke (bold arrow).

The output side of the stroke valve 219 is connected to the first and second preliminary control conduits 221 and 223 on the one hand by first and second preliminary control branch conduits 221b and 223b and on the other hand, Is connected to the long stroke conduit 213 for the control valve 209 by a conduit 227 of the control valve 209.

Since no pressure is applied to the first preliminary control reset conduit 220 and the second preliminary control reset conduit 222 in the initial state of the hydraulic breaker, the elastic force of the spring 228 on both sides of the stroke valve 219 causes the stroke valve 219) is at the intermediate position (second position) (state of FIG. 2). That is, due to the open state of the short stroke conduit 226, a short stroke operation is started.

The hydraulic shock mechanism of the three-stage variable automatic stroke hydraulic breaker at the time of a long stroke (see FIG. 3)

If the chisel 208 does not penetrate into the rock mass to be crushed, the following operation steps occur.

When the piston 202 rises to the short stroke due to the state of the stroke valve 219 in the neutral position (second position), the large control plunger 209 of the control valve 209, through the short stroke conduit 226 and the stroke valve 219, The control valve 209 is changed (valve open) by pressing the surface 209c and the first preliminary control branch conduit 221b and the second preliminary control branch conduit 223b of the stroke valve 219 are opened And pressurized by the stroke plunger bottom surface 219b and the small stroke plunger surface 219c. However, the stroke valve 219 comes to the closed position due to the difference in the pressurized area.

After the control valve 209 is switched to the operating stroke position, the operation of the piston 202 starts in the direction of the operating stroke (bold arrow). At this time, the stroke valve 219 takes the illustrated closed position and the closed position is maintained by the pressure exerted by the preliminary control pressure conduit 225 connected to the pressure conduit 212.

Here, when the piston 202 impacts the chisel 208, the long stroke conduit 213 is depressurized through the circumferential groove 203 and the reduced pressure return conduit 217, and as a result, the control plunger 213 of the control valve 209 The piston 209a is switched to the return stroke position under the influence of the return force generated on the small control plunger surface 209b to start the return stroke of the piston 203. [

In this case, since the piston 202 is not separated from the upper surface of the chisel 208 which collides with the chisel 208, the outlet 221a of the first preliminary control conduit 221 is closed by the front interior 205 State. The piston 202 performs a return stroke while the reduced pressure return conduit 217 is connected to the pressure conduit 212 through the front cylinder chamber portion 207 through the outlet 217a. Thus, an operating pressure is applied to the large control plunger surface 209C and accordingly the control plunger 209a is moved into the operating stroke position where the rear cylinder chamber portion 206 is connected to the pressure conduit (not shown) via the control conduit 214 212 and thus initiates a new actuation stroke. At this time, a setting force is generated in the direction of the long stroke position, and is blocked in the direction of the middle stroke position and the short stroke position. Accordingly, the hydraulic shock mechanism of the three-stage variable-stroke automatic hydraulic breaker according to the present invention is in a state of a long stroke.

The hydraulic shock mechanism of the three-stage variable automatic stroke hydraulic breaker at the middle stroke (see FIG. 4)

When the chisel 208 penetrates into the rock mass to be ground, the following operation steps occur.

After switching the control valve 209 to the operating stroke position and switching the stroke valve 219 to the closed position, the piston 202 first performs the operating stroke. If, during the execution of this operating stroke, the chisel 208 penetrates into the rock mass to be ground, the piston 202 leaves the normal impact surface and takes the advanced position along the chisel 208. As a result of this movement, the outlet 221a of the first preliminary control conduit 221 closed by the front guide portion 205 is opened and the hydraulic connection formed through the circumferential groove 203 and the reduced pressure return conduit 217 . Thus, the stroke valve 219 is switched from the closed position to the open position (state of FIG. 4), whereby the middle stroke conduit 224 is connected to the additional conduit 227, The pressure is reduced through the stroke conduit 213, the circumferential groove 203, and the reduced pressure return conduit 217. By this depressurization, the control valve 209 is also switched to the return stroke position, and accordingly, the piston 202 executes the return stroke. At this time, the outlet 224a of the middle stroke conduit 224 is opened and connected to the pressure conduit 212 through the front cylinder chamber portion 207. Thus, as the control valve 209 connected to the additional conduit 227 is also pressurized, the valve is switched to switch from the middle stroke position to the operating stroke position before the maximum possible stroke is reached, and the operating stroke is initiated. Also, the large stroke plunger surface 219b is exposed to pressure through the first preliminary control branch conduit 221b connected to the middle stroke conduit 224 exposed to the operating pressure, and the first preliminary control conduit 221. [ The small stroke plunger surface 219c is also exposed to pressure through the preliminary control pressure conduit 225 connected to the stroke valve 219. [ However, since the large stroke plunger surface 219b has a larger hydraulic pressure area than the small stroke plunger surface 219c, the stroke valve 219 is converted back to the closed position (first position).

Thereby enabling the piston 202 to respond to the characteristics or behavior of the rock mass to be crushed upon each hit to the chisel 208. When the chisel 208 penetrates into the rock mass to be crushed, the piston performs only the middle stroke so that the individual strike energy is low. If the chisel 208 does not penetrate into the rock mass to be ground, a long stroke is performed with the maximum individual strike energy accordingly.

The hydraulic shock mechanism of the three-stage variable automatic stroke hydraulic breaker in the short stroke (see Fig. 5)

When the chisel 208 penetrates deep into the rock, the following operation steps occur.

After switching the control valve 209 to the operating stroke position and switching the stroke valve 219 to the closed position, the piston 202 first performs the operating stroke. If the chisel 208 penetrates deep into the rock mass to be crushed during the execution of this operating stroke, the piston 202 takes the advanced position along the chisel 208 leaving the normal impact surface. As a result of this movement, the outlet 221a of the first preliminary control conduit 221 closed by the front guide 205 is opened and the outlet 223a of the second preliminary control conduit 223 is also opened The circumferential groove 203, and the reduced-pressure return conduit 217. The pressure- Thus, the stroke valve 219 is switched from the closed position to the open position (second position), whereby the short stroke conduit 226 is connected to the additional conduit 227 and the further conduit 227 is connected to the long stroke Through the conduit 213, the circumferential groove 203, and the reduced pressure return conduit 217. By this depressurization, the control valve 209 is also switched to the return stroke position, and accordingly, the piston 202 executes the return stroke. At this time, the outlet 226a of the short stroke conduit 226 is opened and connected to the pressure conduit 212 through the front cylinder chamber portion 207. The first preliminary control branch conduit 221b, the first preliminary control conduit 221, the second preliminary control branch conduit 223b, the second preliminary control conduit 223 The additional conduit 227 and the long stroke conduit 213 are exposed to pressure through the stroke valve 219 and as a result the control valve 209 is moved to the operating stroke position < RTI ID = 0.0 > And an operation stroke is started. Simultaneously, the large stroke plunger surface 219b of the stroke valve 219 is moved to the closed position shown against the return force exerted on the small stroke plunger surface 219c.

Thereby enabling the piston 202 to respond to the depth of penetration of the rock mass to be crushed upon each hit to the chisel 208. That is, when the chisel 208 penetrates deep into the rock mass to be crushed, the piston performs only the short stroke so that the individual strike energy is low. If the chisel 208 does not penetrate into the rock mass to be ground, a long stroke is performed with the maximum individual strike energy accordingly. Further, when the chisel 208 penetrates into the rock mass to be crushed, the middle stroke is executed with the maximum individual stroke energy.

Reference numeral 228 denotes a spring which is provided on a large stroke plunger surface 219b and a small stroke plunger surface 219c of the stroke valve 219, respectively, to give a mechanical resetting function in response to a change in hydraulic pressure.

As described above, the three-stage variable automatic stroke hydraulic breaker according to the present invention improves the working efficiency because the crushing operation of the chisel is switched to the three kinds of strokes according to the characteristics of the rock, and the stroke range is widened. In addition, the life of the hydraulic breaker is extended to reduce the reflected striking energy by shortening the strokes when the strikes are performed.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is to be understood that the invention is not limited to the disclosed exemplary embodiments, but, on the contrary, Various changes, modifications or adjustments to the example will be possible. Therefore, the scope of protection of the present invention should be construed as including all changes, modifications, and adjustments that fall within the spirit of the technical idea of the present invention.

201: cylinder 202: piston
202a: first piston surface 202b: second piston surface
203: Circumferential groove 204: Rear inner
205: front chamber interior 206: rear cylinder
207: front cylinder 208: chisel
209: Control valve 209a: Control plunger
209b: small control plunger surface 209c: large control plunger surface
210: reset conduit 211: hydraulic pump
212: pressure conduit 212a: pressure conduit outlet
213: Long stroke conduit 213a: Long stroke conduit outlet
214: control conduit 215: return conduit
216: tank 217: reduced pressure return conduit
217a: decompression return conduit outlet 218: alternating pressure conduit
219: Stroke valve 219a: Stroke plunger
219b: large stroke plunger surface 219c: small stroke plunger surface
220: first preliminary control reset conduit 221: first preliminary control conduit
221a: first preliminary control conduit outlet 221b: first preliminary control branch conduit
222: second preliminary control reset conduit 223: second preliminary control conduit
223a: second preliminary control conduit outlet 223b: second preliminary control branch conduit
224: Middle Stroke Conduit 224a: Middle Stroke Conduit Exit
225: reserve control pressure conduit 226: short stroke conduit
226a: Short stroke conduit outlet 227: Additional conduit
228: Spring

Claims (3)

A cylinder 201;
A first piston surface 202a received in the cylinder 201 and axially reciprocated therein and oriented so that an applied pressure acts in the direction of the return stroke, and a second piston surface 202a oriented so that the applied pressure acts in the actuation stroke direction A piston 202 having a second piston surface 202b and a circumferential groove 203 positioned between the first piston surface 202a and the second piston surface 202b;
A pressure conduit (212) for providing an operating pressure through an outlet connected to said cylinder (201);
A reduced pressure return conduit (217) for reducing pressure through an outlet connected to the cylinder (201);
A small control plunger surface 209b for controlling the control plunger 209a and for sending the control plunger 209a to the return stroke position and a control plunger surface 209b for returning the control plunger 209a to the operating stroke position and return stroke position, A control valve 209 having a large control plunger surface 209c;
Which is connected to the control valve 209 and in which the stroke plunger 209a is located and which is connected to the cylinder 201 via the first preliminary control conduit 221 by the first preliminary control reset conduit 220, A small stroke plunger surface 219c connected to the cylinder 201 via a second preliminary control conduit 223 by a second preliminary control reset conduit 222 and a small stroke plunger surface 219c connected to the cylinder 201 via a second pre- A long stroke conduit 213 for operating the piston 202 in a long stroke, a middle stroke conduit 224 for operating the piston 202 in a middle stroke, a short stroke conduit 224 for operating the piston 202 in a short stroke, (216), and a pre-control pressure conduit (225) connected to the pressure conduit (212) for applying pressure thereto; And
And a spring (228) for changing the position of the valve of the stroke valve (219).
The method according to claim 1,
The stroke valve 219 is located between the control valve 209 and the cylinder 201 and the position of the stroke valve 219 is controlled by the pressure applied to the large stroke plunger surface 219b and the small stroke plunger surface 219c , And the piston (202) is divided into a long stroke, a middle stroke, and a short stroke by sensing the position of the piston (202).
The method according to claim 1,
The outlet 217a of the decompression return conduit 217, the outlet 213a of the long stroke conduit 213, the outlet 224a of the middle stroke conduit 224, the outlet 226a of the short stroke conduit 226 Is located at the outlet 213a of the long stroke conduit 213 behind the outlet 217a of the reduced pressure return conduit 217 as viewed in the direction of the front stroke of the piston 202, An outlet 224a of the middle stroke conduit 224 is located after the outlet 213a and an outlet 226a of the short stroke conduit 226 is positioned behind the cylinder 201, Wherein the hydraulic breaker is formed to be connected to the inside of the hydraulic motor.

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