KR101684930B1 - Double Piston Pile driver having a circular crank room - Google Patents

Abstract

The present invention relates to a double piston pile driver including a circular crank room. According to the present invention, the double piston pile driver promotes the simplification of a manufacturing process and the miniaturization thereof by forming a crank room in a circular shape, secures large output stability through a low vibration operation using a double piston, and multiply performs a pneumatic pile function and a function for shaking off a crop by using a reciprocating transfer force. To this end, the double piston pile driver comprises: a crank shaft (1), a crank room (2), a pneumatic piston (10), a weight piston (14), a cancelling piston (20), a crank wheel (30), and a bearing housing (34) as main configurations.

Description

[0001] The present invention relates to a double piston piston having a circular crank chamber,

[0001] The present invention relates to a double piston caster having a circular crank chamber, more specifically, a crank chamber is formed in a circular shape to simplify and miniaturize the manufacturing process, and a high output safety is secured by a low vibration operation using a double piston, And a circular crank chamber for performing a combined function of crop hairs using a reciprocating feed force.

In general, a hanger is a hammer type device that applies a continuous load to crush a file or the like, and the hammer connected to the connecting rod is linearly reciprocated mainly by the eccentric rotational force of the crank shaft, Or a wedge bar is provided at the front of the hammer to crush the crushed material. However, since the hammer directly impacts on the impacted object to generate striking force, the lifetime of the equipment is greatly shortened due to the fatigue load.

Conventional Utility Model Registration No. 20-233200 discloses a technique of transmitting a strong impact force to a pile at a high speed by utilizing the rotational operation force of the exhaust type engine using the organic operation principle of the crankshaft, the connecting rod, the compression piston and the impact piston Technology has been pre-registered.

However, in the related art, the vibration force is severely generated due to the eccentric rotational force of the crankshaft due to the eccentric rotational force of the crankshaft and the reciprocating linear motion of the single connecting rod, and the vibratory force is increased in proportion to the engine rotational speed. There is a limit to the.

In addition, although the compression force is increased as the piston stroke is longer, since the rotation force of the crank arm and the turning radius of the crank arm are increased together, the size of the equipment is inevitably increased. Therefore, considering the portability, The size of the equipment was increased when designing, and the portability was poor.

SUMMARY OF THE INVENTION Accordingly, the present invention has been made to solve the above-mentioned problems, and it is an object of the present invention to provide a crankcase having a circular shape to simplify and miniaturize the manufacturing process, And to provide a double-piston hermetic device having a circular crank chamber that combines the functions of a crop hull using force.

To achieve this object, a feature of the invention is a pneumatic piston (10) which is connected to the crankshaft (1) in the crankcase (2) and in which compression and suction pneumatic pressures are generated in the cylinder A weight piston 14 which is reciprocally transported in the cylinder 12 by a pneumatic piston 10 to provide a striking force and a piston 14 which is connected to the crankshaft 1 and which is connected to the pneumatic piston 10 The crankshaft 1 is connected to the crankshaft 1 so that the crankshaft 1 is rotated and the crankshaft 1 is rotated. The crankshaft 1 is rotated at 180 ° so that the pneumatic piston 10 and the canceling piston 20 are connected to both ends thereof. A crank wheel 30 provided with a pair of crank pins 32 and 32 'forming a crank angle; A bearing housing (34) installed in the crank chamber (2) and rotatably supporting the crank wheel (30); The crankcase 2 is formed with a circular tube portion 3 on the inner circumferential surface thereof and the outer circumferential surface of the bearing housing 34 is machined in the same manner as the circular tube portion 3.

At this time, in the crank chamber 2, the inner space is divided into two by the bearing housing 34 so that the cylinder 12 is communicated with a position corresponding to one inner space, and in the position corresponding to the other inner space, (22) are communicated with each other.

At least one pinhole 33 is formed in the crank wheel 30 at a position corresponding to the crank pin and the crank pin engaged with the pinhole 33 is integrally formed with the crank arm 1a of the crankshaft 1 And a bearing B for supporting a connecting rod 11 connected to the pneumatic piston 10 is inserted into the pin hole 33 so as to be fitted into the pin hole 33. [

An intake hole 40 is formed in the operating section of the weight piston 14 to supply outside air into the cylinder 12 and the intake hole 40 is formed in a position where the pneumatic piston 10 reaches the bottom dead center So that external air can be sucked into the cylinder (12) while the weight piston (14) passes through the intake hole (40) at a time when no compressed air pressure is further increased in the cylinder (12).

A charging hole 50 for supplying external air into the cylinder 12 is formed at a time point when the pneumatic piston 10 is changed from the bottom dead center to the top dead center and suction air pressure acts on the cylinder 12 .

The suction hole 40 and the filling hole 50 are formed so that the direction of air movement is changed through the flow path 62 between the sleeves 60 provided on the outer circumferential surface of the cylinder 12, And purge air is supplied or communicated with the inside of the crank chamber 2 through the extension passage 63 and the handle grip portion 64 is provided on the surface of the sleeve 60. [

The striking rod 70 is provided at the front of the weight piston 14 to transmit a striking force of the weight piston 14 and a hammer H or a wedge W is provided at an end of the striking rod 70 .

A conical protrusion 70a is formed at an end of the hitting rod 70 and is fitted into a conical groove 70b formed in the hammer H or the wedge W. The conical protrusion 70a and the groove 70b are engaged with each other, Is characterized in that it is provided so as to have fluidity in the striking force transmitting direction by engagement of the fixing pin (72) and the long hole (74).

A high work table 80 is also provided which includes a joint portion 82 which is fastened to one side of the barrel body including the cylinder 12 and an extension bar 84 which is connected to the joint portion 82 .

A ring glove 14b is formed so that the weight piston 14 is provided with a base mill 14a for air tightness between the inner wall of the cylinder 12 and the ring glove 14b is formed with an expanded width And the inclined surface 14c is formed so that the diameter increases as the striking force is applied.

The crankshaft 1 is supported on both sides by the main housing 90 and the auxiliary housing 92 and is rotated about the crankshaft 1 between the main housing 90 and the auxiliary housing 92 A drive shaft 96 to which external power is connected is installed in the fluid housing 94 and the drive shaft 96 and the crankshaft 1 are driven by a gear assembly at a predetermined inclination angle .

The crankshaft 1 is driven by an output of a speed reducer 99 for reducing a DC motor 98 rotating at 1 to 30,000 RPM at a ratio of 6 to 8: 1.

The offsetting piston (20) is characterized in that the joint portion (24) is provided at the end of the offset piston (20) so that the vibration transmitting means (26) including the shaking table for harvesting the crop can be detachably attached.

According to the above structure and operation, since the round tube portion of the crank chamber and the corresponding end portions of the bearing housing have the same curvature as that of the circular tube portion, when the bearing housing is assembled, the round tube portions and the rounded surfaces of both ends of the bearing housing are tight The bearing housing is positioned at the center of the circular tube portion, so that the bearing housing is prevented from tilting and flowing right and left, and precision assembly is achieved by an unskilled worker.

The pneumatic piston and the canceling piston are reciprocated in the opposite direction by a pair of crank pins constituting the crank angle of 180 °, so that the work of the hinges and the crop hairs are combined and the vibration is canceled to secure the high output long working safety It is effective.

Further, the crank wheel is rotated at a predetermined position by the crankshaft, and the connecting rod is connected to a pair of crank pins forming a crank angle of 180 ° on the crank wheel so that the pneumatic piston and the offset piston reciprocate in a reciprocating linear motion The diameter of the crank pin can be downsized, and the radius of rotation of the crank pin eccentricity relative to the stroke of the crank pin is reduced.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a view entirely showing an internal structure of a double piston hermitage having a circular crank chamber according to an embodiment of the present invention; FIG.
BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a double-piston hermetic compressor, and more particularly, to a double piston hermetic compressor having a circular crankcase.
BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a double-piston hermetic compressor, and more particularly, to a double piston hermetic compressor having a circular crankcase.
FIG. 4 is a view showing an operation state of an intake hole of a double piston hermitage having a circular crank chamber according to an embodiment of the present invention; FIG.
FIG. 5 is a view showing a state in which a weight piston of a double piston hermitage having a circular crank chamber according to an embodiment of the present invention is pushed by a hitting rod and moved upward; FIG.
FIG. 6 is a view showing a state of operation of a filling hole of a double piston hermitage having a circular crank chamber according to an embodiment of the present invention; FIG.
FIG. 7 is a view showing a sleeve of a double piston hermitage having a circular crank chamber according to an embodiment of the present invention; FIG.
FIG. 8 is a view showing the elevating table of a double piston hanger having a round crank chamber according to an embodiment of the present invention; FIG.
9 is a view showing a ring glove of a double piston hermitage having a circular crank chamber according to an embodiment of the present invention.
10 is a view showing a state in which a hammer or a wedge is applied to a hitting rod of a double piston hermitage having a circular crank chamber according to an embodiment of the present invention.
FIG. 11 is a view showing a structure for transmitting a striking force through a hitting rod of a double piston hanger having a circular crank chamber according to an embodiment of the present invention. FIG.
12 is a view showing a state in which a motor and a speed reducer are applied as a power source to a double piston hermitage having a circular crank chamber according to an embodiment of the present invention.
13 is a view showing a vibration transmitting means using a crop hull of a double piston hermitage having a circular crank chamber according to an embodiment of the present invention.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

The present invention relates to a double piston caster having a circular crank chamber. In this case, the crane chamber is formed in a circular shape to simplify and miniaturize the manufacturing process. In addition, since a high output safety is secured by a low vibration operation using a double piston, The crank chamber 2, the pneumatic piston 10, the weight piston 14, the offset piston 20, the crank wheel 30, and the crankshaft 30 in order to perform the function of the crop hull using the reciprocating transfer force. , And a bearing housing (34).

A double piston hose with a circular crankcase according to the present invention is connected to a crankshaft 1 in a crankcase 2 and is connected to a pneumatic piston 1 in which compression and suction pneumatic pressures are generated in the cylinder 12 by linear reciprocating transfer (10), a pneumatic piston (10) reciprocally reciprocated in the cylinder (12) by a pneumatic pressure and providing a striking force, a piston connected to the crankshaft (1) (20) reciprocatingly reciprocated with respect to the piston (10).

That is, the pneumatic piston 10 is connected to the crankpin through the connecting rod and is linearly reciprocated within the cylinder 12. At this time, due to compression and suction pneumatic pressure generated in the cylinder 12, And is linearly reciprocated within the cylinder 12.

3 (a), suction pneumatic pressure acts on the inside of the cylinder 12 when the pneumatic piston 10 is transferred to the top dead center so that the weight piston 14 moves to the top dead center, When the pneumatic piston 10 changes direction and moves to the bottom dead point, compressed air pressure acts on the inside of the cylinder 12. At this time, the weight piston 14 moves to the bottom dead point by the compressed air pressure acting inside the cylinder 12, And the striking force is continuously generated by the repetitive operation of the pneumatic piston 10 and the weight piston 14.

The striking rod 70 is provided at the front of the weight piston 14 to transmit a striking force of the weight piston 14 and a hammer H or a wedge W is provided at an end of the striking rod 70 do. A multi-cap is interchangeably fastened to the lower portion of the cylinder 12 where the weight piston 14 is installed and the striking rod 70 is linearly reciprocated in the direction of movement of the weight piston 14 in the multi- .

As shown in FIG. 10, a hitting rod 70 equipped with a hammer H is mounted and used in a hemming operation, and a hitting rod 70 installed in a wedge W is replaced in a rock crushing operation do. Alternatively, the hammer H or the wedge W may be provided at the end of the hitting rod 70 in a replaceable manner.

A conical protrusion 70a is formed at an end of the impact rod 70 and is fitted into a conical groove 70b formed in the hammer H or the wedge W. The conical protrusion 70a and the groove 70b are engaged with each other, Is provided so as to have fluidity in the striking force transmitting direction by engagement of the fixing pin (72) and the long hole (74). 11, the long hole 74 is extended in the striking force transmitting direction of the striking rod 70, and the hammer H or the wedge W coupled to the striking rod 70 by engagement with the striking pin 72, The striking load of the striking rod 70 is not directly transmitted to the fixing pin 72 side.

As the cone-shaped protrusions 70a and the grooves 70b increase the impact force transmitting area transmitted from the tactile rod to the hammer H or the wedge W, the deformation of the impact rod 70 is prevented, The fixing pin 72 can secure the fluidity within the elongated hole 74 and prevent the fixing pin 72 from being bent or broken due to the hitting force.

The canceling piston 20 is installed on a crank pin 32 to which the pneumatic piston 10 is connected and another crank pin 32 'provided with a crank angle of 180 °, So as to cancel out the vibration force generated in the pneumatic piston (10) while being reciprocated in the opposite direction. 1, the canceling piston 20 is connected to a crank pin 32 'through a connecting rod and extends in a direction opposite to the stroke direction of the pneumatic piston 10, that is, And is reciprocated.

When the pair of crank pins 32 and 32 'are eccentrically rotated, the pneumatic piston 10 and the canceling piston 20 reciprocate in the opposite directions to each other in a linear reciprocating motion, thereby canceling the vibration force and advantageously reducing fatigue for long- .

On the other hand, the expansion cylinder 22 in which the canceling piston 20 is accommodated is provided so as to be openable and closable by a cap, and the cap is separated from the vibration transmitting means 70 to be described later when used.

In Fig. 13, the canceling piston 20 is provided with the joint portion 24 so that the vibration transmitting means 26 including the shaking table for harvesting the crop can be detachably attached to the end thereof. The vibration transmitting means 26 is formed in a rod shape and has a fastening portion at one end to be fastened to the joint portion 24 and a fastening groove to be fitted to the fruit water at the other end.

The vibration transmitting means 26 is coupled to the joint portion 24 of the canceling piston 20 and the crankshaft 1 is rotated with the vibration transmitting means 26 sandwiched between the fruit juices including the jujubes, 20 is used as a vibrating working machine for shaking off the jujube while being linearly reciprocatingly conveyed by the vibration transmitting means 26. At this time, due to the reciprocating linear reciprocating force of the compression and offset pistons 10, 20, Is reduced, and there is an advantage that the elderly person can carry out the portable operation.

The crank wheel 30 according to the present invention is connected to the crankshaft 1 so as to rotate and has a pair of crankshafts 180 at a crank angle of 180 to connect the pneumatic piston 10 and the canceling piston 20 at both ends thereof. Is provided with pins 32 and 32 'and is rotatably supported on a bearing housing 34 provided in the crank chamber 2. [

1, reference numeral 32 denotes a crank pin, which is directly connected to the crankshaft 1 through a crank arm. Reference numeral 32 'denotes a crank pin. Reference numeral 32 denotes a crank pin. Reference numeral 32 denotes a crank pin. Respectively. Accordingly, when the crankshaft 1 rotates, the pneumatic piston 10 and the canceling piston 20 are linearly reciprocated in opposite directions, and the eccentric vibration force is canceled. In this case, the crank pin 10 and the crank arm 10, and the crank wheel 30 are formed in the same shape and weight so that they have a simple eccentric power canceling structure.

That is, the pair of crank pins 32 and 32 'are provided so as to form a 180 ° crank angle around the crank wheel 30 supported by the bearing housing 34, and one of the crank pins 32 and 32' So that the power of the crankshaft 1 is transmitted. The crank wheel 30 is formed as a circular plate and mounted on a bearing housing 34 bolted to the crank chamber 2 so as to be rotatably supported by the bearing housing 34. The bearing housing 34 has a plurality of balls It is possible to perform long-term no-fuel operation by applying standardized bearing which is installed for rolling motion, and maintenance including replacement of bearings is made easily.

The crank wheel 30 is rotated at a predetermined position by the crankshaft 1 and the pair of crankpins 32 and 32 ' So that the pneumatic piston 10 and the canceling piston 20 reciprocate linearly in mutually opposite directions. Accordingly, the diameter of the crankpins 32 and 32 'can be reduced as shown in FIG. 1, and the maximum turning radius of the connecting rod outer shape is reduced compared to the stroke of the pistons 10 and 20, thereby reducing the overall size of the pistol. Accordingly, the suction and compression pneumatic pressures acting inside the cylinder 22 due to the expansion of the piston 10 (20) are increased, and a strong hitting force is provided.

The rotational inertia of the crankshaft 1 is prevented by the rotational inertia of the crank wheel 30, that is, the rotational inertia force, which is the force that the crank wheel 30 continuously rotates with elasticity, And the force required for the reciprocating linear motion force of the canceling piston (20) are uniformly transmitted, and vibration reduction and high output safety are ensured.

The crank chamber 2 has a circular tubular portion 3 formed on its inner circumferential surface and the outer circumferential surface of the bearing housing 34 is machined in the same manner as the circular tubular portion 3. As shown in FIG. 2, the circular tubular portion 3 of the crankcase 2 is machined into a cylindrical shape by turning, the productivity is improved by shortening the machining time and both ends of the bearing housing 34 corresponding to the circular tubular portion 3, (3) having the same curvature.

When the bearing housing 34 is assembled, the round tube portion 3 and the rounded surfaces of both ends of the bearing housing 34 are tightly engaged with each other. Thus, the bearing housing 34 is positioned at the center of the circular tube portion 3, And thus it is possible to precisely assemble by an unskilled worker. In other words, the bearing housing 34 is inserted into the circular tube portion 3 and is fastened in place by a simple process of bolting on the side surface.

At this time, in the crank chamber 2, the inner space is divided into two by the bearing housing 34 so that the cylinder 12 is communicated with a position corresponding to one inner space, and in the position corresponding to the other inner space, (22) are communicated with each other. That is, the crank chamber 2 is divided into two by the bearing housing 34 to form two hemispherical inner spaces, and the cylinder 12 and the extension cylinder 22 are provided on the upper and lower sides symmetrical with respect to the bearing housing 34, And the pneumatic piston 10 and the offset piston 20 are linearly reciprocated in the opposite directions to each other by the pair of crank pins 32 and 32 '.

At least one pinhole 33 is formed in the crank wheel 30 at a position corresponding to the crank pin and the crank pin engaged with the pinhole 33 is integrally formed with the crank arm 1a of the crankshaft 1 And a bearing B for supporting a connecting rod 11 connected to the pneumatic piston 10 is fitted into the pin hole 33 in a state of being fitted.

1, the crankshaft 1 is inserted into a pinhole 33 of the crank wheel 30 with a bearing B for supporting the connecting rod 11 inserted into a crank pin 32 integrally formed with the crankshaft 1 The crank pin 32 'is formed integrally with the crank wheel 30 and connected to the connecting rod of the canceling piston 20. Since the pair of crank pins 32 and 32 'are integrally provided on the crankshaft and the crank wheel and are easily assembled and installed, safety of the power transmission structure due to the application of the double piston is secured, And the bearing for supporting the connecting rod (B) are used as bearings of the same type as that of the bearing housing (34).

The intake hole 40 according to the present invention is formed in the operating section of the weight piston 14 and is provided to supply outside air into the cylinder 12 so that the pneumatic piston 10 reaches the bottom dead point, 12 so that external air is drawn into the cylinder 12 while the weight piston 14 passes through the intake hole 40 at a time when the compressed air pressure is no longer increased.

The intake hole 40 is formed to penetrate the cylinder 12 in the interval between the top dead center and the bottom dead center of the weight piston 14 and to supply the outside air into the cylinder 12. In this case, 40 are equally arranged at a plurality of positions on the outer circumferential surface of the cylinder 12 as shown in Figs. 1 and 2, so that outside air is sucked into the cylinder 12 at a plurality of positions at the same time.

That is, even when the pneumatic piston 10 reaches the bottom dead center and the cylinder internal compressed air pressure is no longer increased, the weight piston 14 is at a moment when the kinetic energy to move in the striking direction by the compressed air pressure and the inertial force continuously acts When the pneumatic piston 30 changes direction and moves to the top dead point, the suction air pressure acts on the cylinder 12. At this moment, as the weight piston 14 passes through the intake hole 40 as shown in FIG. 4, (12) so that the suction air pressure is canceled.

Accordingly, the kinetic energy of the weight piston 14 to move to the bottom dead center is maximized by the inertia force without being interfered with the suction pneumatic pressure generated during the movement of the pneumatic piston 10 to the top dead center, and a high output hitting force is generated .

On the other hand, when the weight piston 14 moves partly to the top dead center position in the cylinder 12 and the base milling is located above the intake hole, suction pneumatic pressure acts on the inside of the cylinder to move to the top dead center and then to the bottom dead center And the batting operation is repeated. As a result, the hammer H or the wedge W is pushed onto the pit boat as shown in FIG. 5 in order to use the paddle as the striking operation is performed after the weight piston 14 is pushed by the striking rod 70 and moved in the top dead center direction. When the pressure is applied, the striking operation is performed while the striking rod 70 is pushed up. Therefore, the striking force is not generated in the standby state before the striking position is set, and the striking force is maintained in the low vibration state.

At this time, the pneumatic piston 10 is changed from the bottom dead center to the top dead center, and a charging hole 50 for supplying the outside air into the cylinder 12 is formed at the time when the suction air pressure acts on the cylinder 12. The filling hole 50 is formed such that the pneumatic piston 10 is formed in the cylinder 12 in the section between the top dead center and the bottom dead center so that the outside air is supplied into the cylinder 12. 6, when the pneumatic piston 10 moves to the top dead center and the compressed air pressure acts on the inside of the cylinder 12 to move the weight piston 14 to the top dead center, external air is introduced into the cylinder 12 The compressed air pressure in the cylinder 12 is increased when the pneumatic piston 10 is moved to the bottom dead center.

Here, the filling hole 50 is closed when the pneumatic piston 10 is positioned at the bottom dead center, and when the pneumatic piston 10 is turned at the bottom dead center and moves to the top dead center, And it is preferably located 1 to 10 mm above the milling position in the top dead center direction.

The amount of air sucked through the charging hole 50 is set to be smaller than the amount of air sucked through the suction hole 40. This is because when the amount of air sucked through the charging hole 50 is excessively large, If the pneumatic pressure is not generated and it is impossible to move to the top dead center of the weight piston 14 and the air suction amount of the filling hole 50 is excessively narrow, the amount of compressed air recharge is insufficient into the cylinder 12, The amount of air sucked through the suction holes 40 and the filling holes 50 is preferably 6 to 10: 1.

The air inlet hole 40 and the charging hole 50 are formed so that the direction of air movement is switched toward the end of the sleeve 60 through the flow path 62 between the sleeves 60 provided on the outer circumferential surface of the cylinder 12, And a handle holding portion 64 is provided on the surface of the handle. That is, the sleeve 60 is formed in the shape of a circular tube, and the intake hole 40 and the charging hole 50 are formed so as to surround the outer circumferential surface of the cylinder 12. At this time, through the oil passage 62 between the sleeve 60 and the cylinder outer circumferential surface The suction holes 40 and the filling holes 50 communicate with the upper or lower end of the sleeve.

Accordingly, clogging of the intake hole 40 and the filling hole 50 is prevented even when the operator grasps the outer circumferential surface of the cylinder by hand, and the flow path extending to the sleeve end portion is closed by the filter portion to supply purified air , The oil passage 62 of the sleeve 60 is provided so as to communicate with the inside of the crank chamber 2 through the extension oil passage 63 as shown in FIG.

Therefore, since the air remaining in the crank chamber 2 is used as compressed air necessary for operating the cylinder 12, foreign matter is prevented from flowing into the cylinder 12 even in a rural working environment exposed to foreign matter including dusts The internal contamination of the cylinder 12 and damage to the piston milling are prevented, so that the maintenance period is prolonged.

A high work table 80 is also provided which includes a joint portion 82 which is fastened to one side of the barrel body including the cylinder 12 and an extension bar 84 which is connected to the joint portion 82 . In FIG. 8, the joint portion 82 is formed as a clamp type and is fastened to the cylinder 12 on the outer circumferential surface. However, the present invention is not limited to this, and it may be fastened to one side of the hinge body. And the extension bar 84 is connected to adjust the length and angle of the joint portion 82.

Therefore, there is an advantage that piling work of 2 m or more higher than the worker's height is performed without a ladder because the hammers H are lifted up by using the elevated work bench 80 and positioned so that the hammer H is in surface contact with the side of the pile .

A ring glove 34 is formed so that the weight piston 14 is provided with a base mill 32 for sealing the inner wall of the cylinder 12 and the ring glove 34 has an expanded width And the inclined surface 36 is formed so that the diameter of the inclined surface 36 is increased toward the direction in which the hitting force is applied. 9 (a), when the weight piston 14 is moved to the top dead center, the ring milling ring 32 is rotated in the direction of the top dead center of the weight piston 14 by the inclined surface, 9 (b), when the weight piston is moved to the bottom dead center, airtightness between the inner wall of the cylinder and the piston is increased. The inner surface of the cylinder 12 is reduced in airtightness because the depth of the inclined surface 36 of the ring glove 34 is reduced to be smaller than the outer diameter of the weight piston 14. [

When the weight piston 14 is moved to the top dead center by the inclined face 36 of the ring glove 34 and when the piston moves to the bottom dead point, the airtightness between the base ring 32 and the inner wall of the cylinder 12 is different from each other When the pneumatic piston 10 is moved to the top dead center and the bottom dead point, the compressed air pressure acts strongly on the cylinder 10 to maximize the kinetic energy of the piston 10 moving to the top dead center of the weight piston 14, When the piston is moved to the bottom dead center, the frictional force with the inner wall of the cylinder 12 is reduced, so that the inertia energy of the weight piston 14 as well as the compressed air pressure is doubled to increase the kinetic energy required for bottom dead center movement. ) Is prolonged by a decrease in frictional resistance.

The crankshaft 1 is supported on both sides by the main housing 90 and the auxiliary housing 92 and is rotated about the crankshaft 1 between the main housing 90 and the auxiliary housing 92 A drive shaft 96 to which external power is connected is installed in the fluid housing 94 and the drive shaft 96 and the crankshaft 1 are driven by a gear assembly at a predetermined inclination angle Respectively. 1, the main housing 90 is provided at one side of the crank chamber 2 to support the crankshaft 1 through bearings. The auxiliary housing 92 is disposed at a position spaced apart from the main housing 90, And the crankshaft 1 is supported by bearings. The flow housing 94 is pivoted about the crankshaft 1 at the main housing 90 and the auxiliary housing 92 and the gearbox space is ensured such that the gear assembly is installed therein. Here, it is preferable that the gear assembly is selectively applied among gears including a bevel gear, a worm gear, a screw gear, and a hypoid gear, the power transmission direction of which is adjusted to a predetermined angle.

Accordingly, when the operator lifts the airplane and adjusts the height of the drive shaft 96, the flow housing 94 is swiveled to easily change the direction. At this time, the power of the drive shaft 96 The crankshaft 1 is supported at both ends by the main housing 90 and the auxiliary housing 92 while being transmitted through the gear assembly, so that the shaft is prevented from being deflected or the gear assembly being overdisposed .

12, the crankshaft 1 is provided to be driven by an output of a speed reducer 99 which decelerates a DC motor 98 rotating at 1 to 30,000 rpm at a ratio of 6 to 8: 1. At this time, the DC motor 98 is rotated at a speed of 1 to 30,000 RPM by the rechargeable battery, and is decelerated at a rate of 6 to 8: 1 by the speed reducer 99 The crankshaft 1 is rotated by the driving force. Even if a small size is manufactured to carry out the light weight work including the pile piling of the horseshoe, there is an advantage that the power source is reduced in size and weight together with the aged person easily operated.

1, a bar protruding outside the cylinder may be an extension bar for connecting a handle, a handle may be provided on an upper portion of the extension bar to be used for a low work, or an extension bar may be connected to a lower portion to be used as a high- .

10: pneumatic piston 20: offset piston
30: crank wheel 40: intake hole
50: Charging hole 60: Sleeve
70: blow rod 80: elevated workbench
90: Main housing

Claims (13)

A cylinder (12) and an expansion cylinder (22) are provided so as to communicate with the inner space of the crank chamber (2)
A pneumatic piston 10 connected to the crankshaft 1 in the crankcase 2 and generating compression and suction pneumatic pressures in the cylinder 12 by linear reciprocating transfer; A weight piston 14 which is reciprocally transported in the cylinder 12 and provides a striking force; a weight piston 14 which is connected to the crankshaft 1 and is reciprocated so as to reciprocate in the opposite direction to the pneumatic piston 10 in the expansion cylinder 22; A piston (20) is provided,
A pair of crank pins 32 and 32 'that are connected to the crankshaft 1 so as to rotate and have crank angles of 180 ° so that the pneumatic piston 10 and the offset piston 20 are connected to each other A crank wheel 30;
A bearing housing (34) installed in the crank chamber (2) and rotatably supporting the crank wheel (30);
The crankcase (2) has a circular tubular portion (3) formed on an inner circumferential surface thereof and an outer circumferential surface of the bearing housing (34) is machined in the same manner as the circular tubular portion (3) The anti-aircraft. The method according to claim 1,
The crank chamber 2 is divided into two by the bearing housing 34 so that the cylinder 12 is communicated with a position corresponding to the one inner space and the expansion cylinder 22 Wherein the first and second pistons are provided so as to communicate with each other. The method according to claim 1,
At least one pin hole 33 is formed in the crank wheel 30 at a position corresponding to the crank pin and the crank pin to be fastened to the pin hole 33 is integrally connected to the crank arm 1 a of the crank shaft 1 And the pinch hole (33) is fitted into the pinch hole (33) while the bearing (B) for supporting the connecting rod (11) connected to the pneumatic piston (10) is fitted. The method according to claim 1,
The intake hole 40 is formed in the operating section of the weight piston 14 and supplies external air to the inside of the cylinder 12. The intake hole 40 allows the pneumatic piston 10 to reach the bottom dead point, Is provided so that outside air is sucked into the cylinder (12) while the weight piston (14) passes through the intake hole (40) at a time when the compressed air pressure is no longer increased in the cylinder (12) Double pistons. 5. The method of claim 4,
A charging hole 50 for supplying outside air into the cylinder 12 is formed at a time point when the pneumatic piston 10 is changed from the bottom dead center to the top dead center and suction air pressure acts on the cylinder 12 Double piston pistons with circular crankshafts. 6. The method of claim 5,
The suction holes 40 and the filling holes 50 are switched in the direction of air movement through the flow path 62 between the sleeves 60 provided on the outer circumferential surface of the cylinder 12, And the gripper grip portion 64 is provided on the surface of the sleeve 60 so as to communicate with the inside of the crank chamber 2 through the extension passage 63. The double piston piston rod according to claim 1, The method according to claim 1,
A hitting rod 70 which is provided in front of the weight piston 14 so as to be interchangeable and transmits the hitting force of the weight piston 14 and a hammer H or a wedge W at the end of the hitting rod 70 Double piston pistons with circular crankshafts featured. 8. The method of claim 7,
A conical protrusion 70a is formed at an end of the impact rod 70 and is fitted into a conical groove 70b formed in the hammer H or the wedge W. The conical protrusion 70a and the groove 70b are fixed Wherein the piston is provided to have fluidity in the impact force transmitting direction by engagement of the pin (72) and the long hole (74). The method according to claim 1,
A high work table 80 including a joint portion 82 to be coupled to one side of the barrel body including the cylinder 12 and an extension bar 84 connected to the joint portion 82 is provided A double piston piston with a circular crank chamber. The method according to claim 1,
A ring glove 14b is formed so that the weight piston 14 is provided with a base mill 14a for air tightness between the inner wall of the cylinder 12 and the ring glove 14b is formed with an expanded width relative to the base mill 14a. And the inclined surface (14c) is provided so that the diameter increases as the striking force is applied. The method according to claim 1,
The crankshaft 1 is supported on both sides by the main housing 90 and the auxiliary housing 92 and is provided between the main housing 90 and the auxiliary housing 92. The crankshaft 1 is rotatably mounted on the crankshaft 1, A drive shaft 96 to which external power is connected is installed in the fluid housing 94 and the drive shaft 96 and the crankshaft 1 are driven by a gear assembly to transmit power at a predetermined inclination angle Wherein the first and second crankshafts are provided with a circular crank chamber. The method according to claim 1,
Wherein the crankshaft 1 is driven by an output of a speed reducer 99 for reducing a DC motor 98 rotating at 1 to 30,000 RPM at a ratio of 6 to 8: 1. Double piston pistons. The method according to claim 1,
Wherein the offset piston (20) is provided with a joint portion (24) so that a vibration transmitting means (26) including a shaking table for harvesting a crop can be detachably attached to an end of the canopy piston (20).

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