KR101650906B1 - Single acting driving pile machine - Google Patents

Abstract

The present invention relates to a pile driver combined with a single-acting, low-vibrating fruit shaker. The present invention has a lightweight structure having a single-acting crank which offsets vibration of the crank action and provides an excellent portable workability due to low vibration. Especially, in order to complexly perform a pneumatic pile driving function and a mechanic crop shacking function, the present invention comprises a crank pin (10), a pneumatic piston (20), a weight piston (30), and an offset piston (40) as primary elements.

Description

[0001] Single acting driving pile machine [

[0001] The present invention relates to a single acting, low vibration, water softener, and more particularly, to a lightweight structure employing a single acting crank, To a single-acting type low-vibration, water-jet combiner.

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.

Accordingly, it is an object of the present invention to solve the above-mentioned problems, and it is an object of the present invention to provide a motorcycle having a lightweight structure employing a single-acting crank, And an object of the present invention is to provide a single-acting low-vibration,

In order to achieve this object, a feature of the present invention is to provide a crankshaft comprising a crank pin (10) eccentrically rotated by a crankshaft (1), and a crankshaft A pneumatic piston 20 in which a suction pneumatic pressure is generated and a weight piston 30 which is reciprocally transported in the cylinder 22 by a pneumatic pressure and provides a striking force, And an offset piston (40) connected to the rack (50) and the pinion gear (52) so that the reciprocating transfer force is transmitted in the reverse direction, so as to cancel the vibration force generated in the pneumatic piston (20) .

At this time, the pneumatic piston (20) and the offset piston (40) are provided with a recoil gear (50) at a position facing each other with the operating direction thereof coinciding with the plunger, and the recoil gear And are reciprocated linearly in opposite directions to each other.

The expansion cylinder 42 is connected to the rear space of the pneumatic piston 20 through the air passage 43 and is connected to the canceling piston 40 And the suction and compression pneumatic pressures acting on the pneumatic piston (20) act on the rear side of the pneumatic piston (20).

Also, the pinion gear 52 is formed to have a diameter of 70 to 120% based on the diameter of the piston, and a coupling area of 50 to 80% based on the diameter of the piston is secured.

The canceling piston 40 is divided into at least two portions and is provided so that the total vibration canceling force required for canceling the vibrating force generated in the pneumatic piston 20 is divided and arranged by the number of canceling pistons 40 .

The striking rod 60 is disposed in front of the weight piston 30 so as to be interchangeable and transmits the striking force of the weight piston 30 and a hammer H or wedge W is provided at the end of the striking rod 60 .

Further, the canceling piston (40) is characterized in that the joint portion (42) is provided at the end portion so that the vibration transmitting means (70) including the shaking table for harvesting the crop can be detachably attached.

According to the above construction and operation, the vibration is canceled by the reciprocal linear reciprocating force between the pneumatic piston and the offset piston in the lightweight structure employing the single-acting crank, and fatigue is reduced even for a long period of time, .

In addition, there is an effect that a pneumatic hammering function using a pneumatic cylinder and a mechanical hood using a canceling piston are combined using a single device.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a general view showing a single-acting type low vibration-resistant water softener combined with an antidumping agent according to an embodiment of the present invention; Fig.
Fig. 2 is a schematic view showing a single-acting low-vibration water-harvesting combiner according to an embodiment of the present invention
Fig. 3 is a schematic view showing a single-acting type low-vibration, water-hoe combiner according to an embodiment of the present invention in plan view.
4 is a configuration view showing an operating state of a single-acting low-vibration, water-hoe combiner according to an embodiment of the present invention.
5 is a configuration view showing a state where two canceling pistons of a single acting type low vibration resistant water softener combined with an antidumping agent according to an embodiment of the present invention are provided.
6 is a configuration diagram showing a hitting rod of a single-acting low-vibration water softener combined with a single-strut hanger according to an embodiment of the present invention;
FIG. 7 is a view showing a connection state of a vibration transmitting means of a single-acting low-vibration, water-hitting machine for a hybrid vehicle according to an embodiment of the present invention;
FIG. 8 is a view showing a sleeve of a single acting type low vibration resistant water softener combined with a sleeve according to an embodiment of the present invention; FIG.
FIG. 9 is a view showing a connecting rod, a hammer and a wedge connection structure of a single-acting low-vibration water softener combined with an anti-static device according to an embodiment of the present invention.
FIG. 10 is a view showing a high work table of a single-acting type low-vibration water heater and a hybrid vehicle according to an embodiment of the present invention; FIG.

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

FIG. 1 is a schematic view showing the entirety of a single-acting type low-vibration, water-shear combiner according to one embodiment of the present invention, FIG. 2 is a schematic view showing a single- And FIG. 3 is a configuration diagram showing a single acting type low vibration anti-hydrosphere combiner according to an embodiment of the present invention in plan view.

The present invention relates to a single-acting type low-vibration water turbine hovering machine, wherein a lightweight structure employing a single-acting crank is used to offset the cranking vibration, thereby achieving a low vibration and a portable workability. Particularly, a pneumatic hovering function and a mechanical crop hull The pneumatic piston 20, the weight piston 30, and the canceling piston 40 in order to allow the crank pin 10 to be operated.

A single-acting type low-vibration, low-vibration water softener according to the present invention comprises a crank pin (10) eccentrically rotated by a crank shaft (1) A pneumatic piston 20 in which a suction pneumatic pressure is generated and a weight piston 30 which is reciprocally transported in the cylinder 22 by a pneumatic piston 20 and provides a striking force. The crankshaft 1 is provided with a joint at one end to be connected with an external power unit including a lawnmower engine and a rechargeable electric motor, and is connected to the other end so as to eccentrically rotate the crankpin 10.

The crankpin 10 is integrally formed on the crankshaft 1 or is separately formed and coupled to the crankpin 10. The crankpin 10 is inserted into a state in which a bearing for supporting a connecting rod connected to the pneumatic piston 20 is fitted By a fixing means including a fixing washer and a fixing pin.

In addition, the pneumatic piston 20 according to the present invention is connected to the crankpin 10 so that compression and suction pneumatic pressures are generated in the cylinder 22 by linear reciprocating transfer. The pneumatic piston 20 is connected to the crank pin 10 through the connecting rod and is linearly reciprocated within the cylinder 22. The piston 22 is reciprocated by the compression and suction pneumatic pressure generated in the cylinder 22, And is linearly reciprocated within the cylinder 22.

4 (a), suction force acts on the inside of the cylinder 22 when the pneumatic piston 20 is transferred to the top dead center so that the weight piston 30 moves together with the top dead center, and then, as shown in FIG. When the pneumatic piston 20 is turned and moved to the bottom dead point, a compressive force acts on the inside of the cylinder 22. At this time, the weight piston 30 moves to the bottom dead point by the compressive force acting inside the cylinder 22, And the above operation is repeated to continuously generate the hitting force.

The striking rod 60 is disposed in front of the weight piston 30 so as to be interchangeable and transmits the striking force of the weight piston 30 and a hammer H or wedge W is provided at the end of the striking rod 60 do. A multi-cap is interchangeably fastened to a lower portion of the cylinder 22 in which the weight piston 30 is installed. In the multi-cap, a striking rod 60 is disposed in a straight line with the conveying direction of the weight piston 30.

As shown in FIG. 6, when the hammer is used, a hitting rod 60 equipped with a hammer H is mounted and used. In the rock crushing operation, the hitting rod 60 is replaced with a wedge W do. Alternatively, the hammer H or the wedge W may be provided at the end of the hitting rod 60 in a replaceable manner.

At this time, a conical protrusion 60a is formed at an end of the impact rod 60 and is fitted into a conical groove 60b formed on the hammer H or the wedge W. The conical protrusion 60a and the groove 60b, Is provided so as to have fluidity in the striking force transmitting direction by engagement of the fixing pin (70) and the slot (72). 9, the long hole 72 is extended in the striking force transmitting direction of the striking rod 60, and the hammer H or the wedge W coupled to the striking rod 60 by the engagement with the striking pin 70, So that the striking load of the striking rod 60 is not directly transmitted to the side of the fixed pin 70.

As the cone-shaped protrusions 60a and the grooves 60b 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 60 is prevented, The fixing pin 70 is advantageously prevented from being warped or broken due to the striking force by securing fluidity within the elongated hole 72.

The canceling piston 40 according to the present invention is connected to the rak 50 and the pinion gear 52 so that the linear reciprocating force of the pneumatic piston 20 is transmitted in the opposite direction, So as to cancel the power.

At this time, the pneumatic piston (20) and the offset piston (40) are provided with a recoil gear (50) at a position facing each other with the operating direction thereof coinciding with the plunger, and the recoil gear And are reciprocated linearly in opposite directions to each other.

That is, the canceling piston 40 is disposed parallel to one side of the pneumatic piston 20, and is engaged with the lever and the pinion gear. When the pneumatic piston 20 is transferred to the top dead center as shown in FIG. 4 (a) The piston 40 is transferred to the bottom dead center, and the offset piston 40 is transferred to the top dead center when the pneumatic piston 20 is redirected to the bottom dead center as shown in FIG. 4 (b). Accordingly, when the crankshaft 1 is rotated, the pneumatic piston 20 and the canceling piston 40 reciprocate in opposite directions to each other, thereby canceling the vibration, thereby reducing the fatigue of the engine for a long time.

1 and 3, the offset piston 40 is provided at one position on one side of the cylinder 22. However, the present invention is not limited to this, and the offset piston 40 may be divided into at least two positions as shown in FIG. At this time, the total vibration canceling force required for canceling the vibration force generated in the pneumatic piston (20) is divided and distributed by the number of canceling pistons (40). Thus, the weight of each canceling piston 40 is reduced, thereby reducing the load acting on the side of the rack and the pinion gear that transmits the operating force to each of the canceling pistons 40, and the gear size can be downsized.

The expansion cylinder 42 is provided to receive the canceling piston 40 and the expansion cylinder 42 is connected to the rear of the pneumatic piston 20 through the air passage 43 so that the canceling piston 40 Acting suction and compression pneumatic pressures are provided to act behind the pneumatic piston 20. The expansion cylinder 42 is installed in parallel with the side surface of the cylinder 22 and the other end of the expansion cylinder 42 is connected through the air passage 43 The crank pin 10 and the connecting rod are installed in the inside of the body of the propeller, that is, as shown in FIG.

Therefore, when the pneumatic piston 20 moves to the bottom dead center, the offset piston 40 moves to the top dead center and the air inside the expansion cylinder 42 is supplied to the rear side of the pneumatic piston 20 through the air passage 43, When the piston 20 moves to the top dead center, the offset piston 40 moves to the bottom dead center, and the operation of sucking the air present behind the pneumatic piston 20 through the air passage 43 is repeated. Accordingly, the suction and compression force acting on the pneumatic piston 20 in the backward direction of the pneumatic piston 20 during linear reciprocating transportation is canceled by the suction and compression pneumatic pressure in the expansion cylinder 42 moving through the air passage 43 Power loss is reduced.

In addition, since the construction of the transfer passage for the inflow of the outside air and the inside air is omitted in order to release the action repulsive force acting on the back of the pneumatic piston 20, contamination of the inside of the inside of the anti- There is an advantage that the milling damage is prevented and the maintenance period is prolonged.

In addition, the pinion gear 52 is formed to have a diameter of 70 to 120% based on the diameter of the piston, and to secure a coupling area of 50 to 80% based on the diameter of the piston. If the diameter of the pinion gear 52 is less than 70% based on the diameter of the piston, the overall durability of the pinion gear 52 deteriorates due to the gear teeth. If the diameter of the pinion gear 52 exceeds 120%, the entire weight and the piston- , And the pinion gear 52 is preferably formed to have a diameter of 100% based on the diameter of the piston. When the meshing area of the pinion gear 52 engaged with the rec gear 50 formed in the piston is less than 50%, the load can not withstand the instantaneous turning due to the linear reciprocating movement of the piston. When the meshing area exceeds 80% The engagement area of the pinion gear 52 is preferably set to 70% based on the diameter of the piston.

In Fig. 7, the canceling piston 40 is provided with the joint portion 44 so that the vibration transmitting means 70 including the shaking table for harvesting the crop can be detachably attached to the end thereof. The vibration transmitting means 70 is formed in a rod shape and has a fastening portion at one end to be fastened to the joint portion 44 and a fastening groove to be fitted into the fruit water at the other end.

The vibration transmitting means is coupled to the joint portion 44 of the canceling piston 40 and the crankshaft 1 is rotated with the vibration transmitting means sandwiched in the juvenile water, Is used as a vibrating machine for shaking off the jujube while being reciprocated linearly. At this time, due to the reciprocating linear reciprocating force of the compression and offset pistons 20 and 40, the self- There is an advantage.

On the other hand, the joint portion 44 may be formed on both sides of the canceling piston 40 so that the vibration transmitting means 70 can be connected to any one of the two directions.

8, an air hole including an air hole 22a and an auxiliary air hole 22b for sucking and discharging air into the cylinder 22 is formed in the operation section of the pneumatic piston 20 and the weight piston 30, The air hole is provided to be connected to the inner space of the main body housing 2 by a sleeve 23 provided on the outer circumferential surface of the cylinder 22.

That is, the air hole 22a is provided on the cylinder 22 so that outside air is supplied into the cylinder 22 at one side of the section where the weight piston 30 is turned at the top dead center and moved to the bottom dead center. The air hole 22a prevents the impact force of the weight piston 30 from being canceled by the suction force generated when the pneumatic piston 20 is turned at the bottom dead center and moved to the top dead center.

More specifically, when the pneumatic piston 20 reaches the bottom dead center and the compression force is no longer increased, external air flows into the cylinder 22a while the weight piston 30 passes through the air hole 22a , The heavy piston (30) moves to the bottom dead center without being interfered with the suction force generated after the pneumatic piston (20) is turned at the bottom dead center, and a high output striking force is generated. An auxiliary air hole 22b is further formed at an upper position (toward the top dead center of the pneumatic piston) away from the air hole 22a so that external air is added into the cylinder 22 when the pneumatic piston 20 moves to the top dead center The amount of the compressed air in the cylinder 22 is increased to prevent the deterioration of the hitting force due to the repeated operation.

The air holes 22a and the auxiliary air holes 22b are connected to the inner space of the main body housing 2 by the sleeves 23 provided on the outer circumferential surface of the cylinder 22. The sleeve 23 is connected to the inside of the main body housing 2 at one side of the flow path while forming a flow path in a state of being separated from the cylinder outer peripheral surface.

Accordingly, since the air remaining in the main body housing 2 is used as compressed air necessary for operating the cylinder 22, foreign matter is prevented from flowing into the cylinder 22 even in a rural work environment exposed to foreign matter including dust, 22) Internal contamination and damage to the piston milling are prevented, and the maintenance period is prolonged.

The elevating table 84 includes a cylinder 22, a joint portion 82 to be coupled to one side of the barrel body including the main body housing 2, and an extension bar 84 connected to the joint portion 82. (80). In FIG. 10, the joint portion 82 is formed as a clamp type and is fastened to the cylinder 22 on the outer circumferential surface. However, the present invention is not limited thereto. And the extension bar 84 is connected to adjust the length and angle of the joint portion 82.

Accordingly, since the hammers (H) are positioned so as to be in surface contact with the upper surface of the pile by connecting the elevating table (80) to raise the hinge, the pile harnessing operation of 2 m or more higher than the height of the worker is performed without a ladder.

10: crank pin 20: pneumatic piston
30: weight piston 40: offset piston
50: rec gear 60: hitting rod

Claims (10)

A crankpin 10 which is eccentrically rotated by the crankshaft 1; a pneumatic piston 20 connected to the crankpin 10 and generating compression and suction pneumatic pressures in the cylinder 22 by linear reciprocating transfer; A pneumatic piston (20) is provided with a weight piston (30) which is reciprocally transported in the cylinder (22) by pneumatic pressure and which provides a striking force,
An offset piston 40 connected to the rack 50 and the pinion gear 52 so as to transmit the linear reciprocating feed force of the pneumatic piston 20 to cancel the vibrational force generated in the pneumatic piston 20, And a low-vibration low-revving water turbine. The method according to claim 1,
The pneumatic piston 20 and the canceling piston 40 are provided with a recoil gear 50 at a position facing each other with their operating directions on the plunger and the recoil gear 50 is meshed by the pinion gear 52 Wherein the single-action type low-vibration watercraft is provided so as to be linearly reciprocated in opposite directions. The method according to claim 1,
The expansion cylinder 42 is connected to the rear space of the pneumatic piston 20 through the air passage 43 and is operated by the canceling piston 40 And the suction and compression pneumatic pressure acting on the pneumatic piston (20) is applied to the rear of the pneumatic piston (20). The method according to claim 1,
Wherein the pinion gear (52) is formed to have a diameter of 70 to 120% based on the diameter of the piston, and a coupling area of 50 to 80% based on the diameter of the piston is secured. The method according to claim 1,
Characterized in that the cancellation piston (40) is divided into at least two places, and the total vibration canceling force required for canceling the vibration force generated in the pneumatic piston (20) is divided and arranged by the number of offset pistons A single-acting, low-vibration, water-jet combiner. The method according to claim 1,
A hitting rod 60 installed in front of the weight piston 30 for transferring the hitting force of the weight piston 30 and a hammer H or a wedge W provided at the end of the hitting rod 60 Features a single-action, low-vibration anti-tarpaulin combine. The method according to claim 1,
Wherein the canceling piston (40) is provided with a joint portion (44) so that a vibration transmitting means (70) including a shaking table for harvesting crops can be detachably attached to an end thereof. The method according to claim 1,
An air hole including an air hole 22a and an auxiliary air hole 22b for sucking and discharging air into the cylinder 22 is formed in the operation section of the pneumatic piston 20 and the weight piston 30, Is connected to the inner space of the main body housing (2) by a sleeve (23) provided on the outer circumferential surface of the main body (22). The method according to claim 1,
(80) including a cylinder (22), a joint portion (82) to be coupled to one side of the barrel body including the main body housing (2), and an extension bar (84) connected to the joint portion ) Is provided on the upper surface of the base member (2). The method according to claim 6,
A conical protrusion 60a is formed at an end of the impact rod 60 and is fitted into a conical groove 60b formed in the hammer H or the wedge W. The conical protrusions 60a and the groove 60b are fixed And is provided so as to have fluidity in the striking force transmitting direction by engagement of the pin (70) and the long hole (72).

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