JP7257040B2 - power work machine - Google Patents

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power working machine, and more particularly to a power working machine capable of satisfactorily transmitting power from power generating means to power using means via power transmission means.

Examples of portable work machines that are driven by power generated from a power generation source such as an engine include a chain saw and a blower.

An example of a chain saw is described in Patent Document 1. Here, the engine and the saw are integrated, and the driving force of the engine rotates the saw to cut wood and the like.

An example of a blower is described in Patent Document 2. Specifically, a built-in motor operates to rotate a fan, and the rotating fan blows air from a pipe formed at the tip, so cleaning can be performed using a blower.

JP 2019-72898 A Japanese Unexamined Patent Application Publication No. 2019-11728

In the chain saw described in Patent Document 1, since the engine is built in the main body, vibrations generated by the operation of the engine during felling work are transmitted to the body of the worker. It has been found to cause white wax disease. However, sufficient technical proposals have not been made to suppress the vibration generated from the engine in order to prevent white wax disease.

Also, in the chain saw, the number of shafts on the power use side that rotates the saw is one. Similarly, the blower also has one fan shaft. On the other hand, it is conceivable that a plurality of shafts exist on the power generating side that generates power. In such a case, that is, when the number of shafts differs between the power-using side and the power-generating side, no mechanism for effectively transmitting power from the power-generating side to the power-using side has been proposed at present.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a power working machine having a transmission means that eliminates the difference in the number of shafts between the power generating side and the power using side. It is in.

A power working machine according to the present invention includes power generating means for outputting power from a power output shaft, power using means for using the power input from a power input shaft, and the power using means from the power generating means to the power using means. power transmission means for transmitting power, wherein the number of power output shafts is plural, the number of power input shafts is smaller than the number of power output shafts, and the power transmission means The power is transmitted from the power output shaft to the power input shaft via a fluid , and the power generation means, the power use means and the power transmission means are integrated .

A power working machine according to the present invention includes power generating means for outputting power from a power output shaft, power using means for using the power input from a power input shaft, and the power using means from the power generating means to the power using means. power transmission means for transmitting power, wherein the number of power output shafts is plural, the number of power input shafts is smaller than the number of power output shafts, and the power transmission means The power is transmitted from the power output shaft to the power input shaft via a fluid , and the power generation means, the power use means and the power transmission means are integrated . Thus, according to the power working machine of the present invention, the power transmission means transmits the power from the power output shaft to the power input shaft via the fluid. Even if there is, power can be effectively transmitted from the power output shaft to the power input shaft.

BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows the power working machine which concerns on embodiment of this invention, (A) is a side view which shows a chain saw, (B) is a side view which shows a blower. 1 is a diagram showing a power working machine according to an embodiment of the present invention, and is a schematic diagram showing a bush cutter. FIG. 1 is a conceptual diagram showing a situation in which a worker carries a power working machine according to an embodiment of the present invention; FIG. BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows the engine employ|adopted as the power working machine which concerns on embodiment of this invention, (A) is a side view, (B) is a top view. FIG. 4A is a side view and FIG. 4B is a top view showing another form of engine employed in the power working machine according to the embodiment of the present invention;

A power working machine according to the present embodiment will be described below with reference to the drawings. In the following description, overlapping descriptions of constituent elements with the same reference numbers will not be provided.

<Configuration of power working machine>
A configuration of a power working machine according to the present embodiment will be described with reference to FIG. FIG. 1(A) is a side view showing a chain saw 30 as a power working machine, and FIG. 1(B) is a side view showing a blower 50 as a power working machine.

Referring to FIG. 1A, chain saw 30 includes engine 10 as power generation means, power transmission means 41 , power use means 42 , and saw chain 37 . The chainsaw 30 is a portable cutting machine, and is used for cutting wood, for example. Also, the engine 10 , the power transmission means 41 and the power use means 42 are fixed inside the casing 31 . Furthermore, a handle 35 is connected to the end of the casing 31 and a switch 38 is arranged inside the handle 35 .

When using the chainsaw 30, the user holds the handle 35 and presses the switch 38, so that the saw chain 37 rotates at high speed and can cut wood or the like. A specific operation of the chainsaw 30 will be described later.

The engine 10 is power generating means, and its configuration will be described later with reference to FIGS. 4 and 5. FIG. In this embodiment, engine 10 has a plurality of power output shafts 39 , here power output shaft 391 and power output shaft 392 . The power output shaft 391 and the power output shaft 392 are, for example, shafts connected to the crankshaft of the engine. As will be described later, since the engine 10 is a so-called twin crankshaft engine, the vibration and noise generated from the engine 10 are extremely small, thereby preventing the user from contracting white wax disease.

The power using means 42 is a means driven by power transmitted from the engine 10, and is a rotating shaft for rotating the saw chain 37 here. Also, the power using means 42 has one power input shaft 40 to which power is input. The saw chain 37, which is rotatably arranged around the guide 36, is rotated by the rotating shaft of the power using means 42, so that felling can be performed.

The power transmission means 41 is means for transmitting power generated from the engine 10 to the power using means 42 . The power transmission means 41 has fluid pumps 321 and 322 , an oil flow path 34 and a fluid motor 33 . Fluid pump 321 and fluid pump 322 are collectively referred to as fluid pump 32 . The fluid pump 321 is drivingly connected to the power output shaft 391 of the engine 10 via a drive shaft or the like. Fluid pump 322 is drivingly connected to power output shaft 392 of engine 10 via a drive shaft or the like. The fluid motor 33 is drivingly connected to the power input shaft 40 of the power using means 42 via a drive shaft or the like. The oil flow path 34 is a flow path that connects the fluid pumps 321 and 322 to the fluid motor 33, and fluid such as oil flows through the inside thereof.

The power input shaft 40 of the power using means 42 is drivingly connected to the rotary shaft that rotates the saw chain 37 .

The operation of the chain saw 30 configured as described above will be described. When the user presses the switch 38 to turn it on, the power output shaft 391 and the power output shaft 392 are rotated by the power generated by the rotation of the engine 10 . When the power output shaft 391 and the power output shaft 392 rotate, the fluid pumps 321 and 322 also rotate due to their driving force. Oil circulates in the oil flow path 34 by rotating the fluid pump 321 and the fluid pump 322 . This causes the fluid motor 33 to rotate. When the fluid motor 33 rotates, the rotary shaft connected to the power input shaft 40 also rotates in synchronism, causing the saw chain 37 to rotate around the guide 36 at high speed. can.

As described above, the engine 10 has two output shafts, the power output shaft 391 and the power output shaft 392 , while the power using means 42 has one power input shaft 40 . That is, the number of shafts of the engine 10 and the power using means 42 do not match. In this embodiment, the power transmission means 41 is interposed between the engine 10 and the power using means 42, thereby drivingly connecting the engine 10 and the power using means 42 having different numbers of shafts. With such a configuration, power can be effectively transmitted from the engine 10 to the power using means 42 . That is, the driving force generated by the engine 10 is temporarily converted into fluid flow inside the power transmission means 41 and then converted back into the driving force by the power using means 42 .

Furthermore, as will be described later, the engine 10 of this embodiment is a so-called twin crankshaft engine, so the gyroscopic moment is canceled inside the engine 10 . Therefore, an unintended gyroscopic moment is not generated from the chainsaw 30, and the operator can operate the chainsaw 30 accurately and safely.

Further, as will be described later, since the engine 10 is a twin-crankshaft engine, the engine 10 is small and compact, and the overall size of the chain saw 30 is reduced.

A blower 50 as a power working machine will be described with reference to FIG. FIG. 1B is a side view showing the configuration of the blower 50. FIG.

The blower 50 has an engine 10 , power transmission means 41 and a power input shaft 40 . A power output shaft 391 and a power output shaft 392 of the engine 10 are drivingly connected to the fluid pumps 321 and 322 of the power transmission means 41 . Also, the fluid motor 33 of the power transmission means 41 is drivingly connected to the power input shaft 40 of the power use means 42 . Further, the power input shaft 40 is drivingly connected to the fan 53 as the power using means 42 . Furthermore, the engine 10 , the power transmission means 41 and the power use means 42 are housed in the casing 51 . Also, the fan 53 communicates with the blower pipe 52 .

The blower 50 configured as described above operates as follows. When the user performs a predetermined ON operation, the power output shaft 391 and the power output shaft 392 are rotated by the power generated by the rotation of the engine 10 . When the power output shaft 391 and the power output shaft 392 rotate, the fluid pumps 321 and 322 also rotate due to their driving force. Oil circulates in the oil flow path 34 by rotating the fluid pump 321 and the fluid pump 322 . Then, the fluid motor 33 rotates. As the fluid motor 33 rotates, the rotating shaft connected to the power input shaft 40 also rotates in synchronism, thereby rotating the fan 53 at high speed and blowing air from the tip of the blowing pipe 52 to the outside. We can blow away dust, garbage, fallen leaves, etc. with its wind power.

The blower 50 can also achieve the same effects as the chainsaw 30 described above.

The configuration of the bush cutter 45 as a power engine will be described with reference to FIG. The brush cutter 45 is a power machine that cuts grass, trees, and the like by rotating the brush cutter teeth 47 with power generated from the engine 10 . In the explanation of the bush cutter 45, the explanation of the parts overlapping with the chainsaw 30 and the blower 50 is omitted, and the above is used.

Engine 10 is arranged inside casing 31 , and power output shafts 391 and 392 of engine 10 are drivingly connected to fluid pumps 321 and 322 . Also, the fluid pumps 321 and 322 send air taken in from the outside of the casing 31 toward the fluid motor 33 attached to the power usage side via the air flow path 43 . The air flow path 43 is built in a shaft 46 that connects the casing 31 and the brush cutting teeth 47 .

The brush cutting teeth 47 are rotary blades for cutting grass, and the power input shaft 40 is formed at the center thereof. Also, the power input shaft 40 is drivingly connected to the fluid motor 33 . Therefore, when the air from the fluid pump 32 is supplied to the fluid motor 33, the fluid motor 33 is rotated by the air, so that the brush cutting teeth 47 are also rotated at high speed via the power input shaft 40, and the brush cutting operation is performed. can be done effectively.

The air sent from the fluid pump 32 to the fluid motor 33 may be circulated between the two, or the air that rotates the fluid motor 33 may be released to the outside. Further, when the air is discharged to the outside, the air may be discharged forward from the nozzle 44 . With this configuration, the grass and branches that have been cut can be blown forward by rotating the cutting teeth 47, and the cut grass and the like can be gathered at a predetermined location and efficiently. Grass etc. can be removed.

Another form of the blower 50 described above will be described with reference to FIG. In the blower 50 shown in FIG. 1B, the engine 10 and the power using means 42 are integrated, but in the blower 50 shown in this figure, the engine 10 and the power using means 42 are separated. .

Specifically, a person 57 who is a user carries a carrying device 58 on his or her back, and the carrying device 58 has the engine 10 built therein. In addition, the casing 51 incorporates power using means 42 . The engine 10 built in the carrying device 58 and the power using means 42 built in the casing 51 are connected via an oil flow path 34 as the power transmission means 41 .

The blower 50 in such a state operates as follows. When the user performs a predetermined ON operation, the power generated by the rotation of the engine 10 built in the carrying device 58 causes the oil to flow through the oil flow path 34 to the power using means 42 built in the casing 51. sent to That is, oil circulates between casing 51 and carrying device 58 . As a result, the fan 53 (see FIG. 1B) built in the casing 51 rotates at high speed, blowing air from the tip of the blowing pipe 52 toward the outside. can be blown away.

With such a configuration, the heavy engine 10 is supported by the torso of the person 57, so that the inside of the casing 51 can be made lighter, and the burden on the person 57 during work can be reduced. Furthermore, as will be described later, since the engine 10 is a so-called twin-crankshaft engine, the vibration generated from the engine 10 is extremely small. Fatigue can be further reduced.

Here, in the above description, the blower 50 is applied to the form using the carrying device 58, but the chain saw 30 can be applied instead of the blower 50.

<Configuration of Engine 10>
The configuration of the engine 10 applied to the chain saw 30 and the like will be described with reference to FIG. In the description of FIG. 4, each direction of front, back, up, down, left, and right is appropriately used. Here, the vertical direction is the direction in which the piston 13 reciprocates. The front is the direction in which the fluid pumps 321 and 322 are arranged with respect to the engine 10, and the rear is the direction facing the front. The left side is the direction in which the first crankshaft 14 is arranged, and the right side is the direction in which the second crankshaft 24 is arranged.

4A is a side view of the engine 10, and FIG. 4B is a top view of the engine 10. FIG. The first line of symmetry 20 is a line parallel to the reciprocating direction of the piston 13 and passing through the center of the piston pin 16 . Further, referring to FIG. 4(B), the second line of symmetry 21 is a line that coincides with the central axis of the piston pin 16 . Furthermore, the third symmetry line 22 is a line that passes through the intersection of the first symmetry line 20 and the second symmetry line 21 and is perpendicular to the first symmetry line 20 and the second symmetry line 21 .

Referring to FIG. 4B, engine 10 is provided with fluid pumps 321 and 322 . In other words, the engine 10 functions as power generation means for driving the fluid pumps 321 and 322 .

Referring to FIG. 4A, an engine 10 mainly includes a cylinder 12, a piston 13 that reciprocates inside the cylinder 12, and a first crankshaft 14 that converts the reciprocating motion of the piston 13 into rotary motion. , and a second crankshaft 24 for converting the reciprocating motion of the piston 13 into rotary motion. Furthermore, the engine 10 has a first connecting rod 15 connecting the piston 13 and the first crankshaft 14 and a second connecting rod 25 connecting the piston 13 and the second crankshaft 24 . Although not shown here, the cylinder 12 is provided with an intake valve and an exhaust valve. Here, the first connecting rod 15 and the second connecting rod 25 have substantially the same shape and substantially the same length.

The engine 10 is a so-called four-cycle engine, in which combustion inside the cylinder 12 causes the piston 13 to reciprocate in the vertical direction. Rotational power is supplied from the first crankshaft 14 and the second crankshaft 24 to the fluid pumps 321 and 322 .

Furthermore, the engine 10 is a so-called twin crankshaft engine in which the first crankshaft 14 and the second crankshaft 24 are connected to one piston 13 . As a result, the fluid pump 321 and the fluid pump 322 can be driven by the small engine 10, and the rotation fluctuation torque reaction force can be reduced.

The first crankshaft 14 is arranged on the left side of the engine 10 . The first crankshaft 14 has a power output shaft 391 , a first main journal 142 and a first crankpin 141 . The first connecting rod 15 is connected to the first crankpin 141 . Also, the power output shaft 391 is a rod-shaped member, is led out from the main body of the engine 10 , and is drivingly connected to the fluid pump 321 .

The second crankshaft 24 is arranged on the right side of the engine 10 . The second crankshaft 24 has a power output shaft 392 , a second main journal 242 and a second crankpin 241 . The second connecting rod 25 is connected to the second crankpin 241 . Also, the power output shaft 392 is a rod-shaped member, part of which is led out from the main end of the engine 10 and is drivingly connected to the fluid pump 322 .

The first crankshaft 14 and the second crankshaft 24 are arranged symmetrically. That is, the first crankshaft 14 and the second crankshaft 24 are arranged symmetrically with respect to the first symmetry line 20 shown in FIG. 4(A), and the second crankshaft 24 shown in FIG. They are arranged line-symmetrically with respect to the line of symmetry 21 . The first crankshaft 14 and the second crankshaft 24 are always arranged symmetrically during the intake stroke, compression stroke, combustion stroke and exhaust stroke during operation of the engine 10 . With such a configuration, when the engine 10 is running, the rotational moment and vibration are offset by the first crankshaft 14 and the second crankshaft 24, and low vibration and low noise can be realized.

Further, when the engine 10 is operated, the first crankshaft 14 and the second crankshaft 24 rotate in opposite directions. From the viewpoint of FIG. 4A, the first crankshaft 14 rotates clockwise and the second crankshaft 24 rotates counterclockwise. With such a configuration, it is possible to reduce the rotational fluctuation torque reaction force generated when the first crankshaft 14 and the second crankshaft 24 rotate. Furthermore, it is possible to suppress the generation of gyroscopic moment.

The engine 10 of this embodiment does not require a reversing mechanism for reversing the rotational directions of the first crankshaft 14 and the second crankshaft 24 . That is, the first crankshaft 14 and the second crankshaft 24 are separated. Therefore, the overall configuration of the engine 10 can be simplified, and noise generated when the engine 10 is operated can be reduced.

The first connecting rod 15 rotatably connects the piston 13 and the first crankshaft 14 . A first small end portion 151 formed at the upper end of the first connecting rod 15 is rotatably connected to the piston pin 16 of the piston 13 . A first big end 152 formed at the lower end of the first connecting rod 15 is rotatably connected to a first crankpin 141 of the first crankshaft 14 .

The second connecting rod 25 rotatably connects the piston 13 and the second crankshaft 24 . A second small end portion 251 formed at the upper end of the second connecting rod 25 is rotatably connected to the piston pin 16 of the piston 13 . A second big end 252 formed at the lower end of the second connecting rod 25 is rotatably connected to a second crankpin 241 of the second crankshaft 24 .

Here, the position where the first big end 152 is connected to the first crankpin 141 and the position where the second big end 252 is connected to the second crankpin 241 are It is line symmetrical. This symmetry is maintained during the intake, compression, combustion and exhaust strokes.

As shown in FIG. 4A, the first connecting rod 15 and the second connecting rod 25 are arranged symmetrically with respect to the first line of symmetry 20 . The first connecting rod 15 and the second connecting rod 25 are always arranged line-symmetrically during the intake stroke, compression stroke, combustion stroke, and exhaust stroke during operation of the engine 10 .

As shown in FIG. 4B, two first connecting rods 15 are arranged between the piston pin 16 of the piston 13 and the first crankpin 141 of the first crankshaft 14. . Also, the two first connecting rods 15 are arranged symmetrically with respect to the third line of symmetry 22 . Further, the first small end portion 151 of the first connecting rod 15 is connected to the piston pin 16 at a position sandwiching the second small end portion 251 of the second connecting rod 25 in the front-rear direction. For this reason, the first connecting rod 15 and the second connecting rod 25 as a whole are arranged so as to be symmetrical with respect to the third line of symmetry 22 .

With this configuration, the moment is canceled in the direction orthogonal to the piston 13, and the bearing load is uniformed. Therefore, vibrations during operation of the engine 10 are reduced, and reliability is improved. In addition, by arranging two first connecting rods 15 so as to sandwich the second connecting rod 25 in the front-rear direction, the first connecting rod 15 can be connected without preparing a first connecting rod 15 having a special shape. and the symmetry of the second connecting rod 25 can be easily realized.

Here, the fluid pump 321 and the fluid pump 322 can also incorporate balance weights. By doing so, the inertial force can be reduced.

Further, by increasing the rotation speed with a gear or the like, the fluid pumps 321 and 322 are connected to the first crankshaft 14 and the second crankshaft 14 with the balance weights incorporated in the fluid pumps 321 and 322 . 2 It may be rotated at twice the speed of the crankshaft 24 . Thereby, the secondary inertia force can be canceled or reduced.

<Other Forms of Engine 10>
An engine 10 according to another embodiment will be described with reference to FIG. FIG. 5(A) is a side view showing the engine 10, and FIG. 5(B) is a top view thereof. Since the basic configuration of the engine 10 according to other embodiments is the same as that shown in FIG. 4, common constituent members and descriptions thereof will be omitted. In the engine 10 shown in this figure, the positions of the fluid pumps 321 and 322 are optimized for compactness.

Here, each direction used in the description of this embodiment will be described. The first direction is the direction in which the piston 13 moves during the compression stroke. The second direction is the direction opposite to the first direction. The third direction is the direction orthogonal to the first direction and the direction facing the first crankshaft 14 . The fourth direction is the direction orthogonal to the first direction and the direction facing the second crankshaft 24 . The fifth direction is a direction orthogonal to the first direction and parallel to the extending direction of the first crankshaft 14 . The sixth direction is the direction opposite to the fifth direction.

Referring to FIG. 5A, fluid pump 321 is arranged outside and above first crankshaft 14 . Specifically, the fluid pump 321 is arranged on the first direction side and the third direction side of the first crankshaft 14 . Similarly, the fluid pump 322 is positioned outside and above the second crankshaft 24 . Specifically, the fluid pump 322 is arranged on the first direction side and the fourth direction side of the second crankshaft 24 . By disposing the fluid pump 321 and the fluid pump 322 at such positions, the fluid pump 321 and the fluid pump 322 do not protrude to the outside, and the miniaturization of the entire apparatus is achieved.

As shown in FIG. 5A, the first mass 271 is formed in the fluid pump 321, and with such a configuration, the fluid pump 321 can be used as a balancer. As shown in FIG. 5B, a first shaft 281 is attached to the center of the fluid pump 321 so as not to rotate relative to it. The first mass 271 is formed by hollowing out the fluid pump 321 or a member that rotates therewith.

The fluid pump 321 and the first crankshaft 14 are drivingly connected via the first pump gear 291 and the first crank gear 261, which are the first power transmission mechanism. The first pump gear 291 and the first crank gear 261 mesh. The first pump gear 291 is non-rotatably connected to the fluid pump 321 through the first shaft 281 . Gear teeth are formed around the first pump gear 291 and gear teeth are formed around the first crank gear 261 . Here, the diameter of the first crank gear 261 is approximately twice the diameter of the first pump gear 291 , and the number of gear teeth of the first crank gear 261 is twice the number of gear teeth of the first pump gear 291 . Further, the rotation directions of the first crankshaft 14 and the first crank gear 261 are opposite to those of the first pump gear 291 and the fluid motor 33 . 5A, the first crankshaft 14 and first crank gear 261 rotate clockwise, and the first pump gear 291 and fluid motor 33 rotate counterclockwise.

With such a configuration, the rotational speed of the fluid pump 321 becomes twice the rotational speed of the first crankshaft 14 as the engine 10 is operated. Also, the direction of rotation of the fluid pump 321 is opposite to the direction of rotation of the first crankshaft 14 . Therefore, secondary inertia force, torque reaction force, and rotational fluctuation vibration can be made extremely small. Moreover, the side pressure acting on the piston 13 can be canceled, and the friction acting on the piston 13 can be reduced.

As shown in FIG. 5A, the fluid pump 322 is formed with a second mass 272, and with such a configuration, the fluid pump 322 can be used as a balancer. As shown in FIG. 5B, a second shaft 282 is attached to the center of the fluid pump 322 so as not to rotate relative to it. The second mass 272 is formed by hollowing out the fluid pump 322 or a member that rotates therewith.

The fluid pump 322 and the second crankshaft 24 are drivingly connected via a second pump gear 292 and a second crank gear 262, which are the second power transmission mechanism. The second pump gear 292 and the second crank gear 262 mesh. A second pump gear 292 is non-rotatably connected to the fluid pump 322 via a second shaft 282 . Gear teeth are formed around the second pump gear 292 and gear teeth are formed around the second crank gear 262 . Here, the diameter of the second crank gear 262 is approximately twice the diameter of the second pump gear 292 , and the number of gear teeth of the second crank gear 262 is twice the number of gear teeth of the second pump gear 292 . Further, the rotation directions of the second crankshaft 24 and the second crank gear 262 are opposite to those of the second pump gear 292 and the fluid pump 322 . From the perspective of FIG. 5A, the second crankshaft 24 and the second crank gear 262 rotate counterclockwise, and the second pump gear 292 and the fluid pump 322 rotate clockwise.

With such a configuration, the rotation speed of the fluid pump 322 becomes twice the rotation speed of the second crankshaft 24 as the engine 10 is operated. Also, the direction of rotation of the fluid pump 322 is opposite to the direction of rotation of the second crankshaft 24 . Therefore, secondary inertia force, torque reaction force, and rotational fluctuation vibration can be made extremely small.

Referring to FIG. 5B, the first crank gear 261 and the first pump gear 291, which are the first power transmission mechanism, are arranged on the sixth direction side of the piston 13 and the like. Also, the second crank gear 262 and the second pump gear 292, which are the second power transmission mechanism, are arranged on the fifth direction side of the piston 13 and the like. With this configuration, the first crank gear 261 and the second crank gear 262 are arranged to face each other with the piston 13, the fluid pump 321 and the fluid pump 322 interposed therebetween. There is no interference with the 2 crank gear 262. Especially here, the diameters of the first crank gear 261 and the second crank gear 262 are formed large in order to rotate the fluid pumps 321 and 322 at double speed. Therefore, since the engine 10 is a twin-crankshaft engine, even if it is difficult to secure a large gap between the first crankshaft 14 and the second crankshaft 24, the first crank gear 261 and the second crankshaft can be rotated. Interference with the gear 262 can be prevented.

Furthermore, referring to FIG. 5A, since the engine 10 is a small engine with a relatively small displacement, the first crankshaft 14 and the second crankshaft 24 are also small. Therefore, when the engine 10 is viewed from the side, the diameter of the first crank gear 261 is longer than the width of the first crankshaft 14 . Similarly, the diameter of second crank gear 262 is greater than the width of second crankshaft 24 . In this case, the first crank gear 261 and the second crank gear 262 are likely to interfere with each other, but in this embodiment, as shown in FIG. It is arranged on the opposite side across the piston 13 and the like. By doing so, the small engine 10 can be effectively provided with the first crank gear 261 and the second crank gear 262 .

Further, the center 26 (center of gravity) of the fluid pump 321, the center 23 of the piston 13, and the center 19 (center of gravity) of the fluid pump 32 are arranged on a straight line extending along the third and fourth directions. Also, the distance L10 between the center 26 of the fluid pump 321 and the center 23 of the piston 13 and the distance L11 between the center 19 of the fluid pump 322 and the center 23 of the piston 13 are approximately equal. Such a configuration can minimize inertial forces, reaction forces and vibrations.

Also, in a typical engine, the eccentric masses are formed on the first crankshaft 14 and the second crankshaft 24, but in this embodiment, the eccentric masses are formed on the fluid pumps 321 and 322 or members rotating therewith. ing. With such a configuration, the configurations of the first crankshaft 14 and the second crankshaft 24 can be simplified, and the overall configuration of the engine 10 can be made compact.

Although the embodiments of the present invention have been described above, the present invention is not limited to the above embodiments.

For example, a multi-cylinder engine having a configuration other than the twin crankshaft engine shown in FIG. 4 and the like may be employed as the power generation source. Furthermore, an electric motor can also be employed as the power generation source.

Furthermore, in the above-described embodiment, the chain saw 30 and the blower 50 are illustrated as power engines, but other agricultural machines and construction machines can be employed as power working machines.

Furthermore, in the above, the number of shafts on the power output side is two and the number of shafts on the power input side is one, but this number can be changed arbitrarily.

In the above-described embodiment, oil or air is used as the fluid that flows through the power transmission means 41. However, other fluids may be used. Specifically, water or the like may be used. can.
Further, the invention that can be grasped from the above-described embodiment will be described below together with its effects.
A power working machine according to the present invention includes power generating means for outputting power from a power output shaft, power using means for using the power input from a power input shaft, and the power using means from the power generating means to the power using means. and a power transmission means for transmitting power, wherein the power transmission means transmits the power to the power output shaft through a fluid, which is different from the number of the power output shafts and the number of the power input shafts. to the power input shaft. Thus, according to the power working machine of the present invention, the power transmission means transmits the power from the power output shaft to the power input shaft via the fluid. Even if there is, power can be effectively transmitted from the power output shaft to the power input shaft.
Further, in the power working machine of the present invention, the power generating means is an engine, and the engine comprises a piston, a first crankshaft, a second crankshaft, and a second crankshaft connecting the piston and the first crankshaft. 1 connecting rod and a second connecting rod connecting the piston and the second crankshaft, wherein the power output shaft is dynamically connected to the first crankshaft or the second crankshaft. It is characterized by being a straight axis. Thus, according to the power working machine of the present invention, the power generating means includes the first crankshaft and the second crankshaft that are rotated by the reciprocating motion of one piston. Rotational moment and primary vibration are canceled. Furthermore, since the gyroscopic moment is canceled by the rotation of the first crankshaft and the second crankshaft, it is possible to suppress the gyroscopic moment from acting on the power operating machine in an unexpected direction. A power working machine, which is a chain saw, can be used more safely.
Further, in the power working machine of the present invention, the power generation means, the power use means and the power transmission means are integrated. Thus, according to the power working machine of the present invention, the power generation means, the power use means, and the power transmission means are integrated. Since the first connecting rod and the second connecting rod are provided, vibration generated from the entire device can be reduced.
Further, in the power working machine of the present invention, the power transmission means includes a fluid pump rotated by the power output shaft, a fluid motor driven by the fluid flowed by the fluid pump to rotate the power input shaft, characterized by having As a result, according to the power working machine of the present invention, power can be stably transmitted by transmitting power with the fluid pump and the fluid motor. are different, the power can be transmitted satisfactorily.
Further, the power working machine of the present invention is characterized in that the power generating means can be carried close to the torso of the user, and the power using means can be manually operated by the user. Thus, according to the power working machine of the present invention, since the power generating means is of the damping type, transmission of large vibrations from the power generating means to the user's body is suppressed.
Further, in the power working machine of the present invention, an eccentric mass is formed in the fluid pump or a member that is driven to be connected to the fluid pump and rotates. Thus, according to the power working machine of the present invention, the damping effect can be enhanced by using the fluid pump as a balancer.

10 Engine 12 Cylinder 13 Piston 14 First Crankshaft 141 First Crankpin 142 First Main Journal 15 First Connecting Rod 151 First Small End 152 First Large End 16 Piston Pin 19 Center 20 First Line of Symmetry 21 Second Second line of symmetry 22 Third line of symmetry 23 Center 24 Second crankshaft 241 Second crankpin 242 Second main journal 25 Second connecting rod 251 Second small end 252 Second big end 26 Center 261 First crank gear 262 Second crank gear 271 First mass 272 Second mass 281 First shaft 282 Second shaft 291 First pump gear 292 Second pump gear 30 Chainsaw 31 Casing 32 Fluid pump 321 Fluid pump 322 Fluid pump 33 Fluid motor 34 Oil flow path 35 Handle 36 Guide 37 Saw chain 38 Switch 39 Power output shaft 391 Power output shaft 392 Power output shaft 40 Power input shaft 41 Power transmission means 42 Power use means 43 Air flow path 44 Nozzle 45 Brush cutter 47 Brush cutter tooth 50 Blower 51 Casing 52 Blower pipe 53 fan 57 person 58 carrying device

Claims (5)

power generating means for outputting power from a power output shaft;
power using means for using the power input from the power input shaft;
power transmission means for transmitting the power from the power generating means to the power using means;
The power output shaft has a plurality of shafts,
The number of power input shafts is less than the number of power output shafts,
the power transmission means transmits the power from the power output shaft to the power input shaft via a fluid ;
A power working machine , wherein the power generation means, the power use means and the power transmission means are integrated . The power generation means is an engine,
The engine includes a piston, a first crankshaft, a second crankshaft, a first connecting rod connecting the piston and the first crankshaft, and a second crankshaft connecting the piston and the second crankshaft. 2 connecting rods;
The power working machine according to claim 1, wherein the power output shaft is a shaft that is dynamically connected to the first crankshaft or the second crankshaft. 3. The power transmission means includes a fluid pump rotated by the power output shaft, and a fluid motor driven by the fluid flowed by the fluid pump to rotate the power input shaft. The power working machine according to claim 1 or 2 . said power generating means being portable close to a user's torso;
A power working machine according to any one of claims 1 to 3 , wherein said power using means is manually operable by a user. 4. The power working machine according to claim 3 , wherein an eccentric mass is formed on the fluid pump or a member drivingly connected to the fluid pump to rotate.

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