WO2014162803A1 - Engine-driven tool - Google Patents

Engine-driven tool Download PDF

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Publication number
WO2014162803A1
WO2014162803A1 PCT/JP2014/055093 JP2014055093W WO2014162803A1 WO 2014162803 A1 WO2014162803 A1 WO 2014162803A1 JP 2014055093 W JP2014055093 W JP 2014055093W WO 2014162803 A1 WO2014162803 A1 WO 2014162803A1
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WO
WIPO (PCT)
Prior art keywords
engine
slider member
rotating body
working machine
disk
Prior art date
Application number
PCT/JP2014/055093
Other languages
French (fr)
Japanese (ja)
Inventor
健太郎 金谷
石田　茂敏
Original Assignee
日立工機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日立工機株式会社 filed Critical 日立工機株式会社
Publication of WO2014162803A1 publication Critical patent/WO2014162803A1/en

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Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K49/00—Dynamo-electric clutches; Dynamo-electric brakes
    • H02K49/02—Dynamo-electric clutches; Dynamo-electric brakes of the asynchronous induction type
    • H02K49/04—Dynamo-electric clutches; Dynamo-electric brakes of the asynchronous induction type of the eddy-current hysteresis type
    • H02K49/046—Dynamo-electric clutches; Dynamo-electric brakes of the asynchronous induction type of the eddy-current hysteresis type with an axial airgap
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01D—HARVESTING; MOWING
    • A01D34/00—Mowers; Mowing apparatus of harvesters
    • A01D34/01—Mowers; Mowing apparatus of harvesters characterised by features relating to the type of cutting apparatus
    • A01D34/412—Mowers; Mowing apparatus of harvesters characterised by features relating to the type of cutting apparatus having rotating cutters
    • A01D34/63—Mowers; Mowing apparatus of harvesters characterised by features relating to the type of cutting apparatus having rotating cutters having cutters rotating about a vertical axis
    • A01D34/76—Driving mechanisms for the cutters
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01D—HARVESTING; MOWING
    • A01D34/00—Mowers; Mowing apparatus of harvesters
    • A01D34/835—Mowers; Mowing apparatus of harvesters specially adapted for particular purposes
    • A01D34/90—Mowers; Mowing apparatus of harvesters specially adapted for particular purposes for carrying by the operator

Definitions

  • the present invention relates to an engine working machine having a centrifugal clutch such as a brush cutter, a chain saw, or a hedge trimmer, and more particularly to an engine working machine having a brake device that operates during idling.
  • a centrifugal clutch such as a brush cutter, a chain saw, or a hedge trimmer
  • Centrifugal clutches are clutches that transmit power by the frictional force of a clutch shoe provided on the rotating body side such as a crankshaft and a clutch drum provided on the driven side and provided on the outer peripheral side of the clutch shoe. Since the centrifugal force is small during low speed rotation such as in a state, the clutch shoe is located on the inner peripheral side, and the power of the rotating body is not transmitted to the driven side (clutch disengaged state).
  • the centrifugal clutch mechanism has a simple structure, and transmission and disconnection of power is performed at the engine speed, so no special operation for connecting and disconnecting the clutch is required, and it is widely used in portable engine working machines. ing. *
  • the present invention has been made in view of the above background, and an object of the present invention is to provide a brake mechanism having a light and simple structure that can guarantee long-term reliability in an engine working machine having a centrifugal clutch mechanism.
  • Another object of the present invention is to provide a non-contact type brake mechanism that operates in conjunction with opening and closing of an engine throttle.
  • Still another object of the present invention is to provide an engine working machine that is provided with a non-contact type brake mechanism on the drum side of a centrifugal clutch and can quickly reduce the rotation of a cutting blade or the like when the throttle is turned off. There is to do.
  • the contact type brake mechanism is configured to operate.
  • This brake mechanism is preferably an eddy current type brake.
  • a metal rotating body for example, a disk or an annular flange
  • the magnetic means is brought close to (opposed to) the rotating body in a non-contact state so that the magnetic field generated by the field means crosses the rotating body so that the power transmission member as the rotating body is braked by eddy current.
  • Brakes work equipment by generating force.
  • the brake mechanism includes a slider member that moves so as to approach or separate from the rotating body, and a plurality of brake mechanisms that are provided at a plurality of positions of the slider member and sandwiching the metal portion of the rotating body.
  • the slider member When the throttle is fully closed, the slider member is held at a position sandwiching the rotating body, and the magnetic field generated by the field means crosses the rotating body so that the throttle is opened.
  • the slider member When in the state, the slider member is moved to the outer region of the rotating body so that the magnetic field generated by the field means does not cross the rotating body.
  • the rotating body is preferably a disk, an annular plate, a flat plate-like rotating member, or a flange member provided on the clutch drum, and the slider member moves in conjunction with the operation of the throttle wire or lockout lever of the carburetor of the engine.
  • the slider member is moved in a direction parallel to the disk or the annular plate, and the tip portion close to the disk or the annular plate is moved from both sides of the disk or the annular plate.
  • Two arm portions are formed so as to be sandwiched, and a permanent magnet is provided at a position facing the disk or the annular plate of the arm portion.
  • the slider member is an oscillating type whose one end is pivotally supported, has an arm portion on the other end side, and is provided with urging means for urging the arm portion in a direction approaching the rotating body, The slider member is moved against the urging force of the urging means by operating the throttle wire or the lockout lever.
  • the swing shaft of the slider member is arranged so as to be parallel to the direction of the rotation center axis of the centrifugal clutch.
  • the slider member may be provided with a brake shoe that contacts the rotating body or the clutch drum, and a contact-type brake configuration may be used in addition to the non-contact type brake.
  • the non-contact type brake mechanism is operated when the throttle is closed in conjunction with the opening / closing of the throttle of the engine. It is possible to effectively brake a working device such as a cutting blade. Further, since the brake mechanism is a non-contact type, it is possible to suppress an impact generated during braking, and no wear or the like occurs, so that it can withstand long-term use.
  • the brake mechanism is an eddy current type brake and brakes on the work equipment side from the clutch drum of the centrifugal clutch. Therefore, the brake mechanism works extremely effectively on the work equipment rotated or driven by inertia. Can be made.
  • the brake mechanism is a permanent magnet that is provided on the slider member and acts on the rotating body. Therefore, unlike the field means such as an electromagnet, no electric power is required.
  • a brake mechanism with less fear of Further, since the brake is always operated when the throttle is completely closed, and the brake is turned off when the throttle is opened, the brake can be operated in conjunction with the operator's intention and operation. Also, if the operator releases the lockout lever for some reason during the work, the engine speed returns to idling and the centrifugal clutch mechanism also works, so the work equipment can be rotated in a short time. And the operation can be stopped.
  • the rotating body is a disk or an annular plate provided on the clutch drum, and the slider member moves in conjunction with the operation of the throttle wire or lockout lever of the carburetor of the engine.
  • a brake mechanism that operates reliably when the throttle is released or when the lockout lever is released can be realized.
  • the brake mechanism moves in a non-contact state with respect to the power transmission member and is an eddy current brake, the brake mechanism is not applied as rapidly as the contact type brake, so the engine working machine is smooth and easy to use. Can be realized.
  • the two arm portions are formed so as to be sandwiched from both sides of the disk or the annular plate in the slider member, and the permanent magnet is provided at a position facing the plate surface of the arm portion, the structure It is a simple brake mechanism and can realize a highly reliable engine working machine with little risk of failure.
  • the slider member is a swinging type whose one end is pivotally supported, has an arm portion on the other end side, and the urging force of the urging means by operating the throttle wire or the lockout lever. Since the slider member moves against this, a highly reliable brake mechanism that operates reliably in conjunction with the operation of the throttle wire or the lockout lever can be realized.
  • the brake mechanism can be disposed on the outer peripheral portion of the centrifugal clutch mechanism, and the compact engine A work machine can be realized.
  • the slider member is provided with the brake shoe that comes into contact with the rotating body or the clutch drum, so that a strong braking effect can be realized by both the non-contact type brake and the contact type brake.
  • FIG. 3 is a diagram illustrating a brake mechanism 40 according to an embodiment of the present invention, as viewed from a cross-sectional position of the AA portion in FIG. 2 (when the throttle lever is not operated, the brake is on).
  • FIG. 5 is a partial view of the brake mechanism 40 shown in FIG. 4 (a state where the brake is turned off by operating the throttle lever).
  • FIG. 5 is a cross-sectional view taken along a line BB in FIG. FIG.
  • FIG. 6 is a cross-sectional view showing the positional relationship between a slider member 71 and a disk 35 according to a first modification of the embodiment of the present invention, and is a view corresponding to the cross-sectional position of the BB part of FIG.
  • FIG. 6 is a cross-sectional view showing the positional relationship between a slider member 81 and a disk 35 according to a second modification of the embodiment of the present invention, and is a view corresponding to the cross-sectional position of the BB part of FIG.
  • FIG. 6 is a view showing a brake mechanism 240 according to a second embodiment of the present invention, as seen from a position conceived in the cross section of the AA portion of FIG. 2 (the brake lever is operated and the brake is turned off); Status).
  • FIG. 1 is a perspective view showing the overall shape of a brush cutter 100 as an example of an engine working machine.
  • the engine working machine 1 is attached to an engine main body 10 (driving unit) attached to one end of a main pipe 101, a gear unit 102 attached to the other end of the main pipe 101, and a spindle (not shown) in the gear unit 102.
  • the rotating cutting blade (rotating blade) 103 is provided.
  • the cutting blade 103 is attachable to and detachable from a spindle (not shown) provided on the gear unit 102, and a scattering protection cover 105 for preventing scattering of the cut grass is provided in the vicinity of the cutting blade 103. .
  • a handle 106 is assembled by a mounting member 108 at a substantially middle portion of the main pipe 101 in the longitudinal direction.
  • the handle 106 is a metal pipe having a substantially U-shape when viewed from the front, and resin grips 107a and 107b are provided at the tip portion.
  • a throttle lever 109 and a throttle lever lockout 112 are provided near the root of the grip 107a on the side that the operator grips with the right hand, and the operator adjusts the engine speed by operating the throttle lever 109 and trims the engine. The rotational operation speed of the blade 103 is adjusted.
  • An engine 10 is provided on the rear end side of the main pipe 101. Using a general-purpose engine that is small and lightweight and can obtain a large output, fuel can be replenished to enable long-term work. For example, a manual starter is widely used to start the engine. *
  • the throttle cable 110 has a wire disposed on the inner side (inner) and the outer side (outer) covered with a resin cover.
  • the cable 110 is a throttle of a carburetor 29 (see FIG. 2) described later. Connected to the mechanism. When the throttle lever 109 is pulled, a wire (described later) disposed inside the cable 110 is pulled toward the handle, and the throttle of the carburetor 29 is opened.
  • the cable 110 of this embodiment branches near the arrow 111, one cable 110a is connected to the carburetor 29, and the other cable 110b is connected to a brake mechanism described later.
  • FIG. 2 is a longitudinal sectional view showing the internal structure of the engine working machine 1 according to this embodiment.
  • the engine (main body) 10 is a two-cycle small engine, the crankshaft 13 is arranged coaxially with the main pipe 101 (see FIG. 1), and the cylinder 11 extends from the crankcase 14 substantially upward in the vertical direction.
  • the piston 12 is reciprocated up and down in the cylinder 11.
  • the high-voltage current generated by the ignition coil 23 is transmitted to the spark plug 25 through the ignition cord 24 and the plug cap 26.
  • a fuel tank 27 is provided below the crankcase 14 of the engine 10.
  • the fuel tank 27 contains a mixed oil of gasoline and oil for two cycles and is sent to a vaporizer described later. *
  • An end portion of a drive shaft (not shown) is connected to the front side (output side) of the crankshaft 13 via a clutch shaft 36 via a centrifugal clutch 30.
  • An engine cooling fan is integrally formed with the magnet rotor 22 to which the centrifugal clutch 30 is attached.
  • the centrifugal clutch 30 is a known centrifugal clutch in which a clutch shoe (oscillator) 31 is connected to a clutch drum 34 by centrifugal force when the rotation speed of the crankshaft 13 becomes a certain value or more.
  • a flat disk 35 having a circular outer shape is provided on the front side of the clutch drum 34.
  • the clutch drum 34 and the disk 35 are also fixed to the clutch shaft 36, and the clutch shaft 36 is rotatably held on the fan case 5 by a bearing 33.
  • the driving force supplied by the rotation of the engine 10 is provided on the magnet rotor 22 attached to the crankshaft 13, it is transmitted to the clutch drum 34 via the centrifugal clutch 30, and further provided in the main pipe 101 therefrom. This is transmitted to the gear unit 102 and the cutting blade 103 via a shaft (not shown).
  • a manual recoil starter 50 is provided on the rear end side of the crankshaft 13.
  • the recoil starter 50 is rotated at a high speed by pulling a starter rope 52 wound around a reel 51 with a starter handle described later, and the one-way clutch 56 protrudes radially outward by centrifugal force and comes into close contact with the drum 57. Rotate. Since the drum 57 is fixed to the crankshaft 13, when the drum 57 rotates, the crankshaft 13 also rotates and the engine can be started.
  • the released starter rope 52 is wound around the reel 51 by the restoring force of the spiral spring 53. *
  • FIG. 3 is a rear view of the engine working machine 1 according to the embodiment of the present invention.
  • a carburetor 29 is provided on the left side of the engine 10 via an insulator 19 connected to the intake port of the engine 10, and a storage space for an air cleaner that filters the intake air is formed outside (left side) of the carburetor 29.
  • An air cleaner cover 61 is provided.
  • a muffler 16 is provided on the side (right side) of the engine 10, and an exhaust port 16 a serving as an exhaust gas outlet is provided on the rear surface side of the muffler 16.
  • the muffler 16 is covered with a resin muffler cover 8 to prevent the operator from touching it directly.
  • the upper part of the engine 10 is covered with a cylinder cover 7.
  • a recoil starter 50 (see FIG.
  • a starter handle 54 is provided on the left side of the starter case 9.
  • a fuel tank 27 is provided below the crankcase 14.
  • the fuel tank 27 is a container formed of a translucent polymer resin, and a mixed fuel in which gasoline and a predetermined ratio of oil are mixed can be put in by removing the cap 28 attached to the opening.
  • FIG. 4 is a cross-sectional view of the cross-sectional position of the AA portion of FIG.
  • the AA portion in FIG. 2 has a shape when the fan case 5 is viewed from the back side. Since the fan case 5 is manufactured by integral molding of synthetic resin such as plastic, a plurality of ribs for increasing the strength are formed on the inner portion. Further, since the fan case 5 is fixed to the engine 10 by bolts (not shown) at three locations on the outer peripheral side, three screw holes 5c are formed. In the present embodiment, the centrifugal clutch 30 is accommodated in the inner portion of the fan case 5, and the brake mechanism 40 is provided in the vicinity thereof.
  • the brake mechanism 40 is pivotally supported by the rotating shaft 45 with respect to the fan case 5, and is disposed on the radially outer side when viewed from the centrifugal clutch 30.
  • the brake mechanism 40 is configured by a slider member 41 that moves so as to approach or leave the disk 35 that is a rotating body, and a wire 113 branched by a cable 110b is connected to the slider member.
  • An engaging element 114 is formed at the tip of the wire 113 on the slider member side, and the engaging element 114 is attached so as to be fitted into the recess of the slider member 41.
  • a metal cylindrical cap 111 d is provided at the end of the resin cover outside the cable 110 b and is held by a cable attachment portion 5 b provided in the fan case 5. *
  • a well-known centrifugal clutch 30 can be used.
  • the clutch clutch 31 is fixed to the crankshaft 13 with two bolts 32 via a mounting member (not shown), and these are axially connected.
  • a tension spring 33 that is biased toward the center is included.
  • a disk 35 that forms an annular plane region that protrudes to the outer peripheral side of the clutch drum 34.
  • the clutch drum 34 is made of an iron-based or aluminum-based metal material, but the disk 35 is a member for generating eddy currents, so it is important to be made of a metal-based member.
  • the disk 35 is made of an aluminum-based material because of the ease of generating eddy currents.
  • the slider member 41 can swing about 60 degrees around the rotation shaft 45.
  • FIG. 5 is a partial view of the brake mechanism 40 shown in FIG. 4 and omits the description of the surrounding fan case 5 portion.
  • the slider member 41 is a substantially L-shaped member when viewed as shown in FIG. 5, and the arm portion 42 is divided into one side (front side) and the other side (rear side) of the disk 35.
  • a permanent magnet 43 is disposed on a portion of the arm portion 42 that faces the disk 35.
  • the slider member 41 swings against the spring force of the torsion spring 46, and the permanent magnet 43 provided on the arm portion 42 moves radially outward (outer peripheral side) from the outer edge of the rotating region of the disk 35. To do. Due to this movement, the positional relationship such that the disk 35 crosses the magnetic field formed by the permanent magnet 43 is released and no eddy current is generated, so that the brake operation is released.
  • One end 46 a of the torsion spring 46 is held by a rib 5 d provided on the fan case 5, and the other end 46 b is engaged with a part of the main body portion of the slider member 41.
  • the slider member 41 rotates at a certain angle around the rotation shaft 45 provided on the outer periphery of the clutch drum 34.
  • the slider member 41 is constantly urged by a torsion spring 46 toward the center of the disk 35.
  • the slider member 41 is connected by a wire 113 so as to interlock with the operation of the throttle lever 109 or the throttle lever lockout 112 provided on the handle 106.
  • the throttle lever 109 or the throttle lever lockout 112 is not operated, the permanent magnets 43a and 43b of the slider member 41 are positioned on the disk 35 by being biased by the spring 17 so that the permanent magnets 43a and 43b As a result, an eddy current is generated on the disk 35, and a braking force is generated on the clutch drum 34.
  • FIG. 6 is a cross-sectional view taken along the line BB in FIG. 4 and shows the positional relationship between the slider member 41 and the disk 35.
  • Two arm portions 42 extending so as to protrude on both sides of the disk 35 are formed at the tip of the slider member 41.
  • Permanent magnets 43 a and 43 b are provided on the side of the arm portion 42 facing the disk 35.
  • the permanent magnets 43a and 43b are arranged such that the front side has an N-pole and the rear side has an S-pole polarity, and a magnetic field is formed as indicated by a magnetic field line from the permanent magnet 43b toward the 43a side.
  • the arm portion 42 including the permanent magnet 43 a is disposed on the outer periphery of the clutch drum 34, and the two permanent magnets 43 a are provided with a gap larger than the thickness of the disk of the clutch drum 34.
  • the slider member 41 is located at a position where the disk 35 does not face (face to face) between the permanent magnets 43a and 43b that are spaced apart from each other around a rotation shaft 45 provided on the outer periphery of the clutch drum 34. Rotate up to. At this time, in the region where the slider member 41 rotates, there is a gap between the disk 35 and the permanent magnets 43a and 43b, so that they do not contact each other.
  • a plurality (two) of permanent magnets 43a and 43b are provided to form a magnetic field from one permanent magnet side to the other permanent magnet side, and move relative to the magnetic field inside the magnetic field.
  • a metal object rotating body
  • an eddy current is generated in the disk 35, so that a braking force can be obtained on the rotating body.
  • the disk 35 is provided on the front side of the substantially cup-shaped clutch drum 34, and how the disk 35 is attached to the clutch drum 34 is arbitrary. Further, even if a flange-like member (annular flat plate portion) is formed integrally with the clutch drum 34, the same function is achieved.
  • FIG. 7 shows the slider member 71 according to the first modification, and is a view corresponding to the cross-sectional position of the BB portion in FIG.
  • the basic part of the slider member 71 can be manufactured in the same shape and size as the slider member 41.
  • only the permanent magnets 43 a and 43 b are provided on the slider member 41, and the slider member 41 and the permanent magnets 43 a and 43 b are completely in non-contact with the disk 35.
  • a brake shoe 76 is provided on the crotch portion of the two arm portions 72 of the slider member 71 in order to enhance the braking force, and the brake caused by the eddy current is applied.
  • the brake shoe 76 is configured to come into contact with the outer peripheral portion of the disk 35 when the is applied.
  • FIG. 8 shows a slider member 81 according to a second modification, and is a view corresponding to the cross-sectional position of the BB portion of FIG.
  • the basic part of the slider member 81 can be manufactured in the same shape and size as the slider member 41.
  • a part of the clutch drum 34 which is omitted in FIGS. 6 and 7, is also illustrated.
  • the mounting positions of the slider member 71 and the brake shoe 86 shown in FIG. 7 are different.
  • the brake shoe 86 is attached to the tip of the arm portion 82 on the rear side so that the brake shoe 86 comes into contact with the clutch drum 34.
  • the brake mechanism 40 is automatically operated in conjunction with the operation of the throttle lever and / or the lockout lever.
  • the movable member (the cutting blade 103) can be stopped. Further, when the engine 10 is idling and the centrifugal clutch 30 is in a disconnected state, a braking effect can be obtained even when the movable member (the cutting blade 103) moves for some reason. Further, since a completely non-contact brake mechanism can be realized if no brake shoe is used for the brake mechanism 40, an engine working machine with further improved safety can be realized without adversely affecting the operation on the engine 10 side.
  • the brake mechanism 40 of the present embodiment is provided in the vicinity of the centrifugal clutch 30, the brake mechanism 40 is not limited only to that portion, but is arbitrary between the clutch drum 34 and the rotating portion (the cutting blade 103) of the work equipment. You may comprise so that it may provide in a location.
  • an eddy current type non-contact brake mechanism acting on the cutting blade 103 may be provided.
  • FIG. 9 (1) is a diagram showing the arrangement position of the brake mechanism according to the second embodiment.
  • the disk 35 and the clutch drum 34 shown in FIG. 2 are manufactured in an integrated configuration, and a metal rotor that generates eddy currents is formed on the outer peripheral side of the cup-shaped clutch drum 94. And an annular portion 94a extending radially outward.
  • the brake mechanism 40 moves in the radial direction with respect to the annular portion 94a as indicated by an arrow 68. What is necessary is just to comprise the specific structure of the brake mechanism 40 similarly to the structure demonstrated in the 1st Example.
  • the position in the axial direction (front-rear direction) for forming the annular portion 94a is set at the substantially center of the outer peripheral surface, but the position where the axial position is formed is arbitrary. It is. *
  • FIG. 9 (2) is a view showing a brake mechanism showing a modification of the second embodiment.
  • a cylindrical portion 96a extending to the front side of the clutch drum 96 is formed, and a brake mechanism 90 that moves in the axial direction as shown by an arrow 69 with respect to the cylindrical portion 96a is provided.
  • the brake mechanism 90 does not swing with the slider member 41 pivotally supported unlike the brake mechanism 40, but may be a type in which the slider member moves linearly in the axial direction as indicated by an arrow 69. This is because the eddy current is generated not by the disk-shaped member but by the cylindrical member.
  • the permanent magnet is cylindrical when the throttle wire is not pulled or when the lockout lever is released. It may be configured such that the permanent magnet is retracted forward from the cylindrical portion 96a in the axial direction when the throttle wire is pulled when the throttle wire is pulled.
  • the brake means can be realized by forming the metal rotating body at an arbitrary position of the clutch drum of the centrifugal clutch. It should be noted that the place where the metal rotating body is provided is not only provided directly on the clutch drum, but the same effect can be obtained by providing it on the clutch shaft 36, a rotating shaft (not shown), or in the vicinity of the spindle of the gear unit 102. .
  • a slider including a centrifugal clutch that transmits power and a permanent magnet that rotates so as to be engaged without contacting a flange provided on the clutch drum is operated by a throttle or the like.
  • the axial rotation direction of the slider member is set upside down with respect to the first embodiment.
  • the structure in which the slider member 241 is biased toward the center of the disk 35 is left as it is, and the position of the rotation shaft 245 with respect to the rotation direction 234 is configured to be opposite to the slider member 241. That is, in the first embodiment described with reference to FIGS. 4 and 5, the slider member 41 is located on the downstream side (arrow a side) with respect to the rotational direction from the imaginary line 220 connecting the rotational axis to the central axis of the centrifugal clutch 30.
  • the slider member 41 is located downstream of the rotation shaft 45 in the rotation direction.
  • the slider member 241 is located on the upstream side (arrow b side) with respect to the rotational direction from the imaginary line 220 connecting the rotational shaft 245 to the central axis of the centrifugal clutch 30.
  • the slider member 241 is positioned upstream of the rotation shaft 245 in the rotation direction. At this time, the positional relationship of the cable 210b is changed, and the arrangement of the springs 246 may be changed as appropriate.
  • the slider member 241 is urged toward the center of the disk 35.
  • the structure of the rotary shaft 245 with respect to the rotational direction is left on the opposite side of the configuration of FIGS.
  • the shape of the slider 241 can be the same as that of the slider 41 used in the first embodiment, and the positions and shapes of the two permanent magnets attached thereto can be the same.
  • the two permanent magnets are positioned so as to sandwich the disk 35, and an eddy current is generated in the disk.
  • the movement path of the permanent magnet viewed from the direction of FIG.
  • the tangential direction of the movement trajectory when approaching the disk 35 of the permanent magnet and the tangential direction of the circumferential direction of the disk 35 are the same direction, and the angle formed by them is about 50 degrees.
  • the moving direction of the slider member 241 is set so that the moving direction when the slider member 241 approaches the disk and the rotating direction of the disk 35 are the same, and the angle formed by the tangent is less than 60 degrees, preferably as small as possible. To do.
  • a hand-held type brush cutter is used as an example of an engine working machine.
  • other engine working machines such as a chain saw, a hedge trimmer, etc., or a backpack that carries the engine on the back.
  • the present invention may be applied to a working machine of a type.
  • the engine is not limited to a two-cycle engine, and may be a four-cycle engine.
  • the drive source of the work equipment is not limited to the engine but may be an electric type or an air type.

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  • Environmental Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Harvester Elements (AREA)

Abstract

Provided is a braking device for an engine-driven tool, capable of stopping a cutting blade that is rotating by inertia, and also being lightweight and capable of maintaining long-term reliability. The engine-driven tool allows transmission of engine output through a centrifugal clutch to an implement such as a cutting blade, wherein the engine-driven tool is configured so that an eddy-current non-contact braking mechanism (40) is operated when a throttle is in a closed state. In the braking mechanism (40), a disc (35) is provided to the clutch drum (34) of the centrifugal clutch (30), and a permanent magnet is disposed so as to face a rotating body in a non-contact state in a positional relationship such that the magnetic field generated by the permanent magnet intersects the disc (35), whereby an eddy current produces a braking force in the rotating body, stopping the rotary motion of the cutting blade. When a throttle wire is pulled, the braking mechanism (40) is moved and the permanent magnet is moved away from the disc (35), whereby the brake is released.

Description

エンジン作業機Engine working machine
本発明は、刈払機、チェンソー、ヘッジトリマなどの遠心クラッチを有するエンジン作業機に関し、特にアイドリング時に作用するブレーキ装置を有するエンジン作業機に関する。 The present invention relates to an engine working machine having a centrifugal clutch such as a brush cutter, a chain saw, or a hedge trimmer, and more particularly to an engine working machine having a brake device that operates during idling.
刈払機、チェンソー、ヘッジトリマなどの携帯型のエンジン作業機では、エンジンの出力をクランク軸に直接又は間接的に接続された遠心クラッチ機構を介して、刈刃、ソーチェン等を駆動する。遠心クラッチは、クランク軸等の回転体側に設けられたクラッチシューと、駆動される側に設けられクラッチシューの外周側に設けられるクラッチドラムによる摩擦力で動力を伝達するクラッチであり、エンジンがアイドリング状態等の低速回転時には遠心力が小さいためにクラッチシューが内周側に位置しており、回転体の動力を駆動される側には伝達しない（クラッチ断の状態）。エンジンの回転数が上昇して所定の回転数（クラッチ接続回転数）以上になると、遠心力によってクラッチシューが外周側に移動してドラムの内周面と接することにより回転体から駆動される側への動力伝達が行われる（クラッチ接続の状態）。遠心クラッチ機構は構造が簡単あり、動力の伝達及び遮断がエンジンの回転数で行なわれるため、クラッチの接続と遮断のための特別の操作が不要で、携帯型のエンジン作業機においては広く用いられている。　 In portable engine working machines such as a brush cutter, a chain saw, and a hedge trimmer, a cutting blade, a saw chain, and the like are driven through a centrifugal clutch mechanism in which the output of the engine is directly or indirectly connected to a crankshaft. Centrifugal clutches are clutches that transmit power by the frictional force of a clutch shoe provided on the rotating body side such as a crankshaft and a clutch drum provided on the driven side and provided on the outer peripheral side of the clutch shoe. Since the centrifugal force is small during low speed rotation such as in a state, the clutch shoe is located on the inner peripheral side, and the power of the rotating body is not transmitted to the driven side (clutch disengaged state). When the engine speed rises and exceeds a predetermined speed (clutch connection speed), the clutch shoe moves to the outer peripheral side by centrifugal force and comes into contact with the inner peripheral surface of the drum to be driven from the rotating body. Power is transmitted to the clutch (clutch connected state). The centrifugal clutch mechanism has a simple structure, and transmission and disconnection of power is performed at the engine speed, so no special operation for connecting and disconnecting the clutch is required, and it is widely used in portable engine working machines. ing. *
このような遠心クラッチ機構は、エンジンの回転数が低下すると接続が遮断されるため、刈刃等が慣性力により回転を継続してしまうことがある。また、携帯型のエンジン作業機においては、実作業状態にあるとき以外のエンジンの回転数をより迅速に低下させたいという要望があった。このため、エンジン作業機においては遠心クラッチの採用と共に機械的なブレーキ機構を設けることも提案されている。刈払機に用いられるブレーキとして、例えば特許文献１に示されたものがある。このブレーキ装置は、その第６図に開示されているように、ブレーキドラムの外周に接してブレーキシューを配置し、このブレーキシューとアームとの間にブレーキワイヤを張り、ブレーキばねでブレーキワイヤを引き戻すとともに、ブレーキドラムにブレーキシューを押しつける常時作動形の構造であり、アームを操作しない場合には、ブレーキばねでブレーキシューを押しつけ、ブレーキドラムにブレーキが働くというものである。 Since such a centrifugal clutch mechanism is disconnected when the engine speed decreases, the cutting blade or the like may continue to rotate due to inertial force. Moreover, in the portable engine working machine, there has been a demand for more rapidly reducing the engine speed other than in the actual working state. For this reason, it has also been proposed to provide a mechanical brake mechanism along with the adoption of a centrifugal clutch in an engine working machine. As a brake used for a brush cutter, there exists a thing shown by patent document 1, for example. In this brake device, as disclosed in FIG. 6, a brake shoe is disposed in contact with the outer periphery of the brake drum, a brake wire is stretched between the brake shoe and the arm, and the brake wire is attached by a brake spring. It is a structure of a constantly operating type that pulls back and presses the brake shoe against the brake drum. When the arm is not operated, the brake shoe is pressed by the brake spring, and the brake acts on the brake drum.
特開２００２－１８６３２７号公報JP 2002-186327 A
しかし、上記の構造では、ブレーキを長期間使用すると、ブレーキシューは、ブレーキワイヤに連結した位置で次第にすり減り、ブレーキの働きが悪くなり、長期の使用に耐えることができなくなる。この場合、ブレーキシューを交換する必要がある。また、ブレーキ作動時にブレーキシューとブレーキドラムの接触により衝撃が発生するため、操作性が悪化する。また、ブレーキ機構のための部品点数が非常に多く、それゆえブレーキ機構を収容するスペースも大きくなるため携帯型のエンジン作業機の重量、サイズが増大することでコストの増加、作業性の悪化を招くことになる。更に、大きな制動力を発生させようとすると、反対に大きな解除力を要することになり、使い勝手が悪いという問題があった。　 However, in the above structure, when the brake is used for a long period of time, the brake shoe gradually wears out at the position connected to the brake wire, the function of the brake is deteriorated, and the long-term use cannot be endured. In this case, it is necessary to replace the brake shoe. In addition, since an impact is generated by the contact between the brake shoe and the brake drum when the brake is operated, the operability is deteriorated. In addition, the number of parts for the brake mechanism is very large, and therefore the space for accommodating the brake mechanism also becomes large, which increases the weight and size of the portable engine work machine, which increases costs and deteriorates workability. Will be invited. Furthermore, when a large braking force is generated, a large releasing force is required on the contrary, and there is a problem that the usability is poor. *
本発明は上記背景に鑑みてなされたもので、その目的は、遠心クラッチ機構を有するエンジン作業機において、長期間信頼性を保証できる、軽量で簡単な構造のブレーキ機構を提供することにある。　 The present invention has been made in view of the above background, and an object of the present invention is to provide a brake mechanism having a light and simple structure that can guarantee long-term reliability in an engine working machine having a centrifugal clutch mechanism. *
本発明の他の目的は、エンジンのスロットルの開閉に連動させて作動する非接触式のブレーキ機構を提供することにある。　 Another object of the present invention is to provide a non-contact type brake mechanism that operates in conjunction with opening and closing of an engine throttle. *
本発明のさらに他の目的は、遠心クラッチのドラム側に非接触式のブレーキ機構を設けて、スロットルをオフにした際に刈刃等の回転を迅速に低下させることのできるエンジン作業機を提供することにある。 Still another object of the present invention is to provide an engine working machine that is provided with a non-contact type brake mechanism on the drum side of a centrifugal clutch and can quickly reduce the rotation of a cutting blade or the like when the throttle is turned off. There is to do.
本願において開示される発明のうち代表的なものの特徴を説明すれば次の通りである。　 The characteristics of representative ones of the inventions disclosed in the present application will be described as follows. *
本発明の一つの特徴によれば、エンジンの動力を遠心クラッチを介して刈刃等の作業機器に伝達させるエンジン作業機において、エンジンのスロットルの開閉に連動させてスロットルが閉状態の時に、非接触式のブレーキ機構を動作させるように構成した。このブレーキ機構は、渦電流式ブレーキとするのが好ましく、遠心クラッチのクラッチドラムから作業機器側の回転部分に金属製の回転体（例えば円盤、円環状のフランジ）を設け、永久磁石からなる界磁手段を非接触状態で回転体に接近（対向）させて、界磁手段により発生された磁界が回転体を横切るような位置関係とすることで、回転体たる動力伝達部材に渦電流によるブレーキ力を発生させることにより作業機器を制動する。　 According to one aspect of the present invention, in an engine working machine that transmits engine power to a working device such as a cutting blade via a centrifugal clutch, when the throttle is closed in conjunction with opening and closing of the engine throttle, The contact type brake mechanism is configured to operate. This brake mechanism is preferably an eddy current type brake. A metal rotating body (for example, a disk or an annular flange) is provided on the rotating part on the work equipment side from the clutch drum of the centrifugal clutch, and a field composed of a permanent magnet. The magnetic means is brought close to (opposed to) the rotating body in a non-contact state so that the magnetic field generated by the field means crosses the rotating body so that the power transmission member as the rotating body is braked by eddy current. Brakes work equipment by generating force. *
本発明の他の特徴によれば、ブレーキ機構は、回転体に対して接近又は離合可能に移動するスライダ部材と、スライダ部材の複数箇所であって回転体の金属部分を挟む位置に設けられる複数の永久磁石を有し、スロットルが完全に閉状態の時はスライダ部材が回転体を挟む位置に保持されて界磁手段により発生された磁界が回転体を横切るような位置関係とし、スロットルが開状態の時にはスライダ部材を回転体の外側領域に移動させて界磁手段により発生された磁界が回転体を横切らないような位置関係とした。回転体はクラッチドラムに設けられた円盤、円環板、平板状の回転部材、フランジ部材とするのが好ましく、スライダ部材はエンジンの気化器のスロットルワイヤ又はロックアウトレバーの操作と連動して移動するように構成する。　 According to another feature of the present invention, the brake mechanism includes a slider member that moves so as to approach or separate from the rotating body, and a plurality of brake mechanisms that are provided at a plurality of positions of the slider member and sandwiching the metal portion of the rotating body. When the throttle is fully closed, the slider member is held at a position sandwiching the rotating body, and the magnetic field generated by the field means crosses the rotating body so that the throttle is opened. When in the state, the slider member is moved to the outer region of the rotating body so that the magnetic field generated by the field means does not cross the rotating body. The rotating body is preferably a disk, an annular plate, a flat plate-like rotating member, or a flange member provided on the clutch drum, and the slider member moves in conjunction with the operation of the throttle wire or lockout lever of the carburetor of the engine. To be configured. *
本発明のさらに他の特徴によれば、スライダ部材は、円盤又は円環板と平行な方向に移動され、円盤又は円環板に近接する先端部分には、円盤又は円環板の両面側から挟みこむように２つのアーム部が形成され、アーム部の円盤又は円環板に対向する位置に永久磁石が設けられる。スライダ部材は一端が軸支された揺動式であって、他端側にアーム部を有し、アーム部を回転体に対して近接する方向に付勢する付勢手段をスライダ部材に設け、スロットルワイヤ又はロックアウトレバーの操作によって付勢手段の付勢力に抗してスライダ部材が移動させる。スライダ部材の揺動軸は遠心クラッチの回転中心軸方向と平行となるように配置される。尚、ブレーキ効果の補助のためにスライダ部材に回転体又はクラッチドラムと当接するブレーキシューを設けて、非接触式のブレーキに加えて接触式のブレーキ構成を併用するように構成しても良い。 According to still another feature of the present invention, the slider member is moved in a direction parallel to the disk or the annular plate, and the tip portion close to the disk or the annular plate is moved from both sides of the disk or the annular plate. Two arm portions are formed so as to be sandwiched, and a permanent magnet is provided at a position facing the disk or the annular plate of the arm portion. The slider member is an oscillating type whose one end is pivotally supported, has an arm portion on the other end side, and is provided with urging means for urging the arm portion in a direction approaching the rotating body, The slider member is moved against the urging force of the urging means by operating the throttle wire or the lockout lever. The swing shaft of the slider member is arranged so as to be parallel to the direction of the rotation center axis of the centrifugal clutch. In order to assist the braking effect, the slider member may be provided with a brake shoe that contacts the rotating body or the clutch drum, and a contact-type brake configuration may be used in addition to the non-contact type brake.
請求項１の発明によれば、エンジンのスロットルの開閉に連動させてスロットルが閉状態の時に、非接触式のブレーキ機構を動作させるので、遠心クラッチが非接続状態の下で慣性運動をしている刈刃等の作業機器を効果的に制動することができる。また、ブレーキ機構は非接触式であるので、制動時に発生する衝撃を抑制することができ、摩耗等が生じることも無いため、長期間の使用に耐えることができる。請求項２の発明によれば、ブレーキ機構は渦電流式ブレーキで有り、遠心クラッチのクラッチドラムから作業機器側で制動するので、惰性で回転または駆動される作業機器に対してきわめて効果的に作用させることができる。請求項３の発明によれば、ブレーキ機構は、スライダ部材に設けられ回転体に作用する永久磁石であるので、電磁石等の界磁手段と違って電力を必要としないので、構造がシンプルで故障の恐れが少ないブレーキ機構を実現できる。また、スロットルが完全に閉状態の時は常にブレーキが作動して、スロットルを開けた状態でブレーキをオフにするので、作業者の意思や動作と連動させるようにブレーキを作動させることができる。また作業者が何らかの理由で、作業中にロックアウトレバーを開放してしまった場合には、エンジンの回転数がアイドリングに戻ると共に遠心クラッチ機構にもブレーキが働くので、短時間で作業機器の回転や動作を停止させることができる。請求項４の発明によれば制動時には複数の永久磁石によって回転体の金属部分を挟むような位置関係とするので、永久磁石を用いて十分な制動力を実現できる。請求項５の発明によれば、回転体はクラッチドラムに設けられた円盤又は円環板であり、スライダ部材は、エンジンの気化器のスロットルワイヤ又はロックアウトレバーの操作と連動して移動するので、作業者の意思と連動させてスロットル解除時やロックアウトレバー解放時に確実に作動するブレーキ機構を実現できる。また、ブレーキ機構は動力伝達部材に対して非接触状態で移動するうえに、渦電流ブレーキであるため、接触式のブレーキほど急激にブレーキが掛かることが無いため、スムーズで使い勝手の良いエンジン作業機を実現できる。請求項６の発明によれば、スライダ部材に円盤又は円環板の両面側から挟みこむように２つのアーム部が形成され、アーム部の板面に対向する位置に永久磁石が設けられるので、構造的にシンプルなブレーキ機構であり故障の恐れが少なくて信頼性の高いエンジン作業機を実現できる。請求項７の発明によれば、スライダ部材は一端が軸支された揺動式であって、他端側にアーム部を有し、スロットルワイヤ又はロックアウトレバーの操作によって付勢手段の付勢力に抗してスライダ部材が移動するので、スロットルワイヤ又はロックアウトレバーの操作に連動して確実に作動する信頼性の高いブレーキ機構を実現できる。請求項８の発明によれば、スライダ部材の揺動軸は遠心クラッチの回転中心軸方向と平行となるように配置されるので、遠心クラッチ機構の外周部分にブレーキ機構を配置でき、コンパクトなエンジン作業機を実現できる。請求項９の発明によれば、スライダ部材に、回転体又はクラッチドラムと当接するブレーキシューを設けたので、非接触式のブレーキと接触式ブレーキの双方により強力なブレーキ効果を実現できる。　 According to the first aspect of the invention, the non-contact type brake mechanism is operated when the throttle is closed in conjunction with the opening / closing of the throttle of the engine. It is possible to effectively brake a working device such as a cutting blade. Further, since the brake mechanism is a non-contact type, it is possible to suppress an impact generated during braking, and no wear or the like occurs, so that it can withstand long-term use. According to the invention of claim 2, the brake mechanism is an eddy current type brake and brakes on the work equipment side from the clutch drum of the centrifugal clutch. Therefore, the brake mechanism works extremely effectively on the work equipment rotated or driven by inertia. Can be made. According to the invention of claim 3, the brake mechanism is a permanent magnet that is provided on the slider member and acts on the rotating body. Therefore, unlike the field means such as an electromagnet, no electric power is required. A brake mechanism with less fear of Further, since the brake is always operated when the throttle is completely closed, and the brake is turned off when the throttle is opened, the brake can be operated in conjunction with the operator's intention and operation. Also, if the operator releases the lockout lever for some reason during the work, the engine speed returns to idling and the centrifugal clutch mechanism also works, so the work equipment can be rotated in a short time. And the operation can be stopped. According to the fourth aspect of the present invention, since the positional relationship is such that the metal portion of the rotating body is sandwiched between the plurality of permanent magnets during braking, a sufficient braking force can be realized using the permanent magnets. According to the invention of claim 5, the rotating body is a disk or an annular plate provided on the clutch drum, and the slider member moves in conjunction with the operation of the throttle wire or lockout lever of the carburetor of the engine. In conjunction with the operator's intention, a brake mechanism that operates reliably when the throttle is released or when the lockout lever is released can be realized. In addition, since the brake mechanism moves in a non-contact state with respect to the power transmission member and is an eddy current brake, the brake mechanism is not applied as rapidly as the contact type brake, so the engine working machine is smooth and easy to use. Can be realized. According to the invention of claim 6, since the two arm portions are formed so as to be sandwiched from both sides of the disk or the annular plate in the slider member, and the permanent magnet is provided at a position facing the plate surface of the arm portion, the structure It is a simple brake mechanism and can realize a highly reliable engine working machine with little risk of failure. According to the seventh aspect of the present invention, the slider member is a swinging type whose one end is pivotally supported, has an arm portion on the other end side, and the urging force of the urging means by operating the throttle wire or the lockout lever. Since the slider member moves against this, a highly reliable brake mechanism that operates reliably in conjunction with the operation of the throttle wire or the lockout lever can be realized. According to the eighth aspect of the present invention, since the swing shaft of the slider member is disposed so as to be parallel to the direction of the rotation center axis of the centrifugal clutch, the brake mechanism can be disposed on the outer peripheral portion of the centrifugal clutch mechanism, and the compact engine A work machine can be realized. According to the ninth aspect of the present invention, the slider member is provided with the brake shoe that comes into contact with the rotating body or the clutch drum, so that a strong braking effect can be realized by both the non-contact type brake and the contact type brake. *
本発明の上記及び他の目的ならびに新規な特徴は、以下の明細書の記載及び図面から明らかになるであろう。 The above and other objects and novel features of the present invention will become apparent from the following description and drawings.
エンジン作業機の一例である刈払機１００の全体形状を示す斜視図である。It is a perspective view which shows the whole shape of the brush cutter 100 which is an example of an engine working machine. 本発明の実施例に係るエンジン作業機１の内部構造を示す縦断面図である。It is a longitudinal section showing the internal structure of engine working machine 1 concerning the example of the present invention. 本発明の実施例に係るエンジン作業機１の背面図である。It is a rear view of the engine working machine 1 which concerns on the Example of this invention. 本発明の実施例に係るブレーキ機構４０を示す図であって、図２のＡ－Ａ部の断面位置から見た図である（スロットルレバーを操作していない場合でブレーキＯＮの状態）。FIG. 3 is a diagram illustrating a brake mechanism 40 according to an embodiment of the present invention, as viewed from a cross-sectional position of the AA portion in FIG. 2 (when the throttle lever is not operated, the brake is on). 図４に示したブレーキ機構４０の部分図である（スロットルレバーを操作してブレーキがＯＦＦの状態）。FIG. 5 is a partial view of the brake mechanism 40 shown in FIG. 4 (a state where the brake is turned off by operating the throttle lever). 図４のＢ－Ｂ部の断面図であり、スライダ部材４１と円盤３５の位置関係を示す断面図である。FIG. 5 is a cross-sectional view taken along a line BB in FIG. 本発明の実施例の第１の変形例に係るスライダ部材７１と円盤３５の位置関係を示す断面図であって、図４のＢ－Ｂ部の断面位置に相当する図である。FIG. 6 is a cross-sectional view showing the positional relationship between a slider member 71 and a disk 35 according to a first modification of the embodiment of the present invention, and is a view corresponding to the cross-sectional position of the BB part of FIG. 本発明の実施例の第２の変形例に係るスライダ部材８１と円盤３５の位置関係を示す断面図であって、図４のＢ－Ｂ部の断面位置に相当する図である。FIG. 6 is a cross-sectional view showing the positional relationship between a slider member 81 and a disk 35 according to a second modification of the embodiment of the present invention, and is a view corresponding to the cross-sectional position of the BB part of FIG. 本発明の第２の実施例に係るブレーキ機構を示す断面図である。It is sectional drawing which shows the brake mechanism which concerns on the 2nd Example of this invention. 本発明の第２の実施例に係るブレーキ機構２４０を示す図であって、図２のＡ－Ａ部の断面に想到する位置から見た図である（スロットルレバーを操作していてブレーキＯＦＦの状態）。FIG. 6 is a view showing a brake mechanism 240 according to a second embodiment of the present invention, as seen from a position conceived in the cross section of the AA portion of FIG. 2 (the brake lever is operated and the brake is turned off); Status).
以下、本発明の実施例を図面に基づいて説明する。なお、以下の図において、同一の部分には同一の符号を付し、繰り返しの説明は省略する。また、本明細書においては、前後左右、上下の方向は図中に示す方向であるとして説明する。 Embodiments of the present invention will be described below with reference to the drawings. In the following drawings, the same portions are denoted by the same reference numerals, and repeated description is omitted. Further, in this specification, description will be made assuming that the front, rear, left, right, and up and down directions are directions shown in the drawing.
図１はエンジン作業機の一例である刈払機１００の全体形状を示す斜視図である。エンジン作業機１は、メインパイプ１０１の一端に取り付けられたエンジン本体部１０(駆動部)と、メインパイプ１０１の他端側に取り付けられたギヤユニット１０２と、ギヤユニット１０２に図示しないスピンドルに取り付けられた回転する刈刃（回転刃）１０３を有する。刈刃１０３はギヤユニット１０２に設けられたスピンドル（図示せず）に対して着脱可能であり、刈刃１０３の近傍には、刈り払った草の飛散防止のための飛散防御カバー１０５が設けられる。メインパイプ１０１の長手方向のほぼ中間部分には取付部材１０８によってハンドル１０６が組み付けられる。ハンドル１０６は、前方から見た際に略Ｕ字状の形状をした金属製のパイプであり、先端部分には樹脂製のグリップ１０７ａ、１０７ｂが設けられる。作業者が右手で把持する側のグリップ１０７ａの根本付近にはスロットルレバー１０９、スロットルレバーロックアウト１１２が設けられ、作業者は、スロットルレバー１０９を操作することでエンジンの回転数を調整して刈刃１０３の回転動作速度を調整する。メインパイプ１０１の後端側にはエンジン１０が設けられる。小型軽量で大きな出力を得ることができる汎用エンジンを用いて、燃料を補給することにより長時間の作業を可能としたものである。エンジンを起動するために、例えば手動式のスタータが広く用いられる。　 FIG. 1 is a perspective view showing the overall shape of a brush cutter 100 as an example of an engine working machine. The engine working machine 1 is attached to an engine main body 10 (driving unit) attached to one end of a main pipe 101, a gear unit 102 attached to the other end of the main pipe 101, and a spindle (not shown) in the gear unit 102. The rotating cutting blade (rotating blade) 103 is provided. The cutting blade 103 is attachable to and detachable from a spindle (not shown) provided on the gear unit 102, and a scattering protection cover 105 for preventing scattering of the cut grass is provided in the vicinity of the cutting blade 103. . A handle 106 is assembled by a mounting member 108 at a substantially middle portion of the main pipe 101 in the longitudinal direction. The handle 106 is a metal pipe having a substantially U-shape when viewed from the front, and resin grips 107a and 107b are provided at the tip portion. A throttle lever 109 and a throttle lever lockout 112 are provided near the root of the grip 107a on the side that the operator grips with the right hand, and the operator adjusts the engine speed by operating the throttle lever 109 and trims the engine. The rotational operation speed of the blade 103 is adjusted. An engine 10 is provided on the rear end side of the main pipe 101. Using a general-purpose engine that is small and lightweight and can obtain a large output, fuel can be replenished to enable long-term work. For example, a manual starter is widely used to start the engine. *
作業者はスロットルレバーロックアウト１１２を把持した状態で作業を行い、なんらかの要因でスロットルレバーロックアウト１１２の把持を解除した場合には、スロットルレバー１０９が直ちに閉位置に戻り、エンジンの回転数がアイドリング回転数まで落ちるように構成される。スロットル用のケーブル１１０は、内側（インナー）にワイヤが配置され、外側（アウター）が樹脂製のカバーで覆われたものであって、ケーブル１１０は後述する気化器２９（図２参照）のスロットル機構に接続される。スロットルレバー１０９を引くとケーブル１１０の内部に配置されたワイヤ（後述）がハンドル側に引かれて気化器２９のスロットルが開くことなる。本実施例のケーブル１１０は、矢印１１１付近にて分岐し、一方のケーブル１１０ａが気化器２９に接続され、他方のケーブル１１０ｂが後述するブレーキ機構に接続される。 When the operator works with the throttle lever lockout 112 held, and when the throttle lever lockout 112 is released for some reason, the throttle lever 109 immediately returns to the closed position, and the engine speed is idling. It is configured to drop to the rotational speed. The throttle cable 110 has a wire disposed on the inner side (inner) and the outer side (outer) covered with a resin cover. The cable 110 is a throttle of a carburetor 29 (see FIG. 2) described later. Connected to the mechanism. When the throttle lever 109 is pulled, a wire (described later) disposed inside the cable 110 is pulled toward the handle, and the throttle of the carburetor 29 is opened. The cable 110 of this embodiment branches near the arrow 111, one cable 110a is connected to the carburetor 29, and the other cable 110b is connected to a brake mechanism described later.
図２は、本実施例に係るエンジン作業機１の内部構造を示す縦断面図である。エンジン（本体）１０は、２サイクルの小型エンジンであって、クランク軸１３がメインパイプ１０１（図１参照）と同軸上に配置され、シリンダ１１がクランクケース１４から略垂直方向上側に伸びるように配置され、ピストン１２がシリンダ１１内を上下方向に往復移動する。イグニッションコイル２３で発生された高圧電流は、イグニッションコード２４とプラグキャップ２６を介して点火プラグ２５に伝達される。エンジン１０のクランクケース１４の下側には、燃料タンク２７が設けられる。燃料タンク２７には、２サイクル用のガソリンとオイルの混合油が入れられ、後述する気化器に送られる。　 FIG. 2 is a longitudinal sectional view showing the internal structure of the engine working machine 1 according to this embodiment. The engine (main body) 10 is a two-cycle small engine, the crankshaft 13 is arranged coaxially with the main pipe 101 (see FIG. 1), and the cylinder 11 extends from the crankcase 14 substantially upward in the vertical direction. The piston 12 is reciprocated up and down in the cylinder 11. The high-voltage current generated by the ignition coil 23 is transmitted to the spark plug 25 through the ignition cord 24 and the plug cap 26. A fuel tank 27 is provided below the crankcase 14 of the engine 10. The fuel tank 27 contains a mixed oil of gasoline and oil for two cycles and is sent to a vaporizer described later. *
クランク軸１３の前側（出力側）には、遠心クラッチ３０を介して図示しない駆動軸の端部がクラッチシャフト３６を介して連結される。遠心クラッチ３０が取り付けられるマグネトロータ２２には、エンジン冷却用のファンが一体に形成される。遠心クラッチ３０は、クランク軸１３の回転数が一定以上になると遠心力によってクラッチシュー（揺動子）３１がクラッチドラム３４に接続される公知の遠心クラッチである。クラッチドラム３４の前方側には外形が円形であって平板状の円盤３５が設けられる。クラッチドラム３４と円盤３５はクラッチシャフト３６にも固定され、クラッチシャフト３６はベアリング３３によってファンケース５に回転可能に保持される。エンジン１０の回転により供給される駆動力はクランク軸１３に取り付けられているマグネトロータ２２上に設けられたら遠心クラッチ３０を介してクラッチドラム３４に伝わり、そこからさらにメインパイプ１０１内に設けられたシャフト（図示しない）を介してギヤユニット１０２、刈刃１０３へと伝えられる。　 An end portion of a drive shaft (not shown) is connected to the front side (output side) of the crankshaft 13 via a clutch shaft 36 via a centrifugal clutch 30. An engine cooling fan is integrally formed with the magnet rotor 22 to which the centrifugal clutch 30 is attached. The centrifugal clutch 30 is a known centrifugal clutch in which a clutch shoe (oscillator) 31 is connected to a clutch drum 34 by centrifugal force when the rotation speed of the crankshaft 13 becomes a certain value or more. On the front side of the clutch drum 34, a flat disk 35 having a circular outer shape is provided. The clutch drum 34 and the disk 35 are also fixed to the clutch shaft 36, and the clutch shaft 36 is rotatably held on the fan case 5 by a bearing 33. When the driving force supplied by the rotation of the engine 10 is provided on the magnet rotor 22 attached to the crankshaft 13, it is transmitted to the clutch drum 34 via the centrifugal clutch 30, and further provided in the main pipe 101 therefrom. This is transmitted to the gear unit 102 and the cutting blade 103 via a shaft (not shown). *
本実施例の始動装置として、クランク軸１３の後端側に手動式のリコイルスタータ５０が設けられる。リコイルスタータ５０は、リール５１に巻かれたスタータロープ５２を後述するスタータハンドルで引くことにより速い速度で回して、ワンウェイクラッチ５６が遠心力によって径方向外側に突き出てドラム５７と密接してドラム５７を回転させる。ドラム５７はクランク軸１３に固定されているため、ドラム５７が回転するとクランク軸１３も回転しエンジンを始動させることができる。開放されたスタータロープ５２は、スパイラルスプリング５３の復元力によりリール５１に巻き取られる。　 As a starting device of the present embodiment, a manual recoil starter 50 is provided on the rear end side of the crankshaft 13. The recoil starter 50 is rotated at a high speed by pulling a starter rope 52 wound around a reel 51 with a starter handle described later, and the one-way clutch 56 protrudes radially outward by centrifugal force and comes into close contact with the drum 57. Rotate. Since the drum 57 is fixed to the crankshaft 13, when the drum 57 rotates, the crankshaft 13 also rotates and the engine can be started. The released starter rope 52 is wound around the reel 51 by the restoring force of the spiral spring 53. *
図３は、本発明の実施例に係るエンジン作業機１の背面図である。エンジン１０の左側には、エンジン１０の吸気ポートと連結するインシュレータ１９を介して気化器２９が設けられ、気化器２９の外側（左側）には吸入する空気を濾過するエアクリーナの格納空間を構成するエアクリーナカバー６１が設けられる。エンジン１０の側方（右側）にはマフラー１６が設けられ、マフラー１６の後面側には、排気ガスの出口となる排気口１６ａが設けられる。マフラー１６は、作業者が直接触れてしまうのを防止するため、樹脂製のマフラーカバー８で覆われる。エンジン１０は、その上部がシリンダカバー７によって覆われる。クランク軸１３と同軸上であってその後端にはリコイルスタータ５０（図２参照）が設けられ、リコイルスタータ５０はスタータケース９によって覆われる。スタータケース９の左側にはスタータハンドル５４が設けられる。クランクケース１４の下側には燃料タンク２７が設けられる。燃料タンク２７は、半透明の高分子樹脂により形成される容器であって、開口部に取り付けられるキャップ２８を外すことによってガソリンと所定比率のオイルを混合した混合燃料を入れることができる。エンジン１０を始動するときは、作業者は図示しないチョークレバーを引いてからスタータハンドル５４を勢いよく引くことによりエンジン１０が始動する。　 FIG. 3 is a rear view of the engine working machine 1 according to the embodiment of the present invention. A carburetor 29 is provided on the left side of the engine 10 via an insulator 19 connected to the intake port of the engine 10, and a storage space for an air cleaner that filters the intake air is formed outside (left side) of the carburetor 29. An air cleaner cover 61 is provided. A muffler 16 is provided on the side (right side) of the engine 10, and an exhaust port 16 a serving as an exhaust gas outlet is provided on the rear surface side of the muffler 16. The muffler 16 is covered with a resin muffler cover 8 to prevent the operator from touching it directly. The upper part of the engine 10 is covered with a cylinder cover 7. A recoil starter 50 (see FIG. 2) is provided coaxially with the crankshaft 13 and at the rear end thereof, and the recoil starter 50 is covered with a starter case 9. A starter handle 54 is provided on the left side of the starter case 9. A fuel tank 27 is provided below the crankcase 14. The fuel tank 27 is a container formed of a translucent polymer resin, and a mixed fuel in which gasoline and a predetermined ratio of oil are mixed can be put in by removing the cap 28 attached to the opening. When starting the engine 10, the operator pulls a choke lever (not shown) and then pulls the starter handle 54 vigorously to start the engine 10. *
図４は図２のＡ－Ａ部の断面位置を見た断面図である。図２のＡ－Ａ部は、ファンケース５を裏側から見た形となる。ファンケース５はプラスチック等の合成樹脂の一体成形により製造されるので、内側部分には強度を増すための複数のリブが形成される。また、ファンケース５は外周側の３箇所において図示しないボルトによってエンジン１０に固定されるため、３つのネジ孔５ｃが形成される。本実施例においてはファンケース５の内側部分に遠心クラッチ３０が収容され、その近傍にブレーキ機構４０が設けられる。ブレーキ機構４０はファンケース５に対して回転軸４５によって軸支されるもので、遠心クラッチ３０からみて径方向外側に配置される。ブレーキ機構４０は、回転体たる円盤３５に対して接近又は離反可能に移動するスライダ部材４１によって構成され、スライダ部材にはケーブル１１０ｂによって分岐されたワイヤ１１３が連結される。ワイヤ１１３のスライダ部材側の先端部には係合子１１４が形成され、スライダ部材４１の凹部に嵌合するように係合子１１４が取り付けられる。ケーブル１１０ｂの外側の樹脂製のカバーの端部には金属製の円筒キャップ１１１ｄが設けられ、ファンケース５に設けられたケーブル取付部５ｂにて保持される。　 4 is a cross-sectional view of the cross-sectional position of the AA portion of FIG. The AA portion in FIG. 2 has a shape when the fan case 5 is viewed from the back side. Since the fan case 5 is manufactured by integral molding of synthetic resin such as plastic, a plurality of ribs for increasing the strength are formed on the inner portion. Further, since the fan case 5 is fixed to the engine 10 by bolts (not shown) at three locations on the outer peripheral side, three screw holes 5c are formed. In the present embodiment, the centrifugal clutch 30 is accommodated in the inner portion of the fan case 5, and the brake mechanism 40 is provided in the vicinity thereof. The brake mechanism 40 is pivotally supported by the rotating shaft 45 with respect to the fan case 5, and is disposed on the radially outer side when viewed from the centrifugal clutch 30. The brake mechanism 40 is configured by a slider member 41 that moves so as to approach or leave the disk 35 that is a rotating body, and a wire 113 branched by a cable 110b is connected to the slider member. An engaging element 114 is formed at the tip of the wire 113 on the slider member side, and the engaging element 114 is attached so as to be fitted into the recess of the slider member 41. A metal cylindrical cap 111 d is provided at the end of the resin cover outside the cable 110 b and is held by a cable attachment portion 5 b provided in the fan case 5. *
遠心クラッチ３０は広く使われている公知のものを用いることができ、クランク軸１３に図示しない取付部材を介して２本のボルト３２にて固定される２つのクラッチシュー３１と、それらを軸方向中心側に付勢する引っ張りばね３３を含んで構成される。本実施例ではクラッチドラム３４よりも外周側に突出する円環状の平面領域を構成する円盤３５が設けられる。通常クラッチドラム３４は鉄系またはアルミ系の金属材料から構成されるが、円盤３５は渦電流を発生させるための部材となるため金属系の部材で構成することが重要である。本実施例は渦電流の発生のしやすさから円盤３５をアルミ系の材質により構成した。スライダ部材４１は回転軸４５を中心に約６０度揺動可能で有り、図４はスロットルレバー１０９が戻されている状態（アイドリング状態）にあり、この際にはワイヤ１１３はスライダ部材４１の回転軸４５と同軸上に設けられたねじりばね４６の付勢力によって引き延ばされる状態、即ち、係合子１１４が円盤３５側に引っ張られる状態にある。　 A well-known centrifugal clutch 30 can be used. The clutch clutch 31 is fixed to the crankshaft 13 with two bolts 32 via a mounting member (not shown), and these are axially connected. A tension spring 33 that is biased toward the center is included. In this embodiment, there is provided a disk 35 that forms an annular plane region that protrudes to the outer peripheral side of the clutch drum 34. Normally, the clutch drum 34 is made of an iron-based or aluminum-based metal material, but the disk 35 is a member for generating eddy currents, so it is important to be made of a metal-based member. In this embodiment, the disk 35 is made of an aluminum-based material because of the ease of generating eddy currents. The slider member 41 can swing about 60 degrees around the rotation shaft 45. FIG. 4 shows a state in which the throttle lever 109 is returned (idling state). At this time, the wire 113 rotates the slider member 41. The state is extended by the biasing force of the torsion spring 46 provided coaxially with the shaft 45, that is, the engagement element 114 is pulled to the disk 35 side. *
図５は図４に示したブレーキ機構４０の部分図であり、周囲のファンケース５部分の記載を省略したものである。ここでは、スロットルレバー１０９を操作してブレーキ機構４０がＯＦＦとなる状態（ブレーキがかかっていない状態）を示している。スライダ部材４１は、図５のように見た際に略Ｌ字状の部材であって、そのアーム部４２は円盤３５の一面側（前方側）と他面側（後方側）に分かれており、アーム部４２の円盤３５と対面する部分には永久磁石４３が配置される。作業者がスロットルレバー１０９を引くことによりワイヤ１１３がスロットルレバー１０９側に移動する。すると、ねじりバネ４６のばね力に抗してスライダ部材４１が揺動して、アーム部４２に設けられた永久磁石４３が円盤３５の回転領域の外縁よりも径方向外側（外周側）に移動する。この移動によって永久磁石４３によって形成される磁界を円盤３５が横切るような位置関係が解除され、渦電流が発生しない状態となるため、ブレーキの動作が解除された状態となる。ねじりばね４６は一端４６ａがファンケース５に設けられたリブ５ｄにて保持され、他端４６ｂがスライダ部材４１の本体部分の一部に掛合される。作業者がスロットルレバー１０９を戻すか、または、スロットルレバーロックアウト１１２を戻すことによりワイヤ１１３の引っ張り状態が解除され、ねじりばね４６の復帰力によってスライダ部材４１が図５の位置（ブレーキ解除位置）から図４に示す初期位置（ブレーキ動作位置）に戻ることになり、ブレーキが自動的に掛かることになる。このとき、渦電流式のブレーキのため、回転体たる円盤３５の回転が遅くなった場合は制動効果が低くなる。言い換えれば、刃物停止時には制動力は抑制されるため、急激な制動によって刃物停止時の衝撃の発生を低減できる。尚、スロットルレバーロックアウト１１２の解除量に応じて、永久磁石と円盤との間隔が調整できることから、作業者は渦電流による制動効果を任意に調整することができる。　 FIG. 5 is a partial view of the brake mechanism 40 shown in FIG. 4 and omits the description of the surrounding fan case 5 portion. Here, a state where the brake lever 40 is turned off by operating the throttle lever 109 (a state where the brake is not applied) is shown. The slider member 41 is a substantially L-shaped member when viewed as shown in FIG. 5, and the arm portion 42 is divided into one side (front side) and the other side (rear side) of the disk 35. A permanent magnet 43 is disposed on a portion of the arm portion 42 that faces the disk 35. When the operator pulls the throttle lever 109, the wire 113 moves to the throttle lever 109 side. Then, the slider member 41 swings against the spring force of the torsion spring 46, and the permanent magnet 43 provided on the arm portion 42 moves radially outward (outer peripheral side) from the outer edge of the rotating region of the disk 35. To do. Due to this movement, the positional relationship such that the disk 35 crosses the magnetic field formed by the permanent magnet 43 is released and no eddy current is generated, so that the brake operation is released. One end 46 a of the torsion spring 46 is held by a rib 5 d provided on the fan case 5, and the other end 46 b is engaged with a part of the main body portion of the slider member 41. When the operator returns the throttle lever 109 or returns the throttle lever lockout 112, the tension state of the wire 113 is released, and the slider member 41 is moved to the position shown in FIG. 5 (brake release position) by the restoring force of the torsion spring 46. 4 returns to the initial position (brake operating position) shown in FIG. 4, and the brake is automatically applied. At this time, because of the eddy current type brake, the braking effect is reduced when the rotation of the disk 35 as the rotating body is slow. In other words, since the braking force is suppressed when the blade is stopped, the occurrence of an impact when the blade is stopped can be reduced by rapid braking. Since the distance between the permanent magnet and the disk can be adjusted according to the release amount of the throttle lever lockout 112, the operator can arbitrarily adjust the braking effect due to the eddy current. *
以上のようにスライダ部材４１はクラッチドラム３４の外周に設けられた回転軸４５を中心にして、ある一定の角度を回動する。スライダ部材４１は恒常的に円盤３５の中心方向へねじりばね４６により付勢されている。スライダ部材４１には前記ハンドル１０６に設けられたスロットルレバー１０９もしくはスロットルレバーロックアウト１１２の操作と連動するようにワイヤ１１３で接続されている。スロットルレバー１０９もしくはスロットルレバーロックアウト１１２が操作されていない場合はばね１７により付勢されることでスライダ部材４１の永久磁石４３ａ、４３ｂが円盤３５の上に位置することで、永久磁石４３ａ、４３ｂによって円盤３５上に渦電流が発生することでクラッチドラム３４にブレーキ力が生じる。また、スロットルレバー１０９もしくはスロットルレバーロックアウト１１２が操作されている場合、図４に示すようにばね４６の付勢に抗する方向にワイヤ１１３によって引かれることで永久磁石４３ａ、４３ｂが円盤３５から離れた位置へ移動し、渦電流によるブレーキ力は発生しない。 As described above, the slider member 41 rotates at a certain angle around the rotation shaft 45 provided on the outer periphery of the clutch drum 34. The slider member 41 is constantly urged by a torsion spring 46 toward the center of the disk 35. The slider member 41 is connected by a wire 113 so as to interlock with the operation of the throttle lever 109 or the throttle lever lockout 112 provided on the handle 106. When the throttle lever 109 or the throttle lever lockout 112 is not operated, the permanent magnets 43a and 43b of the slider member 41 are positioned on the disk 35 by being biased by the spring 17 so that the permanent magnets 43a and 43b As a result, an eddy current is generated on the disk 35, and a braking force is generated on the clutch drum 34. When the throttle lever 109 or the throttle lever lockout 112 is operated, the permanent magnets 43a and 43b are pulled from the disk 35 by being pulled by the wire 113 in the direction against the bias of the spring 46 as shown in FIG. It moves to a distant position and no braking force due to eddy current is generated.
図６は図４のＢ－Ｂ部の断面図であり、スライダ部材４１と円盤３５の位置関係を示す図である。スライダ部材４１の先端には円盤３５の両面側に突出するように延びる２本のアーム部４２が形成される。アーム部４２の円盤３５に面する側には永久磁石４３ａ、４３ｂが設けられる。永久磁石４３ａ、４３ｂは、例えば前方側がＮ極、後方側がＳ極の極性のように並べて、永久磁石４３ｂから４３ａ側に向かう磁力線で示されるような磁界が形成される。永久磁石４３ａを含むアーム部４２はクラッチドラム３４の外周に配設されており、永久磁石４３ａはクラッチドラム３４の円盤の厚み以上の隙間を持って２個離間され設けられる。スライダ部材４１は、クラッチドラム３４外周に設けられた回転軸４５を中心に離間して設けられている永久磁石４３ａと４３ｂの間に円盤３５が対向（対面）する位置から対向（対面）しない位置までを回動する。この際、スライダ部材４１が回動する領域において、円盤３５と永久磁石４３ａ、４３ｂの間には隙間があるためこれらが接触することはない。このように永久磁石を４３ａ、４３ｂを複数（２つ）設けて、一方の永久磁石側から他方の永久磁石側への磁界を形成し、その磁界の内部にその磁界に対して相対的に移動する金属製の物体（回転体）を晒すことにより、円盤３５に渦電流が発生するため回転体にブレーキ力を得ることができる。円盤３５は、略カップ状のクラッチドラム３４の前方側に設けられるもので、円盤３５をクラッチドラム３４に対してどのように取付けるかは任意である。また、クラッチドラム３４と一体的にフランジ状の部材（円環状の平板部分）を形成しても同等の機能を奏する。　 6 is a cross-sectional view taken along the line BB in FIG. 4 and shows the positional relationship between the slider member 41 and the disk 35. As shown in FIG. Two arm portions 42 extending so as to protrude on both sides of the disk 35 are formed at the tip of the slider member 41. Permanent magnets 43 a and 43 b are provided on the side of the arm portion 42 facing the disk 35. For example, the permanent magnets 43a and 43b are arranged such that the front side has an N-pole and the rear side has an S-pole polarity, and a magnetic field is formed as indicated by a magnetic field line from the permanent magnet 43b toward the 43a side. The arm portion 42 including the permanent magnet 43 a is disposed on the outer periphery of the clutch drum 34, and the two permanent magnets 43 a are provided with a gap larger than the thickness of the disk of the clutch drum 34. The slider member 41 is located at a position where the disk 35 does not face (face to face) between the permanent magnets 43a and 43b that are spaced apart from each other around a rotation shaft 45 provided on the outer periphery of the clutch drum 34. Rotate up to. At this time, in the region where the slider member 41 rotates, there is a gap between the disk 35 and the permanent magnets 43a and 43b, so that they do not contact each other. As described above, a plurality (two) of permanent magnets 43a and 43b are provided to form a magnetic field from one permanent magnet side to the other permanent magnet side, and move relative to the magnetic field inside the magnetic field. By exposing a metal object (rotating body) to be generated, an eddy current is generated in the disk 35, so that a braking force can be obtained on the rotating body. The disk 35 is provided on the front side of the substantially cup-shaped clutch drum 34, and how the disk 35 is attached to the clutch drum 34 is arbitrary. Further, even if a flange-like member (annular flat plate portion) is formed integrally with the clutch drum 34, the same function is achieved. *
以上、本発明の実施形態を説明したが、本発明はこれに限定されることなく例えば以下の変形例を含むものである。図７は、第１の変形例に係るスライダ部材７１を示したものであり、図４のＢ－Ｂ部の断面位置に相当する図である。スライダ部材７１の基本部分はスライダ部材４１と同一形状、同一サイズで製造できる。図６の構成ではスライダ部材４１には永久磁石４３ａ、４３ｂだけが設けられており、スライダ部材４１や永久磁石４３ａ、４３ｂは円盤３５に対して完全に非接触状態にあった。これに対して第１の変形例では、ブレーキ力を強化するために永久磁石７３ａ、７３ｂに加えて、スライダ部材７１の２つのアーム部７２の股部にブレーキシュー７６を設け、渦電流によるブレーキを掛ける際に、ブレーキシュー７６が円盤３５の外周部に接触するように構成した。この構成により、渦電流によるブレーキ効果と、ブレーキシュー７６と円盤３５の摩擦力によるブレーキ効果の双方が得られるために、強力なブレーキ力を得ることができる。　 As mentioned above, although embodiment of this invention was described, this invention is not limited to this, For example, the following modifications are included. FIG. 7 shows the slider member 71 according to the first modification, and is a view corresponding to the cross-sectional position of the BB portion in FIG. The basic part of the slider member 71 can be manufactured in the same shape and size as the slider member 41. In the configuration of FIG. 6, only the permanent magnets 43 a and 43 b are provided on the slider member 41, and the slider member 41 and the permanent magnets 43 a and 43 b are completely in non-contact with the disk 35. On the other hand, in the first modified example, in addition to the permanent magnets 73a and 73b, a brake shoe 76 is provided on the crotch portion of the two arm portions 72 of the slider member 71 in order to enhance the braking force, and the brake caused by the eddy current is applied. The brake shoe 76 is configured to come into contact with the outer peripheral portion of the disk 35 when the is applied. With this configuration, both a braking effect due to eddy current and a braking effect due to the frictional force between the brake shoe 76 and the disk 35 can be obtained, so that a strong braking force can be obtained. *
図８は、第２の変形例に係るスライダ部材８１を示したものであり、図４のＢ－Ｂ部の断面位置に相当する図である。スライダ部材８１の基本部分はスライダ部材４１と同一形状、同一サイズで製造できる。図８においては、図６、図７で図示を省略していたクラッチドラム３４の一部部分も図示している。図８のスライダ部材８１では、図７に示したスライダ部材７１とブレーキシュー８６の取付位置が異なる。ここではブレーキシュー８６を後方側のアーム部８２の先端に取り付け、ブレーキシュー８６がクラッチドラム３４に対して接触するように構成した。このようにクラッチドラム３４に当接する位置にブレーキシュー８６を構成しても渦電流によるブレーキ効果と、ブレーキシュー８６とクラッチドラム３４の摩擦力によるブレーキ効果の双方が得られるために、強力なブレーキ力を得ることができる。　 FIG. 8 shows a slider member 81 according to a second modification, and is a view corresponding to the cross-sectional position of the BB portion of FIG. The basic part of the slider member 81 can be manufactured in the same shape and size as the slider member 41. In FIG. 8, a part of the clutch drum 34, which is omitted in FIGS. 6 and 7, is also illustrated. In the slider member 81 of FIG. 8, the mounting positions of the slider member 71 and the brake shoe 86 shown in FIG. 7 are different. Here, the brake shoe 86 is attached to the tip of the arm portion 82 on the rear side so that the brake shoe 86 comes into contact with the clutch drum 34. Thus, even if the brake shoe 86 is configured at a position in contact with the clutch drum 34, both a braking effect due to eddy current and a braking effect due to the frictional force between the brake shoe 86 and the clutch drum 34 can be obtained. You can gain power. *
本実施例によればスロットルレバー又は／及びロックアウトレバーの操作に連動して、自動的にブレーキ機構４０が動作するようにしたので、スロットルレバー、ロックアウトレバーを戻した際に素早く作業機器側の可動部材（刈刃１０３）を停止させることができるようになった。また、エンジン１０がアイドリング回転時にあって遠心クラッチ３０が非接続状態にあるときに、可動部材（刈刃１０３）が何らかの原因で動いた際にも制動効果を得ることができる。さらに、ブレーキ機構４０にブレーキシューを用いなければ完全に非接触のブレーキ機構を実現できるので、エンジン１０側の運転に悪影響を与えることが無く、安全性を一層高めたエンジン作業機を実現できる。尚、本実施例のブレーキ機構４０は、遠心クラッチ３０の近傍に設けているが、その箇所だけに限定されずに、クラッチドラム３４から作業機器の回転部分（刈刃１０３）の間の任意の箇所に設けるように構成しても良い。例えば図１のような刈払機１００においては、刈刃１０３に対して作用する渦電流方式の非接触ブレーキ機構を設けるようにしても良い。 According to the present embodiment, the brake mechanism 40 is automatically operated in conjunction with the operation of the throttle lever and / or the lockout lever. The movable member (the cutting blade 103) can be stopped. Further, when the engine 10 is idling and the centrifugal clutch 30 is in a disconnected state, a braking effect can be obtained even when the movable member (the cutting blade 103) moves for some reason. Further, since a completely non-contact brake mechanism can be realized if no brake shoe is used for the brake mechanism 40, an engine working machine with further improved safety can be realized without adversely affecting the operation on the engine 10 side. In addition, although the brake mechanism 40 of the present embodiment is provided in the vicinity of the centrifugal clutch 30, the brake mechanism 40 is not limited only to that portion, but is arbitrary between the clutch drum 34 and the rotating portion (the cutting blade 103) of the work equipment. You may comprise so that it may provide in a location. For example, in the brush cutter 100 as shown in FIG. 1, an eddy current type non-contact brake mechanism acting on the cutting blade 103 may be provided.
次に図９を用いて第２の実施例を説明する。第２の実施例においては、金属製の回転体に永久磁石等の界磁手段を非接触状態で接近させることによる渦電流式ブレーキとしたことは上述した第１の実施例と同じ原理である。しかしながら、渦電流を起こすための金属媒体たる回転体の構成が異なる。図９（１）は、第２の実施例に係るブレーキ機構の配置位置を示す図である。第２の実施例では図２で示した円盤３５とクラッチドラム３４を一体構成で製造し、渦電流を発生させる金属製の回転体として、カップ状のクラッチドラム９４の外周側に形成したフランジ状に径方向外側に延びる円環部９４ａにより構成した。そしてブレーキ機構４０が円環部９４ａに対して径方向であって矢印６８のように移動する。ブレーキ機構４０の具体的な構成は第１の実施例で説明した構成と同様に構成すれば良い。尚、図９（１）の例では、円環部９４ａを形成する軸方向（前後方向）の位置を、外周面のほぼ中央にしているが、軸方向位置をどの付近に形成するかは任意である。　 Next, a second embodiment will be described with reference to FIG. In the second embodiment, it is the same principle as in the first embodiment described above that an eddy current type brake is made by bringing a field means such as a permanent magnet close to a metal rotating body in a non-contact state. . However, the configuration of the rotating body, which is a metal medium for causing eddy current, is different. FIG. 9 (1) is a diagram showing the arrangement position of the brake mechanism according to the second embodiment. In the second embodiment, the disk 35 and the clutch drum 34 shown in FIG. 2 are manufactured in an integrated configuration, and a metal rotor that generates eddy currents is formed on the outer peripheral side of the cup-shaped clutch drum 94. And an annular portion 94a extending radially outward. The brake mechanism 40 moves in the radial direction with respect to the annular portion 94a as indicated by an arrow 68. What is necessary is just to comprise the specific structure of the brake mechanism 40 similarly to the structure demonstrated in the 1st Example. In the example of FIG. 9 (1), the position in the axial direction (front-rear direction) for forming the annular portion 94a is set at the substantially center of the outer peripheral surface, but the position where the axial position is formed is arbitrary. It is. *
図９（２）は第２の実施例の変形例を示すブレーキ機構を示す図である。この変形例では、クラッチドラム９６の前方側に延びる円筒形部９６ａを形成して、円筒形部９６ａに対して矢印６９に示すように軸方向に移動するブレーキ機構９０を設けたものである。ここでブレーキ機構９０は、ブレーキ機構４０のようにスライダ部材４１が軸支されて揺動するものでなく、スライダ部材が矢印６９のように軸方向に対してリニアに移動する形式とすると良い。これは渦電流を発生させるのが、円盤状の部材でなくて円筒状の部材だからである。この構成においても、気化器のスロットルワイヤ又はロックアウトレバーの操作と連動して移動するように構成し、スロットルワイヤが引かれていないとき又はロックアウトレバーが離されたときに永久磁石が円筒形部９６ａに対面する位置に来て、スロットルワイヤが引かれているときに永久磁石が円筒形部９６ａから軸方向前方に待避するように構成すると良い。　 FIG. 9 (2) is a view showing a brake mechanism showing a modification of the second embodiment. In this modification, a cylindrical portion 96a extending to the front side of the clutch drum 96 is formed, and a brake mechanism 90 that moves in the axial direction as shown by an arrow 69 with respect to the cylindrical portion 96a is provided. Here, the brake mechanism 90 does not swing with the slider member 41 pivotally supported unlike the brake mechanism 40, but may be a type in which the slider member moves linearly in the axial direction as indicated by an arrow 69. This is because the eddy current is generated not by the disk-shaped member but by the cylindrical member. Even in this configuration, it is configured to move in conjunction with the operation of the throttle wire or lockout lever of the carburetor, and the permanent magnet is cylindrical when the throttle wire is not pulled or when the lockout lever is released. It may be configured such that the permanent magnet is retracted forward from the cylindrical portion 96a in the axial direction when the throttle wire is pulled when the throttle wire is pulled. *
以上のように第２の実施例のように、遠心クラッチのクラッチドラムの任意の箇所に金属製の回転体を形成することによってブレーキ手段を実現できる。尚、金属製の回転体を設ける箇所はクラッチドラムに直接設けるだけで無く、クラッチシャフト３６や図示しない回転軸に、又は、ギヤユニット１０２のスピンドル付近に設けても同様の効果を得ることができる。本発明によるエンジン作業機のブレーキ機構によれば、動力を伝える遠心クラッチとクラッチドラムに設けられたフランジと接触せずに係合するように回動する永久磁石を備えたスライダをスロットル等の操作と連動して動作するように設けた構造とすることで、軽量かつ簡単な構造で、長期に渡り信頼性の高いブレーキ力を発揮するブレーキ機構を提供することができる。 As described above, as in the second embodiment, the brake means can be realized by forming the metal rotating body at an arbitrary position of the clutch drum of the centrifugal clutch. It should be noted that the place where the metal rotating body is provided is not only provided directly on the clutch drum, but the same effect can be obtained by providing it on the clutch shaft 36, a rotating shaft (not shown), or in the vicinity of the spindle of the gear unit 102. . According to the brake mechanism for an engine working machine of the present invention, a slider including a centrifugal clutch that transmits power and a permanent magnet that rotates so as to be engaged without contacting a flange provided on the clutch drum is operated by a throttle or the like. By providing a structure that operates in conjunction with the brake mechanism, it is possible to provide a brake mechanism that exhibits a highly reliable braking force over a long period of time with a light and simple structure.
次に図１０を用いて本発明の第３の実施例を説明する。第１の実施例と同じ構造の部分には同じ番号の参照符号を付している。第３の実施例では、第１の実施例に対してスライダ部材の軸方向の回転方向を上下逆向きに構成したものである。図１０では、スライダ部材２４１が円盤３５の中心方向へと付勢される構造はそのままに、回転方向２３４に対する回転軸２４５の位置をスライダ部材２４１に対して反対側にくるように構成した。つまり、図４、５にて説明した第１の実施例においては回転軸から遠心クラッチ３０の中心軸を結ぶ仮想線２２０よりも回転方向に対して下流側（矢印ａ側）にスライダ部材４１が位置するものであり、スライダ部材４１が回転軸４５よりも回転方向下流側に位置する。これに対して第３の実施例では図１０に示すように、回転軸２４５から遠心クラッチ３０の中心軸を結ぶ仮想線２２０よりも回転方向に対して上流側（矢印ｂ側）にスライダ部材２４１が位置するものであり、スライダ部材２４１が回転軸２４５よりも回転方向上流側に位置する。この際、ケーブル２１０ｂの位置関係が変わり、バネ２４６の配置も適宜変更すれば良い。このように、ばね２４６の付勢に抗する方向にワイヤ２１３によって引かれることで永久磁石が揺動しながら円盤３５に接近する構成において、スライダ部材２４１が円盤３５の中心方向へと付勢される構造はそのままに、回転方向に対する回転軸２４５の位置をスライダ部材２４１に対して図４、図５の構成とは反対側にくるよう構成した。尚、スライダ２４１の形状は第１の実施例で用いたスライダ４１と同一部品を用いることができ、それに取り付けられる２つの永久磁石の位置や形状も同じ構成にすることができる。 Next, a third embodiment of the present invention will be described with reference to FIG. Parts having the same structure as in the first embodiment are given the same reference numerals. In the third embodiment, the axial rotation direction of the slider member is set upside down with respect to the first embodiment. In FIG. 10, the structure in which the slider member 241 is biased toward the center of the disk 35 is left as it is, and the position of the rotation shaft 245 with respect to the rotation direction 234 is configured to be opposite to the slider member 241. That is, in the first embodiment described with reference to FIGS. 4 and 5, the slider member 41 is located on the downstream side (arrow a side) with respect to the rotational direction from the imaginary line 220 connecting the rotational axis to the central axis of the centrifugal clutch 30. The slider member 41 is located downstream of the rotation shaft 45 in the rotation direction. On the other hand, in the third embodiment, as shown in FIG. 10, the slider member 241 is located on the upstream side (arrow b side) with respect to the rotational direction from the imaginary line 220 connecting the rotational shaft 245 to the central axis of the centrifugal clutch 30. The slider member 241 is positioned upstream of the rotation shaft 245 in the rotation direction. At this time, the positional relationship of the cable 210b is changed, and the arrangement of the springs 246 may be changed as appropriate. As described above, in the configuration in which the permanent magnet moves close to the disk 35 while being pulled by the wire 213 in a direction against the urging of the spring 246, the slider member 241 is urged toward the center of the disk 35. The structure of the rotary shaft 245 with respect to the rotational direction is left on the opposite side of the configuration of FIGS. The shape of the slider 241 can be the same as that of the slider 41 used in the first embodiment, and the positions and shapes of the two permanent magnets attached thereto can be the same.
このような配置によって、スライダ部材２４１が移動することにより２つの永久磁石が円盤３５を挟むように位置づけられ、円盤に渦電流を発生させる。この際の図１０の方向から見た永久磁石の移動軌跡は太線２５０のようになる。この際、永久磁石の円盤３５に接近する時の移動軌跡の接線方向と、円盤３５の周方向の接線方向が同じ向きとなり、それらの成す角度が５０度程度となる。スライダ部材２４１が円盤に接近する際の移動方向と円盤３５の回転方向が同じ向きとなって、その接線の成す角が６０度未満、好ましくはできるだけ小さくなるようにスライダ部材２４１の移動方向を設定する。この結果、渦電流による作用に起因して円盤３５の回転によってスライダ部材２４１が中心軸方向に引き込まれる力が発生し、ブレーキ機構２４０が迅速に作動される。尚、第３の実施例では永久磁石の円盤３５に接近する時の移動軌跡の接線方向と、円盤３５の周方向の接線方向が同じ向きとすれば良いので、スライダ部材を揺動式でなくリニア式にして、同様な位置関係とすれば同じような効果が得られる。　 With this arrangement, when the slider member 241 moves, the two permanent magnets are positioned so as to sandwich the disk 35, and an eddy current is generated in the disk. At this time, the movement path of the permanent magnet viewed from the direction of FIG. At this time, the tangential direction of the movement trajectory when approaching the disk 35 of the permanent magnet and the tangential direction of the circumferential direction of the disk 35 are the same direction, and the angle formed by them is about 50 degrees. The moving direction of the slider member 241 is set so that the moving direction when the slider member 241 approaches the disk and the rotating direction of the disk 35 are the same, and the angle formed by the tangent is less than 60 degrees, preferably as small as possible. To do. As a result, a force that pulls the slider member 241 in the direction of the central axis is generated by the rotation of the disk 35 due to the action due to the eddy current, and the brake mechanism 240 is quickly operated. In the third embodiment, since the tangential direction of the movement locus when approaching the disk 35 of the permanent magnet and the tangential direction of the circumferential direction of the disk 35 should be the same direction, the slider member is not oscillating. The same effect can be obtained by using a linear system and a similar positional relationship. *
以上、本発明を実施例に基づいて説明したが、本発明は上述の実施例に限定されるものではなく、その趣旨を逸脱しない範囲内で種々の変更が可能である。例えば、上述の例ではエンジン作業機の例として手持ち式の刈払機を用いて説明したが、その他のエンジン作業機であるチェンソー、ヘッジトリマなどの刃物を備えた作業機や、エンジンを背中に背負う背負い式の作業機に対しても本発明を適用してもよい。また、エンジンは２サイクルエンジンだけに限られずに４サイクルエンジンであってもよい。さらに、作業機器の駆動源はエンジンだけに限られずに電動式やエアー式のもので良い。 As mentioned above, although this invention was demonstrated based on the Example, this invention is not limited to the above-mentioned Example, A various change is possible within the range which does not deviate from the meaning. For example, in the above-described example, a hand-held type brush cutter is used as an example of an engine working machine. However, other engine working machines such as a chain saw, a hedge trimmer, etc., or a backpack that carries the engine on the back. The present invention may be applied to a working machine of a type. The engine is not limited to a two-cycle engine, and may be a four-cycle engine. Furthermore, the drive source of the work equipment is not limited to the engine but may be an electric type or an air type.
１　エンジン作業機　　　　　　　　　　　５　ファンケース
５ａ　脚部　　　　　　　　　　　　　　　５ｂ　ケーブル取付部
５ｃ　ネジ孔　　　　　　　　　　　　　　５ｄ　リブ
７　シリンダカバー　　　　　　　　　　　８　マフラーカバー
９　スタータケース　　　　　　　　　　　１０　エンジン（本体部）
１１　シリンダ　　　　　　　　　　　　　１２　ピストン
１３　クランク軸　　　　　　　　　　　　１４　クランクケース
１５　ボルト　　　　　　　　　　　　　　１６　マフラー
１６ａ　排気口　　　　　　　　　　　　　１９　インシュレータ
２２　マグネトロータ　　　　　　　　　　２３　イグニッションコイル
２４　イグニッションコード　　　　　　　２５　点火プラグ
２６　プラグキャップ　　　　　　　　　　２７　燃料タンク
２８　キャップ　　　　　　　　　　　　　２９　気化器
３０　遠心クラッチ　　　　　　　　　　　３１　クラッチシュー
３２　ボルト　　　　　　　　　　　　　　３３　ベアリング
３４　クラッチドラム　　　　　　　　　　３５　円盤
３６　クラッチシャフト　　　　　　　　　４０　ブレーキ機構
４１　スライダ部材　　　　　　　　　　　４２　アーム部
４３、４３ａ、４３ｂ　永久磁石　　　　　４５　回転軸
４６　バネ　　　　　　　　　　　　　　　４６ａ　（バネの）一端
４６ｂ　（バネの）他端　　　　　　　　　５０　リコイルスタータ
５１　リール　　　　　　　　　　　　　　５２　スタータロープ
５３　スパイラルスプリング　　　　　　　５４　スタータハンドル
５６　ワンウェイクラッチ　　　　　　　　５７　ドラム
６１　エアクリーナカバー　　　　　　　　７１、８１　スライダ部材
７２、８２　アーム部
７３ａ、７３ｂ、８３ａ、８３ｂ　永久磁石
７６、８６　ブレーキシュー　　　　　　　９０　ブレーキ機構
９４、９６　クラッチドラム　　　　　　　９４ａ　円環部
９６ａ　円筒形部　　　　　　　　　　　　１００　刈払機
１０１　メインパイプ　　　　　　　　　　１０２　ギヤユニット
１０３　刈刃　　　　　　　　　　　　　　１０５　飛散防御カバー
１０６　ハンドル　　　　　　　　　　　　１０７ａ、１０７ｂ　グリップ
１０８　取付部材　　　　　　　　　　　　１０９　スロットルレバー
１１０、１１０ａ、１１０ｂ　ケーブル　　１１１ｄ　円筒キャップ
１１２　スロットルレバーロックアウト　　１１３　ワイヤ
１１４　係合子　　　　　　　　　　　　　２１０ｂ　ケーブル
２１３　ワイヤ　　　　　　　　　　　　　２２０　仮想線
２３４　回転方向　　　　　　　　　　　　２４０　ブレーキ機構
２４１　スライダ部材　　　　　　　　　　２４５　回転軸
２４６　バネ　　　　　　　　　　　　　　
２５０　太線（永久磁石の移動軌跡） DESCRIPTION OF SYMBOLS 1 Engine working machine 5 Fan case 5a Leg part 5b Cable attaching part 5c Screw hole 5d Rib 7 Cylinder cover 8 Muffler cover 9 Starter case 10 Engine (main-body part)
11 Cylinder 12 Piston 13 Crankshaft 14 Crankcase 15 Bolt 16 Muffler 16a Exhaust Port 19 Insulator 22 Magnet Rotor 23 Ignition Coil 24 Ignition Cord 25 Spark Plug 26 Plug Cap 27 Fuel Tank 28 Cap 29 Vaporizer 30 Centrifugal Clutch 31 Clutch Shoe 32 Bolt 33 Bearing 34 Clutch drum 35 Disk 36 Clutch shaft 40 Brake mechanism 41 Slider member 42 Arm part 43, 43a, 43b Permanent magnet 45 Rotary shaft 46 Spring 46a (Spring) one end 46b (Spring) other end 50 Recoil starter 51 Reel 52 Star Rope 53 Spiral spring 54 Starter handle 56 One-way clutch 57 Drum 61 Air cleaner cover 71, 81 Slider member 72, 82 Arm parts 73a, 73b, 83a, 83b Permanent magnet 76, 86 Brake shoe 90 Brake mechanism 94, 96 Clutch drum 94a Ring Part 96a Cylindrical part 100 Brush cutter 101 Main pipe 102 Gear unit 103 Cutting blade 105 Scatter protection cover 106 Handle 107a, 107b Grip 108 Mounting member 109 Throttle lever 110, 110a, 110b Cable 111d Cylindrical cap 112 Throttle lever lockout 113 Wire 114 Engagement element 210b Cable 213 Wire 220 Virtual line 234 Rotation direction 240 Brake mechanism 241 Slider member 245 Rotating shaft 246 Spring
250 Bold line (movement trajectory of permanent magnet)

Claims (9)

  1. エンジンの動力を遠心クラッチを介して作業機器に伝達させるエンジン作業機において、前記エンジンのスロットルの開閉に連動させて前記スロットルが閉状態の時に、非接触式のブレーキ機構を動作させることを特徴とするエンジン作業機。 An engine working machine that transmits engine power to a working device via a centrifugal clutch, wherein a non-contact type brake mechanism is operated when the throttle is closed in conjunction with opening and closing of the throttle of the engine. Engine working machine.
  2. 前記ブレーキ機構は渦電流式ブレーキで有り、前記遠心クラッチのクラッチドラムから前記作業機器側の回転部分に金属製の回転体を設け、界磁手段を非接触状態で前記回転体に接近させることにより前記回転体を制動することを特徴とする請求項１に記載のエンジン作業機。 The brake mechanism is an eddy current brake, and a metal rotating body is provided from the clutch drum of the centrifugal clutch to the rotating portion on the work equipment side, and a field means is brought close to the rotating body in a non-contact state. The engine working machine according to claim 1, wherein the rotating body is braked.
  3. 前記ブレーキ機構は、前記回転体に対して接近又は離合可能に移動するスライダ部材と、前記スライダ部材に設けられ前記回転体に作用する永久磁石を有し、前記スロットルが完全に閉状態の時は前記スライダ部材が前記回転体に隣接する位置に保持し、前記スロットルが開状態の時には前記スライダ部材を前記回転体の外側領域に移動させることを特徴とする請求項２に記載のエンジン作業機。 The brake mechanism has a slider member that can move toward or away from the rotating body, and a permanent magnet that is provided on the slider member and acts on the rotating body, and when the throttle is in a completely closed state. The engine working machine according to claim 2, wherein the slider member is held at a position adjacent to the rotating body, and the slider member is moved to an outer region of the rotating body when the throttle is in an open state.
  4. 前記永久磁石は複数用いられ、制動時には複数の前記永久磁石が前記回転体の金属部分を挟むような位置関係とすることを特徴とする請求項３に記載のエンジン作業機。 4. The engine working machine according to claim 3, wherein a plurality of the permanent magnets are used, and the plurality of permanent magnets have a positional relationship so as to sandwich a metal portion of the rotating body during braking.
  5. 前記回転体は前記クラッチドラムに設けられた円盤又は円環板であり、前記スライダ部材は、前記エンジンの気化器のスロットルワイヤ又はロックアウトレバーの操作と連動して移動することを特徴とする請求項４に記載のエンジン作業機。 The rotary body is a disk or an annular plate provided on the clutch drum, and the slider member moves in conjunction with an operation of a throttle wire or a lockout lever of the carburetor of the engine. Item 5. The engine working machine according to Item 4.
  6. 前記スライダ部材は、前記円盤又は円環板と平行な方向に移動され、前記円盤又は円環板に近接する先端部分には、前記円盤又は円環板の両面側から挟みこむように２つのアーム部が形成され、前記アーム部の前記円盤又は円環板に対向する位置に前記永久磁石が設けられることを特徴とする請求項５に記載のエンジン作業機。 The slider member is moved in a direction parallel to the disk or the annular plate, and has two arm portions so as to be sandwiched from both sides of the disk or the annular plate at a tip portion close to the disk or the annular plate. The engine working machine according to claim 5, wherein the permanent magnet is provided at a position facing the disk or the annular plate of the arm portion.
  7. 前記スライダ部材は一端が軸支された揺動式であって、他端側に前記アーム部を有し、前記アーム部を前記回転体に対して近接する方向に付勢する付勢手段を前記スライダ部材に設け、前記スロットルワイヤ又はロックアウトレバーの操作によって前記付勢手段の付勢力に抗して前記スライダ部材が移動させることを特徴とする請求項６に記載のエンジン作業機。 The slider member is an oscillating type whose one end is pivotally supported, has the arm portion on the other end side, and includes an urging means for urging the arm portion in a direction approaching the rotating body. The engine working machine according to claim 6, wherein the slider working member is provided on a slider member, and the slider member is moved against an urging force of the urging means by an operation of the throttle wire or a lockout lever.
  8. 前記スライダ部材の揺動軸は前記遠心クラッチの回転中心軸方向と平行となるように配置されることを特徴とする請求項７に記載のエンジン作業機。 The engine working machine according to claim 7, wherein the swing shaft of the slider member is disposed so as to be parallel to the direction of the rotation center axis of the centrifugal clutch.
  9. 前記スライダ部材に、前記回転体又は前記クラッチドラムと当接するブレーキシューを設けたことを特徴とする請求項１から８のいずれか一項に記載のエンジン作業機。 The engine working machine according to any one of claims 1 to 8, wherein the slider member is provided with a brake shoe that comes into contact with the rotating body or the clutch drum.
PCT/JP2014/055093 2013-03-30 2014-02-28 Engine-driven tool WO2014162803A1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016204916A (en) * 2015-04-20 2016-12-08 株式会社マキタ Shouldering-type fluid device

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0614523A (en) * 1992-06-23 1994-01-21 Sumitomo Special Metals Co Ltd Eddy-current brake
JPH077333U (en) * 1993-06-29 1995-02-03 株式会社丸山製作所 Emergency cutting blade stop device for brush cutter
JPH09275672A (en) * 1996-04-01 1997-10-21 Akebono Brake Ind Co Ltd Eddy current type retarder
JP2002209420A (en) * 2001-01-15 2002-07-30 Honda Motor Co Ltd Bush cutter
JP2012152109A (en) * 2011-01-21 2012-08-16 Yamabiko Corp Braking device of portable implement with centrifugal clutch

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0614523A (en) * 1992-06-23 1994-01-21 Sumitomo Special Metals Co Ltd Eddy-current brake
JPH077333U (en) * 1993-06-29 1995-02-03 株式会社丸山製作所 Emergency cutting blade stop device for brush cutter
JPH09275672A (en) * 1996-04-01 1997-10-21 Akebono Brake Ind Co Ltd Eddy current type retarder
JP2002209420A (en) * 2001-01-15 2002-07-30 Honda Motor Co Ltd Bush cutter
JP2012152109A (en) * 2011-01-21 2012-08-16 Yamabiko Corp Braking device of portable implement with centrifugal clutch

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016204916A (en) * 2015-04-20 2016-12-08 株式会社マキタ Shouldering-type fluid device

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