JP5692564B2 - Brush cutter and power transmission mechanism - Google Patents

Description

  The present invention relates to a brush cutter, and more particularly to a brush cutter that can extend and contract a shaft and a pipe.

  A brush cutter is generally equipped with a cutting blade that rotates at the front end of the pipe, and a prime mover such as an engine that drives the cutting blade is provided at the rear end of the pipe. The prime mover and the cutting blade are connected in the pipe to power the prime mover. It has the structure which has a shaft which transmits to a cutting blade. The brush cutter has better workability when the pipe is kept at a certain length, but it is poor in transportability when the pipe is long. In addition, there is a demand to adjust the length of the pipe depending on the physique of the worker and the work place. Therefore, as shown in Patent Literature 1, a pipe and a shaft in the pipe are expanded and contracted to change the total length of the brush cutter.

  In addition, since the pipe is long, the shaft may be bent in the pipe. However, in order to suppress this bending and hold the shaft in the pipe appropriately, as shown in Patent Document 2. In addition, a bearing such as a bush is interposed between the pipe and the shaft.

JP 59-102320 A Japanese Patent No. 2904767

  The aforementioned bearings are arranged at regular intervals in the pipe. In the brush cutter provided with such a bearing, when the pipe is extended or contracted, the bearing becomes an obstacle and the expansion and contraction amount of the pipe is limited. The amount of expansion and contraction can be increased by setting the bearing spacing large, but in this case, the shaft will bend with respect to the pipe between adjacent bearings, so the shaft retainability to the pipe will deteriorate. It was. Therefore, an object of this invention is to provide the brush cutter which can hold | maintain a shaft suitably with a pipe, ensuring the amount of expansion / contraction.

In order to solve the above-described problems, the present invention provides a prime mover, a shaft that transmits power from the prime mover and transmits power to a mounting portion to which a cutting blade is attached, a pipe that holds the shaft, and the pipe A plurality of bearings rotatably held in the shaft and movable with respect to the pipe and the shaft in an axial direction of the pipe, and disposed in the pipe at intervals in the axial direction; comprising a, the pipe, the inner surface having an engagement portion which Ru extending in the axial direction of the pipe, the bearing is the outer periphery, the outer ring engaged portion is provided to be engaged with the engagement portion The pipe and the shaft are configured to be expandable and contractable in the axial direction, and the plurality of bearings are capable of suppressing relative rotation with respect to the pipe and changing the interval according to expansion and contraction of the pipe and the shaft. A brush cutter configured as described above is provided.

  According to such a configuration, since the bearing can move according to the expansion and contraction of the pipe and the shaft, the bearing does not hinder the expansion and contraction of the pipe and the shaft. Therefore, the amount of expansion and contraction of the pipe and the shaft can be freely set while suitably holding the shaft with the bearing with respect to the pipe. Since the shaft is suitably held by the bearing, the bending generated in the shaft is also suppressed.

  In the brush cutter having the above-described configuration, the plurality of bearings are arranged at substantially equal intervals in the pipe, and the intervals between the plurality of bearings are maintained at equal intervals in accordance with the expansion and contraction of the pipe and the shaft. It is preferable that a holding member is disposed.

  According to such a configuration, the bearings are always kept at substantially equal intervals, so that the shaft can always be suitably held with respect to the pipe.

  Further, it is preferable that the spacing member is constituted by a spring disposed between the adjacent bearings, and the spring is constituted by substantially the same spring coefficient and substantially the same spring length.

According to such a configuration, the distance between adjacent bearings can be maintained at a substantially equal interval with a simple configuration.
Furthermore, the present invention provides a shaft configured to be able to transmit the rotational force from the prime mover to the working portion, and extends in the axial direction while holding the shaft, and is extendable in the axial direction together with the shaft. And a plurality of bearings that are disposed in the pipe at intervals in the axial direction, rotatably hold the shaft, and are movable with respect to the axial direction. a transmission mechanism, the pipe is the inner surface, has an engagement portion which Ru extending in axial direction, the bearing is the outer periphery, an outer ring which engaged portion is provided to be engaged with the engagement portion Each of the plurality of bearings provides a power transmission mechanism that is configured such that relative rotation with respect to the pipe is suppressed and the interval can be changed according to expansion and contraction of the pipe.

  According to the brush cutter of the present invention, the shaft can be suitably held by the pipe while securing the amount of expansion and contraction.

The perspective view of the brush cutter which concerns on embodiment of this invention. Side surface sectional drawing of the brush cutter which concerns on embodiment of this invention. The fragmentary sectional view which shows the pipe of the brush cutter which concerns on embodiment of this invention. Sectional drawing along the IV-IV line of FIG. Sectional drawing along the VV line of FIG. Sectional drawing along the VI-VI line of FIG. Sectional drawing along the VII-VII line of FIG. 1 is a side sectional view (a reduced state) of a brush cutter according to an embodiment of the present invention. The fragmentary sectional view which shows the pipe of the brush cutter which concerns on embodiment of this invention (the state which reduced).

  Hereinafter, a brush cutter according to an embodiment of the present invention will be described with reference to FIGS. 1 to 9. A brush cutter 1 shown in FIG. 1 includes a prime mover portion 2, a pipe portion 3, a shaft portion 4 (FIG. 2), a bearing portion 5 (FIG. 2), a mounting portion 6, and a handle portion 7. It is a tool that performs the brushing work with the cutting blade 10 mounted on the mounting portion 6.

  The prime mover unit 2 includes a housing 21 as an outer shell, and includes an engine (not shown) that is built in the housing 21 and outputs a rotational force. The housing 21 is provided with a fuel tank 22 for storing fuel to be supplied to an engine (not shown) and parts necessary for driving the engine (not shown).

  The pipe part 3 connects between the prime mover part 2 and the mounting part 6, and as shown in FIGS. 2 and 3, the first pipe 31 and the second pipe 32, and the first pipe 31 and the second pipe 3. The pipe holder 3A is connected to the pipe 32. In the following description, in the axial direction of the pipe portion 3, the prime mover portion 2 side is defined as the rear side, and the mounting portion 6 side is defined as the front side.

  The first pipe 31 has a cylindrical shape, the rear end is connected to the prime mover unit 2, and the front end is fixed to the pipe holder 3A. As shown in FIG. 4, in the cross section orthogonal to the front-rear direction, the inner periphery protrudes toward the inside of the first pipe 31 and the other side surface, and the outer periphery is recessed toward the inside of the cylinder. Recesses 31a and 31a are provided. Further, as shown in FIG. 2, a stopper 31B (not shown) that contacts a coil spring 53 (described later) is located at the rearmost end position in the cylinder of the first pipe 31 and in the vicinity of the connection position between the first pipe 31 and the prime mover unit 2. Is provided.

  The second pipe 32 has a cylindrical shape whose outer diameter is smaller than the inner diameter of the first pipe 31, and as shown in FIG. 2, the rear end is inserted into the first pipe 31 and the front end is the mounting portion. 6 is connected. Since the second pipe 32 is smaller in diameter than the inner diameter of the first pipe 31, the first pipe 31 and the second pipe 32 move relative to each other in the front-rear direction with the second pipe 32 inserted into the first pipe 31. can do. As shown in FIG. 4, in the cross section orthogonal to the front-rear direction, the inner surface protrudes toward the inside of the one side surface and the other side surface of the second pipe 32, and the recess 32 a is recessed toward the inside of the tube. , 32a are formed. As shown in FIG. 3, in the vicinity of the rear end of the second pipe 32, a protrusion 32 </ b> A that protrudes from the cylindrical outer periphery is provided. The protruding amount of the protruding portion 32 </ b> A is a protruding amount such that the second pipe 32 can be inserted into the first pipe 31. Further, a holding portion 32 </ b> C that holds the coil spring 53 by inserting a tip portion into a coil spring 53 described later is provided at the rearmost end of the second pipe 32.

  The pipe holder 3A has a substantially cylindrical shape in which a cross section perpendicular to the front-rear direction forms a C shape. As shown in FIG. 3, the first pipe 31 is inserted into the rear end side of the pipe holder 3A, and as shown in FIG. 4, the C-shaped opening of the pipe holder 3A is closed by the screw 3B. The first pipe 31 is fixed so as not to be detached. The front end side of the pipe holder 3 </ b> A is configured such that its cylindrical inner periphery is slightly larger than the outer shape of the second pipe 32. Therefore, when the thumbscrew 3C is closed as shown in FIG. 5, the C-shaped opening of the pipe holder 3A is closed, the cylindrical inner diameter is reduced, and the pipe holder 3A fastens and fixes the second pipe 32. If the thumbscrew 3C is loosened, the second pipe 32 can be moved back and forth with respect to the pipe holder 3A. That is, the second pipe 32 can be fixed relative to the first pipe 31 by closing the thumbscrew 3C, and the second pipe 32 can be moved back and forth relative to the first pipe 31 by loosening the thumbscrew 3C. Further, as shown in FIG. 3, the pipe holder 3A has a configuration in which the large-diameter first pipe 31 is inserted on the rear end side and the small-diameter second pipe 32 is inserted on the front end side. A step 3D is formed at a substantially intermediate position in the front-rear direction on the circumference. Since the protrusion 32A is provided on the second pipe 32 as described above, the protrusion 32A abuts against the step 3D, thereby preventing the second pipe 32 from falling off the pipe holder 3A and the pipe. A maximum length in the front-rear direction of the portion 3 is defined.

  Further, on the inner circumference of the pipe holder 3A, at the place where the first pipe 31 is inserted and the place where the second pipe 32 is inserted, protrusions 3E and 3E (FIG. 4) and protrusions projecting into the cylinder. 3F and 3F (FIG. 5) are provided. When the first pipe 31 is attached to the pipe holder 3A, the convex portions 3E and 3E are inserted into the concave portions 31a and 31a, and when the second pipe 32 is attached to the pipe holder 3A, the convex portion 3F. 3F, the concave portions 32a and 32a are respectively inserted into the convex portions of the pipe holder 3A. Thereby, the relative rotation between the first pipe 31 and the second pipe 32 is suppressed.

  The shaft portion 4 includes a first shaft 41 and a second shaft 42, and is disposed in the pipe portion 3. The first shaft 41 is mainly disposed in the first pipe 31 and has a square cross section orthogonal to the front-rear direction as shown in FIG. 4 and is connected to an engine (not shown) at the rear end to rotate. It is driven. The connection position of the first shaft 41 with an engine (not shown) is in the vicinity of the connection position between the first pipe 31 and the prime mover unit 2. The front end of the first shaft 41 protrudes slightly forward from the front end of the first pipe 31 as shown in FIG.

  The second shaft 42 has a tubular shape and is mainly disposed in the second pipe 32. As shown in FIG. 6, a hole 42a having a square cross section perpendicular to the front-rear direction is formed. 6 is connected to a gear (not shown). The hole 42 a is formed by opening at the rear end position of the second shaft 42 and drilling toward the front side, and the cross section thereof is formed to be slightly larger than the cross sectional outline of the first shaft 41. . Further, the rear end of the second shaft 42 is configured to be at a position substantially equal to the rear end of the second pipe 32 in the front-rear direction. Therefore, as shown in FIG. 3, the tip of the first shaft 41 is inserted into the hole 42 a with the rear end of the second pipe 32 inserted into the front end of the first pipe 31. Since the cross section of the hole 42a is slightly larger than the cross sectional outline of the first shaft 41, the first shaft 41 and the second shaft 42 can move relative to each other.

  The bearing portion 5 is mainly composed of a first bearing 51, a second bearing 52, and a coil spring 53. The first bearings 51 are ball bearings and are arranged in the first pipe 31 side by side in the front-rear direction. Since both have the same shape, the first bearing 51 located on the front side will be described. As shown in FIG. 7, the first bearing 51 is mainly composed of an inner ring 51A, an outer ring 51B, and a ball 51C interposed between the inner ring 51A and the outer ring 51B. The inner ring 51A has a hole 51a having a square cross section slightly larger than the cross-sectional outer shape of the first shaft 41 inside, and the first shaft 41 is inserted into the hole 51a. Since the inner diameter of the hole 51 a is slightly larger than the cross-sectional outer shape of the first shaft 41, the inner ring 51 </ b> A can move back and forth with respect to the first shaft 41. The outer ring 51 </ b> B is configured such that its outer shape is slightly smaller than the inner diameter of the first pipe 31. Therefore, the outer ring 51 </ b> B can move back and forth with respect to the first pipe 31. Since the inner ring 51 </ b> A and the outer ring 51 </ b> B are configured integrally with the ball 51 </ b> C, the first bearing 51 can move back and forth with respect to the first shaft 41 and the first pipe 31. Further, a recess is formed on the outer periphery of the outer ring 51B, and a portion of the recess 31a protruding into the cylinder is inserted into the recess. By adopting such a configuration, the relative rotation of the outer ring 51B with respect to the first pipe 31 is suppressed.

  Further, as shown in FIG. 3, the front end surface and the rear end surface of the first bearing 51 are respectively provided with a first receiving portion 51 </ b> D and a second receiving portion 51 </ b> E that are inserted into the coil spring 53 and receive the coil spring 53. Has been placed. The first receiving portion 51D and the second receiving portion 51E are fixed in contact with only the outer ring 51B. Therefore, the first receiving portion 51D and the second receiving portion 51E are prevented from coming into contact with the inner ring 51A and the ball 51C, and the rotation of the first bearing 51 is prevented from being inhibited by the coil spring 53.

  The second bearing 52 is press-fitted and held in the second pipe 32, and a total of three bearings are arranged at approximately equal intervals at three positions, the vicinity of the mounting portion 6, the position near the rear end, and the center position. Holes 52a through which the second shafts 42 are inserted are formed. Since the hole 52a is slightly larger than the outer shape of the second shaft 42, the second bearing 52 can rotatably support the second shaft 42. The second bearing 52 arranged in the vicinity of the rear end described above rotatably supports the rear end portion of the second shaft 42, but the first shaft 41 is supported on the rear end portion of the second shaft 42. The front end of is inserted. Therefore, the second bearing 52 disposed in the vicinity of the rear end holds the front end portion of the first shaft 41 indirectly via the second shaft 42.

  As shown in FIG. 3, the coil spring 53 that is the spacing member is between the second pipe 32 and the front first bearing 51, between the front first bearing 51 and the rear first bearing 51, They are arranged at three locations between the rear first bearing 51 and the stopper 31B (FIG. 2). A total of three coil springs 53 arranged at each of these three locations are coil springs having the same shape and having substantially the same spring coefficient and substantially the same spring length. Therefore, in the state where the coil spring 53 is arranged in series in the front-rear direction with the first bearing 51 interposed therebetween as described above, a load (compression load) in which the rearward direction is applied to the coil spring 53 positioned on the foremost side. Since the first bearing 51 can freely move back and forth with respect to the first pipe 31 and the first shaft 41, all the coil springs 53 are compressed to the same length. Therefore, the distance between the second pipe 32 and the front first bearing 51, the distance between the front first bearing 51 and the rear first bearing 51, the rear first bearing 51 and the stopper 31B (FIG. The distance between 2) can be the same value.

  A second bearing 52 that indirectly holds the first shaft 41 via the second shaft 42 is disposed at the rear end position of the second pipe 32, and the stopper 31 </ b> B serves as the first shaft 41 and an engine (not shown). Even if the coil spring 53 is urged, the distance between the second bearing 52 at the rear end position of the second pipe and the first bearing 51 on the front side, Both the distance between the one bearing 51 and the rear first bearing 51 and the distance between the rear first bearing 51 and the portion where the first shaft 41 is connected to the engine (not shown) have the same value. The first shaft 41 can always be held in a stable state by the second bearing 52 at the rear end position of the second pipe and the first bearing 51.

  As shown in FIG. 2, the mounting portion 6 is provided at the tip of the second pipe 32, a gear (not shown) connected to the second shaft 42, and a cutting blade connected to the gear (not shown) and driven to rotate. Holding part 61.

  As shown in FIG. 1, the handle portion 7 is provided on an arm 71 having a pair of arm portions, a handle 72 disposed at the distal ends of the pair of arms of the arm 71, and one handle 72. And a throttle 73 for adjusting the output of the engine (not shown).

  The cutting blade 10 is configured in a substantially disc shape, and a sawtooth is formed on the outer peripheral portion, and a hole (not shown) to be attached to the cutting blade holding portion 61 is formed in a substantially central portion of the disc shape.

  When working with the brush cutter 1 having the above-described configuration, as shown in FIGS. 2 and 3, the pipe portion 3 is most extended to close the thumbscrew 3C, whereby the first pipe 31 is interposed via the pipe holder 3A. And the second pipe 32 can be fixed. In this state, the respective coil springs 53 are in the most extended state, but the first bearings 51 can be moved back and forth, and the spring lengths of the respective coil springs 53 are equal, so that the second bearings 52 at the rear end position of the second pipe. The distance between the first bearing 51 on the front side and the distance between the first bearing 51 on the front side and the first bearing 51 on the rear side, the first bearing 51 and the first shaft 41 on the rear side are not shown. The distance between the points connected to is equal.

  Next, when the brush cutter 1 is not in use, as shown in FIG. 8, the pipe portion 3 is in the most contracted state, the thumbscrew 3C is closed, and the first pipe 31 and the second pipe 32 are passed through the pipe holder 3A. And fix. In this state, the second pipe 32 is inserted deep into the first pipe 31. When the second pipe 32 is inserted into the first pipe 31, the coil spring 53 located on the foremost side is urged and compressed by the holding portion 32C as shown in FIG. Even in this state, the first bearing 51 can be moved back and forth, and the spring lengths of the respective coil springs 53 are equal. Therefore, the distance between the second bearing 52 at the rear end position of the second pipe and the first bearing 51 on the front side. The distance between the front first bearing 51 and the rear first bearing 51 is equal to the distance between the rear first bearing 51 and the portion where the first shaft 41 is connected to the engine (not shown). Become.

  By incorporating the first bearing 31 that can move back and forth with respect to the first pipe 31 and the first shaft 41 in the first pipe 31 as described above, the second pipe 32 is inserted into the first pipe 31. However, the first bearing 31 does not hinder the penetration of the second pipe 32 into the first pipe 31. Therefore, as shown in FIG. 9, the second pipe 32 can be inserted into the first pipe 3 as much as possible. Further, by incorporating a coil spring 53 that is urged by the second pipe 32 into contact with the first bearing 31 in the first pipe 31, the rear end of the second pipe is always provided regardless of the overall length of the pipe portion 3 as described above. Between the second bearing 52 at the position and the front first bearing 51, between the front first bearing 51 and the rear first bearing 51, the rear first bearing 51 and the first shaft 41 are shown. The first shaft 41 can be suitably and stably held with respect to the first pipe 31.

  In this embodiment, the coil springs are compressed to make the intervals between the bearings uniform. However, the present invention is not limited to this, and the coil springs may be extended to make the intervals between the bearings uniform. Specifically, as shown in FIGS. 8 and 9, the coil spring 53 is set to a no-load state when the pipe portion 3 is most contracted. Further, the front end and the rear end of the coil spring 53 are joined to members located on the front end side and the rear end side of the coil spring 53. According to such a configuration, as shown in FIGS. 2 and 3, when the pipe portion 3 is extended, the coil spring 53 is similarly extended. However, the coil spring 53 has the same spring coefficient and the same spring length. The extension is also uniform, and therefore, the bearings can be substantially equally spaced.

1 .... Brusher 2 .... Motor part 3 .... Pipe part 3A ... Pipe holder 3B ... Screw 3C ... Wing screw 3D ... Step 4 ... Shaft part 5 ... Bearing part 6 ... Mounting part 7 ...・ Handle part 10 ・ ・ Moving blade 21 ・ ・ Housing 22 ・ ・ Fuel tank 31 ・ ・ First pipe 31a ・ ・ Convex part 31B ・ ・ Stopper 32 ・ ・ Second pipe 32A ・ ・ Protrusion part 32B ・ ・ Stopper 32C ・ ・Holding portion 32a ························· First shaft 42 ··· Second shaft 42a ··· Hole 51 ·· First bearing 51A ·· Inner ring 51B ·· Outer ring 51C ·· Ball 51D ··· First receiving portion 51E ·· Second receiving portion 51a ·· Hole 52 ·· Second bearing 52a ·· Hole 53 ·· Coil spring 61 ·· Cutting blade holding portion 71 ·· Arm 72 ·· Handle 73 ·· Throttle

Claims (4)

Prime mover,
A shaft for transmitting power from the prime mover and transmitting power to a mounting portion to which a cutting blade is mounted;
A pipe holding the shaft;
A plurality of bearings rotatably holding the shaft in the pipe and movable relative to the pipe and the shaft in the axial direction of the pipe and spaced in the axial direction in the pipe And comprising
The pipe, the inner surface having an engagement portion which Ru extending in the axial direction of the pipe,
The bearing has an outer ring provided with an engaged portion that engages with the engaging portion on the outer periphery;
The pipe and the shaft are configured to be stretchable in the axial direction,
The brush cutter, wherein the plurality of bearings are configured such that relative rotation with respect to the pipe is suppressed and the interval can be changed according to expansion and contraction of the pipe and the shaft. The plurality of bearings are equally spaced within the pipe;
The brush cutter according to claim 1, wherein a spacing member is provided in the pipe to maintain a spacing between the plurality of bearings according to expansion and contraction of the pipe and the shaft.   3. The brush cutter according to claim 2, wherein the spacing member is constituted by a spring disposed between the adjacent bearings, and the spring has substantially the same spring coefficient and substantially the same spring length. . A shaft configured to transmit the rotational force from the prime mover to the working part;
A pipe that extends in the axial direction while holding the shaft, and that is configured to be stretchable together with the shaft in the axial direction;
A plurality of bearings disposed in the pipe at an interval in the axial direction, rotatably holding the shaft, and movable relative to the axial direction;
A power transmission mechanism comprising:
The pipe, the inner surface having an engagement portion which Ru extending in axial direction,
The bearing has an outer ring provided with an engaged portion that engages with the engaging portion on the outer periphery;
Each of the plurality of bearings is configured so that relative rotation with respect to the pipe is suppressed and the interval can be changed according to expansion and contraction of the pipe.

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