JP2010158205A - Gardening clipper and blade assembly of the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a pair of gardening clippers preventing an engagement hole of a shear blade from coming off from an eccentric cam. <P>SOLUTION: This pair of gardening clippers includes a pair of shear blades, a crank member which reciprocates a pair of the shear blades by rotation, and a driving mechanism which rotates the crank member. An engagement hole to install the crank member thereinto is formed in each of the shear blades. The crank member has a pair of eccentric cams each engaged with the engagement hole of a pair of the shear blades, and a middle plate set between a pair of the eccentric cams. At least one of the eccentric cams is formed with a flange facing the middle plate, with the shear blade placed between the flanges. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a gardening hair clipper such as a hedge hair clipper used for pruning hedges and a lawn hair clipper used for cutting grass.

  Patent Document 1 discloses a gardening hair clipper. The gardening hair clipper includes a pair of shear blades, a crank member that reciprocates the pair of shear blades by rotating, and a drive mechanism that rotates the crank member. Each shear blade is formed with a fitting hole in which a crank member is disposed, and the crank member is provided with a pair of eccentric cams that respectively fit in the fitting holes of the pair of shear blades. . Each shear blade is provided with a plurality of blades along the reciprocating direction, and the pair of shear blades reciprocate to shear the plants. As disclosed in Patent Document 1, a horticultural hair clipper is known which reciprocates so as to slide a pair of shear blades, or reciprocates so as to swing a pair of shear blades. ing.

  In a gardening hair clipper, the shearing hole of the shear blade may come off from the eccentric cam, and the shearing blade may not operate. Therefore, in the gardening hair clipper of Patent Document 1, a crank member provided with an intermediate plate between a pair of eccentric cams, or a crank member provided with a flange on the outer peripheral surface of each eccentric cam is employed. According to such a crank member, it is possible to prevent the shear blade and the eccentric cam from being unevenly worn, and to prevent the fitting hole of the shear blade from being detached from the eccentric cam.

JP 09-172866 A

In the crank member disclosed in Patent Literature 1, the flange or intermediate plate of the eccentric cam is provided only on one side in the plate thickness direction with respect to the shear blade. Therefore, when a strong external force is applied to the shear blade, for example, when a thick branch is cut, the fitting hole of the shear blade may come off from the eccentric cam.
The present invention solves the above problems. The present invention provides a gardening hair clipper that can reliably prevent a fitting hole of a shear blade from coming off from an eccentric cam.

  A horticultural hair clipper embodied by the present invention includes a pair of shear blades, a crank member that reciprocates the pair of shear blades by rotating, and a drive mechanism that rotates the crank member. Each shear blade is formed with a fitting hole in which a crank member is disposed. The crank member has a pair of eccentric cams that are respectively fitted in fitting holes of the pair of shear blades, and an intermediate plate that is provided between the pair of eccentric cams. At least one eccentric cam is formed with a flange facing the intermediate plate with the shear blade interposed therebetween.

  In this gardening hair clipper, the shear blade is sandwiched from both sides in the thickness direction by the intermediate plate and the flange of the eccentric cam facing the intermediate plate. According to this structure, even when a strong external force is applied to the shear blade, it is reliably prevented that the fitting hole of the shear blade is detached from the eccentric cam.

The flange described above is preferably formed on both of the pair of eccentric cams.
According to this structure, in any shear blade, it is possible to reliably prevent the fitting hole from being removed from the eccentric cam.

The flange described above is preferably formed over the entire circumference of the eccentric cam.
According to this structure, the shear blade is always held between the flange of the eccentric cam and the intermediate plate at the position where the shear blade and the eccentric cam abut regardless of the rotational position of the crank member. Thereby, even when a strong external force is applied to the shear blade, it is possible to prevent the fitting hole of the shear blade from coming off from the eccentric cam. Moreover, the shape of the eccentric cam is simpler and easier to manufacture when the flange is formed over the entire circumference than when the flange is formed only on a part of the outer peripheral surface.

The crank member described above is preferably provided with at least two pins at a position away from the rotating shaft. In this case, it is preferable that a portion on one end side of each pin is connected to the drive mechanism. And it is preferable that the part of the other end side of each pin has a thread part which mutually fastens a pair of eccentric cam and the intermediate | middle plate arrange | positioned between them.
In this structure, torque transmission from the drive mechanism to the crank member and fastening of the pair of eccentric cams and the intermediate plate are realized by a common member. Thereby, the configuration of the crank member can be simplified. In addition, the structure in which the pair of eccentric cams and the intermediate plate are fastened by the threaded portion is easier to assemble than the structure in which welding is performed by caulking and productivity, repairability is increased, and cost is reduced.

It is preferable that the above-described intermediate plate has a disc shape centered on the rotation axis of the crank member. In this case, the radius of the intermediate plate is preferably equal to or larger than the dimension obtained by adding the radius of the flange formed on the eccentric cam to the offset distance from the rotation axis of the crank member to the central axis of the eccentric cam.
If the intermediate plate has a simple disc shape, the structure of the crank member can be simplified. At this time, if the radius of the intermediate plate is large enough to satisfy the above relationship, the intermediate plate reliably faces the entire flange formed on the eccentric cam. As a result, the shear blade that contacts the eccentric cam is securely clamped by the flange of the eccentric cam and the intermediate plate.

The present invention is also embodied in a blade assembly that is removably attached to a gardening hair clipper. This blade assembly includes a pair of shear blades and a crank member that is rotated by a gardening clipper drive mechanism and reciprocates the pair of shear blades by rotating. Each shear blade is formed with a fitting hole in which a crank member is disposed. The crank member has a pair of eccentric cams respectively engaged with fitting holes of the pair of shear blades, and an intermediate plate provided between the pair of eccentric cams. At least one eccentric cam is formed with a flange facing the intermediate plate with the shear blade interposed therebetween.
According to this blade assembly, even when a strong external force is applied to the shear blade, it is reliably prevented that the fitting hole of the shear blade is detached from the eccentric cam.

In the blade assembly described above, it is preferable that the crank member cannot be detached from the pair of shear blades, no matter how the relative movement and relative rotation are performed with respect to the pair of shear blades.
In the shear blade assembly removed from the gardening hair clipper, the crank member can freely move and rotate with respect to the pair of shear blades. At this time, in the conventional blade assembly, the flange or the intermediate plate of the eccentric cam is provided only on one side of the shear blade, and the crank member can be detached from the pair of shear blades. For this reason, when the blade assembly is attached to the gardening clipper, the crank member may fall off from the blade assembly. On the other hand, in the blade assembly according to the present invention, the flange of the eccentric cam and the intermediate plate sandwich the shear blade, and the crank member has a structure that cannot be detached from the pair of shear blades. Can be done easily.

  According to the gardening hair clipper or blade assembly of the present invention, it is possible to reliably prevent the fitting hole of the shear blade from coming off from the eccentric cam.

Side sectional drawing of the hedge clipper of an Example. The figure which expands and shows the II section in FIG. The figure which shows the blade assembly removed from the main body. The figure which decomposes | disassembles and shows a blade assembly.

First, the main features of the embodiments described below are listed.
(Characteristic 1) The shear blade is provided with a fitting hole at its base end.
(Characteristic 2) The fitting hole of the shear blade has an oval shape. The major axis direction of the oval shape is perpendicular to the direction in which the shear blade reciprocates.
(Mode 3) The pair of eccentric cams are offset in directions opposite to each other with respect to the rotation shaft of the crank member. That is, the pair of eccentric cams are arranged so as to eccentrically rotate with a phase difference of 180 ° from each other.
(Form 4) Each cam and the intermediate plate have a disk shape. The radius of the intermediate plate is equal to the offset distance of the eccentric cam plus the radius of the flange formed on the eccentric cam.

  Embodiments of the present invention will be described with reference to the drawings. FIG. 1 shows the appearance of a hedge clipper 10 of this embodiment. The hedge clipper 10 is a power tool mainly used for pruning hedges, and is a kind of gardening clipper.

As shown in FIG. 1, the hedge clipper 10 includes a main body 12 and a blade assembly 100 attached to the main body 12. The blade assembly 100 is fixed to the main body 12 and is detachable from the main body 12.
The blade assembly 100 includes a pair of shear blades 110 and 120 and a crank member 170. Each shear blade 110, 120 is slidably supported, and is configured to reciprocate as the crank member 170 rotates. Each shear blade 110, 120 is provided with a plurality of blades 118, 128 along the reciprocating direction (see FIG. 3), and the pair of shear blades 110, 120 are relatively reciprocated. The structure is such that the branches and leaves are sheared. The configuration of the blade assembly 100 will be described in detail later.

The main body 12 includes a housing 20. The housing 20 is provided with a tip guard 14 for preventing the cutting piece from flying, a front grip 16 and a main grip 22 held by the user. The front grip 16 and the main grip 22 are provided with operation switches 18 and 24 for starting the hedge clipper 10. The two operation switches 18 and 24 are connected within the housing 20 by a link mechanism 28.
Inside the housing 20, a motor 30, a reduction gear 34, and a center shaft 36 are provided. The center shaft 36 rotatably supports the reduction gear 34 and the crank member 170. The reduction gear 34 is engaged with the output shaft 32 of the motor 30 and is configured to be rotated by the motor 30. The reduction gear 34 and the crank member 170 are connected so as not to rotate relative to each other, and the reduction gear 34 and the crank member 170 rotate together. That is, the torque from the motor 30 is transmitted to the crank member 170 via the reduction gear 34. Thus, the motor 30, the reduction gear 34, and the center shaft 36 constitute a drive mechanism that rotates the crank member 170.
Blade assembly 100 is positioned within housing 20 by a plurality of pins 101. The plurality of pins 101 are supported by the left and right side walls of the housing 20. The housing 20 can be disassembled to the left and right. By disassembling the housing 20, the blade assembly 100 can be attached and detached. By assembling the housing 20, the blade assembly 100 is fixed to the housing 20.

FIG. 2 is an enlarged view of a portion indicated by reference numeral II in FIG. FIG. 3 shows the shear blade assembly 100 removed from the body 12. FIG. 4 shows the shear blade assembly 100 in an exploded state. The structure of the shear blade assembly 100 will be described in detail with reference to FIGS. 2, 3, and 4.
The shear blade assembly 100 mainly includes a pair of shear blades 110 and 120, an upper guide plate 102 and a lower guide plate 104 that hold the pair of shear blades 110 and 120 slidably, and a crank member 170. .

  The pair of shear blades 110 and 120 includes an upper shear blade 110 and a lower shear blade 120. A fitting hole 114 is formed in the base end portion 112 of the upper shear blade 110. The fitting hole 114 has an oval shape, and its long diameter extends perpendicular to the direction in which the upper shear blade 110 reciprocates. Similarly, a fitting hole 124 is formed in the base end portion 122 of the lower shear blade 120. The fitting hole 124 has an oval shape, and its long diameter extends perpendicular to the direction in which the lower shear blade 120 reciprocates.

The crank member 170 is disposed in the fitting holes 114 and 124 of the pair of shear blades 110 and 120. The crank member 170 is mainly configured by an upper eccentric cam 130, a lower eccentric cam 140, an intermediate plate 150, and two pin members 160.
Each of the upper eccentric cam 130, the lower eccentric cam 140, and the intermediate plate 150 has a generally disk shape. The upper eccentric cam 130 and the lower eccentric cam 140 have the same diameter. On the other hand, the intermediate plate 150 has a larger diameter than the upper eccentric cam 130 and the lower eccentric cam 140.
The upper eccentric cam 130 is disposed on the upper surface of the intermediate plate 150, and the lower eccentric cam 140 is disposed on the lower surface of the intermediate plate 150. That is, the crank member 170 has a three-layer structure in which three discs of the upper eccentric cam 130, the intermediate plate 150, and the lower eccentric cam 140 are overlapped. The crank member 170 is formed with a rotation center hole 176 through which the center shaft 36 is inserted, and is supported rotatably about the center shaft 36 as a rotation axis.
The two pin members 160 extend from the upper surface of the upper eccentric cam 130 in parallel with the rotation center hole 176 at a position away from the rotation center hole 176. The two pin members 160 are inserted into pin insertion holes 34a provided in the reduction gear 34, and connect the crank member 170 and the reduction gear 34 so that they cannot rotate relative to each other. The configuration of the pin member 160 will be described in detail later.

The upper eccentric cam 130 has a diameter slightly smaller than the short diameter of the fitting hole 114 of the upper shear blade 110 and is fitted into the fitting hole 114 of the upper shear blade 110 with a slight clearance. As shown in FIG. 4, in the upper eccentric cam 130, the rotation center hole 176 is formed at a position (offset position) away from the disc-shaped center axis. Therefore, when the crank member 170 rotates, the upper eccentric cam 130 rotates eccentrically. As the upper eccentric cam 130 rotates eccentrically, the upper shear blade 110 reciprocates so as to advance and retreat relative to the main body 12 (in the left-right direction in FIGS. 1 and 2).
The lower eccentric cam 140 has a diameter slightly smaller than the minor diameter of the fitting hole 124 of the lower shear blade 120 and is fitted in the fitting hole 124 of the lower shear blade 120 with a slight clearance. Match. As shown in FIG. 4, in the lower eccentric cam 140, the rotation center hole 176 is formed at a position (offset position) away from the disc-shaped center axis. Therefore, when the crank member 170 rotates, the lower eccentric cam 140 rotates eccentrically. When the lower eccentric cam 140 rotates eccentrically, the lower shear blade 120 reciprocates with respect to the main body 12 (in the left-right direction in FIGS. 1 and 2).
Here, in the upper eccentric cam 130 and the lower eccentric cam 140, the rotation center hole 176 is offset in the opposite direction. Accordingly, the upper eccentric cam 130 and the lower eccentric cam 140 rotate eccentrically with a phase difference of 180 ° from each other. As a result, the upper shear blade 110 and the lower shear blade 120 reciprocate with a phase difference of 180 ° from each other. That is, while the upper shear blade 110 moves forward relative to the main body 12, the lower shear blade 120 moves backward relative to the main body, and while the upper shear blade 110 moves backward relative to the main body 12, the lower shear blade 120 moves toward the main body 12. Advance to 12

A flange 134 is formed on the outer peripheral surface of the upper eccentric cam 130. The flange 134 is positioned at the upper end of the upper eccentric cam 130 and is formed over the entire circumference of the upper eccentric cam 130. The diameter of the flange 134 is larger than the short diameter of the fitting hole 114 of the upper shear blade 110, and a part of the flange 134 protrudes above the base end portion 112 of the upper shear blade 110. The presence of the flange 134 above the base end 112 of the upper shear blade 110 prohibits the base end 112 of the upper shear blade 110 from moving upward, and the fitting hole 114 is disengaged from the upper eccentric cam 130. Is prevented.
Similarly, a flange 144 is also formed on the outer peripheral surface of the lower eccentric cam 140. The flange 144 is located at the lower end of the lower eccentric cam 140 and is formed over the entire circumference of the lower eccentric cam 140. The diameter of the flange 144 is larger than the short diameter of the fitting hole 124 of the lower shear blade 120, and a part of the flange 144 projects below the base end portion 122 of the lower shear blade 120. The presence of the flange 144 below the base end portion 122 of the lower shear blade 120 prohibits the base end portion 122 of the lower shear blade 120 from moving downward. It is possible to prevent 124 from coming off.

  The intermediate plate 150 is larger than the upper eccentric cam 130 and the lower eccentric cam 140 and is interposed between the base end portion 112 of the upper shear blade 110 and the base end portion 122 of the lower shear blade 120. The presence of the intermediate plate 150 below the base end portion 112 of the upper shear blade 110 prohibits the base end portion 112 of the upper shear blade 110 from moving downward. The fitting hole 114 is prevented from coming off. Further, the presence of the intermediate plate 150 above the base end portion 122 of the lower shear blade 120 prohibits the base end portion 122 of the lower shear blade 120 from moving upward. The fitting hole 124 of the lower shear blade 120 is prevented from being detached.

  As described above, in the blade assembly 100 of the present embodiment, the intermediate plate 150 is provided between the pair of eccentric cams 130 and 140, and each of the eccentric cams 130 and 140 has shear blades 110 and 120. The flanges 134 and 144 facing the intermediate plate 150 are formed. According to this structure, the base end portions 112 and 122 of the shear blades 110 and 120 are held from both sides in the plate thickness direction by the intermediate plate 150 and the flanges 134 and 144 of the eccentric cams 130 and 140 opposed thereto. According to this structure, even when a strong external force is applied to the shear blades 110 and 120, the fitting holes 114 and 124 of the shear blades 110 and 120 are reliably prevented from being detached from the eccentric cams 130 and 140.

  In the blade assembly 100 removed from the main body 12 (see FIG. 3), the crank member 170 can freely move and rotate with respect to the pair of shear blades. At this time, in the blade assembly 100 of the present embodiment, the flanges 134 and 144 of the eccentric cams 130 and 140 and the intermediate plate 150 no matter how the crank member 170 moves and rotates relative to the pair of shear blades 110 and 120. This prevents the crank member 170 from being detached from the pair of shear blades 110 and 120. Therefore, the crank member 170 is not dropped from the blade assembly 100 when the blade assembly 100 is attached to the main body 12 or when the blade assembly 100 is removed from the main body 12. The user can easily perform the operation of replacing the blade assembly 100.

  Here, the relationship between the dimensions of the pair of eccentric cams 130 and 140 and the intermediate plate 150 will be described. The radius of the intermediate plate 150 is equal to the offset distance of the upper eccentric cam 130 plus the radius of the flange 134 of the upper eccentric cam 130. Further, the radius of the intermediate plate 150 is equal to the offset distance of the lower eccentric cam 140 plus the radius of the flange 144 of the lower eccentric cam 140. Here, the offset distance of the upper eccentric cam 130 means the distance from the rotation axis of the crank member 170 (that is, the central axis of the rotation center hole 176) to the disk-shaped central axis of the upper eccentric cam 130. Similarly, the offset distance of the lower eccentric cam 140 means the distance from the rotating shaft of the crank member 170 to the disc-shaped central axis of the lower eccentric cam 140. That is, when the crank member 170 is viewed in plan along the rotation axis thereof, the outer peripheral edge of the flange 134 of the upper eccentric cam 130 is in a positional relationship inscribed in the outer peripheral edge of the intermediate plate 150 and the lower eccentric cam 140. The outer peripheral edge of the flange 144 also has a positional relationship inscribed in the outer peripheral edge of the intermediate plate 150.

According to the dimensional relationship described above, the intermediate plate 150 has a structure facing the entire flange 134 of the upper eccentric cam 130 and also facing the entire flange 144 of the lower eccentric cam 140. According to this structure, the base end portions 112 and 122 of the shear blades 110 and 120 are firmly fitted into the grooves formed by the flanges 134 and 144 and the intermediate plate 150, and the eccentric blades 130 and 140 are connected to the shear blades 110 and 120. The fitting holes 114 and 124 are surely prevented from coming off.
The radius of the intermediate plate 150 is preferably larger than the offset distance of the upper eccentric cam 130 plus the radius of the flange 134 of the upper eccentric cam 130. Even with this structure, the intermediate plate 150 faces the entire flange 134 formed on the upper eccentric cam 130. Similarly, it is preferable that the radius of the intermediate plate 150 is larger than the dimension obtained by adding the radius of the flange 144 of the lower eccentric cam 140 to the offset distance of the lower eccentric cam 140. Even with this structure, the intermediate plate 150 faces the entire flange 134 formed on the upper eccentric cam 130.

Next, the configuration of the pin member 160 will be described. Each pin member 160 has a pin portion 162 located on the upper end side and a screw portion 164 located on the lower end side. The pin portion 162 extends upward from the upper eccentric cam 130 in parallel with the rotation shaft of the crank member 170 and is inserted into the pin insertion hole 34 a of the reduction gear 34. The threaded portion 164 has a shape similar to a hexagon bolt, and is screwed into a fastening hole 178 formed in the crank member 170. Accordingly, the upper eccentric cam 130, the intermediate plate 150, and the lower eccentric cam 140 are fastened to each other in the plate thickness direction by the screw portion 164. In addition, in the fastening hole 178 formed in the crank member 170, a female screw is formed only in a portion formed in the lower eccentric cam 140. Thus, the two pin members 160 are members that connect the reduction gear 34 and the crank member 170 so as not to be relatively rotatable, and are members that fasten the pair of eccentric cams 130 and 140 and the intermediate plate 150 to each other. Since the connection between the reduction gear 34 and the crank member 170 and the fastening of the pair of eccentric cams 130 and 140 and the intermediate plate 150 are realized by the common pin member 160, the structure of the crank member 170 is relatively simple. It has become.
In addition, the structure in which the pair of eccentric cams 130 and 140 and the intermediate plate 150 are fastened by the screw portion 164 is easier to assemble than the structure of joining by welding or caulking, and productivity and repairability are increased. Is also suppressed. In addition, a gap is not formed between the eccentric cams 130 and 140 and the intermediate plate 150, and the situation where the fitting holes 114 and 124 of the shear blades 110 and 112 are detached from the eccentric cams 130 and 140 is reliably prevented.

As mentioned above, although embodiment of this invention was described in detail, these are only illustrations and do not limit a claim. The technology described in the claims includes various modifications and changes of the specific examples illustrated above.
For example, although the hedge clipper 10 embodying the present invention has been described above, the technique described in this embodiment can be applied to other types of gardening clippers such as lawn clippers.
The hedge clipper 10 of this embodiment is a gardening clipper that reciprocates (linearly) so that the pair of shear blades 110 and 120 slide, but the technology described in this embodiment is a pair of It can also be applied to a horticultural hair clipper that reciprocates so that the shear blades of the swaying rocker.

  The technical elements described in this specification or the drawings exhibit technical usefulness alone or in various combinations, and are not limited to the combinations described in the claims at the time of filing. The technology illustrated in this specification or the drawings achieves a plurality of objects at the same time, and achieving one of the objects itself has technical utility.

10: Hedge clipper 12: Main body 30: Motor 32: Motor output shaft 34: Reduction gear 34a: Pin insertion hole 36: Center shaft 100: Blade assembly 110: Upper shear blade 114: Upper shear blade fitting hole 120: Lower Side shear blade 124: Lower shear blade fitting hole 130: Upper eccentric cam 134: Upper eccentric cam flange 140: Lower eccentric cam 144: Lower eccentric cam flange 150: Intermediate plate 160: Pin member 162: Pin Part 164: Screw part 170: Crank member

Claims (7)

A pair of shear blades;
A crank member that reciprocates a pair of shear blades by rotating;
A drive mechanism for rotating the crank member;
Each shear blade has a fitting hole in which a crank member is disposed,
The crank member has a pair of eccentric cams that are respectively fitted in the fitting holes of the pair of shear blades, and an intermediate plate provided between the pair of eccentric cams,
A horticultural hair clipper characterized in that at least one eccentric cam has a flange facing the intermediate plate with a shear blade interposed therebetween.   The gardening hair clipper according to claim 1, wherein the flange is formed on both of the pair of eccentric cams.   The horticultural hair clipper according to claim 1 or 2, wherein the flange is formed over the entire circumference of the eccentric cam. The crank member is provided with at least two pins at a position away from the rotating shaft,
A part on one end side of each pin is connected to the drive mechanism,
The part of the other end side of each pin has a thread part which mutually fastens a pair of eccentric cam and the intermediate | middle plate arrange | positioned among them. Gardening hair clippers. The intermediate plate has a disc shape centered on the rotation axis of the crank member,
5. The radius of the intermediate plate is equal to or greater than the dimension obtained by adding the radius of the flange formed on the eccentric cam to the offset distance from the rotation axis of the crank member to the central axis of the eccentric cam. The gardening hair clipper according to any one of the above. A blade assembly for a gardening hair clipper,
A pair of shear blades;
A crank member that is rotated by a driving mechanism of a gardening hair clipper and reciprocates a pair of shear blades by rotating,
Each shear blade has a fitting hole in which a crank member is disposed,
The crank member has a pair of eccentric cams respectively engaged with the fitting holes of the pair of shear blades, and an intermediate plate provided between the pair of eccentric cams,
A blade assembly characterized in that at least one eccentric cam has a flange facing the intermediate plate with a shear blade interposed therebetween.   The blade assembly according to claim 6, wherein the crank member cannot be detached from the pair of shear blades no matter how the relative movement and relative rotation with respect to the pair of shear blades is performed.

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