JP6163686B2 - Blade sharpening machine and polishing machine - Google Patents

Description

  The present invention relates to a blade sharpening machine or a grinding machine for automatically sharpening blades of knives such as engraving blades and knives.

  A blade sharpening machine (polishing machine) that sharpens a blade of a cutting tool such as an engraving blade or a knife or automatically polishes a test piece or the like is widely commercially available that rotates a disk-shaped or cylindrical grindstone. In a case where a disk-shaped grindstone is rotated around its center and a blade is applied to the rotating grindstone surface for polishing, the peripheral speed varies depending on the distance from the center in each part on the grindstone surface. Accordingly, the portion near the center of the grindstone is practically unusable because the peripheral speed is low. Alternatively, when a wide blade such as a scissors blade is polished, there may be a case where a difference in sharpening occurs at a portion of the blade due to a difference in peripheral speed.

  In addition, in a cylindrical surface grinder or a belt sander (where a belt-shaped grindstone is rotating on a circular track), the speed of each part on the grindstone surface is uniform. However, the cylindrical surface grinder can use only a part of the circumference of the operator (front surface), and when a wide blade is to be polished, a large grindstone must be used. Further, the sharpening surface is not a straight line but an arc. Furthermore, in the belt sander, when the blade is pressed against the both side portions of the belt-shaped grindstone, deflection occurs and the polishing does not work well. As a result, only about half the belt width can be used.

  The present invention has been made in view of the above-described problems, and an object thereof is to provide a blade sharpening machine or a polishing machine having a relatively wide grindstone surface and each part of the grindstone surface moving at a constant speed. .

  The blade sharpening machine or polishing machine of the present invention comprises a face plate for attaching a grindstone to the upper surface, and a mechanism for swinging the face plate in a plane of the upper surface, and each part of the upper surface of the face plate moves at a constant speed with each other. It is characterized by doing.

  In this invention, it is preferable that the said mechanism translates and rotates each part of the said face plate upper surface mutually.

  According to the present invention, the face plate swings at a constant speed. For example, each point in the face plate moves so as to draw a circle having the same diameter. Such a movement is also referred to as revolving around a certain axis. For example, a 100 mm square flat plate does not rotate and each part of the entire surface moves on the circumference of a circle having a diameter of 5 mm. Therefore, the upper surface of the face plate performs circular motion of the same diameter at the same rotational speed, that is, constant velocity motion, at any location on the entire surface.

  Thus, in this invention, since the speed of the whole grindstone is uniform, a uniform grinding | polishing operation | work can be performed on the grindstone whole surface. Therefore, even if the sharpening machine itself is relatively small, a large blade (work) can be sharpened uniformly. In addition, since the width of the grindstone can be widened, a wide blade can be polished. In other words, compared to a grinding device using a disc-shaped grindstone, a cylindrical surface grinder, or a belt sander, it can grind the entire surface of the grindstone at a constant speed, can also grind wide blades, etc. It is excellent in terms of small size.

  Grinding stones are thin plate-shaped whetstones in which abrasive grains and diamond particles are hardened with synthetic resin, sandpaper with paper or cloth as the base, thin-plate diamond whetstones with diamond powder electrodeposited on metal plates, pigs And leather surface of cows.

  In the polishing machine of the present invention, it is possible to polish a test piece other than the blade or a mirror surface. Alternatively, it can be used for chamfering and deburring of machine parts and the like. Moreover, the high-speed translation rotation mechanism of this invention can be utilized also as an agitator or a massage machine. When used for a massage machine, if a solid material having irregularities is pasted instead of a grindstone and used for foot massage, etc., the muscles are loosened and a good massage function can be obtained.

  In the present invention, the radius of translational rotation of the face plate is preferably 0.5 to 5 mm (diameter 1 to 10 mm), and the rotation speed is preferably 1,500 to 24,000 rpm.

  For example, when the radius of translational rotation is 2 mm and the rotational speed is 9000 rpm, the peripheral speed is 1.8 (m / s). This value is as fast as three times the speed at which a skilled person performs hand sharpening (maximum speed of 0.6 m / second). Therefore, it is possible to provide a blade sharpening machine that can be industrially sufficiently realized and can be widely applied to practical applications.

  In the present invention, as the translational rotation mechanism of the face plate, a motor, an eccentric drive portion that receives rotational input from the motor and transmits an eccentric circular motion to the face plate, and a rotation locking portion that stops the rotation of the face plate, Can be provided.

The eccentric drive unit consists of an eccentric rotating shaft that is eccentric to the motor rotating shaft, a rolling bearing that is externally fitted to the eccentric rotating shaft, a bearing holder that covers the outer periphery of the bearing and is attached to the face plate, and a balancer that balances the eccentric weight. Etc.
The rotation locking portion is constituted by a rotation stopping spring or a post that supports the face plate. The spring also acts to prevent the peripheral portion of the face plate from floating up.

In the present invention, the motor is preferably elastically supported.
When the rotational speed of the motor is increased, vibration due to eccentric imbalance may occur, and measures to reduce the vibration are necessary. For example, the motor is mounted on the bottom plate of the casing via an elastic member such as rubber or a spring, or the upper end portion of the motor is connected to the casing upper plate via a rubber ring.

  In the present invention, a chassis that holds the translational rotation mechanism is provided, and as the rotation locking portion, the urging directions are different between the chassis and the face plate, and the face plate is pulled downward. It can have a plurality of springs.

  By such a spring, only the movement on the circumference (revolving motion around the motor rotation axis) of the rotational force of the eccentric drive unit is transmitted to the face plate, and the face plate does not rotate. For example, pulling springs that bias the face plate obliquely downward are attached to a plurality of sides (two or more sides) of the face plate. This spring is preferably used in combination with a post described later.

  In the present invention, it comprises a chassis that holds the translational rotation mechanism, and has a plurality of posts spanned between the upper portion of the chassis and the face plate as the rotation locking portion, It is good also as fixing to either one of a chassis and the said face plate, and fitting through either one and the clearance for the dimension of translation rotation.

With this post, the face plate can be prevented from moving beyond the clearance corresponding to the dimension of translational rotation, and rotation can be stopped.
The post preferably has a base end fixed to the upper portion of the chassis and a tip end fitted to the face plate. Specifically, for example, a counterbore hole is formed on the back surface of the face plate, and the post top portion is fitted therein. Fixing the post to the face plate is not preferable because the weight of the swinging portion increases and vibrations increase.
In addition, it is preferable to attach a rolling bearing and an elastic material (vibration isolation rubber | gum, O-ring, etc.) to a fitting part in order to reduce friction and impact.

  In the present invention, it is preferable that a bearing and / or an elastic material is interposed between the post and the fitting portion.

  In the present invention, an elastic member that includes a chassis that holds the translational rotation mechanism or a casing to which the chassis is fixed, and that connects the upper portion of the chassis or casing and the periphery of the face plate as the rotation locking portion. It is good also as providing.

  Also in this case, the rotation of the face plate can be locked by the elastic member. During translational rotation of the face plate, the elastic member contracts or expands with a change in the distance between the periphery of the face plate and the upper portion of the chassis or casing. Further, since the space between the periphery of the face plate and the chassis or the casing is closed with an elastic member, foreign matter such as dust can be prevented from entering from this clearance.

  In the present invention, a chassis that holds the translational rotation mechanism or a casing to which the chassis is fixed is provided, and a position-adjustable blade or an object to be polished, which is installed on the face plate in a non-contact manner, It is preferable to further provide.

In a blade having a handle such as an engraving blade, it is easy to fix the position of the blade tip with respect to the grindstone by attaching the blade or the handle. By adjusting the position of the splint in the front-rear direction and the up-down direction, the angle and position of the cutting edge relative to the grindstone can be adjusted according to various types of blades and sizes.
Furthermore, if a recess in which a handle or the like of the blade is fitted is formed on the accessory table, the blade or the like can be easily positioned in the left-right direction.

The specific structure of the pedestal includes a pair of parallel strip-shaped vertical plates, a strip-shaped horizontal plate spanning the upper end of the vertical plate, a pedestal formed on the horizontal plate, and an upper side of the pedestal And the pair of vertical plates can be mounted on the chassis or casing so as to be rotatable and slidable in the vertical direction.
This blade attachment stand can also be used for a flat plate polishing machine such as a disk-shaped blade sharpening machine or a belt sander.

  In this invention, it is preferable to provide the chassis holding the said translation rotation mechanism or the casing to which this chassis is fixed, and further to provide the mirror laid on the said faceplate in non-contact.

  According to the present invention, it is easy to observe the positional relationship between the cutting edge and the grindstone surface with a mirror. The mirror can be provided only on the back side of the face plate, on the back side and the left and right sides, or on either the back side or the left and right sides.

  As a specific structure of the mirror, the mirror includes a vertically long left and right plate applied to left and right side plates of the chassis or casing, a rear plate spanned between upper portions of rear edges of the left and right plates, and It has a mirror surface formed on the inner surface upper part of the left and right plates and the inner surface of the rear plate, and the left and right plates can be attached with the chassis or casing sandwiched from the left and right.

  According to the present invention, since the plate is attached to the chassis or the casing by elastic deformation of the plate, the attachment and detachment are easy, and the mirror can be arbitrarily slid in the front-rear direction and the vertical direction. Moreover, it can rotate in the front-back direction around the attachment point. Therefore, the state of the blade edge of the blade can be observed at an arbitrary position.

  In the present invention, it is preferable that the upper surface of the face plate is divided into a plurality of parts and a different type of grindstone is attached to perform a sharpening or polishing operation in a plurality of types of processes.

For example, the shape of the upper surface of the face plate is set to a quadrangle, divided into three regions in the width direction, and three types of belt-shaped sandpapers for rough polishing, intermediate polishing, and finish polishing are sequentially attached to each region. If these three types of grindstones are sequentially applied to pass the cutting edge, the sharpening is completed in a short time. With a rotating disk-shaped object, a rotating cylindrical object, or a belt sander, it is difficult to realize a plurality of types of grindstone areas on one grindstone. It is easy to categorize arbitrarily.
In addition, if the height of the affixed grindstone is made the same, a blade can be smoothly transferred between adjacent grindstones.

  In the present invention, an upper cover portion that protrudes inward is formed on an upper edge of the chassis or a casing to which the chassis is fixed, and a step portion that covers the upper cover is formed on an end surface of the face plate. In addition, during translational swinging of the face plate, a gap between the end face of the face plate and the inner end face of the upper cover portion is equal to or less than a predetermined distance, and the upper cover portion always covers the stepped portion. Is preferred.

  The maximum distance of the gap is preferably 5 mm or less. If it is about 5 mm, it is safe because it is difficult for a finger to enter by mistake. Further, even when the face plate and the upper cover portion spread most during the translational swinging motion, the upper cover portion covers the lower step portion, and therefore, there is no gap between the face plate and the upper cover portion, which is preferable.

  Furthermore, in this invention, it is preferable that the recessed part which the end surface of the said face plate exposes is formed in the one side of the upper edge of the said chassis or the casing to which this chassis is fixed.

  Depending on the type of blade, there is a need or desire to use the corners of the grindstone. According to the present invention, since one side of the face plate is near the end face of the chassis or the casing, it can be sharpened by using the corner of the face plate (the corner of the grindstone) without being obstructed by the chassis or the casing.

  The blade sharpening or polishing method of the present invention is characterized by sharpening or polishing using the blade sharpening machine or polishing machine described above.

  In the present invention, it has a balance weight composed of a plurality of weight members for balancing the eccentric weight of the translational rotation mechanism of the face plate, and the weight member in consideration of the main use conditions of the blade sharpening machine or the polishing machine It is preferable that the number of can be selected.

  The weight member can be, for example, a flat plate-like member, and the eccentric weight or vibration caused by the eccentric weight can be adjusted by changing the number (number) of the weight members. The vibration associated with the eccentric weight varies depending on the usage conditions of the blade sharpener (translational rotation speed of the face plate, weight of the grindstone, mechanical resonance characteristics, etc.), so the number of weight members (number) is changed according to the conditions. By adjusting the eccentric weight, the vibration and backlash of the device can be reduced and the face plate can be rotated stably.

In the present invention, it is preferable to further have a fine adjustment member for finely adjusting the position of the center of gravity of the balance weight.
As the fine adjustment member, for example, a bolt attached to a balance weight can be used. By changing the position of the bolt in the eccentric direction (the direction of the line connecting the rotation center axis and the center of gravity), the eccentric weight can be finely adjusted. In this case, rough adjustment is performed by selecting the number of the weight members described above, and then fine adjustment is performed by adjusting the position of the bolt. Thereby, the eccentric weight can be adjusted more finely, which is effective in reducing vibration and backlash.

  In the present invention, it is more preferable that the mechanism for swinging the face plate has a motor, and the motor is elastically supported in each of the vertical direction and the horizontal direction.

If the motor is elastically supported in the vertical direction and the horizontal direction, the motor can be supported in a state where it is floated inside. For this reason, even when the motor rotates at a high speed and the vibration becomes large, the vibration of the motor is absorbed, so that the chassis and the casing can be prevented from rattling. Further, since the motor is not in direct contact with the chassis or the like, it is possible to suppress noise generated by the motor contacting the chassis or the like when the motor rotates.
Note that “elasticity” includes “viscoelasticity”.

Furthermore, in this invention, it is preferable to provide the chassis which hold | maintains the said translation rotation mechanism, and it is preferable that the bottom part of the said motor is supported by the said chassis via the gel-like damping material.
Rather than supporting the motor in the vertical direction with only the spring, the motor can be supported more stably with less vibration by supporting the bottom of the motor on the chassis via the gel-like member.

  In the present invention, a chassis that holds the translational rotation mechanism is provided, and as the rotation locking portion, the urging directions are different between the chassis and the face plate, and the face plate is pulled downward. A plurality of springs, and a plurality of posts spanned between the upper portion of the chassis and the face plate, one end of the post being fixed to either the chassis or the face plate The other end of the post is preferably in sliding contact with either the chassis or the face plate.

  If the translational rotation speed of the face plate (motor rotation speed) increases, even if the O-ring is fitted to the top of the upper end of the post, the O-ring may come into contact with the peripheral wall of the counterbore hole to generate noise. . Since all the posts are in sliding contact with the face plate, there is no portion where the post may come into contact with the face plate when rotating, so that it is possible to prevent the generation of noise when the face plate rotates at high speed. The surface of each post that makes sliding contact with the face plate is mirror-finished, a Teflon sheet is applied, or the surface of the face plate that makes sliding contact with each post is greased to reduce sliding friction between them. It is preferable to make it.

  The blade sharpening method or the polishing method of the present invention is characterized by sharpening or polishing using the blade sharpening machine or the polishing machine described above.

  As is apparent from the above description, according to the present invention, each part of the face plate swings at a constant speed. In other words, since the upper surface of the face plate on which the grindstone is applied moves at a constant speed anywhere on the entire surface of the grindstone, uniform polishing can be performed on the entire surface of the grindstone. Therefore, a large blade (work) is sharpened uniformly. In addition, since the width of the grindstone can be widened, a wide blade can be polished. Therefore, compared with a grinding apparatus using a disc-shaped grindstone, a cylindrical surface grinder, or a belt sander, a blade sharpening machine having an advantage that it can be polished at a constant speed over the entire surface or a wide blade can be polished. A polishing machine can be provided.

It is a top view which shows the structure of the blade sharpening machine which concerns on the 1st Embodiment of this invention. It is AA sectional drawing of the blade sharpener of FIG. It is a top view which shows the structure of the blade sharpening machine which concerns on the 2nd Embodiment of this invention. It is AA sectional drawing of the blade sharpening machine of FIG. It is a side view which shows the structure of the end surface of the face plate of the blade sharpener of this invention, FIG. 5 (A) shows the side surface which opposes the upper cover part of a casing, FIG.5 (B) shows the side surface which opposes the recessed part of a casing. . It is a perspective view which shows the schematic structure of the whole blade sharpener of FIG. It is a figure explaining the other structure of the rotation latching | locking part of the blade sharpener of this invention, FIG. 7 (A) is a top view, FIG.7 (B) is a sectional side view. It is a perspective view which shows the structure of the blade sharpening machine of FIG. 1 to which the blade attachment stand was attached. It is a side view explaining the attitude | position of a knife attachment stand. It is a perspective view which shows the structure of a mirror plate. It is a perspective view which shows the structure of the blade sharpening machine of FIG. 1 to which the mirror plate was attached. It is sectional drawing which shows the other example of the balancer of the blade sharpener of FIG. It is sectional drawing which shows the structure of the blade sharpening machine which concerns on the 3rd Embodiment of this invention. It is a perspective view which shows the schematic structure of the whole blade sharpening machine of FIG.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
First, the overall structure of the blade sharpener according to the first embodiment of the present invention will be described with reference to FIG.
The blade sharpening machine 1 has a vertically long rectangular parallelepiped shape as a whole, and includes a face plate 20 on which the grindstone 10 is attached to the upper surface, and a mechanism for translationally rotating the face plate 20 on the circumference in the plane of the upper surface. And the casing 3 which accommodates these. The casing 3 is supported by rubber legs 7 at the four corners.

Each part of the blade sharpening machine will be described with reference to FIGS. 1 and 2. FIG. 1 is a top view of a blade sharpening machine (excluding a casing), and FIG. 2 is a cross-sectional view taken along line BB in FIG.
As shown in FIG. 1, the face plate 20 is a plate having a square planar shape. The upper surface of the face plate 20 is basically a horizontal plane. In this example, the size of the face plate 20 is 102 mm long, 102 mm wide, and 5 mm thick. The shape of the side end face of the face plate 20 will be described later.
The shape of the upper surface of the face plate 20 can be a square such as a square or a rectangle, or a circle. The dimension of one side of the face plate 20 is about 100 mm to 200 mm.

  As shown in FIG. 6, the grindstone 10 is attached to the upper surface of the face plate 20. In this example, three types of belt-like sandpapers 10a, 10b, and 10c for rough polishing, intermediate polishing, and finish polishing are attached in order from the back to the front. In this case, it is preferable that the thickness of each strip-shaped sandpaper is the same. If the thickness is different, adjust the height to be constant with an adhesive tape in between. Thereby, a cutter can be smoothly transferred between adjacent hand papers. In addition, you may arrange | position a belt-shaped sandpaper in the left-right direction in order. For example, when sandpaper is applied from left to right in the order of rough polishing, medium polishing, and finish polishing, and a linear blade is applied to the sandpaper in order from left to right, it goes from rough polishing to final polishing. It can be done continuously and is efficient. The type of sandpaper may be one type.

  As clearly shown in FIGS. 2 and 1, the face plate 20 is supported by the chassis 35 by posts 31 and 32 at four corners. The chassis 35 is housed and fixed inside the casing 3 shown in FIG. 6, and is a hollow box-shaped member having four side plates 35a, an upper plate 35b, and a bottom plate 35c. The bottom plate 35 c of the chassis 35 is fixed to the bottom plate 3 c of the casing 3. Note that the side plate 35a of the chassis 35 may be two or three sides facing each other.

  The lower ends of the posts 31 and 32 penetrate the upper plate 35b of the chassis 35 and are fixed with bolts. The upper surfaces of the two posts 31 on one diagonal are flat, and the upper surfaces are in contact with the lower surface of the face plate 20. Two posts 32 on the other diagonal have a small-diameter apex 32a on the upper end surface. The top surface of the top portion 32a is flat, and an O-ring 33 is fitted around the top portion 32a. The top portion 32 a to which the O-ring 33 is fitted is inserted into a counterbore hole 22 formed on the lower surface of the face plate 20, and the upper surface of the top portion 32 a is in contact with the bottom surface of the counterbore hole 22. The radius of the counterbore 22 is larger than the radius of the top portion 32a with the O-ring 33, and is the extent obtained by adding the radius of the eccentric rotational motion described later to this radius. In this example, the counterbore 22 has a depth of 2.5 mm and a diameter of 18.2 mm. The latter two posts 32 on the opposite diagonal also have an action of suppressing the rotation of the face plate 20 described later.

  The translational rocking mechanism includes a motor 40, an eccentric drive unit 50 that is attached to a rotation shaft 41 of the motor 40 and transmits an eccentric rotational motion to the face plate 20, and a rotation locking portion 70 that suppresses the rotation of the face plate 20. These are supported by the chassis 35.

  In the center of the upper plate 35b of the chassis 35, an opening for holding the motor 40 is opened. As the motor 40, for example, a product manufactured by Tokyo Automac Co., Ltd. can be used. The motor 40 is disposed in the hollow portion of the chassis 35 so that the rotation shaft 41 faces vertically. The upper portion of the motor 40 is fixed to the opening of the upper plate 35b with a rubber liner 43, and the rotating shaft 41 protrudes from the upper plate 35b. A plate 45 that is slightly larger than the diameter of the motor 40 is fixed to the lower portion of the motor 40. A spring 47 is interposed between the plate 45 and the bottom plate 3 c of the casing 3. That is, the motor 40 is elastically supported by the spring 47 so as to float from the bottom plate 3 c of the casing 3. When the rotational speed of the motor 40 is increased, vibration due to eccentric imbalance may occur. In this way, vibration can be reduced by elastically supporting the motor 40 with the spring 47.

  The eccentric drive unit 50 is attached to the lower surface of the face plate 20 by being arranged on the outer side of the bearing 53, an eccentric rotating shaft 51 eccentric with the rotating shaft 41 of the motor 40, a rolling bearing 53 fitted on the eccentric rotating shaft 51. Bearing holder 55 and balancer 57 (balance weight) for balancing the eccentric weight.

  The eccentric rotation shaft 51 has a substantially cylindrical shape that is long in the same direction as the rotation shaft 41 of the motor 40, and has a small-diameter upper portion 51a and a large-diameter lower portion 51b. An inner hole 51c is formed on the lower surface of the lower portion 51b. The inner hole 51c extends in parallel with the central axis into which the rotating shaft 41 of the motor 40 is inserted. The center axis A1 of the eccentric rotation shaft 51 and the center axis A2 of the inner hole 51c are eccentric in the horizontal direction. In this example, the distance d between the center axis A2 of the inner hole 51c and the center axis A1 of the eccentric rotation shaft 51 is 1.6 mm. That is, the distance d between the eccentric rotating shaft 51 and the motor rotating shaft 41 is 1.6 mm.

  The balancer 57 is attached with a bolt 58 in the direction of the center axis A2 of the motor rotation shaft 41 (inner hole 51c) with respect to the center axis A1 of the coaxial 51 of the large-diameter lower portion 51b of the eccentric rotation shaft 51. Further, the two split pins 59 pass through the balancer 57 and the rotating shaft 41 of the motor 40 inserted into the inner hole 51 c of the eccentric rotating shaft 51.

  The rolling bearing 53 is held by a bearing holder 55. The bearing holder 55 includes a cylindrical main body portion 55a and a flange portion 55b extending outward from a side surface near the upper end of the main body portion 55a. The bearing 53 is housed in a body portion 55 a of the bearing holder 55 so as not to come off, and is fitted on the small-diameter upper portion 51 a of the eccentric rotating shaft 51. On the lower surface of the face plate 20 is formed a recess 24 into which the upper portion of the main body portion 55a of the bearing holder 55 is fitted. In the bearing holder 55, the main body portion 55 a above the flange portion 55 b is fitted into the concave portion 24 of the face plate 20, and the upper surface of the flange portion 55 b is in contact with the lower surface of the face plate 20. As shown in FIG. 1, the flange portion 55b and the face plate 20 are fixed with screws 61 at six locations.

  The rotation locking portion 70 includes a plurality (eight in this example) of springs 71 spanned between the lower surface of the face plate 20 and the upper plate 35b of the chassis 35. As shown in FIG. 1, two springs 71 are arranged on each side of the face plate 20. On each side, the upper ends of the two springs 71 are fixed to the approximate center of each side of the face plate 20, extend in opposite directions and obliquely downward along each side, and the lower ends are fixed to the corners of the upper plate 35 b of the chassis 35. Has been. That is, the face plate 20 is biased diagonally downward in the opposite direction along the side at the center of each side. In this manner, the face plate 20 is locked by the springs 71 so as not to rotate (spin) on the plane supported by the posts 31 and 32.

  Further, as described above, the two posts 32 on the diagonal are fitted in the counterbore 22 having the top portion 32 a formed on the lower surface of the face plate 20. For this reason, when the face plate 20 tries to rotate (spin), the top portion 32a of the post 32 hits the side surface of the counterbore 22 via the O-ring 33 to prevent the face plate 20 from rotating.

The operation of the sharpening machine 1 will be described.
When the motor 40 is driven to rotate the rotating shaft 41, the eccentric rotating shaft 51 eccentrically attached to the rotating shaft 41 rotates eccentrically with an eccentric distance d (1.6 mm in this example). On the other hand, rotation of the face plate 20 is suppressed by a plurality of springs 71 spanned between the face plate 20 and the chassis 35 and a post 32 inserted in a counterbore 22 formed on the lower surface of the face plate 20. ing. Therefore, even if the eccentric rotary shaft 51 rotates eccentrically, the rotational movement is not transmitted to the face plate 20 and the bearing holder 55 fixed to the face plate 20. The friction between the eccentric rotating shaft 51 and the bearing holder 55 at this time is reduced by the bearing 53. However, with the eccentric rotational movement of the eccentric rotating shaft 51, the outermost periphery of the bearing 53 draws a circle having a radius obtained by adding the eccentric distance d to the radius of the bearing 53. Since the inner peripheral surface of the bearing holder 55 in which the bearing 53 is accommodated is pushed by the outer peripheral surface of the bearing 53, the bearing holder 55 and the face plate 20 fixed to the holder 55 are twice the eccentric distance d. Oscillates in a translational rotation on the circumference. Here, the translational rotation swing means that each point in the face plate 20 draws a circle having the same circumference while maintaining the posture of the face plate 20 on the plane (the posture in the front-rear direction and the left-right direction in the plane). This means the movement that swings. Such movement is also referred to as the face plate 20 revolving around the rotation shaft 41 of the motor 40. In this example, each point in the face plate 20 moves so as to turn on a circumference having a diameter twice the eccentric distance d. Each spring 71 expands and contracts with the movement of the face plate 20 in the front-rear direction and the left-right direction during the translational rotation.

  That is, all the points in the face plate 20 perform a circular motion (that is, constant speed motion) having the same diameter at the same rotational speed. It should be noted that if the rotational speed of the motor 40 is changed to change the rotational speed of the translational rotation of the face plate, the speed naturally changes, but even in that case, the speed of each part of the face plate at a certain timing is the same in any part.

An example of the speed will be described.
In this example, since the eccentric distance d is 1.6 mm, the radius of the circular orbit that performs the translational motion of the face plate 20 is 1.6 mm. The rotation speed of the motor 40 is set to 9000 rpm (150 rps). In this case, the peripheral speed is
150 (rps) × 2 × 0.0016 (m) × π≈1.51 (m / s)
It becomes.

  In addition, in the case of hand sharpening (the sharpening is performed by manually moving the blade on a non-moving grindstone), it is said that the maximum speed is 0.6 m / second by a skilled person. The peripheral speed of the edge sharpener of the present invention is comparable to this value, or greatly exceeds (2-5 times).

  The radius of translational rotation of the face plate 20, that is, the eccentric distance d is preferably 0.5 to 5 mm (diameter 1 to 10 mm), and the rotation speed of the motor 40 is preferably 1,500 to 24,000 rpm. The higher the rotational speed of the motor 40, that is, the faster the translational rotation speed of the grindstone, the smaller the dynamic friction resistance and the greater the grinding force.

  In the case of such high speed movement, vibration due to eccentric imbalance may occur, but this vibration is reduced by the motor 40 being elastically supported by the spring 47. Further, although there is a concern about the floating of the face plate due to the high speed motion, the face plate 20 is maintained so that it does not float because each side is biased downward by the spring 71. Further, since the O-ring 33 is fitted around the top portion 32a of the rotation locking post 32, the sound of collision between the top portion 32a and the inner peripheral surface of the counterbore 22 on the lower surface of the face plate 20 is also reduced. .

  In this example, the two springs 71 are arranged on the four sides of the face plate 20 as the rotation locking portion 70, but the same effect can be obtained on three sides or two sides.

A blade sharpener according to a second embodiment of the present invention will be described with reference to FIGS.
The blade sharpening machine 1A of this example also has the same overall structure as that of FIG. 6, but the method of supporting the motor 40 and the rotation locking portion 70 are different. Hereinafter, only the motor support method and the rotation locking portion will be described. Parts / parts having the same functions and configurations as those in FIGS. 1 and 2 are denoted by the same reference numerals as those in FIGS.

  In this example, the motor 40 is fixed to a motor fixing plate 80 attached to the bottom plate 3 c of the casing 3. The motor fixing plate 80 has opposing side plates 80a, an upper plate 80b between the upper ends of the side plates 80a, and a bottom plate 80c bent outward from the lower ends of the side plates 80b. In the fixing plate 80, each bottom plate 80c is fixed to the bottom plate 3c of the casing 3 with bolts. In the center of the upper plate 80b, an opening through which the lower portion of the motor 40 is passed is opened. The motor 40 is passed through the opening of the upper plate 80b of the motor fixing plate 80 and the opening of the upper plate 35b of the chassis 35 with the rotation shaft 41 oriented vertically, and the rotation shaft 41 extends from the upper plate 35b of the chassis 35. It sticks out. A rubber support block 83 is interposed between the lower end surface of the motor 40 and the bottom plate 3 c of the casing 3. The lower portion of the motor 40 is held against the motor fixing plate 80 by bolts 85 screwed from both side plates 80 a of the motor fixing plate 80. Also in this example, the vibration of the motor 40 can be reduced.

  The rotation locking part 70 of this example does not use a spring, and consists only of an engagement mechanism between the post 32 similar to the post 32 of the blade sharpener in FIG. 1 and the counterbore 22 on the lower surface of the face plate 20. In this example, small diameter top portions 32 a are formed on the upper end surfaces of all posts 32. A bearing 91 is fitted around the top 32 a, and an O-ring 93 is fitted on the bearing 91. The top portion 32 a on which the bearing 91 and the O-ring 93 are fitted is inserted into a counterbore 22 formed on the lower surface of the face plate 20, and the upper surface of the top portion 32 a is in contact with the bottom surface of the counterbore hole 22. The radius of the counterbore 22 is larger than the radius of the top portion 32a with the bearing 91 and the O-ring 93, and is an extent obtained by adding the radius of the eccentric rotational motion to the radius.

  However, in this example, there is a concern that the face plate 20 may be lifted from the post 32. For this reason, the bearing 53 is supported with respect to the eccentric rotating shaft 51 by the screw 95. The screw 95 has a flat plate portion and a screw portion erected at the center of the plate portion. The screw portion is screwed into a screw hole formed on the central axis of the upper surface of the eccentric rotation shaft 51, and the plate portion is accommodated in a recess 24 formed at the center of the lower surface of the face plate 20. At this time, the plate portion covers the upper surface of the inner peripheral portion (inner ring) of the bearing 53. Thereby, the bearing 53 is supported so as not to float with respect to the eccentric rotation shaft 51. Since the bearing 53 is supported by the bearing holder 55 to prevent it from coming off, and the bearing holder 55 is fixed to the face plate 20, the face plate 20 is prevented from being lifted from the eccentric rotating shaft 51.

  In this example, a balancer is not attached to the eccentric rotating shaft 51, but it is preferable to attach a balancer as in FIG. 2 to reduce vibration.

The side end face of the face plate will be described with reference to FIGS.
Since the face plate 20 translates and swings in a plane as described above, a predetermined clearance is required between the periphery of the face plate 20 and the inner surface of the casing 3. As shown in FIG. 6, an upper cover that extends horizontally inward is provided at the upper end of the side plate on the three sides of the casing 3 (in this example, the front side, the left side, and the rear side) so that foreign matter and dust do not enter from the gap. Part 4 is formed. However, the remaining one (right) side plate is formed with a recess 5 in which the side end surface of the face plate 20 is exposed.

  On each side end face of the face plate 20 facing the upper cover part 4 of the casing 3, as shown in FIG. 5A, a lower step part 25 that protrudes outward from substantially the lower half is formed. The upper cover portion 4 covers the lower step portion 25 (overlaps in the vertical direction). On the other hand, on the side end face of the face plate 20 facing the recess 5 of the casing 3, as shown in FIG. 5 (B), an upper step part 26 projecting outward from substantially the upper half is formed. The upper step portion 26 is close to the concave portion 5 of the casing 3, and the upper step portion 26 is positioned above the upper end surface of the side plate of the casing 3.

The translational rotation of the face plate 20 is a reciprocating motion of the face plate in the horizontal direction when viewed from the lateral (horizontal) direction. During the reciprocating motion, as shown in FIG. 5A, when the face plate 20 moves in the innermost direction (the direction away from the upper cover portion 4), the gap between the end face of the face plate 20 and the inner end face of the upper cover portion 4 The distance (clearance) L is the largest, but the distance L is preferably 5 mm or less. If it is about 5 mm, it is safe because it is difficult for a finger to enter by mistake. Furthermore, it is preferable that the upper cover portion 4 covers the lower step portion 25 when it spreads most, because there is no gap between the face plate 20 and the upper cover portion 4 in the plane direction during translation.
Similarly, as shown in FIG. 5B, when the face plate 20 moves in the innermost direction (the direction away from the side plate of the casing 3), the end face of the upper step portion 26 of the face plate 20 and the inner face of the side plate of the casing 3 Is preferably 5 mm or less. The distance L is preferably about -1 mm at the minimum.

  Depending on the type of blade, there is a need or desire to use the corners of the grindstone 10. As shown in FIG. 6, in this blade sharpening machine, one side end face of the face plate 20 (in this example, the right side face in the figure) is exposed from the casing 3, so that the face plate is not obstructed by the casing 3. Twenty corners (grindstone corners) can be used to sharpen.

  Further, as shown in FIG. 5A, the height of the face plate 20 is preferably higher than the height of the upper cover portion 4. The height H is preferably about 0.5 mm. In this case, it is possible to prevent the cutter from hitting the upper cover portion 4 when performing a sharpening operation or a polishing operation of a wide cutter. However, since the grindstone 10 is affixed to the upper surface of the face plate 20 as described above and the actual grindstone surface becomes higher by the thickness of the grindstone 10, even if the height of the face plate 20 and the height of the upper cover portion 4 are the same. Good.

  Further, the corners of the face plate 20 are preferably rounded. The rounding angle is about R0.5. By rounding the corners in this way, there is no danger even if a hand or finger touches the face plate 20 by mistake. Therefore, there is no danger even when the hand is placed on the face plate 20.

With reference to FIG. 7, the other example of the rotation locking part 70 of a blade sharpener is demonstrated. In FIG. 7, the eccentric rotation mechanism is not shown.
In this example, elastic members 97 and 98 such as rubber and spring are connected between the periphery of the face plate 20 and the upper end of the casing 3. As the elastic members 97 and 98, for example, wave rubber (bellows rubber, bellows rubber) can be used. The first elastic member 97 has a substantially semicircular planar shape and a substantially L-shaped cross-section, and the upper side of the casing 3 on which the three sides on which the lower step portion 25 of the face plate 20 is formed and each side are opposed to each other. It is arranged between the edges. The second elastic member 98 has a straight planar shape and a substantially L-shaped cross-sectional shape. The second elastic member 98 has an upper edge of the casing 3 opposite to the one side where the upper step portion 26 of the face plate 20 is formed. Arranged between.

  In this case, as shown in FIG. 7B, the casing 3 has a structure in which the upper cover portion 4 is not provided. And on the three sides where the lower step portion 25 of the face plate 20 is formed, the inner end of the first elastic member 97 is fixed to the end face of the face plate 20, and the outer end is inside the upper edge of the casing 3. It is fixed to. On one side where the upper step portion 26 of the face plate 20 is formed, the inner end of the second elastic member 98 is fixed to the end face of the face plate 20, and the outer end is fixed to the outside of the upper edge of the casing 3. ing.

  In this example, when the face plate 20 is about to rotate, the sides of the face plate 20 are pulled back to the opposite sides of the casing 3 by the elastic members 97 and 98, thereby preventing the face plate 20 from rotating. During the translational rotation of the face plate 20, the elastic members 97 and 98 contract or extend as the distance between the periphery of the face plate 20 and the upper end of the casing 3 changes. Further, since the space between the periphery of the face plate 20 and the casing 3 is closed by the elastic members 97 and 98, there is an advantage that foreign matters such as dust can be prevented from entering from the clearance.

  Moreover, you may use the rotation latching | locking part mentioned above combining several types of methods like the blade sharpener of FIG.

With reference to FIG. 8 and FIG.
The blade attachment stand 100 is used when setting a sharpening blade edge angle or holding a blade having a handle such as an engraving blade so as not to be displaced in the left-right direction, and is detachably mounted on the casing 3. . The blade attachment stand 100 includes a pair of parallel strip-shaped vertical plates 101 and a strip-shaped horizontal plate 102 that spans the upper ends of the vertical plates 101. On the horizontal plate 102, a pedestal 103 to which a handle of a blade is attached is erected along the length direction. On the upper side of the pedestal 103, a plurality of recesses 105 into which a handle is fitted are formed side by side. In this example, the shape of the recess 105 is V-shaped. Alternatively, it can be U-shaped or semicircular.
The left and right vertical plates 101 are provided with long holes 107 along the length direction.

  Both vertical plates 101 are screws 110 with handles that are passed through the long holes 107 and are attached to the left and right side plates of the casing 3. When the screw 110 is loosened, the blade attaching base 100 rotates in the front-rear direction around the screw 110 as shown in FIG. Thereby, the position of the pedestal 105 in the front-rear direction can be changed, and the tip of the cutter can be applied to the desired grindstone upper surface. Furthermore, if the screw 110 is loosened and the vertical plate 101 is slid in the direction of the long hole 107, the height of the base 105 from the face plate 20 can be adjusted. Thus, since the height of the pedestal 105 and the position in the front-rear direction can be adjusted, it is possible to arbitrarily adjust the sharpening surface position of the grindstone and the angle at which the cutter hits the upper surface of the grindstone, and the edge sharpening angle can be set.

  This blade attachment stand 100 can also be used in a flat plate polishing machine such as a disk-shaped blade sharpening machine or a belt sander.

The mirror plate will be described with reference to FIGS.
The mirror plate 120 is used when observing the degree of contact of the blade edge with the grindstone surface, and is attached to the blade sharpening machine 1 so as to be attachable / detachable. The mirror plate 120 includes a vertically long left and right plate 121 applied to the left and right side plates of the casing 3, and a rear plate 122 between upper portions of the rear edges of the left and right plates 121. The interval between the lower portions of the left and right plates 121 is slightly narrower than the interval between the left and right side plates of the casing 3. The upper part of the inner surfaces of the left and right plates 121 and the inner surface of the rear plate 122 are mirror surfaces 125. A thin plate 127 or an elastic member having a certain thickness is attached to the lower part of the inner surface of the left and right plates 121.

  As shown in FIG. 11, the mirror plate 120 is attached so that the left and right plates 121 are elastically deformed and sandwich the casing 3 from the left and right. At this time, the interval between the lower portions of the left and right plates 121 is slightly narrower than the interval between the left and right side plates of the casing 3, and the thin plate 127 is attached to the inner surface of each plate. 120 can maintain the attached posture. Furthermore, the mirror plate 121 can be slid in the front-rear direction and the up-down direction along the side plate of the casing 3, and can be rotated in the front-rear direction at a desired position. With this mirror plate 120, it is possible to observe the degree of contact of the blade with the grindstone surface from the front or side of the blade. Further, since the left and right plates 121 can be easily removed from the casing 3 by opening them to the left and right, they may be removed after the position and posture of the blade edge are determined.

  The mirror plate 120 may be a copy of only the rear side of the face plate 20 or only the rear side and the left or right side.

A modification of the balancer 57 (balance weight) of the eccentric drive unit 50 will be described with reference to FIG.
The balancer 57 in this example includes a plurality of weight members 201. Each weight member 201 is a flat plate-like member (one example is 3.4 g), and is stacked in an eccentric direction (in this example, the horizontal direction, the direction connecting the rotation center axis of the eccentric rotation shaft 51 and the center of gravity). . By adjusting the number of weight members 201, the eccentric (weight) weight can be adjusted. The plurality of weight members 201 are prevented from rotating around the rotation shaft 41 of the motor 40 by the split pins 59 and can be attached to the eccentric rotation shaft 51 by, for example, hexagon socket bolts 58 and nuts 211. At this time, the plurality of weight members 201 are sandwiched and fixed between the nut 211 screwed into the hexagon socket bolt 58 and the eccentric rotating shaft 51.

  Furthermore, the eccentric (weight) weight can be finely adjusted by changing the position of the hexagon socket head cap screw 58 in the eccentric direction (horizontal direction). That is, when the position of the bolt 58 with respect to the eccentric rotation shaft 51 changes, the eccentric weight position moves in the same direction as the changed direction. For example, when the bolt 58 is pulled out in the direction away from the eccentric rotation shaft 51 (right direction in the figure), the eccentric weight position moves outward.

The vibration associated with the eccentric weight varies depending on the usage conditions of the blade sharpener (translational rotation speed of the face plate, weight of the grinding wheel, resonance characteristics of each part of the machine, etc.). It is preferable to adjust so as to minimize vibration and backlash. In this example, a rough adjustment is performed by selecting the number of weight members 201 of the balancer 57, and then a fine adjustment is performed by adjusting the position of the bolt 58.
When changing the number of weight members 201 or adjusting the position of the bolts 58, for example, the nut 211 is fixed with a spanner or the like, and the hexagon socket bolt 58 is pulled out or screwed in a desired direction with a hexagon wrench. . The spanner or wrench can be operated from the space between the posts 31.

A blade sharpener according to a third embodiment of the present invention will be described with reference to FIGS.
The blade sharpening machine 1B of this example also has the same overall structure as that shown in FIG. 2, but the support method of the motor 40 and the support method of the face plate by the post 31 are different. This example is improved so that vibration can be reduced even when the translational rotation speed of the face plate 20 is high (for example, the rotational speed of the motor is 5000 rpm or more). Hereinafter, only the motor support method and the post support method using the post will be described. Parts / parts having the same functions and configurations as those in FIGS. 1 and 2 are denoted by the same reference numerals as those in FIGS.

First, a method for supporting the motor 40 will be described.
The motor 40 is passed through the opening 35d of the upper plate 35b of the chassis 35 with the rotating shaft 41 oriented vertically, and the rotating shaft 41 protrudes from the opening 35d of the upper plate 35b of the chassis 35. A clearance is opened between the rotating shaft 41 and the periphery of the opening 35d. The main body of the motor 40 is elastically supported by a plurality of springs 251 and 252 in each of the vertical direction and the horizontal direction, and is supported on the bottom plate 35c of the chassis 35 via a gel-like vibration isolator 255. Has been.

Motor fixing brackets 260 are attached to the main body of the motor 40 at two locations on the top and bottom. For example, the metal fitting 260 may be a metal fitting that is divided in half. Or a thing like a hose band may be sufficient.
The four vertical support springs 251 are bridged between the upper mounting bracket 260 and the screw portion 38 of the post 31 for fixing the lower end of each post 31 to the upper plate 35b of the chassis 35. As described above, each post 31 is disposed in the vicinity of the four corners of the upper plate 35b of the chassis 35. The four lateral support springs 252 are bridged between the lower mounting bracket 260 and the bolts 280 attached to the approximate center of each side plate 35a of the chassis 35. As described above, the main body of the motor 40 is supported in a posture in which the main body is pulled in each direction by the springs 251 and 252. Here, since the direction in which the motor 40 is pulled by the vertical support spring 251 and the direction in which the motor 40 is pulled by the horizontal support spring 252 are approximately 45 ° in the horizontal plane, the motor 40 can be supported more stably.

  The end of each support spring 251, 252 on the motor side is connected to a hole opened in each mounting bracket 260 via a rubber bush 262. By using the rubber bushing 262, it is difficult for noise to occur between the springs and the metal fittings.

An elongated hole-shaped locking portion is formed at the end of the upper support spring 251 on the screw portion 38 side, and the locking portion is screwed into the screw portion 38 with a nut 270 and a washer 271. Sandwiched between the upper and lower surfaces of the upper plate 35b of the chassis 35. By changing the position of the locking portion, the length of the spring 251 between the fixing bracket 260 and the screw portion 38 of the post 31 can be adjusted.
The end of the lateral support spring 252 on the chassis side plate 35 a side is passed through the bolt 280 and is locked between the head of the bolt 280 and the nut 281. The bolt 280 is screwed from the inside of the side plate 35a of the chassis 35 and is fixed by a nut 283 on the outside of the side plate 35a. The length of the spring 252 between the fixture 260 and the bolt 280 can be adjusted by screwing the bolt 280 into the chassis 35 or pulling it out to change the position of the head.

  As the gel-like vibration-proof material 255 interposed between the lower end surface of the motor 40 and the bottom plate 35c of the chassis 35, an adhesive mat made of an elastomer resin can be used. The motor 40 is mounted on the vibration isolator 255 and is supported in the vertical direction and is not fixed so as not to move. However, the motor 40 is more stable than the case where the motor 40 is supported only by the springs 251 and 252 described above. The motor 40 can be supported more stably through the material 255.

  In this way, the motor 40 is supported on the bottom plate 35c of the casing 35 via the gel-like vibration isolator 255, and is suspended from the upper plate 35b of the chassis 35 by the vertical support spring 251. The springs 251 and 252 are supported in a posture pulled in each direction. That is, the main body of the motor 40 excluding the rotating shaft 41 is elastically supported and can be supported in a posture that floats in the air. Therefore, even when the motor 40 rotates at a high speed and the vibration becomes large, the vibration is absorbed by the springs 251 and 252 and the vibration isolator 255, so that the chassis 35 and the casing 3 can be prevented from rattling. Further, since the main body of the motor 40 is not in direct contact with the chassis 35 and the like, and since the rubber bushing 262 is disposed between the springs 251 and 252 and the metal fitting 260, the metal between the metals due to vibration during motor rotation is arranged. Can reduce the noise generated as much as possible.

  In addition, although the shaft center of the rotating shaft 41 of the motor 40 is connected to the eccentric rotating shaft 51, the main body portion below the rotating shaft 41 is only supported by the springs 251 and 252 and the vibration isolator 255. The axial center is not fixed. For this reason, the length of each spring 252 and 252 is adjusted, and the position of the main-body part of the motor 40 is finely adjusted.

Next, the post 31 will be described.
In this example, the upper end surface of each post 31 is a flat surface, and the upper end surface is in contact with the lower surface of the face plate 20. The portion of the lower surface of the face plate 20 that contacts the upper end surface of each post 31 is a flat surface with no counterbore 22 as shown in FIG. When the face plate 20 is translated, the lower surface of the face plate 20 and the upper end surface of each post 31 are in sliding contact. At this time, in order to reduce sliding resistance, it is preferable that the upper end surface of each post 31 is mirror-finished or a Teflon sheet or the like is attached. Furthermore, it is also preferable to apply grease to the lower surface of the face plate 20.

When the translational rotation speed of the face plate 20 is increased, as shown in FIG. 2, even when the O-ring 33 is fitted into the top 32 a of the upper end of the post 32, the O-ring 33 and the peripheral wall of the counterbore 22 contact each other. Noise may be generated. In FIG. 2, only the two posts 31 on the diagonal are configured such that the upper end surface is in sliding contact with the lower surface of the face plate 20. However, when the face plate 20 rotates at a high speed, four posts 31 are used as in this example. It is preferable that all the posts 31 are configured to be in sliding contact with the face plate 20. In this case, there is no portion where the post 31 may contact when the face plate 20 rotates, and noise can be prevented.
2 and the like, the rotation of the face plate 22 is prevented by the top 32a of the post 32 and the counterbore 22 of the face plate 20. In this example, this rotation prevention is not performed, and the rotation prevention is performed only by the spring 70 spanned between the face plate 22 and the upper surface of the chassis 35. Rotation can be prevented.

In this example, the spanning direction of the plurality of (eight in this example) springs 71 spanned between the lower surface of the face plate 20 and the upper plate 35b of the chassis 35 of the rotation locking portion 70 is: Different from the example of FIG.
That is, in the example of FIG. 2, the upper ends of the two springs 71 are fixed to substantially the center of each side of the face plate 20 in each side of the face plate, and extend in the opposite direction and obliquely downward along each side. Is fixed to the corner of the upper plate 35b of the chassis 35. In this example, as shown in FIG. 14, the two springs 71 on each side have their upper ends fixed near both ends of each side of the face plate 40, and extend inward and obliquely downward along each side. The lower end is fixed to substantially the center of each side of the upper plate 35b of the chassis 35. Even in this case, the face plate 20 is locked by the springs 71 so as not to rotate (spin) on the plane supported by the post 31.

  In this example, the upper end surface of each post 31 is in sliding contact with the lower surface of the face plate 20, but the upper end surface of each post 31 is fixed to the lower surface of the face plate 20, and the lower end surface is the upper plate 35b of the chassis 35. It is good also as a structure which makes the upper surface of sliding contact.

  As shown in FIG. 14, the electric wiring of the motor 40 is connected to the power supply board assembly 300 attached to the inner surface of the side plate 35 a of the chassis 35. A power cord 301 is connected to the power board assembly 300 from the outside. The power supply board assembly 300 includes an on / off switch 303 for the motor 40, a dial (not shown) for changing the rotation speed of the motor 40, and the like.

DESCRIPTION OF SYMBOLS 1 Blade sharpening machine 3 Casing 4 Upper cover part 5 Recessed part 7 Rubber leg 10 Grinding stone 20 Face plate 22 Counterbore hole 24 Recessed part 25 Lower stage part 26 Upper stage part 31, 32 Post 33 O-ring 35 Chassis 38 Post screw part 40 Motor 41 Motor shaft 43 Rubber liner 45 Plate 47 Spring 50 Eccentric drive part 51 Eccentric rotation shaft 53 Bearing 55 Bearing holder 57 Balancer 58 Bolt 59 Split pin 61 Screw 70 Autorotation locking part 71 Spring 80 Motor fixing plate 83 Rubber support block 85 Bolt 91 Bearing 93 O Ring 95 Screw 97, 98 Elastic member 100 Tool attachment base 101 Vertical plate 102 Horizontal plate 103 Base 105 Recess 107 Long hole 110 Screw 120 Mirror plate 121 Left and right plate 122 Rear plate 125 Mirror surface 127 Thin plate 201 C Weight member 211 Nut 251 Vertical support spring 252 Lateral support spring 255 Gel vibration isolator 260 Motor fixing bracket 262 Rubber bushing 270 Nut 271 Washer 280 Bolt 281 Nut 283 Nut 300 Power supply board assembly 301 Power cord 303 On-off switch

Claims (7)

A face plate for attaching a grindstone to the upper surface, and a translational rotation mechanism for swinging the face plate in a plane of the upper surface. The respective parts of the upper surface of the face plate are rotated in parallel with each other, and the upper surface of the face plate is moved at a constant speed. As a translational rotation mechanism that moves, an eccentric drive unit that receives rotational input from a motor and transmits an eccentric circular motion to the face plate, a rotation locking unit that stops rotation of the face plate, the eccentric drive unit, and the rotation locking unit, A plurality of posts spanned between the upper portion of the chassis and the face plate, the posts being attached to either the chassis or the face plate. A blade sharpening machine or a grinding machine, which is fixed and fitted with either one of them through a clearance corresponding to the size of translational rotation. The blade sharpening machine or the polishing machine according to claim 1, wherein a bearing and / or an elastic material is interposed between the post and the fitting portion. 3. The apparatus according to claim 1, further comprising: a chassis that holds the translation rotating mechanism or a casing to which the chassis is fixed, and further includes a mirror that is laid on the face plate in a non-contact manner. The blade sharpener or polisher described. The mirror includes a vertically long left and right plate applied to left and right side plates of the chassis or casing, a rear plate spanned between upper portions of rear edges of the left and right plates, an inner surface upper portion of the left and right plates, and an inner surface of the rear plate. The blade sharpening machine or the polishing machine according to claim 3, wherein the left and right plates are attached with the chassis or casing sandwiched from the left and right sides. A chassis for holding the translational rotation mechanism or a casing to which the chassis is fixed, and an upper cover portion extending inward is formed on an upper edge of the chassis or the casing to which the chassis is fixed; A step portion that covers the upper cover is formed on the end surface, and during translational swinging of the face plate, a gap between the end surface of the face plate and the inner end surface of the upper cover portion is equal to or less than a predetermined distance, The blade sharpening machine or the polishing machine according to any one of claims 1 to 4, wherein the upper cover portion always covers the stepped portion. The blade sharpening machine or the polishing machine according to claim 1, wherein the mechanism for swinging the face plate has a motor, and the motor is elastically supported in each of the vertical direction and the horizontal direction. . The blade sharpening machine or the polishing machine according to claim 6, further comprising a chassis that holds the translational rotation mechanism, wherein a bottom portion of the motor is supported by the chassis via a gel damping agent. .