JP2023116907A - Buff grinder - Google Patents

Abstract

To provide a buff grinder further improved in polishing force by improving a stress transmitting member.SOLUTION: A buff grinder 10 of a rotation polisher includes a surface member 4 contacting a surface to be polished, and a disc-like stress transmitting member fitted to between the surface member 4 and a fitting disc fixed to a drive shaft. The stress transmitting member is provided with a plurality of through holes in the inside away from the outer peripheral end by 3 mm or more. The plurality of through holes have a gross area of cross sections on a surface in parallel to a front surface as a fitting surface of the surface member 4, occupying a ratio of 20%-70% of the area of the front surface, are arranged so as not to form a rotation symmetry centering on a rotation center O of the stress transmitting member, and are set in a form and arrangement so that the positions of the rotation center of the stress transmitting member and a centroid G are shifted, and a distance from the rotation center O to the centroid is a length of 2%-9% of a radius of the front surface.SELECTED DRAWING: Figure 1

Description

The present invention relates to a rotary polisher buffing machine powered by an electric or air driven motor.

Unlike polishers that polish by moving the buffing part in a motion other than rotation such as reciprocating or vibrating, the rotary polisher only gives surface gloss to the surface to be polished as a final polishing of various surfaces such as metal surfaces and painted surfaces. Instead, it is a polisher that removes scratches such as paper grains on the surface to be polished and scrapes the surface, so to speak, for heavy grinding and polishing for adding gloss. In order to perform such buffing, the buffing disc is provided with a surface member attached to the front surface of the buffing disc. Various surface members are used, and buffing is performed by selecting a material according to each stage of the polishing work. This is because a surface member with a large abrasive force that is excellent for heavy grinding will have deeper buff marks after polishing and larger scratches will be left when the abrasive force increases. However, buffing is progressed by sequentially replacing the remaining buff marks with a shallower surface member to make the remaining buff marks inconspicuous and gloss is imparted to the surface to be polished.

However, it is inefficient to replace the surface member at each stage of the buffing work, and there is a demand for a buffing machine with excellent abrading power capable of performing heavy grinding and glossing at all stages. As such a buffing machine, Patent Document 1 proposes a buffing machine that can exert an extremely wide range of cutting and polishing power from strong to weak grinding power with one type of surface member (buff body). there is The buffing machine of Patent Document 1 has a stress transmission member attached between a surface member attached to the front surface and a mounting disc fixed to a drive shaft. It consists of an elastic body made of a sponge material provided with through holes. In this buffing machine, the stress applied to the surface member, which is the polishing surface, is concentrated on the front surface of the portion excluding the portion where the through holes are provided, and a larger force is applied, so the grinding force is originally small. A strong grinding force can be obtained even with the surface member.

As shown in FIGS. 5 to 8 of Patent Document 1, the stress transmission member provided with the above-mentioned through-hole is arranged so that the center of rotation of the stress transmission member In order to match the center of gravity with the center of gravity, the shape and arrangement of each through hole are provided so as to be rotationally symmetrical about the center of rotation. The shape and arrangement of the through holes shown in FIG. 6 of Patent Document 1 are shown in FIG. 6 of the drawings of the present application. As shown in FIG. 6, the through-holes 41 and 42 provided in the stress transmission member 40 form rotational symmetry about the point O, forming six-fold symmetry. In this way, if each through-hole is rotationally symmetrical, the center of rotation and the center of gravity of the stress transmission member will coincide with each other. It is a common practice to provide each through-hole so as to form rotational symmetry, since smooth rotation of the through-holes can be obtained.

However, when the through-holes are provided so as to form rotational symmetry, the through-holes always overlap at the same position at the same period. For example, in the example shown in FIG. 6, every 60° rotation, all the through-holes are at the same overlapping position. They are in the same position, overlapping each other. Therefore, in this stress transmission member, the inner edge portions of the through-holes, where the stress is most concentrated and applied to the surface member, hit the same place at the same cycle, and the polishing force is uneven depending on the place. Since the entire surface to be polished does not receive a uniform polishing force, the polishing force is not good, and further improvement of the polishing force is desired.

Japanese Patent No. 3904619

An object of the present invention is to provide a buffing machine for a rotary polisher in which a stress transmission member having through holes is attached between a surface member attached to the front surface and a mounting disk fixed to a drive shaft, wherein the stress transmission member is improved to provide a buffing machine further improved in polishing power.

The buffing machine of the rotary polisher of the present invention has a surface member in contact with the surface to be polished, and a disc-shaped stress transmission member mounted between the surface member and a mounting disc fixed to the drive shaft. , the stress transmission member is provided with a plurality of through-holes on the inner side at a distance of 3 mm or more from the outer peripheral end, and the plurality of through-holes has a total cross-sectional area in a plane parallel to the front surface, which is the mounting surface of the surface member. occupies 20% to 70% of the area of the front surface, is arranged so as not to form rotational symmetry about the center of rotation of the stress transmission member, and the center of rotation of the stress transmission member is displaced from the center of gravity. The shape and arrangement are set so that the distance from the center of rotation to the center of gravity is 2% to 9% of the radius of the front surface.

Flexible materials made of various types of rubbers and synthetic resins can be used for the disc-shaped stress transmission member, and foamed porous flexible materials are particularly preferable for these flexible materials. A porous flexible material having an apparent specific gravity of 0.06 to 0.4 by foaming a resin or the like can be preferably used. The dimensions are preferably 3 to 15 mm in thickness and 40 to 200 mm in diameter. The preferred range of hardness of the flexible material used for the stress transmission member is measured with a durometer (rubber hardness tester) specified in JIS K 6253-3:2012 or a durometer (rubber hardness tester) improved according to this specification. hardness. According to the type and model of this durometer, the hardness measured with a type A durometer is indicated as A hardness, and the value measured with a type E durometer is indicated as E hardness. Furthermore, with a type F durometer (manufactured by Kobunshi Keiki Co., Ltd., trade name: Asker rubber hardness tester F type), which has been improved so that even softer sponge materials can be properly measured according to the E type specified by JIS. The measured numerical value is indicated as F hardness. The numerical value of hardness measured with a durometer is indicated by 0 to 100 for each type, and the higher the numerical value of hardness, the harder the material. Either type is selected depending on the hardness of the measurement sample, and if the hardness of type A exceeds 90, type D is selected, and if the hardness is less than 20, type E is selected. According to the present invention, when the F hardness exceeds 90, type A or type E is selected and the A hardness or E hardness is measured, and a material having a hardness that can be preferably applied to the present invention can be selected. . Materials with a hardness exceeding A hardness of 50 are too hard, so that the stress transmitted to the surface member varies greatly, the uniformity of the surface gloss of the buffed surface is poor, and a material with a hardness that does not reach F hardness of 70. Since the material is too soft, the stress transmitted to the surface member is reduced, and the buffing operation time is lengthened. In particular, it is more preferable that the hardness is softer than 90 in E hardness and harder than 70 in F hardness. In addition, the plurality of through-holes provided in the stress transmission member may have a circular, oval, oval, drop-shaped, polygonal, or other cross-sectional shape in a plane parallel to the front surface, which is the mounting surface of the surface member. However, in the case of a polygon, it is preferable that each vertex is a circular arc. As described above, it is necessary to set the shape and arrangement so that the positions of the center of rotation and the center of gravity of the stress transmission member do not match.

Further, the stress transmission member having the surface member attached to the front face may be provided with a backing member on the back face, and the buffing machine may be attached to the attachment disc via the backing member.

In the stress transmission member of the buffing disc of the present invention, since the plurality of through-holes do not form rotational symmetry around the center of rotation on the plane of rotation, the through-holes periodically overlap when the buffing disc rotates. Unlike the conventional stress transmission member, the inner edge portion of the through hole, where the stress is most concentrated and applied to the surface member, does not hit the same place at the same period, and the polishing force depending on the place. bias is reduced. Furthermore, since rotational symmetry in the plane of rotation is not formed and the positions of the center of rotation and the center of gravity do not coincide, the buffing machine is unbalanced and the rotating shaft is vibrated. Overlapping of the through-holes can be further prevented, and grinding power and polishing power can be improved.

However, if the unbalance of the buffing machine is too large, the vibration of the rotating shaft will increase, which will not only increase the noise, but also reduce the contact time with the surface to be polished because the buffing machine bounces on the surface to be polished. and the polishing power decreases. Furthermore, it may cause a failure of the rotary polisher. Therefore, by setting the distance between the center of rotation and the center of gravity to be 2 to 9% of the radius of the front surface of the stress transmission member, it is possible to keep the vibration within an appropriate range and prevent such problems from occurring. In addition, by making the material constituting the stress transmission member porous, the specific gravity becomes small, the force that causes the rotation shaft to vibrate can be reduced, the vibration can be kept within an appropriate range, and these problems can be solved. occurrence can be prevented.

FIG. 4A is a plan view and a side view of a buffing machine to which a stress transmission member that does not form rotational symmetry is attached; FIG. 2 is an external perspective view of a rotary polisher to which a buffing disc is attached; FIG. 4 is a side view of a buffing machine with a backing member attached to the back surface of the stress transmission member; FIG. 4 is a plan view of a stress transmission member provided with a through hole having a triangular cross section and not forming rotational symmetry; FIG. 10 is a plan view and a side view of a buffing machine to which a conventional stress transmission member forming rotational symmetry is attached; 1 is a plan view of a conventional stress transmission member forming rotational symmetry; FIG.

BEST MODE FOR CARRYING OUT THE INVENTION A mode for carrying out the buffing machine of the present invention will be described in more detail below with reference to the drawings.

1A and 1B are a plan view and a side view of a buffing machine 10 to which a stress transmission member 1 provided with through holes so as not to form rotational symmetry is attached. The buffing machine 10 has a surface member 4 attached to the front surface of a disk-shaped stress transmission member 1, and a mounting member 5 attached to the back surface. 2, it can be attached to the mounting disc 53 of the rotary polisher 50. As shown in FIG. The mounting disk 53 is fixed to a drive shaft 52 connected to a drive motor housed inside the main body 50 of the rotary polisher 50. In the buffing operation, the mounting disk 53 is operated by the handles 54 and 55 to perform buffing. When a force is applied to the polishing disk 10 and pressed against the surface to be polished, stress is transmitted through the stress transmission member 1 to the surface member 4 attached to the front surface thereof, whereby polishing work can be performed.

The stress transmission member 1 is disc-shaped with a radius r, and has a plurality of through holes 2A to 2E, 3A to 3E, etc. on the inner side at a distance of 3 mm or more from the outer peripheral edge in a direction orthogonal to the front surface, which is the mounting surface of the surface member 4. A rib is formed continuously with a width of 3 mm or more at the outer peripheral end portion where the through hole is not provided. If a through-hole is provided at the outer peripheral end portion and the width of the outer peripheral end portion without the through-hole is not secured to be 3 mm or more, the outer peripheral end portion may be cut off during the buffing operation. 10 damage. Moreover, it is preferable to ensure a width of at least 3 mm between the through-holes. The total cross-sectional area of the plurality of through holes is provided so as to occupy 20% to 70% of the area of the front surface of the stress transmission member 1. Polishing is performed by concentrating and transmitting the stress from the rotating disk 53 . If the ratio of the cross-sectional area of the through-holes to the total area is less than 20%, the stress transmitted to the surface member 4 is not sufficiently concentrated. , the frictional resistance between the surface member 4 and the surface to be polished tends to be excessive.

The stress that is pressed against the surface to be polished and is transmitted to the surface member 4 responsible for polishing is transmitted to the portion of the stress transmission member 1 where the through holes are not provided, so the stress from the rotating disk 53 is concentrated. is transmitted to the surface member 4, and the polishing force by the surface member 4 is strengthened. In particular, the edge portion of the inner surface of the through-hole is a portion where stress is concentrated and transmitted to the surface member 4, and the polishing effect is exhibited more effectively.

In FIG. 1, the stress transmission member 1 has drop-shaped through holes 2A, 2b, 2C, 2D and 2E and circular through holes 3A, 3B, 3C, 3D and 3E in the arrangement described above. , the arrangement of the through-hole 2b among the five droplet-shaped through-holes is different from the arrangement of the other four through-holes 2A, 2C, 2D, and 2E. there is Therefore, these through-holes do not form rotational symmetry around the rotation center O of the stress transmission member 1. In the stress transmission member 1, the rotation center O and the center of gravity G do not match, and the distance e far away. The shape and arrangement of each through-hole are preferably set such that the length of the distance e is 2% to 9% of the radius r of the stress transmission member 1 .

In this way, in the stress transmission member 1 attached to the buffing disc 10, the plurality of through-holes provided do not form rotational symmetry, so the through-holes periodically overlap when the buffing disc 10 rotates. Unlike the conventional stress transmission member, the inner edge portion of the through hole, where the stress is most concentrated and applied to the surface member, does not hit the same place at the same period, and the polishing force depending on the place. bias is reduced. For example, the edge portion 21A of the through hole 2A does not overlap the edge portion 21b of the through hole 2b during rotation. Furthermore, since the positions of the center of rotation O and the center of gravity G do not coincide with each other, the buffing machine 10 is unbalanced and the rotating shaft vibrates. Furthermore, it can prevent and improve grinding power and polishing power.

As described above, the length e of the deviation between the center of rotation O and the center of gravity G is set to 2% to 9% of the radius r of the stress transmission member 1, but if it is less than 2%, buffing Vibration of the rotary shaft during rotation of the buffing machine 10 is small, and the improvement in grinding and polishing power is small. Since it bounces upward, the contact time with the surface to be polished is shortened, and the polishing force is lowered. Furthermore, it may cause a failure of the rotary polisher.

FIG. 3 is a side view of a buffing machine 20 having a backing member 6 provided on the back surface of the stress transmission member 1. The surface member 4 is attached to the front surface of the stress transmission member 1, and the backing member 6 is attached to the back surface. ing. The buffing disc 20 can be attached to the mounting disc 53 of the rotary polisher 50 by means of the mounting member 5 via the backing member 6 in the same manner as the buffing disc 10 described above. As the backing member, the same material as that of the stress transmission member can be used, and the hardness of the material used may be the same, or materials having different hardness may be used.

FIG. 4 is a plan view of the stress transmission member 7 in which a plurality of through holes 71 having triangular cross-sectional shapes are provided so as not to form rotational symmetry. are through-holes with different cross-sectional shapes, but in any of the through-holes, each vertex is arcuate and corners are removed. By making each vertex arc-shaped in this way, it is possible to prevent the stress transmitted at each vertex from concentrating.

In the stress transmission member 7 as well, each through-hole 7 is provided in a shape and arrangement such that the positions of the rotation center 0 and the gravity center G1 do not match, and the rotation center, O, and the gravity center G1 are separated by a distance e1. away. The length of the distance e1 is set to 2% to 9% of the radius of the stress transmission member .

On the other hand, in FIG. 5, similar to the conventionally used stress transmission member, through holes are provided so as to form rotational symmetry about the rotation center O, and a disk-shaped stress transmission member having a radius r is provided. A buffing disc 30 with member 31 is shown. As with the buffing machine 10, the buffing machine 30 has a surface member 4 attached to its front surface for contacting the surface to be polished, and a mounting member 5 attached to its rear surface. Like the disc, it can be attached to the mounting disc 53 of the rotary polisher 50 .

The five through holes 2A, 2B, 2C, 2D and 2E and the five through holes 3A, 3B, 3C, 3D and 3E provided in the stress transmission member 31 are rotationally symmetrical about the rotation center O. forming. That is, each time the stress transmission member 31 is rotated by 72°, the through hole 2A is changed to 2B, and the through hole 3A is changed to 3B. each through-hole overlaps with an adjacent through-hole of the same shape. Furthermore, in the stress transmission member 31 , each through-hole forms rotational symmetry about the rotation center O, so the center of gravity G of the stress transmission member 31 coincides with the rotation center O. Therefore, in the buffing machine 30 to which the stress transmission member 31 is attached, the inner edge portions of the through-holes provided in the stress transmission member 31, which are places where stress is most concentrated and applied to the surface member, have the same period. Since the buffing plate 30 hits the same place, the polishing force is uneven depending on the place, and the entire surface to be polished does not receive a uniform polishing force, so the polishing force is not good. The center of gravity G coincides, no unbalance occurs, no vibration of the rotating shaft occurs, and it is impossible to prevent the through holes from overlapping during rotation.

The buffing machine using the conventional stress transmission member 40 shown in FIG.

As described above, in the present invention, the plurality of through holes provided in the stress transmission member attached to the buffing machine do not form rotational symmetry about the center of rotation of the stress transmission member. In the stress transmission member that rotates with the rotation of , each through hole does not repeat in the same place, and by shifting the center of rotation and the center of gravity of the stress transmission member, vibration of the rotating shaft occurs during rotation during polishing. This prevents each through-hole from being in the same position.

Further, in the above example, the plurality of through holes provided in the stress transmission member 1 are configured to have rotational symmetry about the rotation center O on the front surface of the stress transmission member 1 by changing the shape and arrangement thereof. Although an example in which the through holes are not formed has been shown, even if a plurality of through holes provided in the stress transmission member are provided so as to form rotational symmetry, the rotation axis of the stress transmission member is located at a position different from the center of this rotational symmetry. , so that the center of rotation of the stress transmission member does not coincide with the center of rotational symmetry, that is, the center of gravity. That is, even if the through holes are provided with the shape and arrangement as shown in FIG. 4, the rotation axis of the stress transmission member is set at a position different from the center of gravity G that coincides with the central position of the rotational symmetry of these through holes. It's okay.

The surface member is a member that plays the role of a buff body that contacts and polishes the surface to be polished, and members that have been conventionally used as buffs can be used. A sponge buff made of a foam such as rubber, resin, or the like is used. Cloth buffs are particularly preferred, and woven or knitted fabrics made of fiber materials such as wool, silk, and cotton are used. As the woven fabric, sailcloth, denim, twill fabric, pile woven or knitted fabric, which is a raised fabric, or the like can be used.

Various rubbers and synthetic resins having flexibility can be used for the stress transmission member. Porous soft materials obtained by foaming these materials are particularly preferable. These materials have elasticity and are preferable as stress transmission materials.

Moreover, the mounting member attached to the back surface of the stress transmission member is preferably a hook-and-loop fastener that allows the stress transmission member to be detachably attached to the mounting disk, and one surface is a hook surface and the other surface is a loop surface. It is a member that is detachably attached by If hook-face hook-and-loop fasteners are attached to the front surface of the mounting disk, loop-face hook-and-loop fasteners or loop pile raised fabric may be used on the back of the buffing disc. Such a mounting member can also be used to mount the stress transmission member and the surface member, and can be made detachable so that various combinations can be made according to the state of the surface to be polished.

Hereinafter, as an example, a stress transmission member is made of various materials, a through hole is provided to change the distance e between the center of rotation O and the center of gravity G, and a surface member is attached to the front surface of the stress transmission member, Attached to a rotary polishing tool, the result of buffing is shown.

(Preparation of stress transmission member)
As a material constituting the stress transmission member, a disk-shaped body made of various rubbers and synthetic resins, which are flexible materials, is prepared. The stress transmission member was produced by changing the distance e of . A hardness, E hardness, and F hardness were measured with type A, E, and F durometers. In this hardness measurement, a sample having a sufficient thickness not affected by the sample stage was used.

(Buff polishing test)
A wool buff or sponge buff with a diameter of 90 mm was attached as a surface member to various disc-shaped stress transmission members with a diameter of 80 mm and a thickness of 5 mm. The surface to be polished was coated with a special denatured polyester resin paint (black, product name Protouch, manufactured by Rock Paint Co., Ltd.) and a two-liquid acrylic urethane clear paint (manufactured by Rock Paint Co., Ltd.) as a clear coat, and the panel temperature was 60 ° C. A coated surface dried for 1 hour with a far-infrared heater was used.

The coated surface is covered with sandpaper of various grit to generate paper grains, and then an ultra-fine compound (trade name: Bodycom 1st Neo Black K-Tech) is applied with a rotary polisher equipped with the stress transmission member and buff. (manufactured by Co., Ltd.), it was confirmed whether the grains of each count of paper could be removed, and the grinding power was evaluated. Then, the state of the polished surface after removing the paper grains was evaluated.

(test results)
Tables 1 to 3 show the evaluation results of polishing. Each evaluation result is indicated by Δ, ◯, and ⊚, and each evaluation is as follows.
Vibration of rotating shaft △: Vibration occurs, affecting polishing work.
◯: There is some vibration, but it does not affect work.
A: Almost no vibration.

Polishing evaluation x: Paper grains remain without being erased.
Δ: Paper grains are erased, but a fine striped pattern (texture) is observed.
◯: Paper grains are erased, and no thin striped pattern (texture) is observed.
◎: Paper grains are removed in a shorter time, and thin stripe patterns (texture) are also observed.
will no longer be.

As shown in the test results in Tables 1 to 3, in the stress transmission member made of any material, the distance between the center of rotation and the center of gravity is in the range of 2 to 9% of the radius. Compared to , it is possible to remove the grains of coarser grit sandpaper, exhibit excellent grinding power, and obtain a polished surface in a shorter time without fine stripes (texture), which is excellent. It shows a buffing effect. Further, although the vibration of the rotating shaft is large in a wool buff having a heavy surface member, there is no problem if the distance between the center of rotation and the center of gravity is within the range of 2 to 9% of the radius.

Reference Signs List 10, 20 buffing machine 1 stress transmission member 2A, 2B, 2b, 2C, 2D, 2E, 3A, B, 3C, 3D, 3E through hole 21A, 21B, 21b edge portion 4 surface member 5 attachment member 6 backing member 7 Stress transmission member (triangular through hole)
71 through hole (triangular)
O center of rotation G, G1 center of gravity r radius of stress transmission member e, e1 distance between center of rotation and center of gravity 30 conventional buffing machine 40 conventional stress transmission member 41, 42 through hole 50 rotary polisher
51 main body 52 rotating shaft 53 mounting disk 54, 55 grip

Claims (5)

It has a surface member in contact with the surface to be polished, and a disk-shaped stress transmission member mounted between the surface member and a mounting disk fixed to the drive shaft, the stress transmission member being 3 mm from the outer peripheral edge. A plurality of through-holes are provided on the inner side spaced apart from each other by at least 20% to 70% of the area of the front surface. are arranged so as not to form rotational symmetry around the center of rotation of the stress transmission member, the positions of the center of rotation of the stress transmission member and the center of gravity are displaced, and the distance from the center of rotation to the center of gravity is A buffing machine of a rotary polisher characterized in that the shape and arrangement are set so that the distance is 2% to 9% of the radius of the front surface. 2. The buffing machine of a rotary polisher according to claim 1, wherein said stress transmission member is made of a porous flexible material. 3. A rotary polisher buffing machine according to claim 1, wherein said stress transmission member is made of a material having an A hardness of 50 or more and an F hardness of 70 or more. 4. The cross-sectional shape of the through-hole in a plane parallel to the front surface, which is the mounting surface of the surface member, is circular, elliptical, oval, droplet-shaped, or polygonal. A buffing machine of the rotary polisher according to item 1. A buffing machine for a rotary polisher, wherein a backing member is attached to the back surface of said stress transmission member, and is attached to said attachment disc via said backing member.

Images