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WO2007000074A1 - Dispositif anti-vibration pour machine abrasive, machine comportant ledit dispositif et procédé de nettoyage de surface de pièce de fabrication - Google Patents

Dispositif anti-vibration pour machine abrasive, machine comportant ledit dispositif et procédé de nettoyage de surface de pièce de fabrication Download PDF

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Publication number
WO2007000074A1
WO2007000074A1 PCT/CN2005/000930 CN2005000930W WO2007000074A1 WO 2007000074 A1 WO2007000074 A1 WO 2007000074A1 CN 2005000930 W CN2005000930 W CN 2005000930W WO 2007000074 A1 WO2007000074 A1 WO 2007000074A1
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WO
WIPO (PCT)
Prior art keywords
pad
pads
motor shaft
axis
rotation axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2005/000930
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English (en)
Inventor
Paolo Andriolo
Gianni Borinato
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Positec Power Tools Suzhou Co Ltd
Original Assignee
Positec Power Tools Suzhou Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Positec Power Tools Suzhou Co Ltd filed Critical Positec Power Tools Suzhou Co Ltd
Priority to PCT/CN2005/000930 priority Critical patent/WO2007000074A1/fr
Publication of WO2007000074A1 publication Critical patent/WO2007000074A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B23/00—Portable grinding machines, e.g. hand-guided; Accessories therefor
    • B24B23/02—Portable grinding machines, e.g. hand-guided; Accessories therefor with rotating grinding tools; Accessories therefor
    • B24B23/03—Portable grinding machines, e.g. hand-guided; Accessories therefor with rotating grinding tools; Accessories therefor the tool being driven in a combined movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/32—Correcting- or balancing-weights or equivalent means for balancing rotating bodies, e.g. vehicle wheels
    • F16F15/36—Correcting- or balancing-weights or equivalent means for balancing rotating bodies, e.g. vehicle wheels operating automatically, i.e. where, for a given amount of imbalance, there is movement of masses until balance is achieved

Definitions

  • Anti- Vibration Device for an Abrasive Machine a Machine having such Device and a Method for Cleaning the Surface of a Work Piece
  • the present invention relates to the field of portable power tools for working plane surfaces. It specifically refers to an anti- vibration device for power abrasive tools, preferably for orbit sanders and polishers. It also relates to a power machine incorporating such anti-vibration device, and to a method for abrasively cleaning the surface of a work piece.
  • orbit tools of the above-mentioned type generally include a plate or pad that is normally suited to support an abrasive object, such as a sanding paper.
  • the pad is coupled, by means of proper means of trasmission, to a motor arranged in a housing, which is a case provided with one or more handles.
  • the transmission means can incorporate a cam rotationally driven by the motor shaft.
  • the cam is housed in a circular hole that is placed in the center of the pad.
  • the rotation of the cam drives every point of the pad in a circular orbit whose radius equals the eccentricity of the cam, that is the distance between the rotation axis of the motor shaft and the center of the circular hole which is substantially coincident with the center of the pad that supports the object.
  • said orbit motion can be seen as a linear motion (stroke) in which the pad mass is accelerated in a certain direction.
  • the acceleration produces a reaction force directed in the opposite direction.
  • This reaction force is an unwanted vibration which is transmitted to the machine body and ultimately to the operator's hand and arm.
  • the amplitude of this unwanted vibration depends on the size of the orbit diameter, and on the ratio between the mass of the pad and the mass of the machine.
  • a first type of solution for overcoming the above-mentioned problems is that of adopting one or more eccentric masses or counter-balance weights that move in a direction that is opposed to that of the pad, so that they virtually counterbalance the vibrations.
  • Examples of this kind of solution are illustrated in US 4,660,329, US 4,729,194, US 5,888,128, US 6,244,943, US 6,206,771, US 2001/0003087, DE 3922522, EP 0303955, EP 0455618, WO 98/01733, WO 02/068151.
  • this solution works fine when the pad is not touching the work piece, but displays major limitations in normal working operation.
  • the increase of the working efficiency that is achieved by the increase of the load is exclusively due to the increase of the friction between the working pad and the work piece.
  • the increase of the load unbalances the machine and therefore increases the unwanted vibrations.
  • the diameter of the unwanted vibrations is subtracted from the orbit diameter of the pad. So it must be assumed that the effective working orbit diameter is the result of the theoretical orbit diameter minus that of the unwanted vibrations.
  • a second type of solution for overcoming the above-mentioned problems is that of using elastic materials as an interface between the machine and the operator's hands for dampening the vibrations by transforming the kinetic energy of the vibrations into thermal energy. Examples for solutions of this type are illustrated in US 4,905,772, US 5,453,577, US 5,347,764, US 2001/0011856 Al, WO 03/049902.
  • this second solution does not provide any real advantage.
  • the power tool is free for vibrating with greater amplitude than if it was firmly held by the operator, hi the real world, the operator instinctively feels the decreased efficiency of the machine and tends to grasp it with increased force in an attempt to restore an acceptable efficiency. By doing this, the effeciency of the elastic element is minimized, so that vibrations are transmitted to the operator's hand and arm.
  • the increased muscular force reduces the human body's natural capability of dampening vibrations, therefore making the consequences even worse.
  • an anti- vibration device for an abrasive machine such as for a polishing machine, preferably for a sander machine, which machine is driveable by means of a motor shaft having a rotation axis, characterized in a) a first pad having a first surface and a first predetermined orientation, b) a second pad having a second surface and a second predetermined orientation, wherein said first and second surfaces are determined for attaching an abrasive object thereto, such as a polishing tool or a sanding paper, and wherein said surfaces are arranged substantially in the same plane, and c) means for moving said pads such that they perform orbital rotations preferably about said rotation axis, wherein said orbital rotations are shifted in phase.
  • this anti- vibration device dynamically compensates the inertial and friction forces and reduces vibrations that are transmitted to the motot shaft. These vibrations will be kept low or even completely compensated.
  • the functionality of this device does not depend on the rotation speed, the weight of the machine, the type of the abrasive surfaces, the radius of rotation of the pads, and the load conditions.
  • the active surfaces of the pads are substantially planar and lying in the same plane.
  • one of these surfaces may be substantially central, while the other is peripheral to the first one.
  • the central pad is substantially circular, while the peripheral pad is substantially a ring.
  • the pads may also have a square form, and there may be four or even more of them.
  • the means for moving the pads comprise an eccentric piece assembly that includes at least one pair of cams which are substantially identical to each other, which are longitudinally shifted and which are angularly shifted by 180°.
  • Each one of the cams must be coupled, directly or indirectly, with the motor shaft.
  • Each of them may have a substantially cylindrical shape with an eccentricity relative to the axis of the motor shaft that equals the diameter of the desired orbit trajectory.
  • the external diameter of the inner circular pad may be slightly smaller than the internal diameter of the external ring pad, so that a predetermined minimum gap is left between the pads during operation.
  • suction means such as a fan for removing debris and dust from the work piece. This would replace the holes that are normally included in conventional machines.
  • a method for working on a work piece using a first pad having a first predetermind orientation and a second pad having a second predetermined orientation wherein said pads are driven by means of a motor shaft having a rotation axis.
  • the method is characterized in that said first pad circles about a first axis and said second pad circles about a second axis, wherein said first axis and said second axis preferably coincide.
  • both pads maintain their predetermined orientations.
  • the method may be additionaly characterized in a) using a ring-shaped first pad and a circular shaped second pad, wherein said second pad is arranged within the inner or central space of said first pad, b) circulating the center axis of said second pad about said rotation axis, and c) circulating the center axis of said first pad also about said rotation axis in the same direction of circulation, but angularly shifted or offset by approximately 180° with respect to said center axis of said second pad.
  • a portable abrasive power machine in particular a sander or polisher, comprises a) a housing provided with a handle for an operator, b) an inner space within said housing, c) a motor arranged in said inner space and having a motor shaft with a longitudinal rotation axis, d) at least a first pad for attaching a first abrasive object thereto, and a second pad for attaching a second abrasive object thereto, and e) transmission means and an anti- vibration device for transmitting energy from said motor shaft to said pads, wherein the anti-vibration device is designed as described here-before and in the appended claims.
  • This abrasive power machine or tool may be designed as a "rotary sander”.
  • the power machine may be provided with a weight which is associated with or even directly connected to the motor shaft or which is arranged on a cooling fan, and which has a center of gravity which is located outside the rotation axis of the motor shaft.
  • this abrasive power machine may also be designed as a
  • finishing sander when holding devices, such as connection pieces made of a resilient material, are used.
  • brakes may be used.
  • Fig. 1 is a partially sectioned side view of a portable hand-held power tool, specifically of a
  • Fig. 2 is an exploded perspective view of the anti -vibration device of Fig. 1,
  • Fig. 3 is an exploded cross-sectional view of the anti- vibration device of Fig. 1,
  • Fig. 4 is a view from below at the device of Figs. 1 — 3 in a reduced scale
  • Fig. 5 is a cross-sectional view of the device of Figs. 1 - 3 after assembling
  • Fig. 6 is a perspective view of a double-cam assembly used in the device of Figs. 1—3, Fig. 7 is a cross-sectional view as in Fig. 5, where there is provided a weight on the motor shaft,
  • Fig. 8 a view of eight small sanding particles travelling during operation
  • Figs. 9 - 12 a view of the travelling of another four small sanding particles during operation
  • Fig. 13 is a bottom view of the arrangement of four pads according to a second basic embodiment of an anti- vibration device
  • Fig. 14 is a cross-sectional view as in Fig. 5 with the provision of a weight on a cooling fan
  • Fig. 15 is a side view as in Fig. 1, but incorporating connection pieces, in order to illustrate a
  • Fig. 16 is a side view as in Fig. 1 where brakes are provided.
  • an abrasive power tool I 5 e.g. a sander or polisher, incorporating a preferred embodiment of an anti- vibration device according to the present invention.
  • the power tool 1 essentially includes a housing 2 that has a handle or grip 3 and an inner space 4 for housing a motor 5, for example an electric motor, having a motor shaft 11 with a longitudinal axis 12, which shaft 11 is supported by ball, cylinder or oil bearings 6.
  • the motor 5 can be of a type other than electric, for example pneumatic.
  • the axis 12 will be termed motor shaft axis or rotation axis.
  • the motor 5 may work with any speed, even with very high speeds. In an exemplary design an electric motor 5 was used which had a variable speed from 2.000 to 12.000 rpm.
  • a power switch 7 is placed on the hand grip 3 so that it can be conveniently operated by the operator by connecting the motor 5 with a mains power, or a rechargeable battery, or a compressed air tank, which is not represented in the drawing.
  • the shaft 11 is coupled, by means of mechanical transmission means including an anti- vibration device 10 which are described below, to pads 16, 22 which support substantially plane abrasive objects 8, 9, for instance abrasive layers or sanding papers.
  • the transmission means and the anti -vibration device 10 are suitable to support the abrasive objects 8, 9 and to reduce the amplitude of the vibrations that are conventionally generated by the reaction of the work piece surface on the tool pads 16, 22 and therefore on the motor shaft 11 and consequently on the machine housing 2 and the operator.
  • the transmission means including the anti-vibration device 10 are made so that the pads 16, 22 are distinctive and separated from each other. They have substantially identical mass, and preferably their active surfaces 16b, 22a have substantially identical surface areas Fl, F2. These outside surfaces 16b, 22a are located in the very same plane P.
  • the transmission means which are driven by the motor shaft 11, are designed so that they provide not only rotational motions, but also orbital motions with phase opposition for the pads 16, 22. By the orbital motions they dynamically compensate the inertial forces and the friction forces, and thus reduce the vibrations transmitted back to the motor shaft 11. The orbital motions will be considered first.
  • the transmission and anti- vibration means incorporate a double eccentric piece assembly 18 having cams 18a, 18b that drive the pads 16, 22 with respective orbit motions. This will subsequently be described.
  • the housing 2 includes a collection room 44 above the assembly 18. To this room 44 is connected an air and dust emitting tube 45 which is arranged under the handle 3. A sucking fan (not shown) may be connected to the tube 45 for health protection of the operator.
  • the anti-vibration device 10 for the abrasive machine 1 comprises the first or outer pad 16 which is here in the form of a ring, and which has a central inner space 16a and a first outer surface 16b for attachment of a ring-shaped sanding paper 8. The size of the outer surface area of the outer pad 16 is designated as Fl.
  • the outer pad 16 is joined with a bell-shaped first support 17.
  • the device 10 also comprises a second or inner pad
  • the inner pad 22 which is shaped as a round or circular disc.
  • the inner pad 22 is accomodated in the central inner space 16a of the outer pad 16. It has a second outer surface 22a for attachment of a circular sanding paper 9.
  • the size of the outer surface area of the inner pad 22 is designated as F2.
  • the surfaces 16b, 22a are located substantially in the same plane P (see Figs. 1 and 5).
  • a second support 23 is provided as a central cylindrical holder on the inner surface of the inner pad 22. The support
  • the bell-shaped support 17 of the outer pad 16 has a conical portion 17a and a planar ring portion 17b joined thereto, thereby forming a central lower space 17c.
  • a central cylindrical holder 17d (not shown) which is joined to the ring portion 17b and which forms a central upper space 17e.
  • the space 17e is formed by the portion 17b.
  • at least one air and dust sucking hole 17f may be provided in the support 17, notably in the conical portion 17a.
  • first bearing 13 and a second bearing 19 which both may be ball bearings or cylinder bearings.
  • the outer surface of the first bearing 13 is firmly received in the central upper space 17e of the planar ring portion 17b.
  • the outer surface of the second bearing 19 is firmly received in the space 23a of the cylindrical holder 23 of the inner pad 22.
  • the center of the first bearing 13 is denoted as 13a, its central hole as 14, and its central axis as 15.
  • the center of the second bearing 19 is denoted as 19a, its central hole as 20, and its central axis as 21.
  • Both central axes 15, 21 are arranged parallel to the rotation axis 12, but on opposite sides of the rotation axis 12.
  • the central axis 15 coincides with the central axis of the outer pad 16 including its support 17, and the central axis 21 coincides with the central axis of the inner pad 22 including its support 23.
  • the design is such that the center 25 of gravity of the outer pad 16 including its support 17 and the center 26 of gravity of the inner pad 22 including its support 23 are aligned along a straight line 27 passing vertically through the rotation axis 12 (see Fig. 5).
  • the central axis 15 circulates or orbits about the rotation axis 12. (According to the embodiment of Fig. 15, this occurs while the outer pad 16 maintains its orientation 16z (see Fig.
  • the essential element of the anti- vibration device 10 depicted in Figs. 1 - 7 is the eccentric piece assembly 18. It is here a double piece assembly 18 having a first cam 18a and a second cam 18b which is attached to the first cam 18a.
  • the cams 18a, 18b are substantially identical to each other, they are longitudinally shifted, and they are angularly shifted or offset by about 180° with respect to each other.
  • the eccentric piece assembly 18 is provided with a central hole 18c which goes all the way through and which serves for a firm connection to the motor shaft 11.
  • the central hole axis coincides with the rotation axis 12.
  • the cams 18a, 18b have a substantially a cylindrical shape. They may also have another shape, e.g.
  • the cams 18a, 18b both constitute a monolithe, e.g. made of a block of metal. Alternatively the cams 18a, 18b may originally be single pieces which are later-on firmly connected to each other.
  • first or upper cam 18a is received in the central hole 14 of the first bearing 13 (and fixed therein), and the second or lower cam 18b is received in the central hole 20 of the second bearing 19 (and fixed therein).
  • the rotation of the motor shaft 11 is transferred to the cams 18a, 18b and from there slidingly via the bearings 13 and 19, respectively, to the supports 17 and 23, respectively, and to the associated pads 16 and 22, respectively.
  • the orientations 16z, 22z will be maintained during the entire rotation.
  • both pads 16, 22 will describe eccentric orbits which are shifted in phase by 180° relative to each other.
  • the outer diameter of the inner circular pad 22 may be slightly smaller than the inner diameter of the ring-shaped outer pad 16, so that a predetermined minimum gap 24a may be maintained between the pads 16, 22 during the entire rotationel operation.
  • the whole gap 24 between pad 22 and pad 16 defines a passage for suction of debris and dust coming from the work piece during operation.
  • the suction may be caused by a fan (not shown) associated with the tube 45.
  • a force Kl, K2 is generated and associated with each pad 16, 22, respectively (see Fig. 4).
  • the weight 28 may basically have any shape. Here a cylindrical shape was chosen. Yet, it should be observed that the mass of the outer pad 16 including its support 17 equals the mass of the inner pad 22 including its support 23 plus the mass of the weight 28, since for balancing purposes, not only the mass of the weight 28 is essential, but also its distance q from point 31. The total center of gravity is then positioned in point 31. Li Fig.
  • FIG. 8 a view from below of the outer pad 16 and of the inner pad 22 is illustrated.
  • This view illustrates the function of the device 10.
  • the surfaces 16b, 22a of both pads ⁇ f 6, 22 are located in the very same plane P. And it assumed that their surface areas Fl, F2 are equal. There may be instances where this requirement should not be fulfilled.
  • the center axis 15 of the outer ring pad 16 describes a small circle around the rotation axis 12 of the motor shaft 11, and the center axis 21 of the inner circular pad 22, with a phase shift of 180°, describes also a small circle around the rotation axis 12.
  • These circulations are indicated by two small curved arrows 40, 41, respectively.
  • connection line 42 is shown to connect the axes 15, 12, 21.
  • the distance between the axes 12, 15 equals the distance between the axes 12, 21. This is the preferred design, since it makes the construction simple, but there may be occasions and conditions where a deviation from this condition should be chosen.
  • An arrow 16z is assumed to be fixed on the surface 16b of the outer pad 16. It indicates a predetermined direction or orientation of this outer pad 16 with regard to the machine 1. It is e.g. directed from the front side of the machine 1 to its back side. And an arrow 22z is assumed to be fixed on the surface 22a of the inner pad 22. It similarly indicates a predetermined direction or orientation of this inner pad 22 with regard to the machine 1. For instance, it may also be directed from the front side of the machine 1 to its back side. (It is important to realize that in the embodiment of Fig. 15 these orientations 16z, 22z are maintained during the entire operation of the machine 1. In other words, in all working positions, (five of which are indicated in Fig. 8 by reference signs (1) through (5)) the arrows 16z, 22z are each parallel to a predetermined line which is oriented perpendicularly to the rotation axis 12.)
  • each pad 16, 22 starts to rotate in the same direction as the motor shaft 11, and each pad 16, 22 is accelerated (see arrows 33 and 34) until it finally reaches the same speed as the motor shaft 11.
  • the working piece e.g. the surface of a table made of wood
  • pads Al, A2, A3, A4 arranged in a symmetrical square configuration. They are all arranged in the same plane around the rotation axis 12 of a motor shaft 11. All pads Al - A4 may have any shape, here they have a rectangular, specifically a square shape. All are planar, and all have the same size of surface area Bl - B4 for attachment of equal-size sanding or polishing papers. It is assumed that small sanding particles a, b, c, d are present at the outer corners. During operation, these sanding particles a - d assume the consecutive positions (1), (2), (3), (4) etc., of which only positions (1) and (3) are illustrated.
  • Position (3) results from a shift in the direction of the corner arrows by 45° with respect to position (1).
  • the pads Al - A4 and circular areas Cl - C4 in their centers Sl - S4 are shown in solid lines in position (1), whereas pads Al - A4 and areas Cl - C4 are shown in broken lines in position (3).
  • the centers including center axes of pads Al - A4 are denoted as Sl - S4.
  • Tl, T2, T3, T4 indicate the orbital rotation directions. It is also important to realize that all neighboring pads Al - A4 orbit in opposite direction with respect to each other, whereby the individual orientation 01, 02, 03, 04 of the pads Al, A2, A3, A4 remains unchanged. Thus, vibrations are cancelled.
  • the cam assembly may be similer to that of Fig. 6, i.e. including two (preferably circular or cylindrical) cams for neighboring pads Al, A3 and A2, A4, wherein each of the two cams assemblies is connected to the motor shaft 11.
  • a gear assembly the rotation of the motor rotation axis 12 may be transferred to the four axes Sl, S2, S3, S4, so that the pads Al - A4 rotate in the directions of the arrows Tl - T4.
  • This embondiment can also be designed as a finishing sander.
  • a cooling fan 43 for cooling the motor 4 is connected to the motor shaft
  • a weight 28 is arranged on the lower outer side of the cooling fan 43.
  • the combined center of gravity 29A of the weight 28 and of the cooling fan 43 is located outside the rotation axis 12. In this way unbalances are compensated.
  • connection pieces 46, 47 are elongated and made of an elastic material, such as rubber.
  • the first connection piece 46 is arranged between the outer ring pad 16 and the housing 2
  • the second connection piece 47 is arranged between the inner circular pad 22 and the support 17, i.e. indirectly also between pad 22 and housing 2.
  • the flexible connection pieces 46, 47 prevent the afore-mentioned "pad rotations", while they allow for the "orbital rotations".
  • Fig. 16 there is illustrated that two brakes 50, 51 may be used in the rotary sander of Fig. 1 in order to slow down the rotation of the pads 16 and 22, specifically when there is no load applied to the tool 1.
  • the rotation speed is now kept low because the brakes 50, 51 simulate a load.
  • the brakes 50, 51 are here schematically illustrated as rubber rings of different diameter.
  • R1, R2, R3, R4 axes about which pads Al, A2, A3, A4 and areas Cl, C2, C3,

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)

Abstract

La présente invention concerne une ponceuse à moteur (1) qui comprend un boîtier (2), un moteur électrique (4) agencé dans le boîtier (2), un arbre de moteur électrique (11), une premier patin extérieur ou annulaire (16) pour fixer à celui-ci un premier papier de verre (8), et un second patin intérieur ou circulaire (22) pour fixer à celui-ci un second papier de verre (9). Le dispositif anti-vibration (10) sert à transférer de l’énergie provenant du moteur électrique (4) aux patins (16, 22) avec des mouvements de phase opposée, de sorte que des forces d’inertie et de frottement soient compensées dynamiquement. Simultanément, des vibrations qui sont normalement transmises à l’arbre de moteur électrique (11) et de là à l’opérateur de la machine (1) sont drastiquement réduites. Ceci est également le cas lorsque l’opérateur augmente la force d’opération sur la ponceuse (1) afin d’augmenter la profondeur de ponçage ou d’accélérer l’opération de ponçage. Dans ce but, des cames (18a, 18b) sont fixées sur l’arbre de moteur électrique (11). Les cames (18a, 18b) font tourner les axes centraux (15, 21) des patins (16, 22) autour de l’axe d’arbre de moteur électrique (12) avec un déphasage, de préférence de 180 °.
PCT/CN2005/000930 2005-06-27 2005-06-27 Dispositif anti-vibration pour machine abrasive, machine comportant ledit dispositif et procédé de nettoyage de surface de pièce de fabrication Ceased WO2007000074A1 (fr)

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PCT/CN2005/000930 WO2007000074A1 (fr) 2005-06-27 2005-06-27 Dispositif anti-vibration pour machine abrasive, machine comportant ledit dispositif et procédé de nettoyage de surface de pièce de fabrication

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PCT/CN2005/000930 WO2007000074A1 (fr) 2005-06-27 2005-06-27 Dispositif anti-vibration pour machine abrasive, machine comportant ledit dispositif et procédé de nettoyage de surface de pièce de fabrication

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2072183A1 (fr) 2007-12-22 2009-06-24 J. Wagner GmbH Meuleuse de surfaces
CN119897787A (zh) * 2025-04-01 2025-04-29 雅安成建工业化建筑有限公司 一种桥梁混凝土生产用粗打磨装置

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Publication number Priority date Publication date Assignee Title
US2759305A (en) * 1954-06-11 1956-08-21 Cyclo Mfg Company Portable abrading and polishing machine
CN1169902A (zh) * 1996-05-02 1998-01-14 罗伯特-博希股份公司 手持式磨光机
CN1288406A (zh) * 1998-11-12 2001-03-21 罗伯特·博施有限公司 电动手控磨削机
JP2002233941A (ja) * 2001-02-06 2002-08-20 Makita Corp オービタルサンダ
EP1300218A1 (fr) * 2001-10-02 2003-04-09 The Technology Partnership Public Limited Company Outil
WO2004085114A1 (fr) * 2003-03-28 2004-10-07 The Technology Partnership Plc Outil rotatif possedant des engrenages planetaires en orbite contenant des axes excentriques servant a fixer des plaques de polissage ou de sablage

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2759305A (en) * 1954-06-11 1956-08-21 Cyclo Mfg Company Portable abrading and polishing machine
CN1169902A (zh) * 1996-05-02 1998-01-14 罗伯特-博希股份公司 手持式磨光机
CN1288406A (zh) * 1998-11-12 2001-03-21 罗伯特·博施有限公司 电动手控磨削机
JP2002233941A (ja) * 2001-02-06 2002-08-20 Makita Corp オービタルサンダ
EP1300218A1 (fr) * 2001-10-02 2003-04-09 The Technology Partnership Public Limited Company Outil
WO2004085114A1 (fr) * 2003-03-28 2004-10-07 The Technology Partnership Plc Outil rotatif possedant des engrenages planetaires en orbite contenant des axes excentriques servant a fixer des plaques de polissage ou de sablage

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2072183A1 (fr) 2007-12-22 2009-06-24 J. Wagner GmbH Meuleuse de surfaces
CN119897787A (zh) * 2025-04-01 2025-04-29 雅安成建工业化建筑有限公司 一种桥梁混凝土生产用粗打磨装置

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