EP1586416A2 - Antiruckelvorrichtung - Google Patents

Antiruckelvorrichtung Download PDF

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Publication number
EP1586416A2
EP1586416A2 EP05252417A EP05252417A EP1586416A2 EP 1586416 A2 EP1586416 A2 EP 1586416A2 EP 05252417 A EP05252417 A EP 05252417A EP 05252417 A EP05252417 A EP 05252417A EP 1586416 A2 EP1586416 A2 EP 1586416A2
Authority
EP
European Patent Office
Prior art keywords
pad surface
arrangement
external pad
pad
external
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.)
Granted
Application number
EP05252417A
Other languages
English (en)
French (fr)
Other versions
EP1586416B1 (de
EP1586416A3 (de
Inventor
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 US11/151,050 priority Critical patent/US7104873B1/en
Publication of EP1586416A2 publication Critical patent/EP1586416A2/de
Publication of EP1586416A3 publication Critical patent/EP1586416A3/de
Application granted granted Critical
Publication of EP1586416B1 publication Critical patent/EP1586416B1/de
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
    • 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
    • B24B41/00—Component parts such as frames, beds, carriages, headstocks
    • B24B41/007—Weight compensation; Temperature compensation; Vibration damping

Definitions

  • the present invention relates to an anti-vibration arrangement for an eccentrically rotary and oscillatory tool (eg an abrasive power tool) such as an orbital sander or polisher, to a power tool incorporating the anti-vibration arrangement and to a method for abrading a work piece.
  • an eccentrically rotary and oscillatory tool eg an abrasive power tool
  • an orbital sander or polisher e.g an abrasive power tool
  • a power tool eg an orbital sander or polisher
  • Orbital power tools such as sanders and polishers generally include a pad that is normally adapted to support an abrasive element such as sanding paper.
  • the pad is coupled by a transmission means to a motor arranged in a housing.
  • the transmission means can incorporate a cam rotationally driven by the rotary drive shaft.
  • the cam is housed in a circular aperture that is positioned in the centre 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 ie the distance between the rotary axis of the rotary drive shaft and the centre of the circular aperture which is substantially coincident with the centre of the pad.
  • the orbital motion can be envisaged as a linear motion (or 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 manifests itself as an unwanted vibration which is transmitted to the housing and ultimately to the operator's hand and arm.
  • the amplitude of this unwanted vibration depends on the diameter of the orbit and on the ratio between the mass of the pad and the mass of the tool.
  • An arrangement for overcoming the above-mentioned drawbacks adopts one or more counterbalances (eg eccentric masses or counterweights) that move in a direction opposite to that of the pad to counterbalance the vibrations.
  • counterbalances eg eccentric masses or counterweights
  • Examples of this kind of arrangement are illustrated in US-A-4660329, US-A-4729194, US-A-5888128, US-A-6244943, US-A-6206771, US 2001/0003087, DE-A-3922522, EP-A-303955, EP-A-0455618, WO-A-98/01733 and WO-A-02/068151.
  • this type of arrangement works satisfactorily when the pad is not touching the work piece but displays major limitations in normal use.
  • the load effectively modifies the mass of the pad and the ratio between the mass of the pad and the mass of the counterbalance is altered.
  • the counterbalance fails to eliminate the vibrations induced by the heightened effective mass of the pad.
  • the higher the load the greater the system imbalance and the higher the level of unwanted vibrations.
  • the pad With a load tending to infinity, the pad will be at a standstill and the tool will vibrate with an amplitude equal to the radius of the orbit of the pad.
  • the present invention seeks to overcome certain of the above-described drawbacks by exploiting two or more pads exbiting out-of-phase orbital motion.
  • the present invention provides an anti-vibration arrangement for an eccentrically rotatable and oscillatory tool (eg a motor-driven abrasive tool), the arrangement comprising:
  • the anti-vibration arrangement dynamically compensates for inertial and frictional forces and reduces or eliminates vibrations that are otherwise transmitted to the rotary shaft.
  • the anti-vibration arrangement significantly reduces the risks to the operator's health.
  • the arrangement is easy to use and convenient to maintain and even when the load is unequally shared by the abrasive elements, the residual vibrations are lower than in a conventional machine provided (for example) with a counter-balance mechanism.
  • the motor can be electric or pneumatic.
  • the first pad has essentially the same mass as the second pad.
  • the first external pad surface has essentially the same area as the second external pad surface.
  • the centre of gravity of the first pad and the centre of gravity of the second pad are aligned along a straight line intersecting the rotary axis.
  • the second external pad surface is arranged substantially peripherally and eccentrically with regard to the first external pad surface.
  • the second external pad surface is substantially circular.
  • the first external pad surface is substantially annular.
  • the second external pad surface may be confined within the first external pad surface.
  • the first pad is substantially bell-shaped and comprises a conical main body terminating at an apical end in an annular lip and terminating at a non-apical end opposite to the apical end in a radial collar, the radial collar defining the first external pad surface.
  • the second pad comprises a cylindrical main body capped by a circular plate defining the second external pad surface.
  • the first pad further comprises at least one dust vent.
  • the first orbital axis and the second orbital axis may be coincident or non-coincident.
  • the first orbital axis and/or the second orbital axis may coincide with the rotary axis of the rotary drive shaft.
  • Preferably the first orbital axis and the second orbital axis are common to the rotary axis of the rotary drive shaft.
  • the central axis of the first external pad surface and the central axis of the second external pad surface are arranged parallel to the rotary axis substantially in a common plane therewith.
  • the central axis of the first external pad surface and the central axis of the second external pad surface are equidistant from the rotary axis. This advantageously makes construction simple but there may be occasions where a deviation from this condition is desirable.
  • the transmission means comprises:
  • the cams may be coupled directly or indirectly to the rotary drive shaft.
  • the cams may be any suitable shape (eg cylindrical or elliptical).
  • first cam and the second cam are non-coaxial.
  • the monolithic drive shaft assembly is provided with a central aperture for mounting on the rotary drive shaft, wherein the first cam and the second cam are substantially identical and are longitudinally and angularly displaced.
  • first cam and the second cam are angularly displaced by approximately 180°.
  • first cam and the second cam are each substantially cylindrical and wherein the eccentricity of the first cam and the second cam with respect to the rotary axis equals the orbital diameter.
  • the outer diameter of the second external pad surface is slightly smaller than the inner diameter of the first external pad surface so that a minimum gap is maintained between the second external pad surface and the first external pad surface.
  • the gap defines a passage for emitting debris from a work piece during use.
  • the gap can be connected to suction means such as a fan for removing debris and dust from the work piece. This removes the need for apertures that are normally included in conventional machines.
  • the transmission means comprises: a first bearing mounted on or in the first pad; and a second bearing mounted on or in the second pad.
  • first bearing is mounted on the first cam and the second bearing is mounted on the second cam.
  • first external pad surface and the second external pad surface are substantially rectangular or square.
  • the anti-vibration arrangement of the invention may further comprise any number of additional pads (eg third and fourth pads).
  • additional pads eg third and fourth pads.
  • the central axes of the external pad surfaces of the pads are equidistant from the rotary axis.
  • the total number of pads can be driven by a suitable number of drive shaft assemblies with a suitable disposition ( eg a suitable number of cams).
  • the arrangement comprises four pads with external pad surfaces having individual orbital axes, wherein neighboring pads are adapted to orbit in opposite directions.
  • the individual orbital axes may be non-coincident with the rotary axis.
  • the four pads are disposed in a square configuration.
  • the first external pad surface has a first predetermined orientation and the second external pad surface has a second predetermined orientation, wherein the transmission means is adapted to transmit drive to the first external pad surface and the second external pad surface in a manner such that the first and second predetermined orientations are maintained.
  • the present invention provides a method for abrading a work piece comprising:
  • first orbital axis and the second orbital axis coincide.
  • the first predetermined orientation and the second predetermined orientation are maintained during orbit.
  • the first external pad surface is substantially annular and the second external pad surface is substantially circular and wherein the second external pad surface is arranged within the first external pad surface and the first external pad surface and the second external pad surface are angularly offset by approximately 180°.
  • a portable tool eg a sander or a polisher
  • an anti-vibration arrangement as hereinbefore defined which allows the user to accomplish coarse and/or fine surface sanding work on any material with high efficiency and productivity and with a substantial reduction in vibrations irrespective of the the load applied by the user.
  • an eccentrically rotatable and oscillatory tool eg a portable abrasive tool
  • an eccentrically rotatable and oscillatory tool comprising:
  • the tool comprises: an anti-vibration arrangement as defined hereinbefore, wherein the transmission means couples the rotary drive shaft to the first pad and to the second pad.
  • This tool advantageously does not depend on the rotation speed, the weight, the type of abrasive surface, the radius of rotation of the pads or the load conditions.
  • a counterweight may be added.
  • the counterweight may be any convenient shape.
  • the tool further comprises:
  • the tool further comprises:
  • the tool further comprises:
  • the tool may be a rotary sander, random orbital sander or finishing sander.
  • connection pieces made of a resilient material may be deployed to restrain the tool to regular orbital motion.
  • the pads maintain their predetermined orientations.
  • the tool further comprises:
  • the tool further comprises:
  • the brake (or brakes) permit high rotational speeds to be avoided especially when no load is applied to the pads.
  • the present invention provides a kit comprising a substantially annular sanding paper attachable to a first pad defined hereinbefore and a substantially circular sanding paper attachable to a second pad as hereinbefore defined.
  • FIG. 1 illustrates a rotary sander 1 incorporating a first embodiment of an anti-vibration arrangement 10 according to the present invention.
  • the rotary sander 1 generally includes a housing 2 that has a handle or grip 3 and an internal volume 4 for housing an electric motor 5 with a variable speed of 2000 to 12000 rpm.
  • the housing 2 is provided with an exhaust tube 45 beneath the handle 3 for exhausting air and dust from the interior 44.
  • the electric motor 5 has a rotary drive shaft 11 with a longitudinal rotary axis 12 which is supported at the upper end of the housing 2 by ball, cylinder or oil bearings 6.
  • a power switch 7 is positioned on the handle 3 and the rotary sander 1 is connected to mains power, a rechargeable battery or a compressed air tank which is not represented in Figure 1.
  • the anti-vibration arrangement 10 couples the rotary drive shaft 11 to abrasive elements (such as abrasive layers or sanding papers) for abrading a work piece (not shown) as described
  • the anti-vibration arrangement 10 comprises a bell-shaped first pad 17 having a substantially conical main body 17a enclosing a central lower volume 17c and terminating at an apical end in an annular lip 17b bounding an aperture 17e.
  • the conical main body 17a terminates in a radial collar 16 bounding an aperture 16a and having a first external pad surface 16b for fitting to a substantially planar annular abrasive element 8.
  • the area of the first external pad surface 16b is designated F1.
  • air and dust vents 17f are provided in the conical main body 17a.
  • the anti-vibration arrangement 10 further comprises a second pad 23 having a cylindrical main body 23a capped by a circular plate 22 with a second external pad surface 22a for fitting to a substantially planar circular abrasive element 9.
  • the circular plate 22 is accommodated in the aperture 16a of the radial collar 16.
  • the area of the second external pad surface 22a is designated F2.
  • the anti-vibration arrangement 10 is adapted to reduce the amplitude of vibrations that are generated by the reaction of the first and second external pad surfaces 16b, 22a on the work piece.
  • the anti-vibration arrangement 10 is arranged so that the first and second external pad surfaces 16b, 22a are disposed distinctly and separately from each other.
  • the pads 17 and 23 have substantially identical mass.
  • the first and second external pad surfaces 16b, 22a have substantially identical surface areas F1 and F2 and are located substantially in the same plane P (see Figures 1 and 5).
  • the anti-vibration arrangement 10 is adapted to provide orbital motion to the first and second external pad surfaces 16b, 22a in different phases. Through their out-of-phase motion, the first and second external pad surfaces 16b, 22a dynamically compensate for inertial and frictional forces and thus reduce the vibrations transmitted back to the rotary drive shaft 11.
  • the anti-vibration arrangement 10 further comprises a monolithic drive shaft assembly 18 having first (upper) and second (lower) substantially cylindrical cams 18a, 18b.
  • the drive shaft assembly 18 is provided with a central aperture 18c coincident with the rotary axis 12 for a firm connection to the rotary drive shaft 11 so that the cams 18a, 18b rotate at the same speed as the rotary drive shaft 11.
  • the cylindrical cams 18a, 18b are substantially identical to each other but they are longitudinally displaced (non-coaxial) and angularly offset relative to the plane of the housing by about 180° to drive respectively the first and second pads 17, 23 in an out-of-phase eccentric manner.
  • a first bearing 13 is firmly received in the aperture 17e of the annular lip 17b and is mounted on the cam 18a.
  • a second bearing 19 is firmly received in the cylindrical main body 23a and is mounted on the cam 18b.
  • the first bearing 13 and the second bearing 19 may be ball bearings or cylinder bearings.
  • the centre of the first bearing 13 is denoted as 13a, its central aperture as 14 and its central axis as 15.
  • the centre of the second bearing 19 is denoted as 19a, its central aperture as 20 and its central axis as 21.
  • the outer surface of the first cam 18a is received in the central aperture 14 of the first bearing 13 (and fixed therein) and the second cam 18b is received in the central aperture 20 of the second bearing 19 (and fixed therein).
  • the central axes 15, 21 are arranged parallel to the rotary axis 12 substantially in a common plane therewith.
  • the central axis 15 coincides with the central axis of the first external pad surface 16a and the central axis 21 coincides with the central axis of the second external pad surface 22b.
  • the anti-vibration arrangement is such that the centre of gravity 25 of the first pad 17 and the centre of gravity 26 of the second pad 23 are aligned along a straight line 27 passing through the rotary axis 12 (see Figure 5).
  • the central axis 15 orbits about the rotary axis 12.
  • the central axis 21 orbits about the rotary axis 12 with a phase differential of 180° with respect to the orbit of the central axis 15. Consequently, pads 17 and 23 describe eccentric orbits with a phase differential of 180° relative to each other.
  • the diameter of the circular plate 22 is slightly smaller than the inner diameter of the radial collar 16 so that a gap 24 is maintained between the radial collar 16 and the circular plate 22 during rotation with a predetermined minimum gap 24a.
  • the gap 24 between the radial collar 16 and the circular plate 22 defines a passage for debris and dust from the work piece.
  • forces K1, K2 are generated and associated with the radial collar 16 and the circular plate 22 respectively (see Figure 4). These forces K1, K2 act in opposite directions (due to the phase differential of 180°) and therefore substantially eliminate vibrations which would otherwise be transferred back to the housing 2.
  • a small torque may be generated by forces f1, f2 around a point 30 which is the centre of gravity of the arrangement ( ie of the first and second pads 17, 23, the bearings 13, 19 and the drive shaft assembly 18). These forces f1, f2 are generated by centrifugal effects and may lead to vibrations.
  • a cylindrical counterweight 28 is associated with the rotary drive shaft 11.
  • the counterweight 28 may be firmly mounted directly on the rotary drive shaft I 1 (as in Figure 7) or connected to the drive shaft assembly 18 or it may be mounted on the lower outer side of a cooling fan 43 (as shown in Figure 14) connected to the rotary drive shaft 11 for cooling the motor 4.
  • the centre of gravity 29 of the counterweight 28 is located outside the rotary axis 12 with an eccentricity denoted j in Figure 7 and the total centre of gravity is positioned at point 31.
  • the mass of the first pad 17 equals the mass of the second pad 23 plus the mass of the counterweight 28 because for balancing purposes not only the mass of the counterweight 28 is essential but also its distance q from point 31.
  • the centre of gravity 29A of the counterweight 28 and of the cooling fan 43 is located outside the rotary axis 12.
  • the radial collar 16 is illustrated from below to demonstrate the function of the anti-vibration arrangement 10.
  • the first and second external pad surfaces 16b, 22a are located in the same plane P and their surface areas F1, F2 are equal.
  • the central axis 15 of the radial collar 16 describes a small circle 40 around the rotary axis 12 of the rotary drive shaft 11 and the central axis 21 of the circular plate 22 with a phase differential of 180° also describes a small circle 41 around the rotary axis 12.
  • a connection line 42 connects the axes 15, 12 and 21. The distance between the axes 12 and 15 equals the distance between the axes 12 and 21.
  • an arrow 16z may be assumed to be fixed on the first external pad surface 16b of the radial collar 16. It indicates a predetermined direction or orientation of the radial collar 16 with regard to the rotary sander 1. For example it is directed from the front side of the rotary sander 1 to the back side.
  • an arrow 22z may be assumed to be fixed on the second external pad surface 22b of the circular plate 22. It similarly indicates a predetermined direction or orientation of this circular plate 22 with regard to the rotary sander 1. For instance, it may also be directed from the front side of the rotary sander 1 to the back side.
  • the orientations 16z, 22z are maintained during the entire operation of the rotary sander 1.
  • the arrows 16z, 22z are each parallel to a predetermined line which is oriented perpendicular to the rotary axis 12.
  • the rotary sander 1 operates with no load (eg if it is held in the air so that there is no friction between the first and second external pad surfaces 16b, 22a and the work piece), the radial collar 16 and the circular plate 22 start to rotate in the same direction as the rotary drive shaft 11 and each of the radial collar 16 and the circular plate 22 is accelerated until it reaches the same speed as the rotary drive shaft 11. If a load is applied ( ie if the first and second external pad surfaces 16b, 22a are applied to the surface of the work piece), the radial collar 16 and the circular plate 22 decelerate. The pad rotations tend towards stopping and just a very low rotational speed may remain for coarse sanding. However the speed of orbital rotation (leading to elimination of vibration) and thus fine sanding is strongly related to the motor speed and not to the load applied so that orbital rotations will remain.
  • FIG. 13 a second embodiment of the anti-vibration arrangement of the invention is illustrated. It works on the general principles of the first embodiment described hereinbefore.
  • the pads A1-A4 have a planar square shaped external pad surface B1-B4 with identical surface areas for attachment of equal-size sanding or polishing papers.
  • small sanding particles a, b, c, d are present at the outer corners.
  • these sanding particles a-d adopt consecutive positions (1), (2), (3), (4) 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 centres including central axes of external pad surfaces B1-B4 are denoted S 1-S4.
  • the external pad surfaces B 1-B4 and circular areas C1-C4 in their centres S1-S4 are shown in solid lines in position (1) and in broken lines in position (3).
  • the second embodiment is driven by a drive shaft assembly and a gear assembly.
  • the drive shaft assembly may be similar to that of Figure 6 ie including two cams for neighboring pads A1, A3 and A2, A4, wherein each of the two drive shaft assemblies is connected to the rotary drive shaft 11.
  • the rotation of the rotary axis 12 is transferred to the four axes S1, S2, S3, S4 so that the external pad surfaces B1-B4 rotate in the directions T1-T4.
  • the circles C1-C4 shown in solid line indicate the location of the associated cylindrical cam in the first position (1) whereas the circles shown in broken lines indicate the location of the associated cylindrical cam in the third position (3).
  • a significant reduction of vibrations is obtained.
  • the entire configururation will rotate arround the rotary axis 12, thereby performing pad rotations for coarse sanding.
  • FIG 15 is a partial side view of a finishing sander 1 incorporating the first embodiment of the anti-vibration arrangement of the invention.
  • the finishing sander 1 is essentially identical to the embodiment shown in Figure 1 but additionally comprises a first connection piece 46 and a second connection piece 47.
  • the first and second connection pieces 46, 47 are elongated and made of an elastic material such as rubber.
  • the first connection piece 46 is fixed between the radial collar 16 and the housing 2 and the second connection piece 47 is fixed between the circular plate 22 and the annular lip 17b ( ie indirectly between the second pad 23 and the housing 2).
  • the first and second connection pieces 46, 47 ensure that the first and second pads 17 and 23 cannot rotate about their respective central axes 15 and 21. Since such rotations are prevented, the sanding papers 8 and 9 are restrained to orbit in small circles t as illustrated in Figures 8 to 12. In other words, the flexible connection pieces 46, 47 prevent the pad rotations whilst allowing orbital rotations.
  • FIG 16 there are illustrated two brakes 50, 51 used in a second rotary sander 1 otherwise identical to that of Figure 1.
  • the brakes 50, 51 slow down the rotation of the first and second pads 17 and 23 when there is no load applied to the rotary sander 1.
  • the rotation speed is kept low because the brakes 50, 51 simulate a load.
  • the brakes 50, 51 are illustrated schematically as rubber rings of different diameter.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
EP20050252417 2004-04-16 2005-04-18 Antiruckelvorrichtung Ceased EP1586416B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US11/151,050 US7104873B1 (en) 2005-04-18 2005-06-13 Anti-vibration arrangement

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITVI20040090 ITVI20040090A1 (it) 2004-04-16 2004-04-16 Dispositivo antivibrante per macchina levigatrice motorizzata, e macchina levigatrice incorporante tale dispositivo
ITVI20040090 2004-04-16

Publications (3)

Publication Number Publication Date
EP1586416A2 true EP1586416A2 (de) 2005-10-19
EP1586416A3 EP1586416A3 (de) 2006-04-12
EP1586416B1 EP1586416B1 (de) 2014-06-11

Family

ID=34940895

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20050252417 Ceased EP1586416B1 (de) 2004-04-16 2005-04-18 Antiruckelvorrichtung

Country Status (3)

Country Link
EP (1) EP1586416B1 (de)
CN (1) CN100503164C (de)
IT (1) ITVI20040090A1 (de)

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US10434628B2 (en) 2017-06-26 2019-10-08 X'pole Precision Tools Inc. Grinding machine
EP3421173B8 (de) 2017-06-27 2022-08-17 X'Pole Precision Tools Inc. Schleifmaschine
JP7117832B2 (ja) * 2017-07-24 2022-08-15 京セラインダストリアルツールズ株式会社 ポリッシャ
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CN109176258B (zh) * 2018-09-12 2020-08-18 宁波耀升工具实业有限公司 一种电磨
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WO2019043293A1 (en) 2017-09-01 2019-03-07 Mirka Ltd SPINDLE BEARING COOLING SYSTEM IN ABRASION APPARATUS
EP3676051A4 (de) * 2017-09-01 2021-12-29 Mirka Ltd. Spindellagerkühlanordnung in einem schleifgerät
US11638977B2 (en) * 2017-09-01 2023-05-02 Mirka Ltd. Spindle bearing cooling arrangement in an abrading apparatus
CN113305701A (zh) * 2020-02-26 2021-08-27 南京德朔实业有限公司 砂光机
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IT202100006359A1 (it) * 2021-03-17 2022-09-17 Riccardo Castiglion Testa di lucidatura e/o carteggiatura per il trattamento di superfici
WO2022195493A1 (en) * 2021-03-17 2022-09-22 Castiglion Riccardo Polishing and/or sanding head for surface treatment
CN114851024A (zh) * 2022-05-31 2022-08-05 江苏星浪光学仪器有限公司 一种基于移动互联智能的滤波片生产用抛光机

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CN1748939A (zh) 2006-03-22
EP1586416B1 (de) 2014-06-11
CN100503164C (zh) 2009-06-24
EP1586416A3 (de) 2006-04-12
ITVI20040090A1 (it) 2004-07-16

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