WO2004085114A1 - Rotary work tool with orbiting planetary gears containing eccentric axes for the attachment of polishing or sanding platens - Google Patents

Rotary work tool with orbiting planetary gears containing eccentric axes for the attachment of polishing or sanding platens Download PDF

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Publication number
WO2004085114A1
WO2004085114A1 PCT/GB2003/001376 GB0301376W WO2004085114A1 WO 2004085114 A1 WO2004085114 A1 WO 2004085114A1 GB 0301376 W GB0301376 W GB 0301376W WO 2004085114 A1 WO2004085114 A1 WO 2004085114A1
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WO
WIPO (PCT)
Prior art keywords
axis
planetary gear
work tool
planetary gears
gear
Prior art date
Application number
PCT/GB2003/001376
Other languages
French (fr)
Other versions
WO2004085114A8 (en
Inventor
Philip John Rawlins
Matthew John Carr
Original Assignee
The Technology Partnership Plc
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 The Technology Partnership Plc filed Critical The Technology Partnership Plc
Priority to US10/550,918 priority Critical patent/US20060194528A1/en
Priority to PCT/GB2003/001376 priority patent/WO2004085114A1/en
Priority to EP03715114A priority patent/EP1620229A1/en
Priority to AU2003219306A priority patent/AU2003219306A1/en
Publication of WO2004085114A1 publication Critical patent/WO2004085114A1/en
Publication of WO2004085114A8 publication Critical patent/WO2004085114A8/en

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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
    • B24B7/00—Machines or devices designed for grinding plane surfaces on work, including polishing plane glass surfaces; Accessories therefor
    • B24B7/10—Single-purpose machines or devices
    • B24B7/18—Single-purpose machines or devices for grinding floorings, walls, ceilings or the like
    • B24B7/186—Single-purpose machines or devices for grinding floorings, walls, ceilings or the like with disc-type tools
    • 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
    • B24B41/04—Headstocks; Working-spindles; Features relating thereto
    • B24B41/047—Grinding heads for working on plane surfaces
    • 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
    • B24B47/00—Drives or gearings; Equipment therefor
    • B24B47/10—Drives or gearings; Equipment therefor for rotating or reciprocating working-spindles carrying grinding wheels or workpieces
    • B24B47/12—Drives or gearings; Equipment therefor for rotating or reciprocating working-spindles carrying grinding wheels or workpieces by mechanical gearing or electric power

Definitions

  • This invention relates to worktools and, in particular, rotating worktools, such as sanders and polishing machines, that engage with a surface.
  • Known orbital and random-orbital worktools such as sanders, functioned by driving an abrasive surface in a circular path about a principal drive shaft.
  • a surface may be of fixed orientation or may be free to rotate about an eccentric axis, according to whether the resulting motion is required to be orbital or random-orbital respectively.
  • Such worktools typically suffer from vibration. Vibration in such systems has two distinct components, dynamic (which results from unbalanced centripetal acceleration) and frictional (which results from the translating frictional forces between the working surface of the tool and the work piece).
  • Dynamic imbalance can normally be corrected by distributing counter weights at particular axial, radial and phase positions on the drive axis of the work tool.
  • this approach relies on the working surface of the tool, such as the sanding platen and any attached replacement component, being of constant mass. This means that changing the platen or replacing the working material can often cause unwanted vibration.
  • Vibration experienced in use also often arises from translating frictional forces between the abrasive surface acting so as to make the eccentric drive axis the centre of rotation. In the worst case, these vibrations can be of an amplitude equal to the shaft eccentricity, in the case that the principal drive shaft orbits the stationary eccentric shaft. Frictional vibration increases with increasing contact force, resulting in a reduction of sanding efficiency that tends to zero as the amplitude of vibration tends to the eccentricity of the drive axis. A common misconception is that, by increasing the contact force, an increase in the material removal rate can be achieved. As such, counter-intuitive system behaviour in prior art solutions often results in poor sanding efficiency and high levels of vibration.
  • the present invention aims to reduce markedly vibration arising from translating frictional forces, by ensuring that such forces are reacted within a system of sanding surfaces, thereby increasing the sanding efficiency and the rate of material removal that can be achieved.
  • a work tool comprising: a principal drive shaft with a sun gear attached thereto; at least two planetary gears distributed about the circumference of the sun gear at substantially equal angular separation; and a carriage for constraining the planetary gears such that they maintain their angular separation about the axis of the principal drive shaft, wherein each planetary gear has an eccentric axis in addition to its rotational axis constrained by the carriage, such that each planetary gear can drive, in use, a platen around the respective eccentric axis.
  • phase difference between the rotation of the eccentric axis of any two adjacent planetary gears about the respective rotation of axis is 2 ⁇ r/n radians, wherein n equals the number of planetary gears, n is preferably greater than or equal to 3. This relationship ensures that the centre of mass of the combined system does not depart from the principal axis of rotation.
  • the rotation of the eccentric axis of a first planetary gear about its associated rotational axis has a phase difference in a clockwise direction of 2 ⁇ . M relative to the rotation of the eccentric axis of a second planetary gear about its associated rotational axis, the second planetary gear being adjacent the first planetary gear in a clockwise direction.
  • a worktool comprising: a principal drive shaft with a sun gear attached thereto; n planetary gears distributed about the circumference of the sun gear at substantially equal angular separation; and a carriage for constraining the planetary gears such that they maintain their angular separation about the axis of the principal drive shaft; wherein each planetary gear has an eccentric axis in addition to its rotational axis constrained by the carriage, such that each planetary gear can drive, in use, a platen around the respective eccentric axis, and wherein the rotation of the eccentric axis of a first planetary gear about its associated rotational axis has a phase difference in a clockwise direction of 2 ⁇ r/n relative to the rotation of the eccentric axis of a second planetary gear about its associated rotational axis, the second planetary gear being adjacent to the first planetary gear in a clockwise direction.
  • the arrangement of sanding elements is dynamically balanced, removing the need for the system of counter weights, in conventional sanders.
  • the sanding platens and abrasive surfaces can also be replaced without unduly compromising the dynamic balance.
  • the present invention can be configured to be operable in a number of modes, optimising the motion for a given sanding operation or spatial constraint.
  • the platens may be freely rotating or partially constrained from rotating with respect to the carriage, thereby fixing the orientation of the platens with respect to one another. Partially constraining the platens in this way permits the use of tessellating platen configurations.
  • the worktool may be a sander or a polisher.
  • the principal drive shaft may be connected, optionally through an additional gear mechanism, to an electric motor. Examples of the present invention will now be described with reference to the accompanying drawings, in which:
  • Figures 1 and 2 are isometric and plan views of a worktool according to the present invention
  • Figure 3 is a plan view of a device according to the present invention, with an additional gear shown;
  • Figure 4 is a plan view showing alternative configurations of the platen only.
  • Figure 5 shows the phase relationship between the rotation of the eccentric axis in a preferred example of the present invention.
  • the worktool includes a principal drive shaft 1 and a carriage 4 to which a sun gear 2 is attached.
  • the worktool is typically a sander or polisher.
  • a number of planetary gears 3 are distributed about the circumference of the sun gear 2 at equal angular separations.
  • the planetary gears 3 are constrained by the carriage 4, locating the centres and maintaining the angular separation about the principal axis of the drive shaft 1.
  • Each planetary gear 3 has an eccentric axis 5, in addition to the centre of rotation constrained by the carriage 4, driving a freely rotated or partially rotationally constrained platen 6.
  • each of the platens 8 or 9 can be attached to a respective eccentric axis 5, instead of the circular platen 6 shown in Figure 1.
  • a rectangular platen 10 can be attached to each of the respective eccentric axis 5.
  • the platens 6 Will orbit a fixed centre, with no bulk rotation of the combined system. This constitutes a mode of operation suitable for sanding an inside corner that would be inaccessible by an equivalent single sanding platen of an area equal to the sum of the platen areas.
  • Figure 3 shows an optional additional gear 7 including inwardly facing teeth (not shown) which engage with each of the planetary gears.
  • the gear 7 is concentric with the principal drive axis 1.
  • this additional gear 7 is free to rotate, the above modes are accessible.
  • the platen centres will be driven in a strictly epicyclic motion. This results in higher surface to surface speeds and a corresponding increase in the rate of material removal.
  • Figure 5 shows a simplified plan view of a preferred embodiment showing the particular phase relationship between the rotation of the eccentric axis on each of the planetary gears.
  • variable component of the resulting moments from each of the platens will cancel each other out, ensuring that there is no torsional vibration transmitted to the user. This is true for any number of gears greater than or equal to three.

Abstract

A work tool comprising: a principle drive shaft (1) with a sun gear (2) attached thereto; at least two planetary gears (3) distributed about the circumference of the sun gear (2) at substantially equal angular separations; and a carriage (4) for constraining the planetary gears (3) such that they maintain their angular separation about the axis of the principal drive shaft (1); wherein each planetary gear (3) has an eccentric (5) axis in addition to its rotational axis constrained by the carriage (4), such that each planetary gear (3) can drive, in use, a polishing on sanding platen (6) around the respective excentric axis (5). A phase difference may be provided between the respective adjacent excentric axes (5). The polishing or sanding platens (6) may rotate freely or may be rotationally constrained.

Description

This invention relates to worktools and, in particular, rotating worktools, such as sanders and polishing machines, that engage with a surface. Known orbital and random-orbital worktools, such as sanders, functioned by driving an abrasive surface in a circular path about a principal drive shaft. A surface may be of fixed orientation or may be free to rotate about an eccentric axis, according to whether the resulting motion is required to be orbital or random-orbital respectively. Such worktools typically suffer from vibration. Vibration in such systems has two distinct components, dynamic (which results from unbalanced centripetal acceleration) and frictional (which results from the translating frictional forces between the working surface of the tool and the work piece).
Dynamic imbalance can normally be corrected by distributing counter weights at particular axial, radial and phase positions on the drive axis of the work tool. However, this approach relies on the working surface of the tool, such as the sanding platen and any attached replacement component, being of constant mass. This means that changing the platen or replacing the working material can often cause unwanted vibration.
Vibration experienced in use also often arises from translating frictional forces between the abrasive surface acting so as to make the eccentric drive axis the centre of rotation. In the worst case, these vibrations can be of an amplitude equal to the shaft eccentricity, in the case that the principal drive shaft orbits the stationary eccentric shaft. Frictional vibration increases with increasing contact force, resulting in a reduction of sanding efficiency that tends to zero as the amplitude of vibration tends to the eccentricity of the drive axis. A common misconception is that, by increasing the contact force, an increase in the material removal rate can be achieved. As such, counter-intuitive system behaviour in prior art solutions often results in poor sanding efficiency and high levels of vibration.
The present invention aims to reduce markedly vibration arising from translating frictional forces, by ensuring that such forces are reacted within a system of sanding surfaces, thereby increasing the sanding efficiency and the rate of material removal that can be achieved.
According to the present invention, there is provided a work tool comprising: a principal drive shaft with a sun gear attached thereto; at least two planetary gears distributed about the circumference of the sun gear at substantially equal angular separation; and a carriage for constraining the planetary gears such that they maintain their angular separation about the axis of the principal drive shaft, wherein each planetary gear has an eccentric axis in addition to its rotational axis constrained by the carriage, such that each planetary gear can drive, in use, a platen around the respective eccentric axis.
The phase difference between the rotation of the eccentric axis of any two adjacent planetary gears about the respective rotation of axis is 2τr/n radians, wherein n equals the number of planetary gears, n is preferably greater than or equal to 3. This relationship ensures that the centre of mass of the combined system does not depart from the principal axis of rotation.
In addition to the net linear frictional forces, the frictional force from each of the platens will produce a moment about the centre of the tool (centre of the sun gear). Furthermore, as the planetary gear rotates, the direction and position of the force changes, so the magnitude of the resulting moment will change. If these forces were unopposed, then the resulting varying moment would be transmitted to the user, as a torsional vibration. In order to preserve the dynamic balance of the system and to ensure that this component is cancelled in addition to the dynamic and linear friction forces, it is advantageous to define not only the magnitude of the eccentricity phase relationship between adjacent platens but also the relative direction of that phase relationship.
It is preferable that the rotation of the eccentric axis of a first planetary gear about its associated rotational axis has a phase difference in a clockwise direction of 2ττ. M relative to the rotation of the eccentric axis of a second planetary gear about its associated rotational axis, the second planetary gear being adjacent the first planetary gear in a clockwise direction.
According to a second aspect of the present invention, there is provided a worktool comprising: a principal drive shaft with a sun gear attached thereto; n planetary gears distributed about the circumference of the sun gear at substantially equal angular separation; and a carriage for constraining the planetary gears such that they maintain their angular separation about the axis of the principal drive shaft; wherein each planetary gear has an eccentric axis in addition to its rotational axis constrained by the carriage, such that each planetary gear can drive, in use, a platen around the respective eccentric axis, and wherein the rotation of the eccentric axis of a first planetary gear about its associated rotational axis has a phase difference in a clockwise direction of 2τr/n relative to the rotation of the eccentric axis of a second planetary gear about its associated rotational axis, the second planetary gear being adjacent to the first planetary gear in a clockwise direction.
With the present invention, since the translating frictional forces are mutually reacted, vibration transmitted to the user is, in principle, decoupled from the applied contact force. Similarly, sanding efficiency is not unduly compromised by increasing contact force, permitting higher rates of material removal. Such a feature of the present invention complements user initiation, unlike the prior art systems described above.
Furthermore, the arrangement of sanding elements is dynamically balanced, removing the need for the system of counter weights, in conventional sanders. The sanding platens and abrasive surfaces can also be replaced without unduly compromising the dynamic balance. The present invention can be configured to be operable in a number of modes, optimising the motion for a given sanding operation or spatial constraint.
The platens may be freely rotating or partially constrained from rotating with respect to the carriage, thereby fixing the orientation of the platens with respect to one another. Partially constraining the platens in this way permits the use of tessellating platen configurations.
The worktool may be a sander or a polisher. The principal drive shaft may be connected, optionally through an additional gear mechanism, to an electric motor. Examples of the present invention will now be described with reference to the accompanying drawings, in which:
Figures 1 and 2 are isometric and plan views of a worktool according to the present invention;
Figure 3 is a plan view of a device according to the present invention, with an additional gear shown;
Figure 4 is a plan view showing alternative configurations of the platen only; and
Figure 5 shows the phase relationship between the rotation of the eccentric axis in a preferred example of the present invention.
Referring to Figures 1 and 2, the worktool includes a principal drive shaft 1 and a carriage 4 to which a sun gear 2 is attached. The worktool is typically a sander or polisher. A number of planetary gears 3 are distributed about the circumference of the sun gear 2 at equal angular separations. The planetary gears 3 are constrained by the carriage 4, locating the centres and maintaining the angular separation about the principal axis of the drive shaft 1. Each planetary gear 3 has an eccentric axis 5, in addition to the centre of rotation constrained by the carriage 4, driving a freely rotated or partially rotationally constrained platen 6.
If the platens are partially constrained from rotating, then alternative tessellating platen configurations are possible. Some examples of such configurations are shown in Figure 4 in which each of the platens 8 or 9 can be attached to a respective eccentric axis 5, instead of the circular platen 6 shown in Figure 1. Alternatively, in an embodiment that employs four planetary gears 3, a rectangular platen 10 can be attached to each of the respective eccentric axis 5. When free to rotate, the carriage 4 will be driven by a net torque between the sanding surfaces and the workpiece (not shown) causing the sanding centres to describe a distorted epicycloid where the number of rotations of the respective planetary gear is not purely a function of the sun/planetary gear ratio. This is a random motion most suited to finishing applications.
If the carriage 4 is prevented from rotating, preferably with a user engaged lock, the platens 6 Will orbit a fixed centre, with no bulk rotation of the combined system. This constitutes a mode of operation suitable for sanding an inside corner that would be inaccessible by an equivalent single sanding platen of an area equal to the sum of the platen areas.
Figure 3 shows an optional additional gear 7 including inwardly facing teeth (not shown) which engage with each of the planetary gears. The gear 7 is concentric with the principal drive axis 1. When this additional gear 7 is free to rotate, the above modes are accessible. However, when prevented from rotating, again preferably with a user engaged lock, the platen centres will be driven in a strictly epicyclic motion. This results in higher surface to surface speeds and a corresponding increase in the rate of material removal.
Figure 5 shows a simplified plan view of a preferred embodiment showing the particular phase relationship between the rotation of the eccentric axis on each of the planetary gears.
The orientation of the eccentricity on each gear with respect to the centre of the gear is indicated by arrows 10A, 10B and 10C. If planetary gear 3A is arbitually selected as the reference gear then it can be seen that its eccentric axis 5A is currently orientated such that the arrow 10A is nominally horizontal. Proceeding in a clockwise direction around the sun gear 2 to gear 3D can be seen that the eccentric axis 5B is arranged such that it is rotated by 2π/3 radians in a counter clockwise direction with respect to the eccentricity on gear 3A. Exactly the same relationship is true between gear 3C and 3B and between gear 3A and 3C.
If this relationship is maintained then the variable component of the resulting moments from each of the platens will cancel each other out, ensuring that there is no torsional vibration transmitted to the user. This is true for any number of gears greater than or equal to three.

Claims

1. A worktool comprising: a principle drive shaft with a sun gear attached thereto; at least two planetary gears distributed about the circumference of the sun gear at substantially equal angular separations; and a carriage for constraining the planetary gears such that they maintain their angular separation about the axis of the principal drive shaft; wherein each planetary gear has an eccentric axis in addition to its rotational axis constrained by the carriage, such that each planetary gear can drive, in use, a platen around the respective eccentric axis.
2. A work tool according to claim 1, wherein the phase difference between the rotation of the eccentric axis of any two adjacent planetary gears about the respective rotational axis is 2π/n radians, wherein n equals the number of planetary gears.
3. A work tool according to claim 2, wherein the rotation of the eccentric axis of a first planetary gear about its rotational axis has a phase difference in a clockwise direction of 2ττ/n relative to the rotation of the eccentric axis of a second planetary gear about its associated rotational axis, the second planetary gear being adjacent the first planetary gear in a clockwise direction.
4. A work tool comprising: a principal drive shaft with a sun gear attached thereto; n planetary gears distributed about the circumference of the sun gear at substantially equal angular separation; and a carriage for constraining the planetary gears such that they maintain their angular separation about the axis of the principal drive shaft; wherein each planetary gear has an eccentric axis in addition to its rotational axis constrained by the carriage, such that each planetary gear can drive, in use, a platen around the respective eccentric axis, and wherein the rotation of the eccentric axis of a first planetary gear about its associated rotational axis has a phase difference in a clockwise direction of 2ττ/n relative to the rotation of the eccentric axis of a second planetary gear about its associated rotational axis, the second planetary gear being adjacent to the first planetary gear in a clockwise direction.
5. A work tool according to any one of the preceding claims, wherein the principal drive shaft is connected to a motor.
6. A work tool according to any one of the preceding claims, wherein the platens can rotate freely.
7. A work tool according to any one of claims 1 to 5, wherein the platens are partially rotationally constrained.
8. A work tool according to any one of the preceding claims, arranged to be a polisher.
9. A work tool according to any one of claims 1 to 7, arranged to be a sander.
PCT/GB2003/001376 2003-03-28 2003-03-28 Rotary work tool with orbiting planetary gears containing eccentric axes for the attachment of polishing or sanding platens WO2004085114A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US10/550,918 US20060194528A1 (en) 2003-03-28 2003-03-28 Rotary work tool with orbiting planetary gears containing eccentric axes for the attachment of polishing or sanding platens
PCT/GB2003/001376 WO2004085114A1 (en) 2003-03-28 2003-03-28 Rotary work tool with orbiting planetary gears containing eccentric axes for the attachment of polishing or sanding platens
EP03715114A EP1620229A1 (en) 2003-03-28 2003-03-28 Rotary work tool with orbiting planetary gears containing eccentric axes for the attachment of polishing or sanding platens
AU2003219306A AU2003219306A1 (en) 2003-03-28 2003-03-28 Rotary work tool with orbiting planetary gears containing eccentric axes for the attachment of polishing or sanding platens

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/GB2003/001376 WO2004085114A1 (en) 2003-03-28 2003-03-28 Rotary work tool with orbiting planetary gears containing eccentric axes for the attachment of polishing or sanding platens

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WO2004085114A1 true WO2004085114A1 (en) 2004-10-07
WO2004085114A8 WO2004085114A8 (en) 2005-12-01

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US (1) US20060194528A1 (en)
EP (1) EP1620229A1 (en)
AU (1) AU2003219306A1 (en)
WO (1) WO2004085114A1 (en)

Cited By (9)

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EP1586416A3 (en) * 2004-04-16 2006-04-12 Positec Power Tools (Suzhou) Co., Ltd. Anti-vibration arrangement
US7104873B1 (en) 2005-04-18 2006-09-12 Positec Power Tools (Suzhou) Co. Anti-vibration arrangement
WO2007000074A1 (en) * 2005-06-27 2007-01-04 Positec Power Tools (Suzhou) Co., Ltd. Anti-vibration device for an abrasive machine, a machine having such device and a method for cleaning the surface of a work piece
CN100436063C (en) * 2006-04-12 2008-11-26 厦门大学 Planetary framework diamond abrasive tools
CN100441376C (en) * 2006-05-10 2008-12-10 厦门大学 Pneumatic end-face planetary motion type diamond grinding apparatus
WO2012078087A1 (en) * 2010-12-10 2012-06-14 Jan Urban Thysell A device for grinding of plane surfaces by grinding means
ITRE20130022A1 (en) * 2013-03-26 2014-09-27 Lorenzo Segapeli APPARATUS FOR IMPROVING ROUGH WORKING; GRINDING; POLISH; BRUSHING LAPPING OF SURFACES OF STONE MATERIALS; CERAMIC PRODUCTS; GRES; GRESSMALTATO COMPOSITI VARIOUS
WO2016083637A1 (en) * 2014-11-26 2016-06-02 Estudios De Ingenieria Adaptada, S.L. Motor-driven double-shaft tool holder
CN107336105A (en) * 2017-07-19 2017-11-10 天津大学 A kind of compact-sized planetary polishing device

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DE102007004995A1 (en) * 2007-02-01 2008-08-07 Metabowerke Gmbh Motor-driven eccentric grinder, has grinding blades mountable on eccentrically drivable grinding plate in removable and exchangeable manner, where plate exhibits polygon shape on its plate plane that faces grinding blades in top view
US9239002B2 (en) 2010-08-03 2016-01-19 Heinz-Gustav Reisser Orbiting planetary gearing system and internal combustion engine employing the same
US10035237B2 (en) * 2011-11-02 2018-07-31 The Boeing Company Robotic end effector including multiple abrasion tools
JP6266625B2 (en) * 2012-09-25 2018-01-24 − グスタフ ライサー、ハインツ Orbital planetary gearing system and internal combustion engine employing the same
EP3902656A1 (en) * 2018-12-27 2021-11-03 Robert Bosch GmbH Hand-held power tool
CN110052957B (en) * 2019-04-24 2021-05-21 嘉兴市志华机械有限公司 Double-planetary-gear-train grinding head
CN111571354B (en) * 2020-04-24 2021-12-14 昆山利榕鑫精密机械有限公司 Valve body machining process of pressure regulating valve
CN117644471B (en) * 2024-01-29 2024-04-16 北京特思迪半导体设备有限公司 Method for precisely adjusting eccentricity of eccentric driving mechanism

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CH237159A (en) * 1943-08-19 1945-04-15 Buehler Ag Geb Floor cleaning device.
DE930948C (en) * 1948-09-25 1955-07-28 Mueller Bruetsch & Co Machine for cleaning floors
US2759305A (en) * 1954-06-11 1956-08-21 Cyclo Mfg Company Portable abrading and polishing machine
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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1586416A3 (en) * 2004-04-16 2006-04-12 Positec Power Tools (Suzhou) Co., Ltd. Anti-vibration arrangement
US7104873B1 (en) 2005-04-18 2006-09-12 Positec Power Tools (Suzhou) Co. Anti-vibration arrangement
WO2007000074A1 (en) * 2005-06-27 2007-01-04 Positec Power Tools (Suzhou) Co., Ltd. Anti-vibration device for an abrasive machine, a machine having such device and a method for cleaning the surface of a work piece
CN100436063C (en) * 2006-04-12 2008-11-26 厦门大学 Planetary framework diamond abrasive tools
CN100441376C (en) * 2006-05-10 2008-12-10 厦门大学 Pneumatic end-face planetary motion type diamond grinding apparatus
WO2012078087A1 (en) * 2010-12-10 2012-06-14 Jan Urban Thysell A device for grinding of plane surfaces by grinding means
ITRE20130022A1 (en) * 2013-03-26 2014-09-27 Lorenzo Segapeli APPARATUS FOR IMPROVING ROUGH WORKING; GRINDING; POLISH; BRUSHING LAPPING OF SURFACES OF STONE MATERIALS; CERAMIC PRODUCTS; GRES; GRESSMALTATO COMPOSITI VARIOUS
WO2016083637A1 (en) * 2014-11-26 2016-06-02 Estudios De Ingenieria Adaptada, S.L. Motor-driven double-shaft tool holder
CN107336105A (en) * 2017-07-19 2017-11-10 天津大学 A kind of compact-sized planetary polishing device

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US20060194528A1 (en) 2006-08-31
EP1620229A1 (en) 2006-02-01
AU2003219306A1 (en) 2004-10-18
WO2004085114A8 (en) 2005-12-01

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