EP2127808A1 - Outil électrique - Google Patents

Outil électrique Download PDF

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Publication number
EP2127808A1
EP2127808A1 EP08157146A EP08157146A EP2127808A1 EP 2127808 A1 EP2127808 A1 EP 2127808A1 EP 08157146 A EP08157146 A EP 08157146A EP 08157146 A EP08157146 A EP 08157146A EP 2127808 A1 EP2127808 A1 EP 2127808A1
Authority
EP
European Patent Office
Prior art keywords
drive shaft
power tool
tool according
movement
tool part
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.)
Withdrawn
Application number
EP08157146A
Other languages
German (de)
English (en)
Inventor
Andrew Walker
Timothy Mckay
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.)
Black and Decker Inc
Original Assignee
Black and Decker Inc
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 Black and Decker Inc filed Critical Black and Decker Inc
Priority to EP08157146A priority Critical patent/EP2127808A1/fr
Publication of EP2127808A1 publication Critical patent/EP2127808A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • B24B41/042—Balancing mechanisms

Definitions

  • the present invention relates to power tools and has particular, although not exclusive, relevance to powered sanders.
  • a powered sander may be used to remove paint from wood before re-painting.
  • it may be used in a more aggressive environment to remove rust from metalwork, again, before re-painting.
  • a power tool having the ability to have a varying eccentricity of a tool part of thereof which can be achieved without stopping use of the tool and without the need for two-handed operation is particularly attractive. Furthermore such a tool which achieves static and dynamic balancing automatically on varying the eccentricity of the tool part would have significant advantage over the known proposals. Undesirable vibration effects, for example, can be kept to a minimum, or even avoided altogether.
  • a power tool comprising:
  • control means which simultaneously effects radial opposing movements of the tool part and the counter-weight, not only is the ability to vary the eccentricity of the tool part achieved, but also both the dynamic and static balancing of both the tool part and the counterweight about the central drive shaft is maintained.
  • radial movement of the counterbalance mass is of the same extent as any radial movement of the tool part.
  • the amount of radial movement of the counterbalance mass is also possible for the amount of radial movement of the counterbalance mass to be different from that of the tool part.
  • the power tool includes a slidable member mounted around or within the drive shaft, which slidable member is axially movable with respect to the drive shaft, under influence of the control means, to effect radial movement of both the tool part and the counterbalance mass.
  • a slidable member mounted around or within the drive shaft, which slidable member is axially movable with respect to the drive shaft, under influence of the control means, to effect radial movement of both the tool part and the counterbalance mass.
  • the slidable member may include a first portion having an outer surface angled with respect to the axis of the drive shaft and a second member having an outer surface angled with respect to the axis of the drive shaft.
  • the outer surface of the first portion of the slidable member may be angled to cause movement of the tool part in a first radial direction and the outer surface of the second portion of the slidable member may be angled to cause movement of the counterbalance mass in a second radial direction, wherein the first and second radial directions are diametrically opposite each other with respect to the drive shaft.
  • a single control element-the sliding member- is able to achieve movement both of the tool part and the counterbalance mass, yet in opposite directions.
  • the slidable member may govern the amount of movement of each of the tool part and the counterbalance mass so that, preferably, they each move by the same amount.
  • the first portion of the slidable member comprises a wedge member.
  • the second portion of the slidable member comprises a pin.
  • the pin may be formed within the wedge member.
  • a powered sander shown generally as 2, has a housing 4 surrounding a motor 6.
  • the motor 6 is activated by the user of the sander 2 operating a switch 8 coupled to a manually-actuable trigger 10.
  • the switch is connected to an electrical supply via power cable 12, in known manner.
  • the motor 6 has an output spindle 14 formed with a toothed end for cooperation with a toothed belt 16 which is arranged to rotate a drive shaft 18 of the sander 2 about a rotational axis A-A ( figure 4 ). Hence activation of the motor 6 causes rotation of its output spindle 14 which, in turn, drives the toothed belt 16 in order to rotate the drive shaft 18 about axis A-A.
  • the drive shaft 18 is supported by an upper bearing 20 and a lower bearing 22.
  • the lower bearing 22 surrounds componentry arranged to both vary the eccentricity of a tool part, here a sanding platen 24 coupled to the drive shaft 18 and also the eccentricity of counterbalance mass 26. This will be explained in detail below.
  • the drive shaft 18 is formed as a sleeve and surrounds an internal axially movable slidable member, in this example slide 28.
  • the slide 28 rotates with rotation of the drive shaft 18, and can be axially moved under influence of a control means, to be described further below.
  • the lower end of the slide 28 terminates in two portions: a first portion, in this example a wedge 30 which is axially separated from a second portion, in this example pin 32.
  • a first portion in this example a wedge 30 which is axially separated from a second portion, in this example pin 32.
  • the wedge 30 is angled with respect to the drive axis A-A at a first inclination and the pin 32 is also angled relative to the drive axis A-A at the same angle, but in the opposite direction to that of the wedge 30.
  • the pin 32 is rigidly mounted into the base of wedge 30. No relative movement therebetween is possible.
  • the platen 24 is mounted to a terminal block 34 which is slidably coupled to and driven by the counterbalance mass 26.
  • Shoulder 261 formed on the counterbalance mass 26 fits within a corresponding recess 221 formed in the lower bearing 22, thereby to permit a sliding movement between the mass 26 and bearing 22.
  • the terminal block 34 rotates about a separate axis, B-B, which, as can be seen best from figure 4 , defines an eccentric offset, e, from that of the axis A-A.
  • the lower end of the terminal block 34 has a shoulder 36 formed thereon.
  • the shoulder 36 defines an annular recess for accommodating a bearing 38.
  • the terminal block 34 has an angled recess 35 corresponding to the projection of the pin 32 from the wedge 30.
  • the pin 32 is able to move within the angled recess 35 of the terminal block 34 along axis F-F (see figure 4 ), as will be described below.
  • the bearing 38 is surrounded by a support ring 40 which has a series of internal threads for accepting screws 42.
  • the screws 42 are used for mounting the platen 24 to the bearing 40 and, hence, the terminal block 34. In this manner, therefore, the platen 24 is able to freely rotate about the terminal block 34 and, hence, the eccentric axis B-B.
  • Bearing 38 is retained on the terminal block 34 by a washer 44 and lock screw 46.
  • axial movement of the slide 28 is manually achievable by a control means, in the embodiment of figures 1 and 2 this is a rotatable knob 48, whereas in the embodiment of figures 3 and 4 this is a pivotal actuation rod 50.
  • the knob 48 and the rod 50 operating different ways, they achieve the same effect. That is, to control axial movement of the slide 28 whilst allowing its rotation about axis A-A.
  • the wedge 30 is employed. It can be seen by reference to figure 4 that the outer surface of the wedge 30 is angled in the opposite direction to that of the pin 32 relative to the central drive axis A-A. In fact the outer surfaces of the wedge 30 lie in a direction having the same angle to the axis A-A as does the axis F-F of the pin 32 relative to the central drive axis A-A. In other words, the angular offset of the pin 32 relative to the central drive axis A-A is the same as that of the outer surfaces of the wedge 30.
  • the angular offset of the pin 32 relative to the central drive axis A-A may differ to the angular offset of the outer surfaces of wedge 30. This may achieve differential and opposite movement of the counterbalance mass 26 relative to movement of the platen 24, yet still maintain both static and dynamic balancing of the system in so far as the masses of each of the counterbalance mass 26 and platen 24 and their respective amount of movement are concerned.
  • the counterbalance mass 26, having mass M 1 moves a distance D 1 and platen 24, having mass M 2 moves a distance D 2 , where M 1 >M 2 and D 1 ⁇ D 2 .
  • the embodiment shown in figures 1 and 2 does not utilise a pivotal rod 50 but a rotatable knob 48.
  • Rotation of the knob 48 causes a control block 56 to translate this rotational movement into a linear motion via thread-form 49 in order to move the slide 28 axially up or down, again to achieve movement of the wedge/pin combination as discussed above. Further discussion, therefore, of the differences between the rod 50 and knob 48 is not necessary.
  • the sleeve 18 carries two further counterbalance masses; second counterbalance mass 60 and third counterbalance mass 62. Further discussion of the second and third counterbalance masses will not be given here, as there purpose and effect is well-known to those skilled in the art. Suffice it to say that they are necessary in order to prevent moments manifesting themselves along the drive axis A-A which would otherwise cause imbalance during rotation of the platen 24 and combined with the platen 24 and counterbalance mass 26 constitute a multiple-plane balancing system.
  • the counterbalance mass 26 is formed as a skirt substantially around bearing 38 and axially adjacent platen 24 in order to reduce moments about axis A-A between the two.
  • the drive shaft 18 be formed as a sleeve around the slide 28, the converse could be possible. That is, the slide 28 to be formed as a sleeve around the drive shaft 18. Furthermore, although in the interests of efficient use of space it is highly desirable that the drive shaft 18 and slider 28 be formed concentrically.
  • the sander is initially balanced (both statically and dynamically) at the mid-point of the range of eccentric off-sets achievable by movement of the platen 24 (in other words centred on axis B-B).
  • the offset of the platen during this initial balancing equal to zero (or, in other words, centred on drive axis A-A).
  • the effect of the counterbalance masses 60 and 62 would render such a set-up imbalanced, as, at this initial balancing position, the platen 24 and counterbalance mass 26 are in balance and therefore contribute no effect to balancing. If the platen 24 were to be positioned concentrically with the drive axis A-A during this initial balancing, then the effect of masses 60 and 62 would cause the sander to be imbalanced.
  • the counterbalance mass 26 is itself concentric with the drive axis A-A and, hence, plays no part in balance of the sander.
EP08157146A 2008-05-29 2008-05-29 Outil électrique Withdrawn EP2127808A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP08157146A EP2127808A1 (fr) 2008-05-29 2008-05-29 Outil électrique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP08157146A EP2127808A1 (fr) 2008-05-29 2008-05-29 Outil électrique

Publications (1)

Publication Number Publication Date
EP2127808A1 true EP2127808A1 (fr) 2009-12-02

Family

ID=39882476

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08157146A Withdrawn EP2127808A1 (fr) 2008-05-29 2008-05-29 Outil électrique

Country Status (1)

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EP (1) EP2127808A1 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3115150A4 (fr) * 2014-03-07 2017-10-18 Nitto Kohki Co., Ltd. Machine de polissage
EP3326752A1 (fr) * 2015-11-02 2018-05-30 Lake Country Manufacturing, Inc. Mécanisme de course réglable pour machine orbitale aléatoire
EP3335831A1 (fr) * 2016-10-25 2018-06-20 Karl Heesemann Maschinenfabrik GmbH & Co. KG Affuteuse
CN110039442A (zh) * 2018-01-15 2019-07-23 苏州宝时得电动工具有限公司 打磨工具
US10518384B2 (en) 2015-11-02 2019-12-31 Lake Country Tool, Llc Adjustable stroke mechanism for random orbital machine
WO2022105741A1 (fr) * 2020-11-19 2022-05-27 南京泉峰科技有限公司 Ponceuse
US11493115B2 (en) 2017-10-30 2022-11-08 Lake Country Tool, Llc Adjustable stroke device with cam
US11592055B2 (en) 2018-08-30 2023-02-28 Lake Country Tool, Llc Adjustable stroke device with cam
US11867224B2 (en) 2021-01-27 2024-01-09 Black & Decker Inc. Locking mechanism for two telescoping poles of a power tool
US11878391B2 (en) 2022-03-04 2024-01-23 Lake Country Tool, Llc Adjustable stroke device
US11931851B2 (en) 2019-10-23 2024-03-19 Black & Decker Inc. Pole sander

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0303955A1 (fr) * 1987-08-18 1989-02-22 Miksa Marton Meuleuse portative
US5947804A (en) 1998-04-27 1999-09-07 Ryobi North America, Inc. Adjustable eccentricity orbital tool

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0303955A1 (fr) * 1987-08-18 1989-02-22 Miksa Marton Meuleuse portative
US5947804A (en) 1998-04-27 1999-09-07 Ryobi North America, Inc. Adjustable eccentricity orbital tool

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3115150A4 (fr) * 2014-03-07 2017-10-18 Nitto Kohki Co., Ltd. Machine de polissage
EP3326752A1 (fr) * 2015-11-02 2018-05-30 Lake Country Manufacturing, Inc. Mécanisme de course réglable pour machine orbitale aléatoire
US10144106B2 (en) 2015-11-02 2018-12-04 Lake Country Manufacturing, Inc. Adjustable stroke mechanism for random orbital machine
US10518384B2 (en) 2015-11-02 2019-12-31 Lake Country Tool, Llc Adjustable stroke mechanism for random orbital machine
US10981258B2 (en) 2015-11-02 2021-04-20 Lake Country Tool, Llc Adjustable stroke mechanism for random orbital machine
EP3335831A1 (fr) * 2016-10-25 2018-06-20 Karl Heesemann Maschinenfabrik GmbH & Co. KG Affuteuse
US11674571B2 (en) 2017-10-30 2023-06-13 Lake Country Tool, Llc Adjustable stroke device with cam
US11927250B2 (en) 2017-10-30 2024-03-12 Lake Country Tool, Llc Adjustable stroke device with cam
US11493115B2 (en) 2017-10-30 2022-11-08 Lake Country Tool, Llc Adjustable stroke device with cam
CN110039442A (zh) * 2018-01-15 2019-07-23 苏州宝时得电动工具有限公司 打磨工具
CN110039442B (zh) * 2018-01-15 2024-05-07 苏州宝时得电动工具有限公司 打磨工具
US11592055B2 (en) 2018-08-30 2023-02-28 Lake Country Tool, Llc Adjustable stroke device with cam
US11931851B2 (en) 2019-10-23 2024-03-19 Black & Decker Inc. Pole sander
WO2022105741A1 (fr) * 2020-11-19 2022-05-27 南京泉峰科技有限公司 Ponceuse
US11867224B2 (en) 2021-01-27 2024-01-09 Black & Decker Inc. Locking mechanism for two telescoping poles of a power tool
US11878391B2 (en) 2022-03-04 2024-01-23 Lake Country Tool, Llc Adjustable stroke device

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