EP2008773B1 - Geräuschunterdrückungsbremse für einen automatischen Spindelarretiermechanismus - Google Patents

Geräuschunterdrückungsbremse für einen automatischen Spindelarretiermechanismus Download PDF

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Publication number
EP2008773B1
EP2008773B1 EP07111436A EP07111436A EP2008773B1 EP 2008773 B1 EP2008773 B1 EP 2008773B1 EP 07111436 A EP07111436 A EP 07111436A EP 07111436 A EP07111436 A EP 07111436A EP 2008773 B1 EP2008773 B1 EP 2008773B1
Authority
EP
European Patent Office
Prior art keywords
braking member
output shaft
power tool
rotary power
tool according
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.)
Active
Application number
EP07111436A
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English (en)
French (fr)
Other versions
EP2008773A1 (de
Inventor
Olivier Zeiter
Daniel Brogli
Chi Hoe Leong
Yeo Joanne
Thomas Mathys
Eng Hock Tan
Andreas Schwieger
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to EP07111436A priority Critical patent/EP2008773B1/de
Priority to DE602007012222T priority patent/DE602007012222D1/de
Priority to US12/667,143 priority patent/US20100224382A1/en
Priority to CN2008800221651A priority patent/CN101730612B/zh
Priority to PCT/EP2008/056658 priority patent/WO2009003774A1/en
Publication of EP2008773A1 publication Critical patent/EP2008773A1/de
Application granted granted Critical
Publication of EP2008773B1 publication Critical patent/EP2008773B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools

Definitions

  • the present invention relates to rotary power tools and in particular those tools which are configured with an automatic spindle locking mechanism (ASLM).
  • ASLM automatic spindle locking mechanism
  • an ASLM blocks a rotary tool output shaft from rotating in response to an external applied torque, for example resulting from rotation of a tool-holding chuck coupled to the output shaft.
  • the motor shaft and output shaft of a power tool with an ASLM are typically coupled but with some rotational play remaining between the coupling parts.
  • An undesirable consequence of this ASLM configuration arises when the motor shaft slows after the motor has been shut off. Due to its inertia, the output shaft tends to overtake the slowing motor shaft. Relatively speaking, an output shaft that is rotating faster than the motor shaft is in effect attempting to drive the motor shaft, and this leads to engagement of the ASLM.
  • the locking action triggers a reactive force which slows the output shaft and disengages the ASLM.
  • the motor shaft continues to slow down more rapidly until its speed is once again less than the output shaft, and the process repeats. Repeated engagements, disengagements, and reengagements generate an undesirable chattering noise.
  • U.S. Patent No. 6,311,787 describes a rotary power tool as per the preamble of claim 1 and several means for counteracting this phenomenon, including an automatic brake and an automatic drag system. These are mediated by output shaft-coupled members which make frictional contact either with housing-coupled members or with motor shaft-coupled members, respectively. In both cases, this serves to slow the rotation of the output shaft relative to the motor shaft so that the frequency of chattering noise is reduced or eliminated altogether.
  • a disadvantage of the prior art solution is that the described structures comprise integral aspects of the design, and they cannot be readily incorporated into an existing rotary power tool without requiring an extensive redesign. What is needed is a simpler and less expensive means of achieving a similar outcome, and particularly a solution that can be implemented on an existing rotary power tool design, thereby requiring no redesign of the power train. It is also advantageous if the invention provides for an intuitive and predictable adjustment, so that the process of optimizing the solution for a particular rotary power tool is simplified.
  • a preferred and advantageous place for incorporating the braking member is in a position between the two bearing members, since this provides greater consistency to the amount of braking torque exercised by the braking member on the output shaft.
  • the braking member is ring-shaped, thereby allowing the output shaft to position it radially. This shape ensures consistent and uniform contact with the output shaft and the housing portion via its inner ring surface and outer ring surface, respectively.
  • the braking member is in direct contact with the housing portion to provide means for immobilizing the braking member relative to the rotating output shaft.
  • This contact is advantageously accomplished via an interference fit (i.e., a friction fit), since this requires no additional coupling parts, provides some flexibility and tolerance during assembly and minimizes assembly and material costs.
  • the braking torque exercised by the braking member is of sufficient magnitude so that in the absence of an external torque urging the output shaft to rotate, the rotating velocity of the output shaft is always less than or equal to the rotating velocity of the motor shaft.
  • the rotating velocity of the output shaft is always less than or equal to the rotating velocity of the motor shaft.
  • a predictable way of optimizing the forces of friction and adhesion is by adjusting the width of the inner surface of the braking member independently of the overall width by providing this inner surface with a chamfer-shape.
  • An additional way that the braking member can be kept in non-rotational contact with the housing portion is by providing the outer surface of the braking member with a structure that is complimentary with an inner surface of the housing portion.
  • the braking member can be easily fitted to the housing by an interference fit and not require additional members to stabilize the braking member against rotation
  • the braking member is advantageously composed of a flexible, non-metal material, such as felt, plastic, rubber or foam. In comparison with metals, these materials may have lesser material and manufacturing costs.
  • FIG. 1 A portion of a rotary power tool and particularly a drill/driver according to the present invention is illustrated in schematic form in Fig. 1 .
  • the power source for such tools is typically either AC current or a DC battery.
  • a motor 12 Positioned within the housing 10 of the rotary power tool are a motor 12 driven by this power source and its associated motor shaft 14.
  • a transmission 16 modulates the speed and torque conveyed by the motor shaft 14 to downstream elements in the power train.
  • ASLM automatic shaft locking mechanism
  • ASLM's are well known in the art, and the details of how they operate will not be described in detail in the present description. For examples of different ASLM's, readers are referred instead to U.S. Patent No. 6,311,787 and U.S. Patent Publication No. 2006/0131043 A1 which are hereby incorporated by reference.
  • the transmission 16 may not necessarily be discrete from the ASLM 18. That is, there may be components that function as both part of the transmission 16 and the ASLM 18.
  • Downstream from the ASLM 18 is an output shaft 20.
  • the output shaft 20 may interact directly with the ASLM 18 or it may be coupled to one or more other elements in between.
  • a housing portion 28 comprises the portion of housing 10 that is coaxial with and surrounds the output shaft 20.
  • the output shaft 20 is coupled with this housing portion 28 via two ring-shaped ball bearings 22 and 24 which serve to stabilize the shaft.
  • an output interface 26 At the end of the output shaft 20 is an output interface 26 for attaching a tool holder such as a drill chuck or the like. Alternatively tools can be attached directly to the output shaft 20 itself.
  • a braking member comprising a felt ring 30 is positioned between the two ball bearings 22 and 24. It surrounds the output shaft 20 and preferably is secured by an interference (friction) fit with housing portion 28. The resulting friction between the felt ring 30 and the housing portion 28 is much greater than the friction between it and the output shaft 20. As a result, the braking member will not rotate relative to the housing portion 28 when the output shaft 20 is rotating at typical operating speeds in the range of 400-1400 RPM. The friction can be of sufficient magnitude so that no means for maintaining the position of the braking member in the axial direction are necessary.
  • the bearings 22 and 24 would serve to confine the braking member to the generally appropriate axial location around the output shaft 20, which is preferably at any axial point that is between the two bearings. Any friction resulting from contact of the braking member with the side of the ring-shaped ball bearing 22 is negligible in comparison to the frictional force exerted on the output shaft 20.
  • the braking member is positioned in the space between the bearings 22 and 24, but it may alternatively be positioned outside of them provided there is sufficient axial space to accommodate the braking member and there is no interference with other structures.
  • the felt ring 30 is seen in isolation in Fig. 3 and is characterized by an inner diameter 32, an outer diameter 34, and a thickness 36.
  • the inner diameter 32 and the outer diameter 34 are chosen so as to satisfy the preferred frictional conditions discussed above. However, particular care has been taken to adjust the inner diameter 34 so as to control the frictional force between the inner surface 38 of the felt ring 30 and the output shaft 20. In a preferred scenario, this braking torque is just exactly enough so that the down-coasting velocity of the output shaft 20 is slowed to a rate exactly equal to that of the motor shaft 14. When this condition is satisfied, there is no engagement of the ASLM 18 when the power is cut to the motor.
  • this preferred scenario does not define the preferred embodiment, since with repeated use of the tool, there is wear on the felt ring 30, and this may alter the amount of friction between the braking member and the output shaft 20.
  • the braking member described here is not intended to provide support for the output shaft 20. It is intended to be of inexpensive construction, and is designed not for minimizing friction, but for introducing friction.
  • the amount of braking torque it exerts is preferably adjustable and the alternative embodiment described below provides one manner of achieving precision in controlling this parameter during design of the tool.
  • a second embodiment for a braking member, comprising an elastic ring 40 made of soft resilient material is shown in isolation in Fig. 4 .
  • the elastic material may be a rubber, such as nitrile butadiene rubber (NBR), a plastic, such as acetal polyoxymethelene (POM), or a cellular urethane foam, such as Poron ® (a registered U.S. trademark of Rogers Corporation), each of which could have the appropriate combination of elasticity and strength to serve as the braking member.
  • NBR nitrile butadiene rubber
  • POM acetal polyoxymethelene
  • Poron ® a registered U.S. trademark of Rogers Corporation
  • the outer surface 41 of the elastic ring 40 is configured to have what can be generally characterized as protrusions 42 and recesses 44. In this case, these features are intended to cooperate with complementary recesses 46 and protrusions 48 respectively that may be present on the inner surface 49 of the housing portion 28 (see Fig. 2 ). Such cooperation would potentially lessen the extent to which a friction fit between the elastic ring 40 and the housing portion 28 is necessary.
  • Alternative means for securing the braking member against rotation include configuring the housing portion 28 with pin-like structures (not shown) that would puncture and deeply penetrate the braking member during the housing assembly process.
  • a braking member without cooperating features can be used (see Fig. 3 ) since the braking member is composed of compliant material.
  • Protrusions and recesses could also be provided on the felt ring 30. However this may be more complicated or costly from a manufacturing standpoint versus an elastic ring 40 which can be made from a variety of materials that lend themselves well to injection molding. Hence when more complicated surface contours are desired, the braking member is preferably manufactured from moldable materials.
  • Changing the contact area with the output shaft 20 by varying the inner surface 50 of elastic ring 40 is one way to optimize the amount of braking provided by the brake member.
  • the inner surface 50 of the elastic member 40 can be chamfered to create a chamfered surface 52.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Claims (11)

  1. Kraftangetriebenes Drehwerkzeug, umfassend:
    einen Motor (12);
    eine von dem Motor (12) angetriebene Motorwelle (14);
    eine über einen automatischen Spindelarretiermechanismus (18) mit der Motorwelle (14) gekoppelte Ausgangswelle (20),
    einen die Ausgangswelle (20) umgebenden Gehäuseteil (28); und
    ein Bremsglied (30, 40), das bezüglich des Gehäuseteils (28) nicht drehbar ist; wobei das Bremsglied (30, 40) immer dann ein Bremsmoment auf die Ausgangswelle (20) ausübt, wenn sie sich dreht; dadurch gekennzeichnet, dass das Bremsglied (30, 40) ringförmig ist und eine Innenfläche (38, 50) aufweist, die eine Reibkraft auf die Ausgangswelle (20) ausübt.
  2. Kraftangetriebenes Drehwerkzeug nach Anspruch 1, dadurch gekennzeichnet, dass die Ausgangswelle (20) durch mindestens zwei Lagerglieder (22, 24) stabilisiert wird und das Bremsglied (30, 40) zwischen den mindestens zwei Lagergliedern (22, 24) positioniert ist.
  3. Kraftangetriebenes Drehwerkzeug nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Bremsglied (30, 40) ringförmig ist und die Ausgangswelle (20) entlang ihrer Innenfläche (38, 50) berührt.
  4. Kraftangetriebenes Drehwerkzeug nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Bremsglied (30, 40) in direktem Kotakt mit dem Gehäuseteil (28) steht.
  5. Kraftangetriebenes Drehwerkzeug nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Bremsglied (30, 40) und der Gehäuseteil (28) durch eine Presspassung gekoppelt sind.
  6. Kraftangetriebenes Drehwerkzeug nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass eine Innenfläche (50) des Bremsglieds eine abgeschrägte Fläche (52) aufweist.
  7. Kraftangetriebenes Drehwerkzeug nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass eine Außenfläche (41) des Bremsglieds (30, 40) eine Struktur aufweist, die zu einer Innenfläche (49) des Gehäuseteils (28) komplementär ist.
  8. Kraftangetriebenes Drehwerkzeug nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Bremsmoment eine ausreichende Größe aufweist, so dass bei Fehlen eines äußeren Drehmoments, das die Ausgangswelle (20) in Drehung versetzt, die Drehgeschwindigkeit der Ausgangswelle (20) immer kleiner gleich der Drehgeschwindigkeit der Motorwelle (14) ist.
  9. Kraftangetriebenes Drehwerkzeug nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Bremsglied (30, 40) aus einem flexiblen Nichtmetallmaterial besteht.
  10. Kraftangetriebenes Drehwerkzeug nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Bremsglied (30) aus Filz besteht.
  11. Kraftangetriebenes Drehwerkzeug nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass das Bremsglied (40) aus Kunststoff, Kautschuk oder Schaumstoff besteht.
EP07111436A 2007-06-29 2007-06-29 Geräuschunterdrückungsbremse für einen automatischen Spindelarretiermechanismus Active EP2008773B1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP07111436A EP2008773B1 (de) 2007-06-29 2007-06-29 Geräuschunterdrückungsbremse für einen automatischen Spindelarretiermechanismus
DE602007012222T DE602007012222D1 (de) 2007-06-29 2007-06-29 Geräuschunterdrückungsbremse für einen automatischen Spindelarretiermechanismus
US12/667,143 US20100224382A1 (en) 2007-06-29 2008-05-30 Noise elimination brake for automatic spindle locking mechanism
CN2008800221651A CN101730612B (zh) 2007-06-29 2008-05-30 一种旋转电动工具
PCT/EP2008/056658 WO2009003774A1 (en) 2007-06-29 2008-05-30 Noise elimination brake for automatic spindle locking mechanism

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07111436A EP2008773B1 (de) 2007-06-29 2007-06-29 Geräuschunterdrückungsbremse für einen automatischen Spindelarretiermechanismus

Publications (2)

Publication Number Publication Date
EP2008773A1 EP2008773A1 (de) 2008-12-31
EP2008773B1 true EP2008773B1 (de) 2011-01-26

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ID=38740301

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07111436A Active EP2008773B1 (de) 2007-06-29 2007-06-29 Geräuschunterdrückungsbremse für einen automatischen Spindelarretiermechanismus

Country Status (5)

Country Link
US (1) US20100224382A1 (de)
EP (1) EP2008773B1 (de)
CN (1) CN101730612B (de)
DE (1) DE602007012222D1 (de)
WO (1) WO2009003774A1 (de)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100992956B1 (ko) * 2008-10-07 2010-11-09 엘지이노텍 주식회사 스핀들 모터
DE102009054929B4 (de) 2009-12-18 2022-08-11 Robert Bosch Gmbh Handwerkzeugmaschinenvorrichtung
DE102011005553A1 (de) * 2010-10-15 2012-04-19 Robert Bosch Gmbh Handgeführtes Elektrowerkzeug mit einer Spindellockvorrichtung
US9481080B2 (en) 2011-07-29 2016-11-01 Black & Decker Inc. Multispeed power tool
DE102013212193A1 (de) 2013-06-26 2014-12-31 Robert Bosch Gmbh Handwerkzeugmaschine mit einer Spindellockvorrichtung
USD899806S1 (en) * 2019-03-28 2020-10-27 San Jamar, Inc. Roll towel dispenser lockout
US11975436B2 (en) 2021-03-08 2024-05-07 Milwaukee Electric Tool Corporation Spindle lock for power tool

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US1904322A (en) * 1932-03-26 1933-04-18 Independent Pneumatic Tool Co Stud setting tool
US3419087A (en) * 1967-03-30 1968-12-31 Chicago Pneumatic Tool Co Torque controlled electric nut-runner with solenoid brake
SE398207B (sv) * 1975-02-11 1977-12-12 Atlas Copco Ab Sett att vid en skruv- eller mutterdragare reducera inverkan av ett skruvforbands styvhet pa det slutliga atdragningsmomentet samt skruv- eller mutterdragare for genomforande av settet
US4947939A (en) * 1989-11-20 1990-08-14 Wonder Hung Structure of motorized screw bolt driving tool
JP3675527B2 (ja) * 1995-08-03 2005-07-27 有限会社村技術綜合研究所 出力軸のロック装置
US6128984A (en) * 1995-09-25 2000-10-10 Haupt; Chett D. Micro-torque limiting, shock limiting tool and subassembly
US6497316B1 (en) * 2000-01-18 2002-12-24 Mobiletron Electronics Co., Ltd. Powered, unidirectional output controlling apparatus
US6311787B1 (en) * 2000-04-18 2001-11-06 Black & Decker Inc. Power driven rotary device
US7063201B2 (en) * 2001-11-27 2006-06-20 Milwaukee Electric Tool Corporation Power tool and spindle lock system
US6454020B1 (en) * 2002-01-29 2002-09-24 Jenn Feng Industrial Co., Ltd. Locking device for output shaft of electric tools
US20060243469A1 (en) * 2003-06-11 2006-11-02 Webster Craig D Handwheel-operated device
US20060024141A1 (en) * 2004-07-30 2006-02-02 Hilti Aktiengesellschaft Power tool with an intermittent angular torque pulse
DE102004055237A1 (de) * 2004-11-16 2006-05-18 Robert Bosch Gmbh Mitnahme- und Blockiervorrichtung

Also Published As

Publication number Publication date
CN101730612B (zh) 2013-01-23
EP2008773A1 (de) 2008-12-31
CN101730612A (zh) 2010-06-09
DE602007012222D1 (de) 2011-03-10
WO2009003774A1 (en) 2009-01-08
US20100224382A1 (en) 2010-09-09

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