WO1994019152A1 - A vibration-free grinding machine - Google Patents

A vibration-free grinding machine Download PDF

Info

Publication number
WO1994019152A1
WO1994019152A1 PCT/SE1994/000149 SE9400149W WO9419152A1 WO 1994019152 A1 WO1994019152 A1 WO 1994019152A1 SE 9400149 W SE9400149 W SE 9400149W WO 9419152 A1 WO9419152 A1 WO 9419152A1
Authority
WO
WIPO (PCT)
Prior art keywords
vibration
outer case
grinding
grinding machine
power unit
Prior art date
Application number
PCT/SE1994/000149
Other languages
French (fr)
Inventor
Nils B. G. Ribbing
Original Assignee
Ribbing Nils B G
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 Ribbing Nils B G filed Critical Ribbing Nils B G
Priority to EP94908555A priority Critical patent/EP0675781A1/en
Publication of WO1994019152A1 publication Critical patent/WO1994019152A1/en

Links

Classifications

    • 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
    • B25F5/006—Vibration damping means
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B23/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01B23/06—Adaptations for driving, or combinations with, hand-held tools or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B63/00—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices
    • F02B63/02—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices for hand-held tools

Definitions

  • This invention relates to a hand-held power tool to be used primarily for grinding and similar operations.
  • the static and dynamic vibration generated by the machine are dampened by means of shock and vibration-absorbing elements positioned in a special geometrical arrangement, between the relatively lightweight motor and spindle unit and the outer case, which is equipped with handles. This enables the motor and spindle unit to move in three dimensions relative to the outer case.
  • the working movement of the shock and vibration- -absorbing elements is never exceeded by the amplitude of the vibration and the working speed is much higher than the cri ⁇ tical resonance speed of the machine.
  • SUBSTITUTESHEET other grinding wheels have an almost axial contact.
  • the angle of contact also varies according to the type of work to be carried out.
  • the machine has to be held in the best way to balance the forces resulting from the weight of the machine, the operating pressure on the work piece, and the grinding friction force.
  • Machines that vibrate with a constant frequency and amplitude are easier to devibrate.
  • chain saws have successive ⁇ sfully been equipped with devibrated handles.
  • a devibrated handle on a grinding machine usually consists of a rubber block mounted between the machine and the handle/s.
  • the improvement is marginal since the handles are light in weight relative to that of the machine.
  • the rubber blocks need to be rather stiff to accomodate the large bending moments the handles are exposed to during certain grinding operations.
  • Such a machine is inconvenient and tiring to hold. This results from the operators' hands being more widely spaced due to the presence of the rubber blocks. This results in higher bending moments on the wrists which leads to the operator having to hold the machine even more firmly.
  • the frequency and amplitude of the vibration changes during the grinding operation due to the wear of the grinding/cutting wheel. Differences in the wear make the wheels deviate from their original rotational symmetrical shape which may become eccentric, oval or polygonal. These differences in shape com ⁇ bined with different angles of contact and operating pressures, result in grinding machines with devibrated handles similar to those of e.g., chain saws, the machine will easily enter a critical resonance phase. The same resonance phase easily occurs in grinding machines where the vibration-damping ele ⁇ ments consist of rubber rings such as O-rings which compress far less than the amplitude. With a machine running at a criti ⁇ cal resonance speed, the vibrations become amplified and are transferred to the hands of the operator.
  • the intention is to isolate the vibration of a hand-held com ⁇ pressed air-driven grinding machine as closely as possible to the source that is at the grinding wheel, and to prevent as efficiently as possible the vibration from spreading to the handles and to the hands of the operator.
  • the machine which is equipped with a speed governor, works at a speed above that of the critical resonance speed.
  • the drive unit i.e., the pneumatic motor with its integral drive spindle, is made as light as possible.
  • a low weight has been achieved through manufacturing certain parts, such as end plates, of aluminium instead of steel. At the same time, numerous holes have been drilled in the rotor to lighten it.
  • the motor housing is supported by soft shock and vibration-absorbing elements which are positioned in such a way that the vibration caused by the imbalance of the grinding wheel and by torsional vibration of the motor are absorbed in three dimensions.
  • the motor housing ⁇ support in the outer case is sufficiently rigid to resist the operating pressure against the workpiece without the the motor housing touching the outer case.
  • Side forces which occur at different angles of contact between the grinding wheel and the workpiece are absorbed by the upper shock and vibration-absorbing elements, each of which is mounted with its compression/elongation axis intersecting approximately the contact point/periphery of the grinding wheel.
  • the trigger handle and the support handle are mounted rigidly on the outer case without any resilient elements while the whole drive unit remains "floating".
  • Figure 1 shows a vertical section through the grinding machine fitted with a depressed centre grinding wheel.
  • the drive unit with its integrated drive spindle is shown as well as the upper and lower shock and vibration-absorbing elements.
  • Figure 1 also shows the compressed air regulating valve together with a flexible membrane which seals the motor housing and the outer case.
  • Figure 2 shows a vertical section of the lower part of the machine with a cutting wheel installed.
  • the machine is fitted with fixed wheel guards.
  • Figure 3 shows a vertical section of the lower part of the machine fitted with a cup grinding wheel with an integral rotary wheel guard.
  • Figure 4 shows a vertical section of the machine where the lower positioned shock and vibration-absorbing element con ⁇ sists of a resilient ring.
  • Figure 4 is another embodiment of the innovation.
  • Figure 5 shows a section along the A-A line in Figure 1 with the positioning of the lower shock and vibration-absorbing elements. Two of these elements are mounted radially and one tangentially. With this arrangement, all vibration and shock forces from any direction are absorbed.
  • Figure 6 shows a section along the B-B line in Figure 1 with the arrangement of the upper shock and vibration-absorbing elements. This section also applies to Figure 4.
  • Part 1 designates the outer case, and 2 the housing of the drive unit with its integral spindle, 13.
  • the upper shock and vibration-absorbing elements are designatet 3 and the lower ones 4 and 4'.
  • the grinding machine can be fitted with
  • SUBSTITUTESHEET different types of grinding wheel; 5 shows a depressed centre grinding wheel, 6 a cutting wheel and 7 a cup wheel.
  • the trigger handle, 9, consists of a pneumatic valve, 15, which is actuated by the trigger, 11. Compressed air flows from the pneumatic valve to the air motor through a flexible hose, 10.
  • a flexible membrane, 12 prevents the exhaust air from escaping through the gap between the outer case, 1, and the housing of the drive unit, 2. Instead, an expansion chamber is formed between the outer case and the housing of the drive unit and it acts as a silencer.
  • the lower shock and vibration-absorbing elements, 4 and 4', as well as the membrane, 12, can be replaced by a resilient ring, 16.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Grinding Of Cylindrical And Plane Surfaces (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Polishing Bodies And Polishing Tools (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)

Abstract

An arrangement to devibrate a hand-held, compressed air-driven rotary grinding machine with vertical spindle. A grinding machine equipped with an unbalanced and unequally worn grinding wheel vibrates severely and will injure the operator. To avoid vibration reaching the hands of the operator, the drive unit (2) with its integral spindle (13) is supported by shock and vibration-absorbing elements (3, 4, 4', 16) in the outer case (1) where it is able to move in three dimensions. The working movement (compression-elongation as well as sideways) of the elements is never exceeded by the amplitude of the vibration that occurs when the machine runs at a normal working rotational speed, which is much higher than the critical resonance speed. The drive unit (2) is very lightweight in relation to the outer case (1) and to the grinding wheel (5, 6, 7). As a result of this, the grinding wheel will centre itself automatically when the critical resonance speed is passed. Compressed air is supplied to the motor through a flexible hose (10).

Description

TI TLE :
A VIBRATION-FREE GRINDING MACHINE.
SPECIFICATION.
This invention relates to a hand-held power tool to be used primarily for grinding and similar operations.
The static and dynamic vibration generated by the machine are dampened by means of shock and vibration-absorbing elements positioned in a special geometrical arrangement, between the relatively lightweight motor and spindle unit and the outer case, which is equipped with handles. This enables the motor and spindle unit to move in three dimensions relative to the outer case. The working movement of the shock and vibration- -absorbing elements is never exceeded by the amplitude of the vibration and the working speed is much higher than the cri¬ tical resonance speed of the machine.
BACKGROUND.
The vibration generated by hand-held power tools e.g., chain saws, grinding machines, impact wrenches etc. is liable in time to injure the operator. Injuries caused by vibration are known to result in circulatory changes in the fingers and hands. These symptoms, known as "white fingers", include numbness (parasthesia) and loss of temperature and tactile sensations. When using high-powered tools, vibration is more easily transferred to the hands since the operator has to hold such tools very firmly. This applies particularly to large grinding machines which sometimes have a power output of many horsepower/kilowatt and are used together with dep¬ ressed centre grinding wheels, cutting wheels or cup wheels. The machine has to be held differently for different grinding operations depending on which grinding wheels are used. A cutting wheel has a radial contact with the workpiece whilst
SUBSTITUTESHEET other grinding wheels have an almost axial contact. The angle of contact also varies according to the type of work to be carried out. The machine has to be held in the best way to balance the forces resulting from the weight of the machine, the operating pressure on the work piece, and the grinding friction force.
Machines that vibrate with a constant frequency and amplitude are easier to devibrate. For example, chain saws have succes¬ sfully been equipped with devibrated handles. However, the situation for grinding machines is much more complicated. A devibrated handle on a grinding machine usually consists of a rubber block mounted between the machine and the handle/s. The improvement is marginal since the handles are light in weight relative to that of the machine. The rubber blocks need to be rather stiff to accomodate the large bending moments the handles are exposed to during certain grinding operations. Such a machine is inconvenient and tiring to hold. This results from the operators' hands being more widely spaced due to the presence of the rubber blocks. This results in higher bending moments on the wrists which leads to the operator having to hold the machine even more firmly.
The frequency and amplitude of the vibration changes during the grinding operation due to the wear of the grinding/cutting wheel. Differences in the wear make the wheels deviate from their original rotational symmetrical shape which may become eccentric, oval or polygonal. These differences in shape com¬ bined with different angles of contact and operating pressures, result in grinding machines with devibrated handles similar to those of e.g., chain saws, the machine will easily enter a critical resonance phase. The same resonance phase easily occurs in grinding machines where the vibration-damping ele¬ ments consist of rubber rings such as O-rings which compress far less than the amplitude. With a machine running at a criti¬ cal resonance speed, the vibrations become amplified and are transferred to the hands of the operator.
SUBSTITUTESHEET THE PURPOSE OF THE INVENTION AND ITS MOST IMPORTANT CHARACTERISTICS.
The intention is to isolate the vibration of a hand-held com¬ pressed air-driven grinding machine as closely as possible to the source that is at the grinding wheel, and to prevent as efficiently as possible the vibration from spreading to the handles and to the hands of the operator. The machine, which is equipped with a speed governor, works at a speed above that of the critical resonance speed. To keep the critical resonance speed as low as possible, the drive unit i.e., the pneumatic motor with its integral drive spindle, is made as light as possible. A low weight has been achieved through manufacturing certain parts, such as end plates, of aluminium instead of steel. At the same time, numerous holes have been drilled in the rotor to lighten it. The motor housing is supported by soft shock and vibration-absorbing elements which are positioned in such a way that the vibration caused by the imbalance of the grinding wheel and by torsional vibration of the motor are absorbed in three dimensions. When the grinding wheel is not balanced, it automatically becomes centred around its outer periphery while the rotary centre moves eccentrically or like a pendulum, depending on the size and the shape of the grinding wheel. However, the motor housing^ support in the outer case is sufficiently rigid to resist the operating pressure against the workpiece without the the motor housing touching the outer case. Side forces which occur at different angles of contact between the grinding wheel and the workpiece are absorbed by the upper shock and vibration-absorbing elements, each of which is mounted with its compression/elongation axis intersecting approximately the contact point/periphery of the grinding wheel. The trigger handle and the support handle are mounted rigidly on the outer case without any resilient elements while the whole drive unit remains "floating".
SUBSTITUTE SHEET GENERAL DESCRIPTION OF FIGURES 1-6.
Figure 1 shows a vertical section through the grinding machine fitted with a depressed centre grinding wheel. The drive unit with its integrated drive spindle is shown as well as the upper and lower shock and vibration-absorbing elements. Figure 1 also shows the compressed air regulating valve together with a flexible membrane which seals the motor housing and the outer case.
Figure 2 shows a vertical section of the lower part of the machine with a cutting wheel installed. In Figures 1 and 2, the machine is fitted with fixed wheel guards.
Figure 3 shows a vertical section of the lower part of the machine fitted with a cup grinding wheel with an integral rotary wheel guard.
Figure 4 shows a vertical section of the machine where the lower positioned shock and vibration-absorbing element con¬ sists of a resilient ring. Figure 4 is another embodiment of the innovation.
Figure 5 shows a section along the A-A line in Figure 1 with the positioning of the lower shock and vibration-absorbing elements. Two of these elements are mounted radially and one tangentially. With this arrangement, all vibration and shock forces from any direction are absorbed.
Figure 6 shows a section along the B-B line in Figure 1 with the arrangement of the upper shock and vibration-absorbing elements. This section also applies to Figure 4.
DESCRIPTION OF PARTS 1-16 IN FIGURES 1-6.
Part 1 designates the outer case, and 2 the housing of the drive unit with its integral spindle, 13. The upper shock and vibration-absorbing elements are designatet 3 and the lower ones 4 and 4'. The grinding machine can be fitted with
SUBSTITUTESHEET different types of grinding wheel; 5 shows a depressed centre grinding wheel, 6 a cutting wheel and 7 a cup wheel. When work is carried out with a depressed centre grinding wheel or with a cutting wheel, the machine must be provided with a fixed wheel guard, 14. The trigger handle, 9, consists of a pneumatic valve, 15, which is actuated by the trigger, 11. Compressed air flows from the pneumatic valve to the air motor through a flexible hose, 10. When operating the grinding machine, the operator has to hold the trigger handle, 9, and the support handle, 8. A flexible membrane, 12, prevents the exhaust air from escaping through the gap between the outer case, 1, and the housing of the drive unit, 2. Instead, an expansion chamber is formed between the outer case and the housing of the drive unit and it acts as a silencer. The lower shock and vibration-absorbing elements, 4 and 4', as well as the membrane, 12, can be replaced by a resilient ring, 16.
SUBSTITUTESHEET

Claims

1. Arrangement for hand-held, compressed air-driven grinding machines comprising a power unit (2) lodged in an inner housing where said power unit has an integral spindle (13) and said inner housing is mounted flexibly in three dimensions in an outer housing (1 ) c-h-a-r-a-c-t-e-r-i-z-e-d i-n:
that said inner housing by means of one or more upper located shock and vibration-absorbing elements (3) and/or lower located shock and vibration-absorbing elements (4, 4') either arran¬ ged in a series or consisting of a soft, resilient ring (16) which has a working movement in three dimensions which is never exceeded by the amplitude of the vibration when the grinding machine runs at its working speed, which is much higher than the critical resonance speed, which results in no significant vibration being transferred to said outer case and to the handles (8, 9).
2. Grinding machine according to claim 1, c-h-a-r-a-c-t-e-r-i-z-e-d i-n:
that said flexibly mounted power unit obtains compressed air through a hose (10) which is flexible in three dimen¬ sions and is connected to a manually operated pneumatic valve (15) mounted in the handle on the outer case and that said power unit by means of a flexible membrane (12) is sealed off against said outer case to make use of the volume between said inner and outer cases as a silencer.
3. Grinding machine according to claims 1 and 2, c-h-a-r-a-c-t-e-r-i-z-e-d i-n:
that it is intended to be used together with depressed centre grinding wheels (5), cutting wheels (6) as well as with cup wheels (7) and that the air motor with end-plates of light metal and the rotor with numerous holes to lighten it, is very light compared with said outer case.
SUBSTITUTESHEET
PCT/SE1994/000149 1993-02-23 1994-02-23 A vibration-free grinding machine WO1994019152A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP94908555A EP0675781A1 (en) 1993-02-23 1994-02-23 A vibration-free grinding machine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE9300594A SE504437C2 (en) 1993-02-23 1993-02-23 Device for vibrating rotary grinder with self-centering grinding wheel
SE9300594-0 1993-02-23

Publications (1)

Publication Number Publication Date
WO1994019152A1 true WO1994019152A1 (en) 1994-09-01

Family

ID=20388990

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE1994/000149 WO1994019152A1 (en) 1993-02-23 1994-02-23 A vibration-free grinding machine

Country Status (3)

Country Link
EP (1) EP0675781A1 (en)
SE (1) SE504437C2 (en)
WO (1) WO1994019152A1 (en)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000054931A1 (en) * 1997-11-10 2000-09-21 Marc Ferland Concrete finishing machine
EP1129819A1 (en) * 2000-03-03 2001-09-05 Kress-elektrik GmbH + Co. Elektromotorenfabrik Bearing of a transmission element in a casing
WO2006061389A1 (en) * 2004-12-07 2006-06-15 Black & Decker Inc. Vibration attenuated power tool
WO2007141065A1 (en) * 2006-06-02 2007-12-13 Robert Bosch Gmbh Hand-held grinder and vibration decoupling device for a hand-held grinder
WO2008115807A2 (en) 2007-03-16 2008-09-25 Black & Decker Inc. Low vibration sander with a flexible top handle
WO2012049155A1 (en) * 2010-10-14 2012-04-19 Robert Bosch Gmbh Hand-held machine tool
WO2016127930A1 (en) * 2015-02-15 2016-08-18 苏州宝时得电动工具有限公司 Power tool
EP3257636A4 (en) * 2015-02-15 2018-11-07 Positec Power Tools (Suzhou) Co., Ltd Power tool
WO2020161026A1 (en) * 2019-02-07 2020-08-13 Festool Gmbh Machine tool having a balancing device
WO2022090898A1 (en) * 2020-10-28 2022-05-05 3M Innovative Properties Company Reusable hub assembly for abrasive articles

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3345784A (en) * 1964-12-29 1967-10-10 Rockwell Mfg Co Orbital finishing sander
CH573798A5 (en) * 1973-07-14 1976-03-31 Metabowerke Kg
US4140446A (en) * 1976-09-23 1979-02-20 Atlas Copco Aktiebolag Rotary pneumatic tool with vibration absorbing means
US4268233A (en) * 1978-05-16 1981-05-19 Atlas Copco Aktiebolag Hand held rotary machine tool with vibration insulating means
DE4000861A1 (en) * 1990-01-13 1991-07-18 Licentia Gmbh Hand-held electric power tool e.g. percussion drill - has vibration decoupling of handgrip from motor by using rubber mounts between inner motor casing and outer tool casing
DE2912718C2 (en) * 1979-03-30 1992-04-30 Robert Bosch Gmbh, 7000 Stuttgart, De

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3345784A (en) * 1964-12-29 1967-10-10 Rockwell Mfg Co Orbital finishing sander
CH573798A5 (en) * 1973-07-14 1976-03-31 Metabowerke Kg
US4140446A (en) * 1976-09-23 1979-02-20 Atlas Copco Aktiebolag Rotary pneumatic tool with vibration absorbing means
US4268233A (en) * 1978-05-16 1981-05-19 Atlas Copco Aktiebolag Hand held rotary machine tool with vibration insulating means
DE2912718C2 (en) * 1979-03-30 1992-04-30 Robert Bosch Gmbh, 7000 Stuttgart, De
DE4000861A1 (en) * 1990-01-13 1991-07-18 Licentia Gmbh Hand-held electric power tool e.g. percussion drill - has vibration decoupling of handgrip from motor by using rubber mounts between inner motor casing and outer tool casing

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000054931A1 (en) * 1997-11-10 2000-09-21 Marc Ferland Concrete finishing machine
EP1129819A1 (en) * 2000-03-03 2001-09-05 Kress-elektrik GmbH + Co. Elektromotorenfabrik Bearing of a transmission element in a casing
WO2006061389A1 (en) * 2004-12-07 2006-06-15 Black & Decker Inc. Vibration attenuated power tool
WO2007141065A1 (en) * 2006-06-02 2007-12-13 Robert Bosch Gmbh Hand-held grinder and vibration decoupling device for a hand-held grinder
US8038513B2 (en) 2006-06-02 2011-10-18 Robert Bosch Gmbh Manual power sander, and vibration isolation device of a manual power sander
CN101460283B (en) * 2006-06-02 2014-06-25 罗伯特·博世有限公司 Hand-held grinder and vibration decoupling device for a hand-held grinder
EP2125290A4 (en) * 2007-03-16 2013-10-09 Black & Decker Inc Low vibration sander with a flexible top handle
WO2008115807A2 (en) 2007-03-16 2008-09-25 Black & Decker Inc. Low vibration sander with a flexible top handle
EP2125290A2 (en) * 2007-03-16 2009-12-02 Black & Decker, Inc. Low vibration sander with a flexible top handle
CN103153537A (en) * 2010-10-14 2013-06-12 罗伯特·博世有限公司 Hand-held machine tool
WO2012049155A1 (en) * 2010-10-14 2012-04-19 Robert Bosch Gmbh Hand-held machine tool
US9641046B2 (en) 2010-10-14 2017-05-02 Robert Bosch Gmbh Hand-held machine tool having a damping element
WO2016127930A1 (en) * 2015-02-15 2016-08-18 苏州宝时得电动工具有限公司 Power tool
EP3257636A4 (en) * 2015-02-15 2018-11-07 Positec Power Tools (Suzhou) Co., Ltd Power tool
US10888988B2 (en) 2015-02-15 2021-01-12 Positec Power Tools (Suzhou) Co., Ltd Power tool
WO2020161026A1 (en) * 2019-02-07 2020-08-13 Festool Gmbh Machine tool having a balancing device
WO2022090898A1 (en) * 2020-10-28 2022-05-05 3M Innovative Properties Company Reusable hub assembly for abrasive articles

Also Published As

Publication number Publication date
SE9300594D0 (en) 1993-02-23
EP0675781A1 (en) 1995-10-11
SE9300594L (en) 1994-08-24
SE504437C2 (en) 1997-02-10

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