EP2377647A1 - Outil manuel - Google Patents

Outil manuel Download PDF

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Publication number
EP2377647A1
EP2377647A1 EP11158200A EP11158200A EP2377647A1 EP 2377647 A1 EP2377647 A1 EP 2377647A1 EP 11158200 A EP11158200 A EP 11158200A EP 11158200 A EP11158200 A EP 11158200A EP 2377647 A1 EP2377647 A1 EP 2377647A1
Authority
EP
European Patent Office
Prior art keywords
tool
hand tool
drive
drive shaft
coupling member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP11158200A
Other languages
German (de)
English (en)
Other versions
EP2377647B1 (fr
Inventor
Jürgen Blickle
Joachim Clabunde
Mark Heilig
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.)
C&E Fein GmbH and Co
Original Assignee
C&E Fein GmbH and Co
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 C&E Fein GmbH and Co filed Critical C&E Fein GmbH and Co
Publication of EP2377647A1 publication Critical patent/EP2377647A1/fr
Application granted granted Critical
Publication of EP2377647B1 publication Critical patent/EP2377647B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B24B23/04—Portable grinding machines, e.g. hand-guided; Accessories therefor with oscillating grinding tools; Accessories therefor

Definitions

  • the invention relates to a hand tool, in particular a tool for grinding or cutting, with a housing with a gear head, with a rotatably driven by a motor drive shaft which can be coupled via a coupling drive with a tool spindle to the drive, wherein the tool spindle to their storage rotationally oscillatory drivable and designed to receive a tool.
  • Such a hand tool is from the EP 1 428 625 A1 known.
  • an oscillating drive with an oscillating driven about its longitudinal axis output shaft for driving a tool in which an eccentric shaft arranged on an eccentric cooperates with a recorded on the output shaft eccentric fork.
  • the eccentric shaft is arranged parallel to the output shaft.
  • Hand Tools are widely used in the performance of craft activities such as grinding, cutting, sawing or cutting.
  • Hand Tools with rotary oscillatory operated tools are suitable for many activities, because of the high-frequency pivotal movement of the tool can thus be worked very accurately, power-saving and safe.
  • the pivoting angle to be achieved by design can only assume relatively small values within a narrow bandwidth.
  • the eccentricity of the eccentric shaft and the distance between the eccentric shaft and the output shaft are determining and limiting design parameters.
  • the invention has for its object to provide a hand tool with an improved oscillation, which has a simple structure and can be operated particularly wear.
  • a small space should be claimed as possible and the hand tool can be handled as ergonomically as possible, it should be possible in particular a low-vibration operation.
  • the coupling drive has a coupling member which is mounted on the tool spindle eccentrically to the longitudinal axis.
  • the object of the invention is achieved in this way.
  • a considerable pivot angle of the tool spindle can be achieved with relatively small movements of the coupling member.
  • an oscillation of the tool can be effected, which allows a high removal or cutting performance and can improve the performance of the hand tool.
  • the coupling drive is designed as a planar coupling drive.
  • the coupling drive is designed as a rocker arm, wherein the coupling member is rotatably mounted on the drive shaft eccentrically to a drive axis.
  • the desired pivot angle, by which the oscillation of the drive shaft is characterized are determined by specific design of the links of the coupling drive particularly simple and accurate.
  • the eccentricity of the drive shaft, the eccentricity of the tool spindle, the length of the coupling member and the distance between the drive shaft and the tool spindle can be varied and adapted within wide limits.
  • other boundary conditions such as space requirements, soft as possible force curves while avoiding shock and jerk loads and to be achieved instantaneous translations, are taken into account.
  • the drive shaft is mounted parallel to the tool spindle in the gear head.
  • the transmission housing manufacturing can simplify a transmission housing can be divided approximately in a plane spanned by the drive shaft and the tool spindle plane or in a plane perpendicular to both the drive axle and the tool spindle. It may result in a particularly simple structure and easier installation.
  • the drive shaft has an eccentric portion on which the coupling member is mounted.
  • the drive shaft can be produced in a particularly simple and highly accurate manner.
  • Suitable methods for this can be eccentric turning or eccentric grinding. Since with a suitable design of the coupling drive only a relatively small eccentricity of the eccentric portion relative to an axis of the drive shaft is required, this can be made in one piece together with the eccentric portion.
  • the eccentricity of the eccentric portion is less than 3 mm, more preferably less than 2 mm, even more preferably about 1.25 mm. With one revolution around the drive axle, the eccentric stroke is twice the eccentricity.
  • the eccentric portion between a first bearing and a second bearing of the drive shaft is arranged.
  • loads in particular radial loads, which act on the eccentric portion, are introduced via the drive shaft in both bearings and distributed to these.
  • the load on the individual bearings can be significantly reduced.
  • the coupling member has a first bearing and a second bearing, which are preferably designed as a rolling bearing, more preferably as a needle bearing.
  • first storage and the second storage can also be designed as a sliding bearing. Also, it can be effected by suitable material pairings and adequate lubrication overall a significant reduction caused by static friction or sliding friction wear or heat generation.
  • a thrust washer for limiting the axial position of the coupling member is arranged on the drive shaft.
  • This measure has the advantage that the first bearing and the second bearing of the coupling member designed only as a radial bearing and need not be designed to absorb axial forces.
  • the structure of the coupling drive can to further simplify. A reduction of the mass of the coupling member and consequently a reduction of vibrations caused by the coupling drive can be effected.
  • the thrust washer is preferably hardened and has a high surface accuracy at significantly reduced roughness.
  • a thrust bearing may be provided on the thrust washer, which may help to further minimize the friction and wear between the coupling member and the thrust washer.
  • mass balance is provided on the coupling drive.
  • the drive shaft has at least one cheek which effects a mass displacement directed counter to the eccentricity of the bearing of the coupling member away from the drive axle, wherein preferably two cheeks are provided with an axial spacing, between which the coupling member is mounted, more preferred If the thrust washer is designed as a second cheek.
  • the cheek may be a separate, preferably pressed onto the drive shaft part, as well as the cheek can be integrally formed together with the drive shaft.
  • free mass forces in particular free first-order inertial forces
  • overall the level of vibration can be further reduced.
  • the handling and ergonomics as well as the life of the hand tool can be further improved.
  • cheek can be designed as material addition, on the other hand, the eccentricity counteracted mass displacement by targeted removal of component geometry, so for example by drilling or milling in the area around the eccentric can be realized.
  • the tool spindle on both sides held spindle pin, between the ends of the coupling member is received.
  • This design can also help to avoid a tilting moment in the operation of the coupling drive. Furthermore, a high load on the bearing of the spindle pin, as it can occur when unilaterally held spindle pin, avoided.
  • the spindle pin can also be fixed to the coupling member and mounted as its component on the tool spindle.
  • a motor shaft is interposed, which is coupled via a transmission with the drive shaft.
  • the transmission allows a translation or reduction of the engine speed, so that on the one hand particularly powerful motors, such as those with very high power density, can be selected and operated in the range of their optimal speed, and on the other hand, on the tool spindle a defined oscillation frequency can be effected for the intended purpose is particularly suitable.
  • a suitable motor has a rated speed of about 25,000 to 31,000 min -1, preferably from about 28,000 min -1, have.
  • high power can be provided while providing high airflow through a fan to provide efficient cooling of the engine and other components of the hand tool.
  • oscillating-powered hand tools are usually operated at oscillation frequencies of between 5,000 and 25,000 oscillations per minute.
  • the frequency of oscillation is preferably between 9,000 and 13,000 oscillations per minute, more preferably about 11,000 oscillations per minute.
  • the transmission has a gear ratio in the range of 2.2: 1 to 2.8: 1, preferably of about 2.5: 1.
  • the transmission is designed as a toothed gearing, preferably as a bevel gear stage.
  • the motor shaft and the drive shaft can be arranged at an angle to each other, in particular no parallel arrangement of motor shaft and drive shaft is required.
  • a gearing which is designed as a bevel gear
  • the transmission may be formed as a spur gear, crown gear or helical gear, which also special requirements for the position and assignment between the motor shaft and drive shaft and to the translation to be realized can be met.
  • the transmission on bevel gears with straight or curved toothing is not limited.
  • Straight bevel gears can be produced in a particularly simple and cost-effective manner.
  • Bevel gears with curved teeth are characterized by particularly high running quality, load capacity and reduced running noise.
  • the motor shaft is arranged perpendicular to the drive shaft.
  • the hand tool can be equally suitable for grinding applications as well as for cutting applications and, thanks to good handleability, enable simple, fatigue-free operation.
  • an eccentrically received spindle pin counterbalanced mass balance is provided on the tool spindle.
  • the mass balance is preferably realized by an offset region, which causes a mass displacement opposing mass arrangement, so that there is a mass compensation with respect to the longitudinal axis of the tool spindle.
  • the offset region is formed on a rotationally fixed to the tool spindle to this recorded driver. More preferably, the driver is also configured to receive the spindle pin.
  • the tool spindle can also be particularly simple, preferably rotationally symmetrical, held in the region of the coupling drive itself. Elaborate production steps can be avoided.
  • the mass balance on the tool spindle can also be designed to compensate for the mass forces caused by the design of the coupling member.
  • part of the mass of the coupling member is taken into account by the mass balance of the tool spindle and another part of the mass of the coupling member of the mass balance of the drive shaft.
  • Fig. 1 an inventive hand tool is shown and designated overall by the reference numeral 10.
  • the hand tool 10 has a housing 12 and in its front region a gear head 14, to which a tool 16, in the present case a grinding tool, is assigned.
  • Hand tools with oscillation drive can also be operated with cutting tools or cutting tools.
  • Abrasive tools can be designed for surface grinding, such as the tool 16, as well as for grinding grooves or the like with abrasives attached peripherally to a tool, in general also for grinding free-form surfaces.
  • Another use for hand tools with oscillating drive is the polishing with polishing tools.
  • usable tools can be circular, so as grinding wheels or circular saw blades.
  • suitable tools can be readily implemented also segmented.
  • almost any, adapted to the particular application tool shapes are conceivable. Such embodiments allow applications that can not be covered with other types of tools.
  • a line 20 is provided, which can be coupled to a supply network. It is readily conceivable to operate a hand tool according to the invention independently of the line, for example with an energy store, such as an accumulator. In addition to electric motor drives can also be used to drive hand tools according to the invention also pneumatic motors.
  • the hand tool 10 is characterized by a special oscillation drive, as described below with reference to FIG Fig. 2 to 6 is explained in more detail.
  • Fig. 2 shows a perspective view of the hand tool 10 in the region of the gear head 14th
  • the gear head 14 has a gear housing 22, in which a tool spindle 24 is received, which is about its longitudinal axis 26, as indicated by the arrow denoted by 27, rotationally oscillated drivable.
  • Resulting pivoting angle can be approximately between 1 ° and 12 °.
  • Small oscillation angles can be used on the one hand for particularly hard materials and on the other hand for applications requiring high precision. Large swivels are attached to softer workpieces, such as wood. If enough power is available, a large amount of material removal can be achieved with large swiveling angles.
  • a pivoting angle of ⁇ 12 ° is preferred, for example, when using a sanding disk with a diameter of about 150 mm, more preferably the pivoting angle is about 6 °.
  • the tool spindle 24 further has a spindle pin 28 on which a coupling member 32 of a coupling drive 30 is received.
  • the coupling drive 30 is designed as a crank, cf. this too Fig. 4 and Fig. 5 ,
  • the coupling member 32 is received on the spindle pin 28 via a bearing 33 in the form of a needle bearing.
  • a second bearing 34 of the coupling member 32 is arranged on a drive shaft 36.
  • the drive shaft 36 is rotatably driven about its drive shaft 38, as indicated by an arrow designated 39.
  • the coupling member 32 is received via the bearing 34 on an eccentric portion 42 of the drive shaft 36.
  • the eccentric portion 42 is disposed on the drive shaft 36 between a cheek 40 and a thrust washer 44.
  • the thrust washer 44 is used for the axial position limitation of the coupling member 32. This avoids excessive unwanted axial contact of the coupling member 32 with other components of the drive shaft 36 or the tool spindle 24 and, consequently, excessive heat generation and increased wear.
  • the thrust washer 44 advantageously has a strength-increasing or wear-minimizing surface treatment, at least in the region in which contact takes place with the coupling member 32. Such a treatment can also be done on the coupling member 32.
  • the cheek 40 is rotatably connected to the drive shaft 36, such as by a press fit.
  • the cheek 40 is not rotationally symmetrical, but has a projection in the direction opposite to the displacement of the eccentric portion 42 of the drive shaft 38, see. also Fig. 3 and Fig. 6 , In this way, a compensation of the conditional by the design of the eccentric portion 42 with the bearing 34 and the coupling member 32 mass offset can be done.
  • the thrust washer 44 similar to the cheek 40 in order to effect around the coupling member 32 around an at least substantially symmetrical mass balance.
  • tilting moments in the coupling drive 30 caused by the coupling element 32 can be reduced or avoided altogether in the case of a symmetrical mass balance.
  • the cheek 40 can also perform the function of a thrust washer to cause an axial position limitation of the coupling member 32.
  • the cheek 40 as well as the thrust washer 44 have a strength-increasing or wear-minimizing surface.
  • the drive shaft 36 is received in the transmission housing 22 via a first bearing 46 and via a second bearing 48. It is provided to arrange the coupling drive 30 between the first bearing 46 and the second bearing 48 in order to allow a distribution of acting loads on both bearings.
  • This central storage allows, in contrast to flying bearings, a uniform distribution, in particular radial forces, as they arise during the movement of the coupling member 32.
  • the drive shaft 36 is coupled via a gear 49 with a motor shaft 58.
  • the gear 49 is designed as a bevel gear and has a via a nut 52 fixed to the drive shaft 36 wheel 50.
  • the wheel 50 may be approximately pressed on the drive shaft 36 or be positively fixed by a shaft-hub connection.
  • the wheel 50 is driven by a pinion 54 disposed on the motor shaft 58.
  • the toothing of the pinion 54 with the teeth of the wheel 50 is engaged.
  • the toothing can be designed as a straight toothing or curved toothing.
  • the reduction of the bevel gear stage of the transmission 49 is approximately in the range between 2.2: 1 and 2.8: 1, preferably about 2.5: 1.
  • the input speed generated by a motor 56 are converted into a rotational speed of the drive shaft 36, which is decisive for the frequency of the rotational oscillations generated on the tool spindle 24. To the extent that the speed is reduced, also increases the transferable to the tool 16 torque.
  • the motor 56 and the pinion 54, a fan 60 and a bearing 62 are interposed on the motor shaft 58.
  • the operated with the rotational speed of the engine 56 fan 60 can cause the range of the preferred nominal speeds of the motor 56 of about 25,000 min -1 to 31,000 min -1, more preferably from about 28,000 min -1, a particularly high air throughput.
  • the motor 56 is sufficiently cooled.
  • heat can be dissipated from the gear head 14, consequently, a temperature level in particular of the coupling drive 30 and the gear 49 are maintained during operation, in which increase the life of the components involved and reduce the susceptibility to wear.
  • a bell 76 is further provided in the housing 12, which is designed to channel the air flow, cf. Fig. 3 , Particularly advantageously, a part of the air flow can be used to suck off chips and abrasive particles removed by means of a vacuum through the tool 16 and remove them from a workpiece.
  • a driver 64 is provided, which is adapted to carry the spindle pin 28 on which the coupling member 32 is mounted.
  • the driver 64 is rotatably connected to the tool spindle 24, this advantageously a press connection is provided.
  • the driver 64 has a first driver arm 66 and a second driver arm 68, cf. also FIGS. 5 and 6 ,
  • the driver arms 66, 68 take on the spindle pin 28 on both sides, so that this is essentially claimed by the coupling member 32 only to shear and in particular undergoes no unilateral bending load.
  • To increase the wear resistance of the spindle pin 28 is preferably cured, to improve the smooth running surface treatment is further preferably provided in order to make geometrical tolerances and roughness depths to a suitable extent.
  • Fig. 3 further shows the mounting of the tool spindle 24 in the gear housing 22.
  • the tool spindle 24 is formed via a first bearing 70, formed as Ball bearing, and a second bearing 72, formed as a needle bearing, received on the transmission housing 22. Applied axial loads are absorbed by the first bearing 70 in a known manner.
  • the tool 16 is received on the tool spindle 24 by means of a tool attachment 74.
  • the tool attachment 74 is according to Fig. 3 designed as non-positive attachment in the form of a screw.
  • the fastening of the tool 16 to the tool spindle 24 can take place via a positive connection, while a force-locking component can also contribute to securing the positive connection. That in the Fig. 3 shown tool 16 is particularly suitable for surface grinding of larger areas, but can be used due to its construction with at least partially elastic support materials even in areas curved surfaces and workpieces.
  • the nominal diameter of the tool 16 may be about 150 mm in order to produce a fast work progress and a high grinding removal. This diameter is reflected in the design of the dimensions of the gear housing 22, which extends bell-shaped, starting from the tool 16. This space is used by the drive shaft 36, which thus claimed no significant additional space in the hand tool 10.
  • Fig. 4 is one of the Fig. 3 derived, but not to scale for this section through the coupling drive 30 shown in the gear head 14.
  • the coupling drive 30 is designed as a rocker arm.
  • the revolving crank is embodied by the eccentric portion 42 of the drive shaft 36.
  • the crank length that is, the eccentricity of the eccentric portion 42, is preferably about 1.0 to 2.0 mm, more preferably 1.25 mm.
  • the maximum crank stroke is twice the crank length.
  • the crank length is indicated by a double arrow marked 78.
  • the coupling member 32 connects, the coupling length by a designated 80 Arrow is indicated.
  • the coupling length can be about 22 to 30 mm, preferably the coupling length is about 26.5 mm.
  • a rocker connects, which is presently formed by the spindle pin 28 and the recorded on the tool spindle 24 driver 64.
  • the length of the rocker is indicated by a double arrow designated 82.
  • the swing length is about 20 to 28 mm, more preferably about 24 mm.
  • Another necessary determining variable of the coupling drive 30 is the axial distance between the spindle axis 26 and the drive shaft 38 indicated by a double arrow indicated by 84. This distance is preferably about 30 to 40 mm, more preferably about 35 mm.
  • pivoting angle With the exemplified configuration of the coupling drive 30 small pivoting angle can be effected, as they are particularly suitable for typical applications of the hand tool 10 according to the invention.
  • a pivoting angle of about ⁇ 3 ° results, a total of 6 °.
  • Such pivoting can be achieved with geometrically similar, so scaled interpretations of the rocker arm.
  • Such alternative designs can be used, for example, if reinforced components are required to transmit even greater power, or if the components are to be miniaturized for weight reduction.
  • crank length 78 and the swing arm length 82 are suitable for this purpose.
  • the coupling member 32 interacts permanently with the eccentric portion 42 of the drive shaft 36 and the spindle pin 28 of the tool spindle 24 together, in particular is permanently on the bearings 33, 34 to this.
  • a rattling during operation of the coupling drive 30, caused for example by unintentional release of individual members of the coupling drive 30 from each other, effectively avoided become.
  • a short-term interruption of the motion and power transmission associated with the rattling can also be avoided, whereby the performance of the hand tool 10 can increase.
  • FIGS. 7 and 8 A modified embodiment of a hand tool according to the invention is in the FIGS. 7 and 8 shown.
  • a mass balance is taken into account on the tool spindle 24.
  • This design can be provided in addition to the mass balance on the drive shaft 36 or alone.
  • the mass balance is realized by an offset region 65 in the form of a radial projection on the driver 64a.
  • This causes a mass displacement, which by the design of the driver arms 66, 68, the spindle pin 28 and the bearing 33 (see. Fig. 5 ) is directed contrary conditional mass arrangement.
  • the mass balance takes place to the effect that a resulting center of gravity has the smallest possible distance from the longitudinal axis 26 of the tool spindle 24, more preferably located on the longitudinal axis 26.
  • the offset portion 65 may be such a transverse axis 69 which intersects the longitudinal axis 26 and an axis through the spindle pin 28, that a countermass center of gravity thereby the transverse axis 69 is as close as possible or even coincides with this.
  • the design of the coupling member 32 can be taken into account in the mass balance.
  • the coupling member 32 is in operative relationship both with the tool spindle 24 and with the drive shaft 36.
  • part of the mass of the coupling member 32 that dynamically acts on the spindle pin 28 of the tool spindle 24 can be compensated by a corresponding counterweight in the offset portion 65.
  • the intended center of gravity of the coupling member partial mass does not lie on the transverse axis 69. Therefore, it may be advantageous to also space the counterweight center of mass in the opposite direction from the transverse axis 69. Accordingly, the offset region 65 can also be asymmetrical with respect to the transverse axis 69.
  • Another portion of the mass of the coupling member 32 may be compensated by mass balancers on the drive shaft 36, such as the cheek 40 or the thrust washer 44. Overall, a significant reduction in vibration can thus be achieved with little constructional effort.
  • a hand tool 10 which, with a simple, durable construction, can provide an effective oscillation drive, the pivot angle of which is particularly suitable for conventional applications, in particular grinding applications.
  • the pivot angle to be achieved by simple geometric changes can be varied within wide limits.
  • a relatively small eccentricity of the eccentric portion 42 of the drive shaft 36 is sufficient to cause sufficiently large pivot angle of the tool spindle 24.
  • the coupling drive 30, which "translates" the eccentric stroke of the drive shaft 36 particularly high in an oscillating angle resulting on the tool spindle 24.
  • the low eccentricity of the drive shaft 36 reduces the present at this mass imbalance. It is particularly preferred to provide a counterweight in the form of the cheek 40 for further minimization of mass imbalance or for vibration reduction on the drive shaft 36. Since already the eccentricity is small, just the cheek 40 requires only small additional masses to bring about a satisfactory mass balance. Overall, the weight of the arrangement can be kept small. For further vibration reduction, measures for balancing the mass can also be taken into account on the tool spindle 24.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
EP20110158200 2010-04-16 2011-03-15 Outil manuel Not-in-force EP2377647B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010015560A DE102010015560A1 (de) 2010-04-16 2010-04-16 Handwerkzeug

Publications (2)

Publication Number Publication Date
EP2377647A1 true EP2377647A1 (fr) 2011-10-19
EP2377647B1 EP2377647B1 (fr) 2012-12-12

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EP (1) EP2377647B1 (fr)
DE (1) DE102010015560A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108115621A (zh) * 2016-11-28 2018-06-05 罗伯特·博世有限公司 便携式工具机、工具接收部及用于振荡地驱动工具接收部的方法
US10137592B2 (en) 2013-05-06 2018-11-27 Milwaukee Electric Tool Corporation Oscillating multi-tool system
CN115070574A (zh) * 2022-06-30 2022-09-20 滁州市盛捷新材料有限公司 一种制冰槽表面加工装置
CN117961752A (zh) * 2024-04-01 2024-05-03 四川恒迪新材料集团有限公司 一种便于调节的墙板加工用抛光设备

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103894926A (zh) * 2012-12-28 2014-07-02 苏州宝时得电动工具有限公司 磨削动力工具

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DE3447828A1 (de) * 1984-12-29 1986-07-03 Walter Dipl.-Ing. 6908 Wiesloch Brunnenkant Motorisch antreibbarer schleifapparat
US4922612A (en) * 1988-06-16 1990-05-08 Henry E. Bruce Oscillatory saw
WO2003095862A1 (fr) * 2002-05-14 2003-11-20 Skf Autobalance Systems Ab Systeme et procede de compensation automatique des forces de resistance non equilibrees
EP1428625A1 (fr) 2002-12-13 2004-06-16 C. & E. FEIN GmbH Mécanisme d'entraínement oscillant
DE102006055523A1 (de) * 2006-11-24 2008-05-29 Robert Bosch Gmbh Schwenkpendelwerkzeug

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Publication number Priority date Publication date Assignee Title
DE3447828A1 (de) * 1984-12-29 1986-07-03 Walter Dipl.-Ing. 6908 Wiesloch Brunnenkant Motorisch antreibbarer schleifapparat
US4922612A (en) * 1988-06-16 1990-05-08 Henry E. Bruce Oscillatory saw
WO2003095862A1 (fr) * 2002-05-14 2003-11-20 Skf Autobalance Systems Ab Systeme et procede de compensation automatique des forces de resistance non equilibrees
EP1428625A1 (fr) 2002-12-13 2004-06-16 C. & E. FEIN GmbH Mécanisme d'entraínement oscillant
DE102006055523A1 (de) * 2006-11-24 2008-05-29 Robert Bosch Gmbh Schwenkpendelwerkzeug

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10137592B2 (en) 2013-05-06 2018-11-27 Milwaukee Electric Tool Corporation Oscillating multi-tool system
US10940605B2 (en) 2013-05-06 2021-03-09 Milwaukee Electric Tool Corporation Oscillating multi-tool system
US11724413B2 (en) 2013-05-06 2023-08-15 Milwaukee Electric Tool Corporation Oscillating multi-tool system
CN108115621A (zh) * 2016-11-28 2018-06-05 罗伯特·博世有限公司 便携式工具机、工具接收部及用于振荡地驱动工具接收部的方法
EP3330044A1 (fr) * 2016-11-28 2018-06-06 Robert Bosch GmbH Machine-outil portative
CN108115621B (zh) * 2016-11-28 2022-09-20 罗伯特·博世有限公司 便携式工具机、工具接收部及用于振荡地驱动工具接收部的方法
CN115070574A (zh) * 2022-06-30 2022-09-20 滁州市盛捷新材料有限公司 一种制冰槽表面加工装置
CN115070574B (zh) * 2022-06-30 2023-10-20 滁州市盛捷新材料有限公司 一种制冰槽表面加工装置
CN117961752A (zh) * 2024-04-01 2024-05-03 四川恒迪新材料集团有限公司 一种便于调节的墙板加工用抛光设备
CN117961752B (zh) * 2024-04-01 2024-06-07 四川恒迪新材料集团有限公司 一种便于调节的墙板加工用抛光设备

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DE102010015560A1 (de) 2011-12-15
EP2377647B1 (fr) 2012-12-12

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