EP2404702B1 - Schwingschleifer - Google Patents

Schwingschleifer Download PDF

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Publication number
EP2404702B1
EP2404702B1 EP11169235.6A EP11169235A EP2404702B1 EP 2404702 B1 EP2404702 B1 EP 2404702B1 EP 11169235 A EP11169235 A EP 11169235A EP 2404702 B1 EP2404702 B1 EP 2404702B1
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EP
European Patent Office
Prior art keywords
balancer
center
orbital sander
eccentric shaft
base
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
EP11169235.6A
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English (en)
French (fr)
Other versions
EP2404702A3 (de
EP2404702A2 (de
Inventor
Fumihide Sugita
Hirokazu Hagiwara
Yonosuke Aoki
Ryo Sunazuka
Yasumasa Nakane
Naoki Fujimatsu
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.)
Makita Corp
Original Assignee
Makita Corp
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Filing date
Publication date
Priority claimed from JP2010154911A external-priority patent/JP5539799B2/ja
Priority claimed from JP2010280698A external-priority patent/JP2012125897A/ja
Priority claimed from JP2010280697A external-priority patent/JP5520799B2/ja
Application filed by Makita Corp filed Critical Makita Corp
Publication of EP2404702A2 publication Critical patent/EP2404702A2/de
Publication of EP2404702A3 publication Critical patent/EP2404702A3/de
Application granted granted Critical
Publication of EP2404702B1 publication Critical patent/EP2404702B1/de
Active 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
    • B24B23/04—Portable grinding machines, e.g. hand-guided; Accessories therefor with oscillating 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
    • B24B41/04—Headstocks; Working-spindles; Features relating thereto
    • B24B41/042—Balancing mechanisms

Definitions

  • the present invention relates to an orbital sander including a base that is provided below a main body including a motor and that performs orbital motion through rotation of the motor.
  • a rotary shaft projects below a main body including a motor, and a base is coupled via two bearings that are upper and lower bearings to an eccentric shaft provided at the lower end of the rotary shaft.
  • a balancer is provided at the lower end of the eccentric shaft to project to a side opposite the side of eccentricity of the eccentric shaft.
  • the balancer rotates along with the orbital motion of the base to produce a centrifugal force in order to reduce vibration of the main body.
  • the balancer is made of a single material such as die-cast zinc or sintered iron, and accordingly the overall weight of the balancer is heavy, and the degree of freedom in designing the position of the center of gravity and the weight is low. Therefore, the size of the balancer is increased to produce a centrifugal force required to reduce vibration along with the size of the orbital sander, which may incur an increase in weight.
  • This object can be achieved by providing an orbital sander according to claim 1.
  • an orbital sander in which a main body including a motor is provided with a rotary shaft that is rotatable by driving the motor and an eccentric shaft that is positioned eccentrically with respect to a center of rotation of the rotary shaft and that performs circular orbital motion along with rotation of the rotary shaft, and a portion of the eccentric shaft that projects downward from the main body is provided with a base coupled via two bearings that are upper and lower bearings and a balancer projecting to a side opposite a side of eccentricity of the eccentric shaft, in which the center of gravity of the base is positioned between the two upper and lower bearings.
  • rotary shaft refers to a spindle as the final rotary shaft for a product with speed reduction through gears, and to a motor shaft for a product with no speed reduction through gears (so-called “motor direct drive”).
  • a second aspect provides the orbital sander according to the first aspect, in which the balancer is provided above the lower bearing.
  • a third aspect provides the orbital sander according to the second aspect, in which an outer portion of the balancer is formed to be bent downward.
  • a fourth aspect provides the orbital sander according to any one of the first to third aspects, in which the balancer is connected using a key to a portion of the eccentric shaft located between the two upper and lower bearings, and a clearance is provided between upper and lower ends of the key and the two upper and lower bearings, respectively.
  • a fifth aspect provides the orbital sander according to the fourth aspect, in which the key is disposed on a line in a direction of eccentricity of the eccentric shaft as seen from an axial direction of the eccentric shaft.
  • a sixth aspect provides the orbital sander according to any one of the first to fifth aspects, in which a retainer that holds the lower bearing is fixed to a lower end of the eccentric shaft by a screw provided at the center of rotation of the rotary shaft.
  • the balancer projects downward such that a lower end of the balancer is positioned between a center of the lower bearing and a lower surface of the base in an up-down direction.
  • the balancer is formed by combining a plurality of members with each other, and for at least some of the plurality of combined members, a member located farther from a center of the rotary shaft or the eccentric shaft is formed from a material that is higher in specific gravity than a material forming a member located closer to the center.
  • the lower bearing in addition to the effect of the first aspect, can be positioned close to the lower end of the base. Therefore, the distance between the two upper and lower bearings can be secured to suitably support the eccentric shaft at two points.
  • the center of gravity of the balancer can be aligned with the center of gravity of the base, which enables more stable orbital motion.
  • the key does not interfere with the bearings to incline the bearings during assembly of the key, which prevents deterioration in balance.
  • the radial dimension of the balancer can be reduced by extending the balancer downward. Therefore, projection of the balancer in the radial direction can be suppressed to achieve a reduction in overall size.
  • the centrifugal force is defined by weight x turning radius x angular speed 2 , and therefore the weight of the balancer can be reduced by providing the balancer at a position at which the turning radius of the balancer is large.
  • FIG. 1 is a longitudinal cross-sectional view showing an example of an orbital sander.
  • An orbital sander 1 includes a base 5 formed in a rectangular shape as viewed in plan and provided below a main body 2 housing a motor 3 facing downward.
  • a gear 10 provided at the upper end of the spindle 7 meshes with a pinion of the output shaft 4.
  • Reference numeral 11 denotes a handle provided to project from a side surface of the housing 6 and including a switch 12 and a trigger 13.
  • Reference numeral 14 denotes a discharge nozzle that discharges dust.
  • a lower portion of the spindle 7 that projects from the housing 6 is formed as an eccentric shaft 7A that is eccentric with respect to the center of rotation of an upper portion of the spindle 7.
  • the center portion of the base 5 is rotatably coupled to the lower end of the eccentric shaft 7A via a ball bearing 15 serving as a lower bearing.
  • the ball bearing 15 is held in a cylindrical boss 16 provided to project from the center portion of the base 5.
  • a bearing retainer 17 in the shape of a deep dish that is circular as viewed in plan is provided on the upper surface of the base 5.
  • the downwardly facing opening edge of the bearing retainer 17 is fixed to the base 5 by a plurality of screws 19, 19, ....
  • Reference numeral 20 denotes a retainer attached to the lower end of the eccentric shaft 7A by a countersunk screw 21 to hold the lower end of the ball bearing 15.
  • the countersunk screw 21 is screwed coaxially with the center of rotation of the spindle 7.
  • a through hole 22 for the countersunk screw 21 in the retainer 20 has a stepped shape formed by a tapered portion 23 with which the head portion of the countersunk screw 21 is fitted and an equal diameter portion 24 through which the threaded portion of the countersunk screw 21 passes. This prevents the countersunk screw 21 from projecting from the lower surface of the retainer 20 while securing the thickness (strength) of the retainer 20.
  • a clearance hole 25 that facilitates screwing of the countersunk screw 21 is formed in a portion of the base 5 that opposes the retainer 20. In spite of the presence of the clearance hole 25, the lower surface of the retainer 20 is set to be positioned above the lower surface of the base 5.
  • a pad 26 generally in the same shape as the base 5 is provided on the lower surface of the base 5.
  • Sanding paper can be provided in a tensioned state on the lower surface of the pad 26 through clamp mechanisms 27, 27 provided at both ends of the base 5 in the longitudinal direction.
  • a rubber sleeve 28 in the shape of cylindrical bellows is provided to extend between an opening at the lower end of the housing 6 and the upper surface of the base 5 including the bearing retainer 17.
  • the rubber sleeve 28 restricts rotation of the base 5 about the eccentric shaft 7A.
  • a balancer 29 is connected using a key 30 to a portion of the eccentric shaft 7A located between the ball bearings 18, 15. As also shown in FIG. 3 , the balancer 29 is formed by combining two members, namely an inner member 31 connected to the eccentric shaft 7A and an outer member 32 coupled to the inner member 31.
  • the inner member 31 is made of aluminum (specific gravity: 2.7) with a relatively low specific gravity, and includes a tubular portion 33 externally mounted on the eccentric shaft 7A to be integrally connected to the eccentric shaft 7A using the key 30, and a pair of arms 34, 34 provided to project from the tubular portion 33 in radial directions that are different from each other.
  • the angle between the arms 34, 34 is generally 90°.
  • a clearance C is provided between the upper and lower ends of the key 30 and the ball bearings 18, 15, respectively.
  • the clearance C prevents the ball bearings 18, 15 from being inclined during assembly of the key 30.
  • the key 30 is disposed on a line in the direction of eccentricity of the eccentric shaft 7A as seen from the axial direction of the eccentric shaft 7A to maintain the balance.
  • the outer member 32 is made of brass (specific gravity: 8.4) with a higher specific gravity than the inner member 31, and has a semi-circular shape as viewed in plan.
  • the arms 34, 34 are coupled to the upper surface of the outer member 32 by screws 35, 35 so that the outer member 32 forms a downwardly projecting portion. In this state, the lower end of the outer member 32 is positioned between the center of the lower ball bearing 15 and the lower surface of the base 5.
  • Reference numeral 36 denotes a spacer made of a resin and interposed between each arm 34 and the outer member 32.
  • a portion of the outer member 32 located between the arms 34, 34 forms a thick portion 37 projecting upward with respect to both ends of the outer member 32.
  • the tubular portion 33 of the balancer 29 contacts the upper and lower ball bearings 18, 15 to function as a spacer that keeps the gap between the ball bearings 18, 15.
  • a recessed portion 38 in a ring shape matching the rotational orbit of the outer member 32 is provided to be recessed in the upper surface of the base 5.
  • the outside inwardly facing surface of the recessed portion 38 forms a rising portion 39 that closely conforms to the outer surface of the outer member 32.
  • the opening edge of the bearing retainer 17 is connected to the rising portion 39 through spigot joint to secure the attachment precision of the bearing retainer 17.
  • a center of gravity P of the base 5 is positioned between the ball bearings 18, 15 (between the respective centers thereof).
  • the balancer 29 is shaped to be bent downward as a whole. Accordingly, the center of gravity of the balancer 29 can be aligned with the center of gravity P of the base 5.
  • the ball bearing 15 With the balancer 29 positioned above the lower ball bearing 15, the ball bearing 15 can be positioned close to the lower end of the base 5.
  • the balancer 29 performs rotational motion on the side opposite the base 5, which produces a centrifugal force to reduce vibration along with the orbital motion of the base 5.
  • the center of gravity P of the base 5 is positioned between the ball bearings 18, 15.
  • the outer member 32 is made of brass, which has a higher specific gravity than the inner member 31.
  • the outer member 32 projects in the up-down direction to secure a required mass as described above.
  • the outer member 32 is not excessively large in the radial direction, and a portion around the eccentric shaft 7A including the bearing retainer 17 can be made compact.
  • the center of gravity P of the base 5 is positioned between the two upper and lower ball bearings 18, 15.
  • inclination of the eccentric shaft 7A along with the orbital motion of the base 5 can be effectively suppressed to reduce generation of vibration.
  • the ball bearing 15 can be positioned close to the lower end of the base 5. Therefore, the distance between the ball bearings 18, 15 can be secured to suitably support the eccentric shaft 7A at two points.
  • the center of gravity of the balancer 29 can be aligned with the center of gravity P of the base 5, which enables more stable orbital motion.
  • the balancer 29 is key-connected to a portion of the eccentric shaft 7A located between the upper and lower ball bearings 18, 15, and the clearance C is provided between the upper and lower ends of the key 30 and the ball bearings 18, 15, respectively.
  • the key 30 does not interfere with the ball bearings 18, 15 to incline the ball bearings 18, 15 during assembly of the key 30, which prevents deterioration in balance.
  • the key 30 is positioned on a line in the direction of eccentricity of the eccentric shaft 7A as seen from the axial direction of the eccentric shaft 7A, and the countersunk screw 21 for attaching the retainer 20 is provided at the center of rotation of the spindle 7.
  • the balancer 29 is coupled to the eccentric shaft 7A at a position above the ball bearing 15, and the balancer 29 projects downward such that the lower end of the balancer 29 is positioned between the center of the ball bearing 15 and the lower surface of the base 5 in the up-down direction.
  • the radial dimension of the balancer 29 can be reduced by extending the balancer 29 downward. Therefore, projection of the balancer 29 in the radial direction can be suppressed to achieve a reduction in overall size.
  • a portion of the base 5 that holds the ball bearing 15 is formed as the cylindrical boss 16 extending upward, and the inner surface of the outer member 32 of the balancer 29 is formed in an arcuate shape, as viewed in plan, that closely conforms to the outer surface of the boss 16.
  • the outer surface of the outer member 32 of the balancer 29 is formed in an arcuate shape as viewed in plan, the recessed portion 38 in a ring shape matching the rotational orbit of the outer member 32 is formed in the upper surface of the base 5, and the outside inwardly facing surface of the recessed portion 38 forms the rising portion 39 located close to the outer surface of the outer member 32.
  • the gap between the balancer 29 and the base 5 is not increased even if the balancer 29 is provided with the outer member 32 projecting downward.
  • the clearance hole 25 is formed in a portion of the base 5 that opposes the retainer 20, and the lower surface of the retainer 20 is positioned above the lower surface of the base 5.
  • the clearance hole 25 also facilitates screwing of the retainer 20 or the like.
  • the retainer 20 is attached to the eccentric shaft 7A by the countersunk screw 21, and the through hole 22 for the countersunk screw 21 in the retainer 20 has a stepped shape formed by the tapered portion 23 with which the head portion of the countersunk screw 21 is fitted and the equal diameter portion 24 through which the threaded portion of the countersunk screw 21 passes.
  • the balancer 29 contacts the upper and lower ball bearings 18, 15.
  • the balancer 29 can be utilized as a spacer between the ball bearings 18, 15, and the dimension in the up-down direction can be minimized even if the two ball bearings 18, 15 are provided.
  • the upper ball bearing 18 is held by the bearing retainer 17, the downwardly facing opening edge of which is attached to the upper surface of the base 5, and the bearing retainer 17 is formed in the shape of a circle as viewed in plan with the inner surface of the bearing retainer 17 located close to the outer surface of the outer member 32 of the balancer 29.
  • the ball bearing 18 can be held with a compact configuration with no wasted space in the radial direction.
  • the balancer 29 is formed by combining the inner member 31 and the outer member 32 with each other, and of both the members, the outer member 32, which is located farther from the center of the eccentric shaft 7A, is formed from a material that is higher in specific gravity than the material forming the inner member 31, which is located closer to the center.
  • the degree of freedom can be enhanced in designing the position of the center of gravity and the weight, and a centrifugal force required to reduce vibration can be effectively produced.
  • the inner member 31 is provided with the pair of arms 34, 34 projecting from the center of the eccentric shaft 7A in radial directions that are different from each other, and the outer member 32 is connected to the arms 34, 34.
  • the inner member 31 can be connected to the outer member 32 with a minimum necessary additional component and without increasing the weight of the inner member 31.
  • a portion of the outer member 32 that is interposed between the pair of arms 34, 34 is formed as the thick portion 37 which is thicker than other portions in the axial direction of the eccentric shaft 7A.
  • the position of the center of gravity and the weight can be set easily by the outer member 32 formed with the thick portion 37.
  • the bearings for the eccentric shaft are not limited to a ball bearing, and other types of bearings such as a needle bearing may also be used.
  • the material of the inner member of the balancer is not limited to aluminum, and other materials with a specific gravity of 3 or less such as a magnesium alloy (specific gravity: 1.81) and a resin (specific gravity: 1.5 or less) may also be used.
  • a specific gravity of 3 or less such as a magnesium alloy (specific gravity: 1.81) and a resin (specific gravity: 1.5 or less) may also be used.
  • other materials with a specific gravity of 6 or more such as die-cast zinc (specific gravity: 6.6), copper alloys other than brass such as bronze (specific gravity: 8.4), iron (specific gravity: 7.85), lead (specific gravity: 11.4), tungsten (specific gravity: 19.3), and high specific-gravity resins may also be used.
  • the structure for connection between the inner member and the outer member may be appropriately selected from insert molding, press fitting, crimping, welding, and so forth besides screwing described above.
  • the respective specific structures of the inner member and the outer member may be appropriately changed in accordance with various conditions such as a required centrifugal force.
  • the spacer may be omitted, the number of the arms may be increased or reduced, and/or the arms may be replaced with a fan-shaped coupling portion.
  • the balancer is not necessarily composed of two members, and may be composed of three or more members combined with each other. In this case, it is sufficient to set the magnitude relationship in specific gravity by changing the materials of at least some of the combined members. For example, it is considered to determine the materials of the members such that the specific gravity of the materials of the members becomes gradually higher as the member is located farther from the center of the eccentric shaft, to change the material of a group of a plurality of members located closer to the center and the material of a group of a plurality of members located farther from the center in order to set the magnitude relationship in specific gravity, to change the materials of a plurality of members positioned between the innermost side and the outermost side with respect to the center in order to set the magnitude relationship, or the like.
  • the inner member and the outer member themselves may be divided into a plurality of components.
  • the members may be composed of a plurality of plate-like bodies stacked in the up-down thickness direction to be connected, which enhances the degree of freedom in designing the weight or the like of each of the members.
  • the balancer may be integral and undividable into a plurality of members.
  • the retainer may be attached by a component other than the countersunk screw, and the balancer and the bearings may be supported using a structure other than key connection or the retainer.
  • an eccentric sleeve may be externally mounted at the lower end of a non-eccentric spindle to form an eccentric shaft, and the base may be coupled to the eccentric shaft, and a bar-like foot may be provided to extend between the housing and the base in place of the rubber sleeve.
  • the present invention may also be applied to a random orbital sander in which the base itself rotates in addition to performing circular orbital motion.
  • the balancer is provided to the motor shaft, the magnitude relationship in specific gravity of a plurality of members may be set with respect to the center of the motor shaft.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)

Claims (16)

  1. Schwingschleifmaschine, in welcher ein Hauptkörper (2), der einen Motor (3) enthält, mit einer Drehwelle, die durch Antreiben des Motors (3) drehbar ist, und einer exzentrischen Welle (7A), die exzentrisch mit Bezug auf ein Drehzentrum der Drehwelle positioniert ist und die eine kreisförmige Orbitalbewegung einher mit einer Drehung der Drehwelle ausführt, und ein Teil der exzentrischen Welle (7A), der nach unten von dem Hauptkörper (2) vorsteht, ist mit einer Basis (5) vorgesehen, die mittels zweier Lager, die ein oberes Lager und ein unteres Lager (18), (15) sind, gekoppelt ist, und einem Ausgleichsbauteil (29) vorgesehen ist, das zu einer Seite vorsteht, die einer Seite der Exzentrizität der exzentrischen Welle (7A) gegenüberliegt, dadurch gekennzeichnet, dass
    der Schwerpunkt der Basis (5) zwischen den zwei oberen und unteren Lager (18), (15) angeordnet ist.
  2. Schwingschleifmaschine nach Anspruch 1, bei der
    das Ausgleichsbauteil (29) oberhalb des unteren Lagers (15) vorgesehen ist.
  3. Schwingschleifmaschine nach Anspruch 2, bei der
    ein äußerer Teil (32) des Ausgleichsbauteils (29) so ausgebildet ist, dass es nach unten gebogen ist.
  4. Schwingschleifmaschine nach einem der Ansprüche 1 bis 3, bei der
    das Ausgleichsbauteil (29) unter Verwendung einer Passfeder (30) mit einem Teil der exzentrischen Welle (7A), der sich zwischen den zwei oberen und unteren Lager (18), (15) befindet, verbunden ist, und ein Zwischenraum zwischen dem oberen und dem unteren Ende der Passfeder (30) und den zwei oberen und unteren Lager (18), (15) jeweils vorgesehen ist.
  5. Schwingschleifmaschine nach Anspruch 4, bei der
    die Passfeder (30) von einer axialen Richtung der exzentrischen Welle (7A) gesehen auf einer Linie in einer Richtung der Exzentrizität der exzentrischen Welle (7A) angeordnet ist.
  6. Schwingschleifmaschine nach einem der Ansprüche 1 bis 5, bei der
    eine Halterung (20), die das untere Lager (15) hält, an ein unteres Ende der exzentrischen Welle (7A) durch eine Schraube fixiert ist, die in dem Drehzentrum der Drehwelle vorgesehen ist.
  7. Schwingschleifmaschine nach einem der Ansprüche 1 bis 6, bei der
    das Ausgleichsbauteil (29) nach unten vorsteht, so dass ein unteres Ende des Ausgleichsbauteils (29) zwischen einem Zentrum des unteren Lagers (15) und einer unteren Oberfläche der Basis (5) in einer Oben-Unten-Richtung positioniert ist.
  8. Schwingschleifmaschine nach Anspruch 7, bei der
    ein Teil der Basis (5), der das untere Lager (15) hält, in einer Form eines Zylinders, der nach oben vorsteht, ausgebildet ist, und eine innere Oberfläche eines Teils des Ausgleichsbauteiles (29), das nach unten vorsteht, in einer Bogenform ausgebildet ist, die in einer Draufsicht gesehen nahezu einer äußeren Oberfläche des Halteteils entspricht.
  9. Schwingschleifmaschine nach Anspruch 7 oder 8, bei der
    eine äußere Oberfläche des vorstehenden Teils des Ausgleichstücks (29) in der Draufsicht gesehen in einer Bogenform ausgebildet ist, ein ausgenommener Teil (38) in einer Ringform, die der Drehumlaufbahn des vorspringenden Teils entspricht, in einer oberen Oberfläche der Basis (5) ausgebildet ist, und eine äußere nach innen zeigende Oberfläche des ausgenommenen Teils (38) einen hochstehenden Teil (39) ausbildet, der nahe der äußeren Oberfläche des vorstehenden Teils liegt.
  10. Schwingschleifmaschine nach Anspruch 6, bei der
    ein Durchgangsloch (25) in einem Teil der Basis (5) ausgebildet ist, der der Halterung (20) gegenüberliegt, und eine untere Oberfläche der Halterung (20) ist oberhalb einer unteren Oberfläche der Basis (5) positioniert.
  11. Schwingschleifmaschine nach Anspruch 6 oder 10, bei der
    die Halterung (20) an die exzentrische Welle (7A) durch eine Senkschraube (21) angebracht ist, und ein Durchgangsloch (22) für die Senkschraube (21) in der Halterung (20) eine abgestufte Form aufweist, die durch einen kegelförmigen Teil (23), in welchen ein Kopfteil der Senkschraube (21) gepasst ist, und einem Teil mit gleichmäßigen Durchmesser (24) ausgebildet ist, durch welchen ein Gewindeteil der Senkschraube (21) passiert.
  12. Schwingschleifmaschine nach einem der Ansprüche 7 bis 11, bei der
    das Ausgleichsbauteil (29) sowohl das obere als auch das untere Lager (18), (15) berührt.
  13. Schwingschleifmaschine nach Anspruch 12, bei der
    das obere Lager (18) durch eine Lagerhalterung (17) gehalten ist, eine nach unten gerichtete Öffnungskante von dieser an die obere Oberfläche der Basis (5) angebracht ist und die Lagerhalterung (17) in der Draufsicht gesehen in einer Form eines Kreises mit einer inneren Oberfläche der Lagerhalterung (17) nahe der äußeren Oberfläche des vorspringenden Teils des Ausgleichsbauteils (29) befindlich, ausgebildet ist.
  14. Schwingschleifmaschine nach einem der Ansprüche 1 bis 13, bei der
    das Ausgleichsbauteil (29) durch Kombinieren einer Mehrzahl von Bauteilen miteinander ausgebildet ist, und zumindest für einige der Mehrzahl der kombinierten Bauteile ein Bauteil, das sich weiter weg von einem Drehzentrum der Drehwelle oder der exzentrischen Welle (7A) befindet, aus einem Material ausgebildet ist, das ein höheres spezifisches Gewicht ein Material aufweist, das ein Bauteil ausbildet, das näher zu dem Zentrum liegt, bei der bevorzugt das Bauteil, das näher zu dem Zentrum liegt, aus einem Material mit einem spezifischen Gewicht von 3 oder weniger ausgebildet ist, und das Bauteil, das weiter weg von dem Zentrum liegt, aus einem Material mit einem spezifischen Gewicht von 6 oder mehr ausgebildet ist.
  15. Schwingschleifmaschine nach Anspruch 14, bei der
    die Mehrzahl der Bauteile ein inneres Bauteil (31), das näher zu dem Zentrum liegt, und ein äußeres Bauteil (32) enthält, das weiter weg von dem Zentrum liegt, bei der das innere Bauteil (31) mit einem Paar von Armen (34), (34) vorgesehen ist, wobei die Arme von dem Zentrum in radialen Richtungen, die unterschiedlich voneinander sind, vorstehen, und das äußere Bauteil (32) an die Arme (34), (34) verbunden ist.
  16. Schwingschleifmaschine nach Anspruch 15, bei der
    ein Teil des äußeren Bauteils (32), das zwischen dem Paar der Arme (34) eingefügt ist, als ein dicker Teil (37) ausgebildet ist, der dicker als andere Teile in einer axialen Richtung der exzentrischen Welle (7A) ist.
EP11169235.6A 2010-07-07 2011-06-09 Schwingschleifer Active EP2404702B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2010154911A JP5539799B2 (ja) 2010-07-07 2010-07-07 オービタルサンダ
JP2010280698A JP2012125897A (ja) 2010-12-16 2010-12-16 オービタルサンダ
JP2010280697A JP5520799B2 (ja) 2010-12-16 2010-12-16 オービタルサンダ

Publications (3)

Publication Number Publication Date
EP2404702A2 EP2404702A2 (de) 2012-01-11
EP2404702A3 EP2404702A3 (de) 2013-12-18
EP2404702B1 true EP2404702B1 (de) 2015-05-27

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RU (1) RU2011127850A (de)

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JP6972556B2 (ja) * 2017-01-10 2021-11-24 株式会社ジェイテクト 研削加工装置及び研削加工方法
JP7117832B2 (ja) * 2017-07-24 2022-08-15 京セラインダストリアルツールズ株式会社 ポリッシャ
EP3501753B1 (de) * 2017-12-21 2021-03-31 Guido Valentini Handgeführtes elektrisches oder pneumatisch angetriebenes werkzeug

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06226709A (ja) * 1993-01-29 1994-08-16 Makita Corp 電動工具の集塵装置
DE102004047808A1 (de) * 2004-09-29 2006-03-30 Robert Bosch Gmbh Schleifhandwerkzeugmaschine, insbesondere Akkuschleifhandwerkzeugmaschine
JP5039574B2 (ja) * 2008-01-11 2012-10-03 リョービ株式会社 バッテリー付き電動工具

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