EP0230621B1 - Exzenterschleifer mit einer Vorrichtung zum Verändern der Schleifbewegung - Google Patents

Exzenterschleifer mit einer Vorrichtung zum Verändern der Schleifbewegung Download PDF

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Publication number
EP0230621B1
EP0230621B1 EP19860117679 EP86117679A EP0230621B1 EP 0230621 B1 EP0230621 B1 EP 0230621B1 EP 19860117679 EP19860117679 EP 19860117679 EP 86117679 A EP86117679 A EP 86117679A EP 0230621 B1 EP0230621 B1 EP 0230621B1
Authority
EP
European Patent Office
Prior art keywords
frictional
toothed
housing
grinding wheel
toothed rings
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.)
Expired - Lifetime
Application number
EP19860117679
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0230621A3 (en
EP0230621A2 (de
Inventor
Manfred Ing. Stäbler
Walter Barth
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
Publication of EP0230621A2 publication Critical patent/EP0230621A2/de
Publication of EP0230621A3 publication Critical patent/EP0230621A3/de
Application granted granted Critical
Publication of EP0230621B1 publication Critical patent/EP0230621B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B23/00—Portable grinding machines, e.g. hand-guided; Accessories therefor
    • B24B23/02—Portable grinding machines, e.g. hand-guided; Accessories therefor with rotating grinding tools; Accessories therefor
    • B24B23/03—Portable grinding machines, e.g. hand-guided; Accessories therefor with rotating grinding tools; Accessories therefor the tool being driven in a combined movement

Definitions

  • the invention is based on an eccentric sander according to the preamble of claim 1.
  • Such an eccentric sander is available on the market and published in print in "Technical reports for metalworking” on April 3, 1983 under the title “Rotex”
  • the new dimension of grinding means that an optimal adaptation of such an eccentric grinder to practical requirements is not yet possible.
  • the jump between real coarse grinding and fine grinding is too big.
  • a further gear stage with changed diameters of the friction or gear wheels is to remedy this defect to provide, but this is only conceivable in the known manner with a considerable enlargement of the gear part of the eccentric sander.
  • the eccentric sander according to the invention with the characterizing features of claim 1 has the advantage of optimal grinding performance with an extremely compact design and simple gear structure.
  • the friction or toothed rings can be arranged close to one another and can be made to roll alternately in a space-saving manner by friction or toothed rings engaging between them on the housing.
  • the third grinding movement which produces the finest grinding, can be easily achieved by an intermediate position in which the eccentric does not necessarily roll.
  • the grinding movement he creates follows a cycloid with a superimposed rotary movement that depends on the pressure.
  • the path of the individual abrasive grains per revolution of the eccentric is the smallest here.
  • the diameter of the external friction or toothed ring connected to the grinding plate is smaller than the diameter of the internal friction or toothed ring connected to the grinding plate, and that the difference in the effective diameters of these friction or toothed rings is the difference between the effective diameters of the Friction or sprockets on the housing plus four times the eccentricity of the eccentric corresponds. This results in a particularly space-saving possibility of arranging the contact points for the two positive gear connections offset by 180 ° from one another.
  • FIG. 1 shows a section through an eccentric grinder equipped according to the invention in the gearbox and grinding plate area
  • FIG. 2 shows a partial section II-II to FIG. 1
  • FIG. 3 shows a section through an eccentric grinder equipped according to another exemplary embodiment, like FIG. 1 and
  • FIG. 4 shows a partial section IV -IV to Figure 3.
  • an eccentric grinder 1 has a housing 2 which forms a bell 3.
  • a motor is housed, of which only the drive shaft 4 is shown.
  • This drive shaft 4 protrudes into the interior of the bell 3 and carries an intermediate piece 5.
  • the intermediate piece 5 is designed as a crank and has a cylindrical recess 6 located eccentrically to the drive shaft 4.
  • the eccentricity that is to say the distance between the axis of the drive shaft 4 and the center axis of the recess 6 is denoted by x.
  • two ball bearings 7 are inserted, which receive a support pin 8 for a grinding plate 9.
  • a pot-shaped rotating part 10, a spring washer 11 and a screw 13 screwed into a threaded bore 12 in the support pin 8 serve to fix the grinding plate 9 on the support pin 8.
  • a soft-elastic covering 14 is glued onto the outer end face of the grinding plate 9, which is to accommodate the actual one Sanding sheet 15 is used.
  • the grinding plate 9 On its inner end face, the grinding plate 9 has a double toothed ring 16, which is aligned concentrically with the longitudinal axis of the support pin 8 and thus eccentrically with the drive shaft 4.
  • the Double sprocket 16 has an inner sprocket 17 and an outer sprocket 18.
  • Both sprockets are axially offset from one another, so that a gap remains in the axial direction between them, into which a double sprocket 19 with an outer sprocket 20 and an inner sprocket 21 can engage.
  • This double ring gear 19 is formed as an end flange of a sleeve 22 concentrically providing the drive shaft 4.
  • This sleeve 22 is guided in a housing-fixed ring 23 which has two slots 24 and 25 running in the direction of a helical line. Pins 26 and 27 protrude into these slots. These pins 26 and 27 are fastened in bores in the sleeve 22 and each carry a slide ring 28. They are both secured with locking washers 29.
  • a knurled nut 31 is screwed on as a handle. 32 with a connection piece is designated, with the suction paths 33 arranged inside the bell 3 can be connected to a dust extraction device.
  • a double arrow 34 in FIG. 1 indicates the axial mobility of the sleeve 22 within the bell 3.
  • a double arrow 35 in FIG. 2 illustrates the actuating movement which can be carried out with the aid of the knurled nut 31 for changing over the grinding movements.
  • each abrasive grain of the abrasive sheet 15 fastened on the grinding plate 9 describes a pericycloid in which the rotational movement corresponds to the direction of rotation of the eccentric. This means that the path of the abrasive grains is the largest per revolution of the eccentric.
  • a double toothed ring 36 is used instead of the double toothed ring 16 and two separate toothed rings, an outer toothed ring 37 and an inner toothed ring 38 are used instead of the double toothed ring 19.
  • the double ring gear 36 has an inner ring gear 39 and an outer ring gear 40 in one plane.
  • a ring 41 which is inserted into the bell 3 and which directly supports this outer ring gear 37 serves as a guide for the outer ring gear 37.
  • An intermediate sleeve 42 is inserted between the outer ring gear 37 and the inner ring gear 38. This intermediate sleeve 42 thus serves as a guide for the inner ring gear 38.
  • Both the intermediate sleeve 42 and the bell 3 have slots 43 running in their circumferential direction.
  • the outer ring gear 37 and the inner ring gear 38 have two slots 44 and 45 provided with an opposite pitch.
  • a bolt 46 engages, the knurled nut 31 diametrically opposite, one of the slots 43 in the intermediate sleeve 42 and one of the slots 44 and 45 in the outer ring gear 37 and in the inner ring gear 38, respectively.
  • the bolt 46 is secured by axial lock washers 29.
  • a bolt 47 penetrates next to one of the slots 43 in the intermediate sleeve 42 and one of the slots 44 and 45 the slot in the bell 3, also designated 43.
  • the bolt 47 is provided with a screw thread at its outwardly projecting end. Like the bolt 27, it carries the knurled nut 31.
  • Embodiment according to Figures 1 and 2 described gear connection for rough grinding. If the bolt 47 is adjusted to a middle position, any transmission connection between one of the outer ring gears and one of the inner ring gears is omitted. The position for fine grinding results, as has also already been described for the exemplary embodiment according to FIGS. 1 and 2. If the operator adjusts to the other end position with the aid of the knurled nut 31, the inner ring gear 38 engages in the outer ring gear 40. The gear connection is thus established, with which an average grinding is achieved. It can be seen that the outer ring gear 37 and the inner ring gear 38 perform an opposite axial movement when adjusted by means of the knurled nut 31. The grinding results are the same as when using the eccentric grinder according to FIGS. 1 and 2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
EP19860117679 1986-01-29 1986-12-18 Exzenterschleifer mit einer Vorrichtung zum Verändern der Schleifbewegung Expired - Lifetime EP0230621B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3602571A DE3602571C2 (de) 1986-01-29 1986-01-29 Exzentertellerschleifer mit einer Vorrichtung zum Verändern der Schleifbewegung
DE3602571 1986-01-29

Publications (3)

Publication Number Publication Date
EP0230621A2 EP0230621A2 (de) 1987-08-05
EP0230621A3 EP0230621A3 (en) 1988-07-13
EP0230621B1 true EP0230621B1 (de) 1991-03-06

Family

ID=6292833

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19860117679 Expired - Lifetime EP0230621B1 (de) 1986-01-29 1986-12-18 Exzenterschleifer mit einer Vorrichtung zum Verändern der Schleifbewegung

Country Status (4)

Country Link
US (1) US4727682A (ja)
EP (1) EP0230621B1 (ja)
JP (1) JPH0710490B2 (ja)
DE (2) DE3602571C2 (ja)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3625535C2 (de) * 1986-07-29 1994-05-11 Festo Kg Exzentertellerschleifer
DE3642741A1 (de) * 1986-12-13 1988-06-23 Bosch Gmbh Robert Exzenterschleifer
DE3809930A1 (de) * 1988-03-24 1989-10-05 Bosch Gmbh Robert Exzenterschleifer
DE3942301C1 (ja) * 1989-12-21 1991-02-14 Robert Bosch Gmbh, 7000 Stuttgart, De
GB9123502D0 (en) * 1991-11-06 1992-01-02 Black & Decker Inc Sanding apparatus
JP3063872B2 (ja) * 1992-06-08 2000-07-12 株式会社マキタ 研磨機
DE4233729A1 (de) * 1992-10-07 1994-04-14 Bosch Gmbh Robert Exzentertellerschleifer mit Schleiftellerbremse
DE4233728A1 (de) * 1992-10-07 1994-04-14 Bosch Gmbh Robert Exzentertellerschleifer
US5518442A (en) 1993-01-22 1996-05-21 Porter-Cable Corporation Sander
US5392568A (en) * 1993-12-22 1995-02-28 Black & Decker Inc. Random orbit sander having braking member
US5580302A (en) * 1994-02-28 1996-12-03 Black & Decker Inc. Random orbit sander having air directing baffle
US5941765A (en) * 1996-11-19 1999-08-24 Porter Cable Corporation Sander
US6213851B1 (en) 1998-07-07 2001-04-10 Delta International Machinery Corp. Abrading apparatus
DE19963831B4 (de) * 1999-12-30 2006-04-06 Robert Bosch Gmbh Exzentertellerschleifer mit einem Gehäuse
US8100745B2 (en) * 2007-03-16 2012-01-24 Black & Decker Inc. Low vibration sander with a flexible top handle
US20100009608A1 (en) * 2008-07-08 2010-01-14 Lo Ping-Hsiang Electric polishing gun
US10414014B2 (en) 2017-09-19 2019-09-17 Campbell Hausfeld, Llc Multifunction rotary tool including driveshaft
US10603760B2 (en) 2017-09-19 2020-03-31 Campbell Hausfeld, Llc Multifunction rotary tool including hub

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2794303A (en) * 1955-06-16 1957-06-04 David R Wickes Power-driven hand tool
US3482362A (en) * 1966-01-28 1969-12-09 Ingersoll Rand Co Double acting sander head
US3857206A (en) * 1973-03-08 1974-12-31 Nat Detroit Inc Co Compound motion rubbing machine
JPS5454035A (en) * 1977-10-06 1979-04-27 Canon Inc Image formation
JPS55150964A (en) * 1979-05-04 1980-11-25 Kinichi Takeuchi Grinding device capable of performing combined motion of rotation and circular motion
JPS5627773A (en) * 1979-08-09 1981-03-18 Uriyuu Seisaku Kk Oscillator device of orbital sanding machine
DE2938704C2 (de) * 1979-09-25 1984-03-15 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Exzentertellerschleifer
FR2529497A1 (fr) * 1982-07-02 1984-01-06 Black & Decker Inc Perfectionnement aux outils portables a plateau vibrant, notamment aux ponceuses vibrantes
CA1204067A (en) * 1983-04-29 1986-05-06 Miksa Marton Clutch assembly for sanding head
JPS60135171A (ja) * 1983-12-23 1985-07-18 Konpakuto Tool Kk 研磨機

Also Published As

Publication number Publication date
DE3602571A1 (de) 1987-07-30
JPS62181866A (ja) 1987-08-10
DE3602571C2 (de) 1998-09-24
JPH0710490B2 (ja) 1995-02-08
EP0230621A3 (en) 1988-07-13
EP0230621A2 (de) 1987-08-05
US4727682A (en) 1988-03-01
DE3677948D1 (de) 1991-04-11

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