EP0341242B1 - Exzenterschleifer - Google Patents

Exzenterschleifer Download PDF

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Publication number
EP0341242B1
EP0341242B1 EP19870907579 EP87907579A EP0341242B1 EP 0341242 B1 EP0341242 B1 EP 0341242B1 EP 19870907579 EP19870907579 EP 19870907579 EP 87907579 A EP87907579 A EP 87907579A EP 0341242 B1 EP0341242 B1 EP 0341242B1
Authority
EP
European Patent Office
Prior art keywords
ring
rolling
rings
eccentric
grinding disc
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
EP19870907579
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0341242A1 (de
Inventor
Walter Barth
Karl Heinz Braunbach
Manfred Stäbler
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.)
OFFERTA DI LICENZA AL PUBBLICO
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 EP0341242A1 publication Critical patent/EP0341242A1/de
Application granted granted Critical
Publication of EP0341242B1 publication Critical patent/EP0341242B1/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 relates to an eccentric grinder, the type defined in the preamble of claim 1.
  • Eccentric grinders of this type offer the option of driving the sanding plate in three different forms of movement and thereby producing different grinding patterns.
  • the grinding plate is idling, ie without the rolling movement of the grinding plate turntable on the assigned rolling rings, a fine sanding is achieved since the movement of each individual grinding grain per revolution of the eccentric is very small.
  • the grinding plate is forced against the direction of rotation of the eccentric, which is caused by the external drive means of the second grinding plate rotating ring rolling in the rolling means of the second rolling ring, describes each abrasive grain on the grinding plate a hypocycloid, so that the path of the abrasive grains per eccentric revolution is increased and thus a larger grain removal is forced.
  • the micrograph changes accordingly.
  • each abrasive grain When the grinding plate is forced into the direction of rotation of the eccentric, which is caused by the inner drive means of the first grinding plate rotating ring rolling in the rolling means of the first rolling ring, each abrasive grain describes a pericycloid. The grinding path of the abrasive grains per eccentric revolution becomes maximum. This grinding movement causes the greatest grain abrasion and is therefore well suited for rough grinding.
  • the two rolling rings are fastened to a sleeve fixed in the housing as a double ring gear with internal and external teeth.
  • the two grinding plate swivel rings which are also designed as toothed rings, are arranged axially offset from one another and rigidly connected to the grinding plate.
  • the sleeve is axially displaceable in three positions.
  • the eccentric grinder according to the invention with the characterizing features of claim 1 has the advantage that the desired switchover option for the grinding movement of the grinding plate is achieved with an extremely small axial overall height of the grinder housing.
  • the switchover can be carried out quickly without having to wait for the sanding plate to come to a standstill, since the sanding plate slewing rings and their associated rolling rings do not first have to be brought into engagement on different levels, but are in constant engagement with one another from the start.
  • the changeover can thus be carried out without gear wear even during the grinding process, i.e. without the drive being switched off.
  • the switching device is user-friendly and easy to use.
  • the constant engagement of the slewing rings and rolling rings prevents the rolling rings from turning up during their freewheeling, since the rolling rings are exposed to a certain amount of friction in their guides.
  • the turning and rolling rings can be designed either as sprockets according to the embodiment in claim 13 or as friction rings according to the embodiment in claim 16.
  • An advantageous embodiment of the invention also results from claim 4.
  • good transfer of the heat generated by friction in the mutually engaging drive and rolling means and in the ring guides of the rolling rings is in the Interior of the housing achieved, where the heat is then dissipated by air movement.
  • appropriate metals e.g. Sintered metals
  • a smooth sliding of the rolling rings in the ring guides is possible. If the turning and rolling rings are designed as toothed rings, the result is a low-noise gear with small manufacturing tolerances.
  • An advantageous embodiment of the invention also results from claim 14.
  • the sine toothing results in a soft, wear-free engagement which is achieved by the rotating and rolling rings designed as toothed rings.
  • the type of toothing is less sensitive to grinding dust than an involute toothing.
  • the simultaneous engagement of several teeth is ensured by the slight difference in diameter of the part circles of the rotating and rolling rings.
  • the eccentric grinder seen in longitudinal section in FIG. 1 has a pot-like or bell-like housing 10, which is closed at the lower open edge with a metallic support plate 11.
  • a suction nozzle 13 In the interior 12 of the housing 10 opens a suction nozzle 13, through which air and thus heat and dust can be extracted from the housing interior 12.
  • an eccentric 15 In the interior of the housing 12 there is an eccentric 15 which is rotatably driven by means of an electric motor (not shown) via its drive shaft 14.
  • a grinding plate 16 is rotatably mounted in the eccentric 15.
  • a support pin 18 is mounted in a recess 17 of the eccentric 15 via a ball bearing 19, which projects through a through opening 19 in the support plate 11 and carries the grinding plate 16 at the free end.
  • the grinding plate 16 is fixed on the trunnion 18 by a screw 21 screwed into a threaded bore 20 in the trunnion 18.
  • a soft-elastic covering 22 is glued onto the outer end face of the grinding plate 16 and serves to receive the actual grinding sheet 23.
  • the axis of rotation 24 of the grinding plate 16 and the support pin 18 runs parallel to the axis of rotation 25 of the eccentric 15 and thus the output shaft 14 in the existence of the eccentricity e.
  • the grinding plate 16 On the rear side facing the support plate 11, the grinding plate 16 carries two rotating rings 26 and 27 which are fastened concentrically to its axis of rotation 24 and which are preferably formed in one piece with the grinding plate 16.
  • Each ring gear 26, 27 is formed by a ring gear, wherein the first slewing ring 26 with a larger diameter has an internal toothing 28 and the second slewing ring 27 with a smaller diameter has an external toothing 29. Internal toothing 28 and external toothing 29 can also be assigned to the other ring gear.
  • Each of the two turntables 26, 27 is assigned a rolling ring 30 and 31, which is also designed as a ring gear.
  • the rolling rings 30, 31 are rotatably held in ring guides 32, 33 which are fixed concentrically on the support plate 11.
  • the first rolling ring 30 with the larger diameter has an external toothing 34 and the second rolling ring 31 with the smaller diameter has an internal toothing 35.
  • the internal toothing 28 of the first rotating ring 26 is aligned with the external toothing 34 of the first rolling ring gear 30 and the external toothing 29 of the second rotating ring 27 stands in constant engagement with the internal toothing 35 of the second rolling ring 31.
  • the teeth are designed as so-called sine teeth, which are schematically outlined in FIG. 8.
  • the rolling rings 30, 31 are made of metal, preferably sintered metal, and the rotating rings 26, 27 are made of plastic.
  • the ring guides 32, 33 are formed by an axially projecting on the support plate 11 and integrally with this annular web 36 and an annular flange 37 fastened on the end face of the annular web 36, which projects radially beyond the annular web 36 on both sides.
  • two concentric ring grooves are defined as ring guides by the ring web 36, the support plate 11 and the ring flange 37, in which the rolling rings 30, 31 lie on their rear sides facing away from the toothings 34, 35.
  • the two rolling rings 30, 31 can either rotate freely in the ring guides 32, 33 or alternately on the Carrier plate 11 are fixed non-rotatably, whereby a total of three different types of movement of the grinding plate 16 can be achieved.
  • a switching device 38 with three switching positions is provided, which has a switching lever 39 which can be pivoted into the three switching positions and a locking device 40 which is actuated by the switching lever 39.
  • the locking device 40 is designed so that it alternately holds one of the two rolling rings 30, 31 non-rotatably on the support plate 11 in the two extreme positions of the switching lever 39 and the two rolling rings 30, 31 in the middle position of the switching lever lying between the two extreme positions returns free rotation in the ring guides 32 and 33.
  • both rolling rings 30, 31 are freely rotatable in the ring guides 32, 33, the grinding plate 16 is driven solely via the eccentric 15, the grinding plate 16 being freely rotatable about its axis of rotation 25.
  • the grinding plate therefore executes a movement during grinding which follows a cycloid with a superimposed rotary movement, the superimposition of the rotary movement being dependent on the pressure during grinding.
  • the path of every single abrasive grain per eccentric revolution is very small, which results in a very fine grinding pattern.
  • the first rolling ring 30 with the external toothing 34 is fixed non-rotatably on the support plate 11, the first rotating ring 26 with its internal toothing 28 rolls on the first aberrating ring 30 in the external toothing 34 thereof.
  • Each grinding grain of the abrasive sheet 23 describes a pericycloid when grinding in this setting, in which the rotational movement coincides with the direction of rotation of the eccentric 15. As a result, the path of the abrasive grains is the greatest per revolution of the eccentric 15. This grinding movement causes the greatest stock removal and is therefore well suited for rough grinding. If the inner rolling ring 31 is non-rotatably held on the support plate 11, the second rotating ring 27 rolls with its external toothing 29 in the internal toothing 35 of the second rolling ring 31. Each abrasive grain of the abrasive sheet 23 now describes an elongated hypocycloid, moving against the direction of rotation of the eccentric 15. This results in a greater removal than in the case of free-wheel grinding of the two rolling rings 30, 31, but also less removal than in the grinding movement described above, in which the first rolling ring 30 is held. In contrast, the micrograph is correspondingly finer.
  • the switching device 38 with locking device 40 can be designed in various ways.
  • the locking device 40 has a plurality of recesses designed as blind or through holes 41 in the end faces of the rolling rings 30, 31 facing the support plate 11 and two locking members each guided in an axial bore 42 in the support plate 11, which here as round pins 43 are formed.
  • the round pins 43 are hinged to a rocker arm 44, on both sides of the fulcrum.
  • the rocker arm 44 is connected to the switch lever 39 in such a way that the rocker arm 44 tilts to the right or to the left when the switch lever 39 is pivoted out of its central position shown in FIG. 1, as a result of which one of the two pins 43 into a pocket or through bore 41 in one of the rolling rings 30, 31 immersed and thereby fixed non-rotatably on the support plate 11.
  • the locking device 240 has a pawl 245 with a cross-sectional sector which extends within a circumferentially extending through opening 246 in the support plate 11 over a circumferential section of the ring web 36 and by means of a cutting edge bearing 247 is supported on this.
  • the free ends 248 and 249 form locking members which are able to engage in recesses 250, 251 in the form of ring sections in the end faces of the rolling rings 30, 31 facing the support plate 11.
  • a link groove 253 extends in the longitudinal direction thereof, in which the switching lever 239 of the switching device 238, which engages over the pawl 245, engages with a link pin 254.
  • the switch lever 239 protrudes in the radial direction through a slot 255 in the housing 10 and can be pivoted manually in the circumferential direction of the housing.
  • the course of the link groove 253 in the pawl 245 is now set such that when the link pin 254 is moved as a result of the pivoting of the switching lever 239 from approximately the center of the longitudinal extension of the link groove 253 (shown in FIG.
  • the locking device 340 has an interlocking element which can be pivoted alternately into the ring guides 32, 33 and at least one interlocking recess provided in each rolling ring 30, 31 and corresponding to the interlocking element.
  • the form-locking element is designed as a ratchet lever 357 which is pivotably mounted on the ring web 36.
  • the pawl lever 357 is rigidly connected to the changeover lever 339 via a bolt 358 which is guided through the ring web 36 and the support plate 11 and which projects radially out of this through a slot 355 in the housing 10 and can be pivoted manually in the circumferential direction of the housing.
  • the form-fitting recesses are designed as radial recesses 356 and 359 in the circumferential surfaces of the rolling rings 30, 31 facing the ring web 36, into which the pawl lever 357 can engage with two end lugs 360, 361.
  • the positive-locking element is designed as a cam 462, which is connected to the changeover lever in the same way as the pawl lever 357.
  • the cam 462 can engage in one of the radial recesses 456 or 459 in the two rolling rings 30, 31 by pivoting the changeover lever and thereby block each of them against rotation.
  • the rolling rings 30, 31 can be blocked by clamping them in the ring guides 32, 33 as a result of the rotation of the cam 462.
  • the cam 462 then provides a frictional engagement element represents the rolling rings 30, 31 in their ring guides 32, 33 non-positively.
  • the locking device 540 also has a force-locking element which fixes the rolling rings 30, 31 in their ring guides 32, 33 in a force-locking manner.
  • This force-locking element here consists of brake shoes 563, which are pivotally mounted on the ring web 36 over its circumference by means of pivot pins 564.
  • the brake shoes 563 have an outer friction surface 565 and an inner friction surface 566, which can alternately be pressed against the rear sides of the rolling rings 30, 31 facing the web 36.
  • the pressure is applied via an eccentric cam 567, which is connected to the switch lever (not shown here) and can be rotated in an oval passage opening 568 in the brake shoes 563.
  • the eccentric cam 567 By pivoting the switch lever, the eccentric cam 567 is pivoted to the right or left and thereby presses the associated brake shoes 563 against the outer rolling ring 30 or the inner rolling ring 31. If several brake shoes 563 are provided, the eccentric cams 567 must be mechanically synchronized with one another. It is also possible to dispense entirely with the brake shoes and to design the eccentric cam 567 in such a way that it acts non-positively on the rear sides of the rolling rings 30, 31 facing the web 36.
  • the invention is not restricted to the exemplary embodiments described above.
  • the slewing rings and their rolling rings can also be designed as friction rings instead of gear rings, which are in engagement with one another via internal or external friction surfaces.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
EP19870907579 1986-12-13 1987-11-21 Exzenterschleifer Expired - Lifetime EP0341242B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863642741 DE3642741A1 (de) 1986-12-13 1986-12-13 Exzenterschleifer
DE3642741 1986-12-13

Publications (2)

Publication Number Publication Date
EP0341242A1 EP0341242A1 (de) 1989-11-15
EP0341242B1 true EP0341242B1 (de) 1991-07-10

Family

ID=6316195

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19870907579 Expired - Lifetime EP0341242B1 (de) 1986-12-13 1987-11-21 Exzenterschleifer

Country Status (5)

Country Link
US (1) US4918868A (ja)
EP (1) EP0341242B1 (ja)
JP (1) JP2557928B2 (ja)
DE (2) DE3642741A1 (ja)
WO (1) WO1988004218A1 (ja)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3906549A1 (de) * 1989-03-02 1990-09-06 Bosch Gmbh Robert Exzenterschleifer
GB9123502D0 (en) * 1991-11-06 1992-01-02 Black & Decker Inc Sanding apparatus
US5392568A (en) * 1993-12-22 1995-02-28 Black & Decker Inc. Random orbit sander having braking member
CA2220776A1 (en) * 1996-11-13 1998-05-13 Allen Sommers Eccentric grinder loading system
US6213851B1 (en) 1998-07-07 2001-04-10 Delta International Machinery Corp. Abrading apparatus
DE19952108B4 (de) * 1999-10-29 2007-09-20 Robert Bosch Gmbh Exzentertellerschleifmaschine
DE19963831B4 (de) * 1999-12-30 2006-04-06 Robert Bosch Gmbh Exzentertellerschleifer mit einem Gehäuse
US6386947B2 (en) 2000-02-29 2002-05-14 Applied Materials, Inc. Method and apparatus for detecting wafer slipouts
DE10104993A1 (de) * 2001-02-03 2002-08-22 Bosch Gmbh Robert Handwerkzeugmaschine zum Schleifen, Polieren oder dergleichen
DE10134308A1 (de) 2001-07-14 2003-01-30 Bosch Gmbh Robert Handwerkzeugmaschine

Family Cites Families (5)

* 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
FR2529497A1 (fr) * 1982-07-02 1984-01-06 Black & Decker Inc Perfectionnement aux outils portables a plateau vibrant, notamment aux ponceuses vibrantes
DE3602571C2 (de) * 1986-01-29 1998-09-24 Bosch Gmbh Robert Exzentertellerschleifer mit einer Vorrichtung zum Verändern der Schleifbewegung
DE3609441A1 (de) * 1986-03-20 1987-09-24 Bosch Gmbh Robert Exzenterschleifer mit einer vorrichtung zum veraendern der schleifbewegung

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
Patent Abstracts of Japan, vol 5, no 80 (M-70)(752), 26 May 1981, & JP,A,5627773 ( URIU SEISAKU K.K.) 18 March 1981 *
Patent Abstracts of Japan, vol 9, no 297 (M-432)(2020), 25 November 1985 & JP,A,60135171 (KONPAKUTO TSUURU K.K.) 18 July 1985 *
Patent Abstracts of Japan, vol. 5, no 22 (M-54)(694), 10 February 1981, & JP,A,55150964 (KINICHI TAKEUCHI) 25 November 1980 *

Also Published As

Publication number Publication date
JPH02501548A (ja) 1990-05-31
DE3771342D1 (de) 1991-08-14
DE3642741A1 (de) 1988-06-23
EP0341242A1 (de) 1989-11-15
WO1988004218A1 (en) 1988-06-16
US4918868A (en) 1990-04-24
JP2557928B2 (ja) 1996-11-27

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