US3857206A - Compound motion rubbing machine - Google Patents

Compound motion rubbing machine Download PDF

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Publication number
US3857206A
US3857206A US00339164A US33916473A US3857206A US 3857206 A US3857206 A US 3857206A US 00339164 A US00339164 A US 00339164A US 33916473 A US33916473 A US 33916473A US 3857206 A US3857206 A US 3857206A
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US
United States
Prior art keywords
eccentric
drive shaft
casing
shaft
shoe
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
US00339164A
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English (en)
Inventor
E Heffran
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.)
NAT DETROIT Inc CO
Original Assignee
NAT DETROIT Inc 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 NAT DETROIT Inc CO filed Critical NAT DETROIT Inc CO
Priority to US00339164A priority Critical patent/US3857206A/en
Priority to CA193,942A priority patent/CA984612A/en
Priority to GB984974A priority patent/GB1405398A/en
Priority to DE2410689A priority patent/DE2410689C2/de
Priority to FR7407797A priority patent/FR2220347B1/fr
Priority to JP2646474A priority patent/JPS5633225B2/ja
Priority to IT20907/74A priority patent/IT1007688B/it
Application granted granted Critical
Publication of US3857206A publication Critical patent/US3857206A/en
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

  • ABSTRACT A portable sander having an air motor with an output shaft driving an eccentric, parallel shaft on which an inverted cup-shaped casing is journaled for eccentric motion about the driving shaft.
  • a pinion gear is fast on the motor housing around the motor shaft and meshes with a larger ring gear fast in the upper end of the casing to rotate the casing about an eccentric axis as it moves about the axis of the driving shaft.
  • the casing carries a rubbing shoe to which a sheet of sandpaper is attached for contact with a work surface.
  • the primary object of the presentinvention is to improve the performance of machines of the foregoing character by a basic structural change making possible the more effective utilization of available power and providing an improved and more effective compound motion of abrasive particles on the shoe relative to a work surface. More specifically, the invention utilizes the motion produced by moving the ring member around a stationary wheel member to obtain epicycloidal motion of the abrasive particles, and this is believed to be responsible for the more effective rubbing action.
  • FIG. 1 is a side elevational view of a portable sander embodying the novel features of the present invention, certain parts of the sander being broken away and shown in section.
  • FIG. 2 is an enlarged fragmentary cross-sectional view taken substantially along the line 22 of FIG. 1.
  • FIG. 3 is a fragmentary cross-sectional view taken along the line 3-3 of FIG. 2.
  • FIG. 4 is a view similar to FIG. 3 with the parts in moved positions.
  • FIG. 5 is an enlarged view schematically illustrating the paths followed by particles on the rubbing shoe during operation of the sander.
  • the invention is embodied in a portable sander l0 powered by a motor in a hollow frame or housing 11 beneath which a rubbing shoe I2 is supported for gyratory motion about the axis 13 of the depending motor shaft I4.
  • the lower end portion of the motor shaft projects through and is joumaled in an anti-friction bearing 15 (FIG. 2) fitted in a plate 18 forming the bottom wall of the motor housing.
  • the rubbing shoe is carried by an eccentric indicated generally at 19 on the lower end of the drive shaft.
  • the sander 10 is powered by a rotary air motor which receives air under pressure through a flexible hose 20 connected to the free end of a handle 21 on the housing 11 and communicating with the motor through 'an air passage in the handle.
  • the flow of air to the motor is controlled by a lever 22 extending outwardly from the casing along the top of the handle and movable toward and away from the latter to open and close a valve 23 interposed between the air passage and the motor.
  • the construction and operation of the motor and the control valve are well known to those skilled in the art and thus are not described in detail herein.
  • the eccentric 19 comprises a crank disk 24 secured to the lower end of the drive shaft 14 beneath the bearing 15 with a second shaft 25 projecting downwardly from the disk in radially offset parallel relation with the drive shaft.
  • the rubbing shoe 12 is supported on a carrier 26 joumaled on the eccentric shaft 25 to turn about the axis 27 of such shaft and to wobble eccentrically about the axis 13 of the drive shaft.
  • the shoe comprises a pad 28 of resiliently yieldable material secured to the underside of a flat circular backing plate 29 fastened to the carrier in a plane perpendicular to the axes of the shafts 14 and 25.
  • a sheet 30 of abrasive material such as sandpaper is fastened to the underside of the pad for rubbing engagement with a work surface.
  • rotation of the motor shaft 14 at high speed swings the carrier 26 about the axis 13 ofthe motor shaft to impart a gyratory or wobbling motion to the rubbing shoe l2 and to the abrasive particles on the sheet 30 of abrasive material fastened to the shoe.
  • the amount of eccentricity of the shaft 25 determines the amount of lateral motion or throw of the rubbing shoe during each revolution of the drive shaft.
  • the eccentricity may be one-eighth of an inch. It will be understood by those skilled in the art, however, that the representative figure given above is not critical and will vary according to the size of the machine and the type of the rubbing action desired.
  • a secondary turning or rolling motion is imparted to the shoe 12 to rotate the latter about the axis 27 of the eccentric shaft 25 as the shoe gyrates about the drive shaft 14.
  • This secondary motion prevents the formation of circular grooves in the work surface by the abrasive particles on the shoe by moving the particles along non-circular paths.
  • the compound motion of the shoe assists in the automatic removal of the foreign material that tends to accumulate between and around the abrasive particles and thus unloads the abrasive sheet in service use.
  • an improved and more effective compound motion of the shoe 12 is produced by a positive drive comprising a circular gear wheel or pinion 3l stationarily mounted on the machine frame 11 and drivingly engaging a ring gear 32 movable with the carrier 26, the ring gear being larger than and encircling the stationary pinion gear.
  • a positive drive comprising a circular gear wheel or pinion 3l stationarily mounted on the machine frame 11 and drivingly engaging a ring gear 32 movable with the carrier 26, the ring gear being larger than and encircling the stationary pinion gear.
  • the pinion 31 is integral with the underside of the plate 18, the pinion and the plate being formed by conventional powdered metal techniques.
  • the carrier 26 is an inverted cup-shaped casing having a cylindrical body 26a abutting against and secured by screws 33 to the backing plate 29.
  • the top wall 34 of the cup is disposed immediately beneath the crank disk 24 and is formed with a central circularopening 35 in which an antifriction bearing 36 is fitted.
  • the eccentric shaft extends downwardly through this bearing, there being a counterweight 37 fastened to and projecting radially from the lower end portion of the shaft beneath the cup wall 34.
  • the bearing 36 mounts the cup 26 and the shoe l2 rotatably on the eccentric shaft 25 in coaxial relation therewith.
  • FIGS. 3 and 4 show two extreme positions of the ring gear and the carrier relative to the pinion and the drive shaft and the corresponding position of the eccentric shaft 25.
  • the pinion 31 has fewer teeth than the ring gear 32.
  • the amount of eccentricity of the shaft 25 is a factor in determining the tooth differential and also in determining the proper size differential between the ring gear and the pinion, the gear sizes being correlated with the eccentricity to insure that the ring gear remains in meshing engagement with the pinion during gyration of the carrier 26.
  • the specific numbers of teeth determine the ratio of the gearing and are a matter of sound design choice.
  • the ring gear is shown as having 39 teeth while the stationary gear has 36 teeth.
  • the superior abrasive action obtained with this construction is believed to be the result of several unique effects of the drive arrangement.
  • the rolling motion of the carrier 26 and the shoe 12 is forward, that is, in the same direction as the rotation of the drive shaft 14 and the gyration of the carrier, as indicated by the arrows in FIG. 5.
  • the illustrative sander with 36 teeth on the pinion and 39 teeth on the ring gear, has a lower gear ratio than a similar sander with a counter-rotating shoe. The increased power thus available at the shoe makes it possible to operate the sander effectively with greater rubbing pressures.
  • each particle travels generally along an epicycloidal path, that is, a path of the type generated by a point on an imaginary circle rolling on the outside of a larger base circle 41.
  • Such a path comprises a plurality of arcs 42 curving outwardly from a point on the base circle and then back to an angularly spaced point where the next arc of the path begins. It is believed that such epicycloidal paths produce the optimum amount of particle travel and abrasive contact with the work per revolution of the drive shaft 13 and thus result in optimum rubbing efficiency.
  • the gears 31 and 32 located adjacent the upper end of the carrier 26 there is ample room within the carrier for the counterweight 37 which is advantageously positioned directly adjacent the top of the shoe 12.
  • the addition of the carrier to the gyrating mass not only increases the mass but also raises the center of gravity of the mass into a horizontal plane well above the plane of the shoe.
  • the gear location and the hollow carrier it is possible to locate the center of gravity of the counterweight in the same horizontal plane as the center of gravity of i the gyrating mass thereby to provide optimum counterbalancing of the shoe for smooth and vibration-free operation.
  • the carrier is of relatively large diameter as a result of being fixed to the ring gear and thus provides a large, rugged and stable support upon which to mount the shoe 12.
  • a compound motion rubbing machine the combination of, a frame, a drive shaft journaled on said frame with one end portion projecting downwardly therefrom, an eccentric shaft mounted on the projecting end portion of said drive shaft in radially offset parallel relation therewith, an inverted cup-shaped casing disposed around said eccentric shaft and rotatably mounted thereon for gyratory motion about the axis of said drive shaft as the latter rotates, a pinion gear stationarily mounted on the underside of said frame in coaxial relation with said drive shaft, said casing having a coaxial annular rim I loosely encircling said pinion gear, a ring gear larger than said pinion gear fast in said rim and disposed around the pinion gear in meshing engagement with one side of the latter, and a rubbing shoe mounted on the lower end of said casing for movement therewith in rubbing engagement with a work surface, the amount of eccentricity of said eccentric shaft and the sizes of said gears being correlated to produce simultaneous gyrating and rotating motion of said casing during
  • a compound motion rubbing machine the combination of, a frame, a drive shaft joumaled on said frame with one end portion projecting downwardly therefrom, an eccentric on the projecting end portion of said drive shaft, a hollow carrier disposed around said eccentric and rotatably mounted thereon for eccentric motion with the eccentric about the axis of said drive shaft, a pinion gear stationarily mounted on the underside of said frame in coaxial relation with said drive shaft, said carrier having an annular rim projecting upwardly beyond said eccentric in loosely telescoping relation with said pinion gear, a ring gear larger than said pinion gear mounted inside said rim and meshing with the pinion gear to roll around the latter during eccentric motion of said carrier and thereby rotate the carrier about said eccentric, and a rubbing shoe fast on the lower end of said carrier for compound motion in rubbing engagement with a work surface.
  • a compound motion rubbing machine the combination of, a frame, a drive shaft joumaled on said frame, a second shaft eccentrically carried by said drive shaft for eccentric motion about the axis thereof during rotation of the drive shaft, a cup-shaped casing rotatably mounted on said second shaft for eccentric motion therewith about said axis and simultaneous rotation about the axis of said second shaft, a pinion gear staframe, a second shaft eccentrically carried by said drive shaft foreccentric motion about the axis thereof during rotation of the drive shaft, a gear wheel stationarily mounted on said frame in coaxial relation with said drive shaft, a ring gear internally larger than the exterior of said gear wheel rotatably mounted on said second shaft in coaxial relation therewith for eccentric motion about said axis, said ring gear being disposed around said gear wheel and in rolling engagement therewith to be turned by the gear wheel during said eccentric motion, and a rubbing shoe carried by said ring gear for simultaneous eccentric and turning movement relative to said frame whereby points on said shoe move along generally epicycloidal paths
  • a compound motion rubbing machine the combination of, a frame, a drive shaft journaled on said frame, an eccentric on said drive shaft, a carrier rotatably mounted on said eccentric for eccentric motion about the axis of said drive shaft during rotation of the latter, a wheel stationarily mounted on said frame in coaxial relation with said drive shaft, a ring internally larger than the exterior of said wheel disposed around the latter in continuous rolling engagement therewith, said ring being mounted on said carrier to rotate the latter as it moves eccentrically around said axis, and a rubbing shoe mounted on said carrier for movement therewith in rubbing engagement with a work surface.

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  • 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)
US00339164A 1973-03-08 1973-03-08 Compound motion rubbing machine Expired - Lifetime US3857206A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US00339164A US3857206A (en) 1973-03-08 1973-03-08 Compound motion rubbing machine
CA193,942A CA984612A (en) 1973-03-08 1974-03-04 Compound motion rubbing machine
GB984974A GB1405398A (en) 1973-03-08 1974-03-05 Compound motion rubbing machine
DE2410689A DE2410689C2 (de) 1973-03-08 1974-03-06 Handschleifmaschine
FR7407797A FR2220347B1 (it) 1973-03-08 1974-03-07
JP2646474A JPS5633225B2 (it) 1973-03-08 1974-03-08
IT20907/74A IT1007688B (it) 1973-03-08 1974-04-08 Levigatrice a moto composto

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US00339164A US3857206A (en) 1973-03-08 1973-03-08 Compound motion rubbing machine

Publications (1)

Publication Number Publication Date
US3857206A true US3857206A (en) 1974-12-31

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Family Applications (1)

Application Number Title Priority Date Filing Date
US00339164A Expired - Lifetime US3857206A (en) 1973-03-08 1973-03-08 Compound motion rubbing machine

Country Status (7)

Country Link
US (1) US3857206A (it)
JP (1) JPS5633225B2 (it)
CA (1) CA984612A (it)
DE (1) DE2410689C2 (it)
FR (1) FR2220347B1 (it)
GB (1) GB1405398A (it)
IT (1) IT1007688B (it)

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4322921A (en) * 1979-09-25 1982-04-06 Peter Maier Eccentric plate grinder
EP0102107A1 (en) * 1982-08-02 1984-03-07 Chicago Pneumatic Tool Company Rotary and orbital sander
US4845898A (en) * 1986-09-04 1989-07-11 Licentia Patent-Verwaltungs-Gmbh Orbital sander
USD314900S (en) 1987-10-19 1991-02-26 National-Detroit, Inc. Abrading machine
USD353310S (en) 1993-05-04 1994-12-13 Shinano, Inc. Dual action sander
USD377892S (en) * 1995-09-11 1997-02-11 K.K.U. Limited Sander
USD380659S (en) * 1996-03-27 1997-07-08 K.K. U. Limited Sander
USD381248S (en) * 1996-04-30 1997-07-22 K.K.U. Limited Sander
USD381570S (en) * 1996-04-30 1997-07-29 K.K.U. Limited Sander
USD385765S (en) * 1996-04-30 1997-11-04 K.K.U. Limited Sander
USD386377S (en) * 1995-09-11 1997-11-18 K.K.U. Limited Sander
US5702287A (en) * 1990-08-17 1997-12-30 Haney; Donald E. Sander with orbiting platen and abrasive
USD405334S (en) 1996-11-05 1999-02-09 K.K.U. Limited Sander
WO1999054087A2 (en) 1998-04-23 1999-10-28 Gary Rudolph Apparatus and method for rotary motion conversion and waste product collection unit
USD427498S (en) * 1999-06-29 2000-07-04 Ingersoll-Rand Company Dual action sander
USD427871S (en) * 1999-06-29 2000-07-11 Ingersoll-Rand Company Dual action sander
USD442839S1 (en) 1999-06-29 2001-05-29 Ingersoll-Rand Company Palm sander
USD443492S1 (en) 1999-06-29 2001-06-12 Ingersoll-Rand Company Palm sander
US6511701B1 (en) * 2000-05-09 2003-01-28 3M Innovative Properties Company Coatings and methods
EP1027958A3 (de) * 1999-02-11 2003-04-16 TTS Tooltechnic Systems AG & Co. KG Exzenterteller-Schleifmaschine
EP1491291A1 (de) * 2003-06-27 2004-12-29 Festool GmbH Exzentertellerschleifer
US7004818B1 (en) 1990-08-17 2006-02-28 Haney Donald E Sander with orbiting platen and abrasive
US7198557B2 (en) 2001-08-02 2007-04-03 Haney Donald E Sanding machine incorporating multiple sanding motions
US20150014013A1 (en) * 2011-12-23 2015-01-15 Robert Bosch Gmbh Electrically Operable Machine Tool
EP3055585A4 (en) * 2013-10-10 2017-06-28 Arbortech Industries Ltd Rotary gear transmission for tools
US12673407B2 (en) 2023-05-16 2026-07-07 Black & Decker Inc. Oscillating tool

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3602571C2 (de) * 1986-01-29 1998-09-24 Bosch Gmbh Robert Exzentertellerschleifer mit einer Vorrichtung zum Verändern der Schleifbewegung
DE3615799C2 (de) * 1986-05-10 1994-10-13 Bosch Gmbh Robert Exzenterschleifer mit einer Vorrichtung zum Verändern der Schleifbewegung
IT209516Z2 (it) * 1986-12-22 1988-10-10 Valentini Guido Utensile elettrico portatile con movimento orbitale bilanciato.
DE9111520U1 (de) * 1991-09-17 1993-01-28 Werkzeug GmbH, 5441 Weibern Exzenterschleifkopf
US11493115B2 (en) * 2017-10-30 2022-11-08 Lake Country Tool, Llc Adjustable stroke device with cam

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2178937A (en) * 1938-07-19 1939-11-07 Charles P Nieder Tool sharpener
US2740237A (en) * 1954-09-10 1956-04-03 Spitfire Tool Co Lapping machine
US3105328A (en) * 1960-11-03 1963-10-01 Hamilton Watch Co Apparatus for lapping thin articles
US3199251A (en) * 1963-12-20 1965-08-10 Black & Decker Mfg Co Driving mechanism for abrading tool
US3205622A (en) * 1963-02-25 1965-09-14 Treffle J Leveque Rotatable grinding and surfacing tool
US3287859A (en) * 1965-08-23 1966-11-29 Treffle J Leveque Rotatable grinding and surfacing tool

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2025208A1 (de) * 1970-05-23 1971-12-02 C F Scheer & Cie, 7000 Stuttgart Feuerbach Schwingschleifer

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2178937A (en) * 1938-07-19 1939-11-07 Charles P Nieder Tool sharpener
US2740237A (en) * 1954-09-10 1956-04-03 Spitfire Tool Co Lapping machine
US3105328A (en) * 1960-11-03 1963-10-01 Hamilton Watch Co Apparatus for lapping thin articles
US3205622A (en) * 1963-02-25 1965-09-14 Treffle J Leveque Rotatable grinding and surfacing tool
US3199251A (en) * 1963-12-20 1965-08-10 Black & Decker Mfg Co Driving mechanism for abrading tool
US3287859A (en) * 1965-08-23 1966-11-29 Treffle J Leveque Rotatable grinding and surfacing tool

Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4322921A (en) * 1979-09-25 1982-04-06 Peter Maier Eccentric plate grinder
EP0102107A1 (en) * 1982-08-02 1984-03-07 Chicago Pneumatic Tool Company Rotary and orbital sander
US4467565A (en) * 1982-08-02 1984-08-28 Chicago Pneumatic Tool Company Rotary and orbital sander
US4845898A (en) * 1986-09-04 1989-07-11 Licentia Patent-Verwaltungs-Gmbh Orbital sander
USD314900S (en) 1987-10-19 1991-02-26 National-Detroit, Inc. Abrading machine
US7004818B1 (en) 1990-08-17 2006-02-28 Haney Donald E Sander with orbiting platen and abrasive
US5702287A (en) * 1990-08-17 1997-12-30 Haney; Donald E. Sander with orbiting platen and abrasive
USD353310S (en) 1993-05-04 1994-12-13 Shinano, Inc. Dual action sander
USD386377S (en) * 1995-09-11 1997-11-18 K.K.U. Limited Sander
USD377892S (en) * 1995-09-11 1997-02-11 K.K.U. Limited Sander
USD380659S (en) * 1996-03-27 1997-07-08 K.K. U. Limited Sander
USD385765S (en) * 1996-04-30 1997-11-04 K.K.U. Limited Sander
USD381570S (en) * 1996-04-30 1997-07-29 K.K.U. Limited Sander
USD381248S (en) * 1996-04-30 1997-07-22 K.K.U. Limited Sander
USD405334S (en) 1996-11-05 1999-02-09 K.K.U. Limited Sander
WO1999054087A2 (en) 1998-04-23 1999-10-28 Gary Rudolph Apparatus and method for rotary motion conversion and waste product collection unit
WO1999054087A3 (en) * 1998-04-23 2000-02-10 Gary Rudolph Apparatus and method for rotary motion conversion and waste product collection unit
US20050090190A1 (en) * 1998-04-23 2005-04-28 Mr. Gary Rudolph Same-RPM Rotary Motion to Eccentric Rotary Motion Conversion and Waste Product Collection
US20040123688A1 (en) * 1998-04-23 2004-07-01 Gary Rudolph Same-RPM Rotary Motion to Eccentric Rotary Motion Conversion and Waste Product Collection
US6634437B1 (en) * 1998-04-23 2003-10-21 Gary Rudolph Apparatus and method for rotary motion conversion and waste product collection unit
EP1027958A3 (de) * 1999-02-11 2003-04-16 TTS Tooltechnic Systems AG & Co. KG Exzenterteller-Schleifmaschine
USD427498S (en) * 1999-06-29 2000-07-04 Ingersoll-Rand Company Dual action sander
USD443492S1 (en) 1999-06-29 2001-06-12 Ingersoll-Rand Company Palm sander
USD442839S1 (en) 1999-06-29 2001-05-29 Ingersoll-Rand Company Palm sander
USD427871S (en) * 1999-06-29 2000-07-11 Ingersoll-Rand Company Dual action sander
US6511701B1 (en) * 2000-05-09 2003-01-28 3M Innovative Properties Company Coatings and methods
US7198557B2 (en) 2001-08-02 2007-04-03 Haney Donald E Sanding machine incorporating multiple sanding motions
EP1491291A1 (de) * 2003-06-27 2004-12-29 Festool GmbH Exzentertellerschleifer
US20150014013A1 (en) * 2011-12-23 2015-01-15 Robert Bosch Gmbh Electrically Operable Machine Tool
EP3055585A4 (en) * 2013-10-10 2017-06-28 Arbortech Industries Ltd Rotary gear transmission for tools
US9873178B2 (en) 2013-10-10 2018-01-23 Arbortech Industries Limited Rotary gear transmission for tools
US12673407B2 (en) 2023-05-16 2026-07-07 Black & Decker Inc. Oscillating tool

Also Published As

Publication number Publication date
FR2220347B1 (it) 1979-10-19
JPS5633225B2 (it) 1981-08-01
GB1405398A (en) 1975-09-10
CA984612A (en) 1976-03-02
DE2410689A1 (de) 1974-09-12
DE2410689C2 (de) 1982-12-16
FR2220347A1 (it) 1974-10-04
IT1007688B (it) 1976-10-30
JPS49125992A (it) 1974-12-03

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