US3584424A - Means for generating involute and noninvolute gears - Google Patents

Means for generating involute and noninvolute gears Download PDF

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Publication number
US3584424A
US3584424A US693233A US3584424DA US3584424A US 3584424 A US3584424 A US 3584424A US 693233 A US693233 A US 693233A US 3584424D A US3584424D A US 3584424DA US 3584424 A US3584424 A US 3584424A
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main
frame
generatrix
workgear
swing
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US693233A
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Peter Herbert Cleff
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23F—MAKING GEARS OR TOOTHED RACKS
    • B23F5/00—Making straight gear teeth involving moving a tool relatively to a workpiece with a rolling-off or an enveloping motion with respect to the gear teeth to be made
    • B23F5/02—Making straight gear teeth involving moving a tool relatively to a workpiece with a rolling-off or an enveloping motion with respect to the gear teeth to be made by grinding
    • B23F5/06—Making straight gear teeth involving moving a tool relatively to a workpiece with a rolling-off or an enveloping motion with respect to the gear teeth to be made by grinding the tool being a grinding disc with a plane front surface
    • B23F5/065—Making straight gear teeth involving moving a tool relatively to a workpiece with a rolling-off or an enveloping motion with respect to the gear teeth to be made by grinding the tool being a grinding disc with a plane front surface and the grinding disc axis varying angularly with respect to the workpiece axis
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23F—MAKING GEARS OR TOOTHED RACKS
    • B23F23/00—Accessories or equipment combined with or arranged in, or specially designed to form part of, gear-cutting machines
    • B23F23/003—Generating mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23F—MAKING GEARS OR TOOTHED RACKS
    • B23F23/00—Accessories or equipment combined with or arranged in, or specially designed to form part of, gear-cutting machines
    • B23F23/08—Index mechanisms

Definitions

  • the principal object of this invention is to provide a generative gear grinding or finishing machine which is versatile and fast in operation.
  • a second object of the invention is the provision of means whereby a rotating grinding or finishing wheel is made to carry out most, if not all, motions necessary to generate by means of its straight line generatrix, which may be constituted by a line lying in the operative transverse plane of said grinding wheel or by the external straight line conegeneratrix of a conical grinding wheel of more than I50 arcdegrees included cone angle, either true-involute or near-involute helicoids on the workgear to be ground.
  • a third object of this invention is the provision of the basic means for the grinding of noninvolute external gears by either the straight wheel/generative" or “formed-wheel/generative” process, or internal involute gears by the latter method.
  • a machine for generating the finished form of gear teeth on a work gear comprises a worktable adapted to carry said workgear and rotatable about an axis, means for step-by-step indexing of said worktable carrying said workgear about said axis, a finishing wheel having an operative part defining a generatrix to suit a given tooth form, a power-driven rotatable spindle carrying said finishing wheel, a two-part swing frame angularly movable about a pair of main pivots whose common axis is always normal to said generatrix and has a given angular relationship, in accordance with the given tooth for, to said work table axis, means for movably connecting said spindle to said swing frame so as to allow movement of said spindle and said generatrix relative to said swing frame in a plane of right angles to the common axis of said main pivots, a main swivel frame bearing said pair of main pivots, a main feed slide slidable
  • FIG. 1 is a plan view of the machine, illustrating its basic components and its modus operandi in accordance with the invention
  • FIG. 2 is an enlarged diagrammatic plan view of the grinding head mechanism of FIG. 1, illustrating the kinematic and mathematic principles thereof,
  • FIG. 3 is an enlarged diagrammatic plan view of the correlator mechanism of FIG. I, in its preferred form
  • FIG. 4 shows the various forms of grinding wheel generatrix employable on a gear grinding machine in accordance with the invention
  • FIG. 5 illustrates an alternative arrangement of grinding head mechanism/correlator mechanism
  • FIG. 6 is a plan view of a complete grinding head mechanism/correlator mechanism combination as shown diagrammatically in FIG. 5.
  • swing-frame 25 and exten sion 27 are operationally integral, once 27 has been set to the correct perpendicular radial distance from the axis of the swing-frame pivots 26.
  • the swing-frame 25 is made to oscillate around its pivots 26 by means of a mechanism (not shown) of the lever/crank type the lever of which is represented by swing-frame 25. The amount of such oscillation is determined by the magnitude of the roll angle required for the grinding of a given work gear tooth.
  • a grinding spindle 28, with a drive motor 29, grinding wheel 30 and grinding wheel dressing and wear compensating device 31, is movably suspended from the extension 27 of swingframe 25 by two two-pivot links 32, 33 of equal or near equal length, respectively pivoted at 34, 35 on the grinding spindle and at 36, 37 on the extension 27 of the swing-frame 25.
  • a rectilinear guide bar 38 which is integral with said spindle and whose centerline is parallel to the (rectilinear) generatrix of grinding wheel 30.
  • Swing-frame 25 carries a pivot 43 at its outer end, i.e. the end away from its main pivots 26. On said pivot 43 there is rotatably held a bellcrank lever 42 with two length-adjustable arms 41 and 44. Arm 41 of bellcrank lever 42 carries at its free end a pivot 40 to which is rotatably attached a rectilinear guide bar follower 39, said guide bar follower being always in sliding contact with the aforementioned guide bar 38 integral with grinding spindle 28.
  • the distance of pivot 40 from bellcrank lever pivot 43 is adjustable (as already mentioned) and is normally made equal to a which is equal to the setting distance of swing-frame main pivot 26 from the base cylinder of the workgear being ground, said setting distance being measured along the common normal between the axis of pivots 26 and the axis of the workgear.
  • the second arm 44 of bellcrank lever 42 also carries a pivot at its free end, i.e. pivot 45.
  • Distance of pivot 45 from bellcrank lever main pivot 43 is adjustable.
  • the perpendicular distance of the centerline of arm 44 from the bellcrank lever main pivot 43 is adjustable.
  • pivot 45 will describe a curve relative to swivelframe 22, the shape of said curve being determined by the grinding wheel generatrix, by the tooth profile it is desired to grind, the distance a,,, the lengths respectively of bellcranklever arms 41 and 44; and the perpendicular offset of the centerline of arm 44 from the bellcrank lever main pivot 43.
  • the correlator mechanism itself is fully illustrated in FIG. 3. It is basically of the known single crossed-slide chain" type in its most general form. As such it has, just as any other basic four-link mechanism, three external adjustments P,, P,,, and Tr, and six internal adjustments P, through P as shown and described.
  • the correlator mechanism is driven from swingframe 25 through pivot 43 mounted thereon, through arm 44 of bellcrank lever 42 and thence through pivot 45 onto its output member 46 (FIG. I).
  • the terms output” and input must here be understood and applied in the correct sense; and thus 46 is output member vis-a-vis the swing-frame but input member vis-a-vis the movement of the grinding wheel generatrix relative to the swing-frame.
  • a machine in accordance with the invention intended to finish, e.g. by grinding, the precut tooth flanks of cylindrical gears with either spur or helical, or either true-involute, near-involute or noninvolute tooth profiles, has as a base a substantial bed I. At one end of this bed is mounted a rotary indexable worktable 2 carrying secured thereto a workgear (i.e. gear to be ground) 3 with precut teeth 4.
  • a workgear i.e. gear to be ground
  • Tooth-by-tooth indexing of this table may be carried out by means of master worm 5, driven by motor 6 through speed-change gears 7, precision clutch 8, worm shaft 9, and drive-engaging master wormwheel 10 which is integral with worktable 2, and under index control of worm shaft rotation from control box 11. Indexing may also be performed under the control of an angular (radial) diffraction grating or similar unit in coaxial drive-connection with the table spindle, in which case motor 6, speed-change gears 7, precision clutch 8, worm shaft 9, master worm and master wormwheel are merely the means for driving table and workgear into the correct angular position as determined by preset decade counters or tape-stored information.
  • a column or stanchion l2 At the other end of bed 1 there is provided a column or stanchion l2, slidably adjustable along said bed to a predetermined distance from the axis of rotation of worktable 2 plus workgear 3.
  • a feed-slide 13 Slidably mounted on this column is a feed-slide 13 which can be reciprocatingly moved by means of a feed-screw l4 journaled in column 12, and a nut 15 in engagement therewith and secured to said feed-slide.
  • Power-drive to the feed-screw is taken from worm shaft 9 via precision clutch 16, differential l7, lead-change gears 18, line shaft 19, worm and wormwheel 21, the latter drive-connected to feed-screw 14. In this way the following essential drive combination may be obtained:
  • a swivel-frame 22 Located on feed-slide l3 and angularly adjustable thereagainst around an axis coplanar with, and at right angles to the table axis, is a swivel-frame 22, its location relative to 13 being controlled by spigot 23 and secured by clamping bolts 24.
  • a swing-frame 25 of substantially rectangular cross section is oscillatingly supported from the swivel-frame 22 by a pair of large pivots 26, the common axis of which is set to a predetermined perpendicular distance a,,+R,, from the worktable axis, in which sum 0,, is equal to the perpendicular distance of the swing-frame axis from the tangent plane to the base cylinder of the workgear and lying at right angles to the longitudinal centerline of the machine, and R, is equal to the base cylinder radius of said workgear.
  • Swing-frame 25 carries a right angle extension 27 whose perpendicular radial distance from the axis of pivots 26 is adjustable to permit of correct positioning radially of the grinding wheel generatrix with respect to the axis of said pivots 26.
  • a grinding spindle 28 with drive motor 29, grinding wheel 30 and grinding wheel dressing and wear compensating device 31, is movable suspended from said extension 27 by two links 32, 33 of equal or near equal length, respectively pivoted at 34, 35 on the grinding spindle and at 36, 37 on the swingframe extension.
  • a straight line guide bar 38 Integral with grinding spindle 28 and parallel to the, in this instance, rectilinear generatrix of grinding wheel 30, there is provided a straight line guide bar 38. Said guide bar is slidably engaged by a guide bar follower 39 pivotally connected at 40 to one arm 41 of a fixed angle bellcrank lever 42 pivoted at 43 on swing-frame 25, a certain predetermined radial distance away from the axis of swing-frame pivots 26.
  • Distance 40-43 is adjustable and normally made equal to d
  • the other arm 44 of bellcrank lever 42 and carrying a pivot 45 at its outer end, is also adjustable relative to pivot 43 both as regards length 45- 43 and the perpendicular distance of its centerline from the axis of pivot 43.
  • FIG. 2 illustrates more clearly than FIG. 1 the components just described in the preceding three paragraphs, and their functions, both mathematically and kinematically.
  • FIG. 2 also demonstrates two methods of profile generation which may be employed in conjunction with a rectilinear grinding wheel generatrix, in a gear grinding machine in accordance with the invention.
  • the first method generates the involute from its origin A on the base cylinder of radius R and using a, as the basic distance parameter;
  • the second method generates the involute from one of its points A away from A to the same base cylinder radius R, but using a (a,,. a,,) as distance parameter.
  • FIG. 1 shows pivot 45 drive-connected to the output member 46 of a correlator mechanism which essentially comprises: a baseplate 47 adjustably (P,, P,,, 11') secured to swivel-frame 22, a swinging guide block 48 pivoted on 47 by means of pivot 49, a pair of rectilinear guideways 50 adjustably secured to 47 in the direction of parameter p (parallel to coordinate axis 1 a right-angled cruciform output member 46 with centerline center 51 whose one leg 52 is pivotally connected at 53 to slide 54 which is slidable in guideways S0, and whose other leg 55 is arranged to slide through swinging guide block 48, and finally an output pivot 56 whose axis is coaxial with that of pivot 45 of bellcrank lever 42, and which can be positionally adjusted duodirectionally with respect to the centerlines of both leg 52 and leg 55 of output member 46.
  • a baseplate 47 adjustably (P,, P,,, 11') secured to swivel-frame 22
  • correlator mechanism shown in FIG. 1 and FIG. 3 is of the KAPPA or PAN-KAPPA-type with a total of nine independently adjustable parameters, P,, P,,, 1r p 11 1 p p,, p,;. Additional Parameters are L and A r as indicated in FIG. 2.
  • true-involute, near-involute and noninvolute external helicoids may be produced.
  • convexly curved grinding wheel generatrix, FIG. 4, C internal helicoids of true-involute, near-involute and noninvolute-type may be generated by what may be termed the formed wheel/generative" process.
  • the grinding wheel generatrix shown in FIG. 4, D which is concavely curved, may be used to advantage for the production of special external tooth profiles, also by the formed wheel/generative process.
  • FIGS. 5 and 6 illustrate another possible form of correlator mechanism in accordance with the invention.
  • Swing-frame 25 pivoted at 26, right-angle extension 27, parallelogram suspended grinding spindle 28, a straight line guide bar 38 and guide bar follower 39 with pivot 40, are the same components described previously with reference to FIGS. 1, 2, 3 and 4.
  • the bellcrank lever 42 still pivoted on 25 by means of pivot 43, is now however different from the one previously described.
  • lts pivot 45 at the outer end of its one arm 44 is now connected to the outer end 56 of a radius arm 57 which is pivoted on swivel-frame 22 by means of pivot 48, and whose pivot distance 57-58 is equal to the pivot distance 26-43 of the main swing-frame 25.
  • the other arm 41 of bellcrank lever 42 has now machined into it a pair of rectilinear guideways 60 along which a slide block 59, pivoted to guide bar follower 39 by pivot 40, can be moved in timed relation to the angular oscillation of swing-frame 25.
  • FIG. 6 One means of achieving such time related movements of swing-frame 25 relative to swivel-frame 22, and of slide block 59 relative to guideways 60 in arm 41 of bellcrank lever 42, is shown in FIG. 6 in the form of a fully adjustable slider-crank mechanism having adjustment parameters q 1 q and q,,.
  • This correlator mechanism is, however, only suitable for the generation of true-involute or near-involute tooth profiles if pivot 45 is constrained to move on a circular path. If this path of pivot 45 be made noncircular, by means not shown, but easily synthesized by those skilled in the art, additional requirements as regards tooth profile generation may be met.
  • a machine for generating the finished form of gear teeth on a workgear comprising a worktable adapted to carry said workgear and rotatable about an axis, means for step-by-step indexing of said worktable carrying said workgear about said axis, a finishing wheel having an operative part defining a generatrix to suit a given tooth form, a power-driven rotatable spindle carrying said finishing wheel, a two-part swing frame angularly movable about a pair of main pivots whose common axis is always normal to said generatrix and has a given angular relationship, in accordance with the given tooth form, to said worktable axis, means for movably connecting said spindle to said swing frame so as to allow movement of said spindle and said generatrix relative to said swing frame in a plane at right angles to the common axis of said main pivots, a main swivel frame bearing said pair ofmain pivots, a main feed slide slidable on a main
  • R is the base cylinder radius of said workgear from which the given tooth form is developed
  • said correlating means comprises a substantially parallelogram linkage having a coupler link, a set of rectilinear guideways mounted on and at right angles to the centerline of said coupler link, a first slide movable in said rectilinear guideways and reciprocatingly driven by a universal slidercrank mechanism activated by the relative motion between the said swing-frame, which represents one crank of said parallelogram linkage, and said coupler link, said first slide engaging through a second slide pivoted thereon a rectilinear guide-bar mounted on said spindle parallel to said generatrix, and said generatrix being rectilinear.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Grinding And Polishing Of Tertiary Curved Surfaces And Surfaces With Complex Shapes (AREA)
  • Grinding Of Cylindrical And Plane Surfaces (AREA)
  • Gear Processing (AREA)
US693233A 1967-01-06 1967-12-26 Means for generating involute and noninvolute gears Expired - Lifetime US3584424A (en)

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Application Number Priority Date Filing Date Title
GB843/67A GB1217674A (en) 1967-01-06 1967-01-06 Improvements in and relating to means for generating involute and non-involute gears

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US3584424A true US3584424A (en) 1971-06-15

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US693233A Expired - Lifetime US3584424A (en) 1967-01-06 1967-12-26 Means for generating involute and noninvolute gears

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US (1) US3584424A (de)
CH (1) CH490919A (de)
DE (1) DE1652794A1 (de)
FR (1) FR1605087A (de)
GB (1) GB1217674A (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4512109A (en) * 1981-07-07 1985-04-23 Bhs-Dr. Ing Hofler, Maschinenbau Gmbh Rolling gear apparatus for an involute tooth gear cutting machine
CN111097974A (zh) * 2019-12-27 2020-05-05 湖南工业大学 一种利用无理论误差指状刀具展成加工螺旋内齿轮的方法
CN116135463A (zh) * 2023-04-14 2023-05-19 苏州吉光模具制造有限公司 一种法兰打磨设备及其使用方法

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3564212D1 (en) * 1985-03-12 1988-09-15 C M P I S N C Di De Toni Apoll A machine for working circular profile edges of slabs of marble, granite, and the like

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2368559A (en) * 1942-05-14 1945-01-30 Fellows Gear Shaper Co Method and apparatus for smoothfinish gear grinding
US2567460A (en) * 1947-09-17 1951-09-11 Maag Zahnraeder & Maschinen Ag Machine for grinding gear wheels

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2368559A (en) * 1942-05-14 1945-01-30 Fellows Gear Shaper Co Method and apparatus for smoothfinish gear grinding
US2567460A (en) * 1947-09-17 1951-09-11 Maag Zahnraeder & Maschinen Ag Machine for grinding gear wheels

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4512109A (en) * 1981-07-07 1985-04-23 Bhs-Dr. Ing Hofler, Maschinenbau Gmbh Rolling gear apparatus for an involute tooth gear cutting machine
CN111097974A (zh) * 2019-12-27 2020-05-05 湖南工业大学 一种利用无理论误差指状刀具展成加工螺旋内齿轮的方法
CN116135463A (zh) * 2023-04-14 2023-05-19 苏州吉光模具制造有限公司 一种法兰打磨设备及其使用方法
CN116135463B (zh) * 2023-04-14 2023-06-23 苏州吉光模具制造有限公司 一种法兰打磨设备及其使用方法

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DE1652794A1 (de) 1971-02-25
FR1605087A (de) 1973-01-12
GB1217674A (en) 1970-12-31
CH490919A (de) 1970-05-31

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