US3753319A - Control of tooth flank grinding machines for helical gears - Google Patents

Control of tooth flank grinding machines for helical gears Download PDF

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Publication number
US3753319A
US3753319A US00187792A US3753319DA US3753319A US 3753319 A US3753319 A US 3753319A US 00187792 A US00187792 A US 00187792A US 3753319D A US3753319D A US 3753319DA US 3753319 A US3753319 A US 3753319A
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United States
Prior art keywords
grinding
motion
control plate
control
ram
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Expired - Lifetime
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US00187792A
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English (en)
Inventor
M Mesey
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.)
Maag Gear Wheel and Machine Co Ltd
Maag Zahnrader und Maschinen AG
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Maag Zahnrader und Maschinen AG
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Priority claimed from DE19702050946 external-priority patent/DE2050946C3/de
Application filed by Maag Zahnrader und Maschinen AG filed Critical Maag Zahnrader und Maschinen AG
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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
    • 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
    • B23F23/12—Other devices, e.g. tool holders; Checking devices for controlling workpieces in machines for manufacturing gear teeth
    • B23F23/1237—Tool holders
    • B23F23/1262—Grinding disc holders; Disc-type milling-cutter holders
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T409/00—Gear cutting, milling, or planing
    • Y10T409/10—Gear cutting
    • Y10T409/101431—Gear tooth shape generating
    • Y10T409/105883—Using rotary cutter
    • Y10T409/106201—Plural rotary cutters

Definitions

  • ABSTRACT A control means for a tooth flank grinding machine operating in accordance with the indexing generating method has an arrangement for varying the grinding stroke length during a traverse so that it increases from a minimum at the beginning of a traverse and reduces again towards the end of the traverse, so reducing the over-run of the grinding wheels in the end regions of the traverse. The velocity of the generating motion is controlled concurrently in reverse proportion to the grinding stroke length.
  • the invention relates to control means on a tooth flank grinding machine for helical gears adapted to operate in accordance with the indexing generating method.
  • Machines of this kind may be used for the socalled l5/20 grinding method in which there can be two concave conical grinding wheels to machine the left-hand and right-hand tooth flanks, although there are also examples of tooth flank grinding machines known, also adapted to operate in accordance with the indexing generating method, in which one grinding wheel is provided with a double cone adapted to machine simultaneously the left-hand and right-hand tooth flank on both sides of a tooth gap.
  • a control apparatus arranged to determine the length of grinding stroke in the traverse of the grinding means of the machine over the generating zone, said apparatus including position-limiting elements determining the reversal points of the grinding strokes and said elements being adapted to act so as to increase the length of stroke from a minimum at the beginning of the traverse ofthe generating zone to a maximum in a central region of the zone and to reduce the length of stroke again towards the end of the traverse of said zone.
  • control means in which the motion of a ram adapted to support the grinding wheel is controlled by adjustable stop abutments and a switch co-operating therewith, the zone in which the motions'are performed depending on the position of an adjustable rail which performs a motion corresponding to the rectilinear component of the generating motion between the workpiece and the grinding member.
  • the stop abutments are adjustably mounted on a guide formed on the ram and the associated switch is retained in a guide, disposed in parallel to the direction of motion of the ram and may be adjusted by means of a screw spindle which extends in the same direction.
  • the rotation of the screw spindle required for adjusting the switch may be provided by means of an electric rotary transmitter which is electrically coupled to a second rotary transmitter.
  • the sec- 0nd rotary transmitter is disposed in the casing of a sensing unit which is mounted on the column bed of the machine.
  • the sensing pin of the sensing unit bears on a rail which is mounted in a workpiece slide and encloses an adjustable angle with the direction of relative motion between the column and the workpiece slide.
  • said type of control means when employed in the present invention, it is preferably so constructed that a pair of spaced stop abutments or other members arranged to co-operate with a switch of said switching means to define, in the direction of said rectilinear component motion, limits of a zone in which said switch can be reciprocated at the rate of the ram motion and at an angle to said direction corresponding to the helix angle of the workpiece tooth system.
  • the stop members may be constructed as linear members or rails forming opposite side limits of the zone of travel of said switch, the boundaries of said zone between the spared linear limits thus formed then being defined by end stop elements which are also adjustable.
  • the switch is mounted on a nut through which a screw spindle extends, it can be advantageous in carrying out the present invention if the screw spindle is coupled to a drive transmission of the reciprocating ram.
  • the switch is preferably of a form adapted to operate without physical contact with the templates or rails.
  • the linear stop members are preferably mounted on a control plate so as to be adjustable in the sliding direction thereof, said control plate being adapted to slide at an angle to said members.
  • the guide for the sliding movement of the control plate may be formed on a part of the grinding machine, for example on the machine column, which performs the rectilinear component of the generating motion relative to a rotating machine table; the control plate may itself be coupled to a guide for the aforementioned machine part by means of a reduction transmission.
  • the additional end stop elements referred to above are preferably associated with a second switch which is also adapted to reciprocate at the rate of the ram stroke.
  • the second switch is conveniently carried by a second nut through which a second screwed spindle extends which is also coupled to the drive of the reciproeating ram.
  • the stop members are coupled with, a control cam which controls the generating velocity so that they operate in conjunction therewith, said cam control being exercised so that said velocity diminishes with an increasing length of ram stroke and increases with a decreasing length of ram stroke.
  • the control cam may have a rectilinear characteristic, parallel to its direction of motion to give a series of uniform velocity storkes.
  • the control cam comprises two control arms which are adjustably mounted on the control plate.
  • the cam can have a follower member that is the adjusting member of a potentiometer which controls the rotational velocity of an electric motor for the generating motion.
  • FIG. 1 shows the general construction of the machine in perspective
  • FIG. 2 shows schematically the workpiece to be ground with two grinding wheels disposed in front thereof and the surface traversed by the grinding wheels, which includes some over-run;
  • FIG. 3 shows schematically the same surface traversed as in FIG. 2, together with a corresponding diagram of the generating velocity referred to a horizontal base line, and
  • FIG. 4 shows a control unit for the machine of FIG. 1, the surface traversed by the grinding wheels being marked in analogy with the schematic illustration in FIGS. 2 and 3.
  • the tooth flank grinding machine is mounted on a baseplate 1 on which a platen 2 is carried in longitudinally slidable manner.
  • a column 3 is disposed to slide transversely on the sliding platen 2 and a pivoting plate 4 for adjusting the helix angle B of the teeth to be ground is adjustably mounted on said column.
  • the pivoting plate 4 has a ram guide formed on it, a ram 5 being adapted to reciprocate in the direction of the tooth helix angle on said guide.
  • Two convex conical disc-shaped grinding wheels 6 and 7 are carried by the ram 5 so that their grinding planes are disposed at the operative angles of 20 respectively of the teeth to be ground. Each of the two grinding wheels 6 and 7 is driven by a separate motor 9.
  • a bed 10 for a rotatable workpiece table 11 with a vertical axis is mounted on the baseplate 1 and a gearwheel 12 which is to be ground is clamped on the table 11.
  • a wormwheel l3, driven by a worm 14, is secured to the workpiece table.
  • the generating motion is compounded by a rotating motion of the table 11 with the workpiece 12, and a corresponding tangential motion of the two grinding wheels 6 and 7 resulting from transverse displacement of the column 3.
  • These motions are produced by a generating motor 15 which is mounted on the bed 10 and drives a shaft 19 through a generating worm 16, a generating wormwheel l7 and a generating clutch 18.
  • the drive for the transverse displacement of the column 3 is derived from the shaft 19 through two bevel gears 20 and 21, a shaft 22, two bevel gears 23 and 24, a shaft 25 on which a gearwheel 26 is mounted, a clutch 27 with clutch spring 28 and a shaft 29, module change gears 30, 31, 32 and 33 and a shaft 34 with a gearwheel 35.
  • the drive is then transmitted from there through an intermediate gear 36 to a gearwheel 37 which is mounted on a shaft 38.
  • the rotary motion of the shaft 38 is transmitted to a bevel gear 39, from there to a bevel gear 40 and a module spindle 41.
  • the module spindle 41 engages with a nut 42 which is mounted on the column 3 and so displaces the column 3 transversely.
  • the drive for the rotary motion of the workpiece table 11, and therefore of the gearwheel 12 which is to be ground, is taken from the gearwheel 26 and comprises a gearwheel 43, a clutch 44 with clutch spring 45, a shaft 46 and gearwheel 47 mounted thereon and functioning as a first change gear for adaptation of the table motion to the number of teeth on the workpiece to be ground. Further change gears 48, 49 and 50 mesh with the change gear 47.
  • the last-mentioned change gear 50 is secured to a shaft 51 that also carries the worm l4 and thus drives the table 11 with the gearwheel 12 which is to be ground.
  • the tangential motion of the column 3 is matched to the rotating motion of the workpiece 12, by means of the module change gears 30 to 33 and the change gears 47 to 50, thus producing the generating motion between the grinding wheels 6 and 7 and the workpiece 12.
  • the area traversed by the grinding wheels will be a parallelogram A B C D.
  • the traverse area actually required for grinding the tooth flanks is further defined by the two perpendicular lines B, C, and D, A,.
  • the resultant surface area namely A, B B, C, D D,, marked in FIGS. 2, 3 and 4, represents only approximately 60 percent of the parallelogram A B C D in the illustrated example.
  • the grinding stroke will be of minimum length HS min; it then increases to the maximum length HS max in the middle zone HWm of the generating motion and then diminishes towards the end of the generating motion to the minimum length HS min again.
  • a control unit 52 shown in detail in FIG. 4, is provided for controlling the grinding stroke, that is to say the length, position and reversing points thereof.
  • the unit comprises a first switch 53, adapted to operate without physical contact, as for example a magnetically or photoelectrically operated switch, mounted on a nut 54 which is reciprocated in synchronism with the motion of the grinding wheels 6 and 7 along a spindle 55 by opposite rotational movements of the spindle.
  • the spindle 55 is coupled through bevel gears 56 and 57 to a shaft 58 and this in turn is coupled through bevel gears 59 and 60 in the centre of the pivoting plate 4 to a shaft 61 that is driven by a ram spindle 64 through bevel gears 62 and 63.
  • the ram spindle 64 is itself driven through a wormwheel 65, a worm 66 and a shaft 67 by a reversing motor 68 to reciprocate the grinding wheels 6 and 7. 1
  • the control unit 52 also comprises a control plate 70, positioned so as to be horizontally slidable in the unit, one end of a wire rope 69 being mounted on said control plate.
  • the wire rope 69 runs over a small pulley 71 which is mounted on a larger pulley 72, supported in the column 3.
  • One end of a second wire rope 73 is mounted on the pulley 72 and the other end of said wire rope is mounted on a smaller pulley 74.
  • a larger pulley 75 is coaxial with and fixed to the smaller pulley 74 and both are supported together in the column 3.
  • One end of a third wire rope 76 is mounted on the large pulley 75, the other end of said wire rope being attached to a block 77 of the sliding platen 2.
  • the pulleys 71, 72 and 74, 75 function as a reduction transmission and transfer the tangential generating motion between the column 3 and the sliding platen 2 to the control plate 70.
  • the wire ropes 69, 73 and 76 are tensioned by means of two springs 78 which bias the control plate 70.
  • control rails 79 and 80 acting as spaced stop members are mounted on the control plate 70 for coaction with the switch 53.
  • the control rails 79 and 80 extend at an angle, in the illustrated example relative to the direction of motion of the control plate 79, and relative to the longitudinal axis of the spindle 55 they each subtend an angle corresponding to the helix angle of the teeth of the workpiece and are adjustable parallel to themselves towards and away from each other.
  • the control unit 52 also incorporates a shaft 81 which is rotationally coupled through bevel gears 82, 83 and 84 to a threaded spindle 85 that engages a nut 86 on which a switch 87 is disposed.
  • Opposite end limiting positions of the switch 87 are defined by separate stop abutments 88, 89 respectively and these limiting positions correspond to the upper and lower limiting position of the ram 5. The distance between these positions therefore corresponds to the hypothetical ram stroke I-I
  • the reciprocating motion of the ram 5, produced by the reversing motor 68 and corresponding to the line B-B begins when the tooth flanks of the gearwheel 12 are first contacted by the two grinding wheels 6 and 7.
  • the grinding stroke then has the length l-IS min shown in FIG. 2. This is achieved by virtue of the switch 53, which co-operates with the control rail 80 as it reciprocates at the same rate as the ram 5 to provide the upper limit of the stroke.
  • the lower limit of the stroke is provided by the switch 87, co-operating with the stop abutment 89 and also reciprocating at the same rateas the ram 5.
  • the generating motion starts simultaneously with the ram motion: the generating motor turns the gearwheel 12 and drives the column 3 to produce the aplitiste tangential motion thereto. Accordingly, the control plate 70 of the control unit 52 is also moved so that the grinding stroke, limited at the top by the control rail 80 and limited at the bottom by the stop abutment 89, is gradually increased from B-B to A,-B," when it will have assumed the magnitude H The lower limit of the grinding stroke H to the line A "-C is then controlled by the control rail 79 in the further course of the generating motion.
  • the speed of the ram will be constant with the exception of the brief reversing point zones because of the preselected speed of the reversing motor 68.
  • the speed of the reciprocating motion of the two grinding wheels 6 and 7 will thus also be constant. This arrangement ensures that the grinding stroke rate per unit time is approximately inversely proportional to the grinding stroke length: the shorter the strokes, the greater their frequency; the longer the strokes, the smaller their frequency.
  • the generating speed is determined by the rotational speed of the generating motor 15, which in turn depends on the position of a cam follower roller 90 of a potentiometer 91 as indicated in FIG. 4.
  • a horizontal I W (FIG. 3) corresponding to the lower end face of the workpiece 12 extends through the area A B-B -C -D-D traversed by the grinding wheels.
  • the point B corresponds to a required .maximum generating velocity v the portion of the generating traverse along the line W between points A to C to a required minimum generating velocity v,,,,,,, and the point D again to the maximum generating velocity v,,,,,,.
  • the generating velocity over the traverse of the area is thus required to vary in accordance with the curve K.
  • the required velocity characteristic is obtained by a I form of cam that includes elements 92 and 93 adjustably disposed on the control plate of the control unit 52 to perform the function of obtaining the inclined sections of the curve K in FIG. 3.
  • the horizontal section of the curve K is obtained by an intermediate part of the cam formed by a horizontal edge of the control plate 70 between the elements 92, 93.
  • the potentiometer 91 is mounted on the control unit 52. If the control plate 70 is displaced in synchronism with the generating motion, the cam elements 92 and 93 will influence the rotational speed of the generating motor 15 through the roller 90 of the potentiometer 91, since the potentiometer is mounted on the control unit, thus providing the velocity characteristic shown at the bottom of FIG. 3. Optimum values are obtained if the generating velocity varies in inverse proportion to the grinding stroke length.
  • the length of grinding stroke will vary automatically relative to the tooth helix angle.
  • the length of grinding stroke remains constant if the tooth helix angle is 0; it will then be defined by only the two stop abutments 88 and 89, which would be adjusted in accordance with the tooth width of the workpiece 12.
  • the length of the grinding strokes would then be defined by only the two control rails 79 and 80, which would be adjusted in accordance with the generating path or generatrix line in which is the tooth system data for generating the teeth.
  • the programme for controlling the length of grinding stroke and the beginning and end points will be defined by the combined adjustment of the two end abutment stops 88 and 89, the two control rails 79 and and the angular setting of the spindle 55.
  • the generating position is the parameter for this.
  • a tooth flank grinding machine for helical gears operating in accordance with the indexing generating method and having control apparatus determining the length of stroke of the grinding means of the machine in the traverse of said means over th generating zone
  • the improvement comprising position-limiting means in said control apparatus varying the reversal points of the grinding strokes, said means including parts movable in coordinated relationship with the stroke of said grinding wheels, members cooperable with said movable parts for causing the length of grinding stroke to increase from a minimum at the beginning of the traverse of the generating zone to a maximum in a central region of the zone, and other members cooperable with said movable parts to reduce the length of stroke again towards the end of the traverse of said zone.
  • control apparatus controls the movements of a ram supporting the grinding means and comprises a first switch means and a control plate means having a relative motion to said first switch means determined by the rectilinear component of the generating motion between the workpiece and the grinding means, means being provided for adjusting the relative position of the control plate means and the first switch means, control stop means having spaced stop elements operable in conjunction with said control plate means, a second switch means cooperable with said stop elements to define limits in said rectilinear motion direction, ofa zone of motion of said second switch means, switch drive means actuating said relative motion of said first switch means in a reciprocating manner in synchronism with the ram motion and at an angle to said recilinear component direction corresponding to the helix angle of the workpiece teeth.
  • a machine wherein a nut carries said first switch means and a screw spindle coupled to the reciprocating drive of the ram supporting the grinding means has said nut threaded upon it whereby the first switch means is reciprocated in synchronism with the ram motion.
  • control plate means includes spaced linear stop members, the zone of travel of said first switch means being defined by the boundaries of the zone extending between said spaced linear stop members.
  • a machine wherein a nut carries said second switch means and a screw spindle coupled to the reciprocating drive of the ram supporting the grinding means has said nut threaded upon it whereby the second switch means moves in synchronism with the ram motion.
  • a machine according to claim 1 wherein a control cam is coupled to said control plate means to be displaced synchronously therewith, said control cam determining the generating velocity of the machine and being arranged in such manner that the velocity decreases with increase of ram stroke and increases with decrease of ram stroke.
  • control cam has a middle zone corresponding to the zone of maximum ram stroke, a linear profile being formed on the cam in said middle zone parallel to the displacement direction of the cam.
  • control plate means includes a control plate slidably mounted in the control apparatus and movable in synchronism with the ram, said stop members and the control cam being carried by said control plate, said cam comprising two control bars that are adjustable angularly relative to the control plate, said two bars representing opposite end regions of the cam profile.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Grinding And Polishing Of Tertiary Curved Surfaces And Surfaces With Complex Shapes (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
US00187792A 1970-10-16 1971-10-08 Control of tooth flank grinding machines for helical gears Expired - Lifetime US3753319A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19702050946 DE2050946C3 (de) 1970-10-16 Steuervorrichtung für die Lage des Stößelhubes des die Arbeitsbewegung ausführenden Stößels an einer nach dem Teilwälzverfahren arbeitenden Zahnflankenschleifmaschine für Schrägstirnräder

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US3753319A true US3753319A (en) 1973-08-21

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US00187792A Expired - Lifetime US3753319A (en) 1970-10-16 1971-10-08 Control of tooth flank grinding machines for helical gears

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US (1) US3753319A (enrdf_load_stackoverflow)
JP (1) JPS5410755B1 (enrdf_load_stackoverflow)
CH (1) CH529604A (enrdf_load_stackoverflow)
FR (1) FR2111211A5 (enrdf_load_stackoverflow)
GB (1) GB1334966A (enrdf_load_stackoverflow)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3916569A (en) * 1973-03-26 1975-11-04 Maag Zahnraeder & Maschinen Ag Methods of and means for producing helically toothed gears
US4028992A (en) * 1975-11-20 1977-06-14 Kuehnle Manfred R Method and means for making helical races
WO1984004064A1 (en) * 1983-04-15 1984-10-25 Ingersoll Milling Machine Co Method of generating involute tooth forms with a milling cutter
US4551954A (en) * 1983-03-11 1985-11-12 Maag Gear-Wheel & Machine Company Limited Method for controlling a grinding stroke in a gear tooth flank grinding machine
US4606153A (en) * 1983-07-08 1986-08-19 Maag Gear-Wheel & Machine Company Limited Method for controlling a grinding stroke in a gear tooth flank grinding machine operating on the indexing generating principle
RU2131795C1 (ru) * 1996-09-24 1999-06-20 Тамбовский государственный технический университет Зубошлифовальный станок с гидравлическими связями для цилиндрических зубчатых колес
US20120258647A1 (en) * 2011-03-29 2012-10-11 Liebherr-Verzahntechnik Gmbh Gear cutting machine
US20140030965A1 (en) * 2011-03-25 2014-01-30 Dalian Kede Numerical Control Co., Ltd. Fully symmetric cutter grinding machine with 5-axis and grinding wheel head bracket thereof

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH660462A5 (de) * 1981-09-14 1987-04-30 Maag Zahnraeder & Maschinen Ag Waelzverfahren zur spangebenden bearbeitung evolventenfoermiger zahnflanken mit profil- und laengskorrekturen.
CH661460A5 (de) * 1983-11-28 1987-07-31 Mo Z Shlifovalnykh Stankov Zahnflankenschleifmaschine.
CH662301A5 (de) * 1983-12-27 1987-09-30 Mo Z Shlifovalnykh Stankov Verfahren zum schleifen von zaehnen gezahnter werkstuecke.
CH664717A5 (de) * 1984-11-03 1988-03-31 Maag Zahnraeder & Maschinen Ag Verfahren und vorrichtung zur herstellung evolventenfoermiger zahnflanken.
DE3734828C1 (de) * 1987-10-14 1989-01-12 Hurth Masch Zahnrad Carl Verfahren zum Teilwaelzschleifen von Zahnraedern sowie eine dafuer geeignete Maschine
CN111097977B (zh) * 2019-12-27 2021-07-13 湖南工业大学 一种齿轮加工的无理论误差分度方法、分齿机构

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1169261A (en) * 1967-03-28 1969-11-05 Inst Werkzeugmaschinen Method of and apparatus for modifying the position of the stroke movement of a ram in gear tooth profile grinding machines

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1169261A (en) * 1967-03-28 1969-11-05 Inst Werkzeugmaschinen Method of and apparatus for modifying the position of the stroke movement of a ram in gear tooth profile grinding machines

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3916569A (en) * 1973-03-26 1975-11-04 Maag Zahnraeder & Maschinen Ag Methods of and means for producing helically toothed gears
US4028992A (en) * 1975-11-20 1977-06-14 Kuehnle Manfred R Method and means for making helical races
US4565474A (en) * 1980-11-01 1986-01-21 The Ingersoll Milling Machine Company Method of generating involute tooth forms with a milling cutter
US4551954A (en) * 1983-03-11 1985-11-12 Maag Gear-Wheel & Machine Company Limited Method for controlling a grinding stroke in a gear tooth flank grinding machine
WO1984004064A1 (en) * 1983-04-15 1984-10-25 Ingersoll Milling Machine Co Method of generating involute tooth forms with a milling cutter
US4606153A (en) * 1983-07-08 1986-08-19 Maag Gear-Wheel & Machine Company Limited Method for controlling a grinding stroke in a gear tooth flank grinding machine operating on the indexing generating principle
RU2131795C1 (ru) * 1996-09-24 1999-06-20 Тамбовский государственный технический университет Зубошлифовальный станок с гидравлическими связями для цилиндрических зубчатых колес
US20140030965A1 (en) * 2011-03-25 2014-01-30 Dalian Kede Numerical Control Co., Ltd. Fully symmetric cutter grinding machine with 5-axis and grinding wheel head bracket thereof
US9028299B2 (en) * 2011-03-25 2015-05-12 Dalian Kede Numerical Control Co., Ltd. Fully symmetric cutter grinding machine with 5-axis and grinding wheel head bracket thereof
US20120258647A1 (en) * 2011-03-29 2012-10-11 Liebherr-Verzahntechnik Gmbh Gear cutting machine

Also Published As

Publication number Publication date
FR2111211A5 (enrdf_load_stackoverflow) 1972-06-02
DE2050946A1 (de) 1972-04-20
GB1334966A (en) 1973-10-24
JPS5410755B1 (enrdf_load_stackoverflow) 1979-05-09
CH529604A (de) 1972-10-31

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