US3877273A - Gear rolling method and apparatus - Google Patents

Gear rolling method and apparatus Download PDF

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Publication number
US3877273A
US3877273A US393500A US39350073A US3877273A US 3877273 A US3877273 A US 3877273A US 393500 A US393500 A US 393500A US 39350073 A US39350073 A US 39350073A US 3877273 A US3877273 A US 3877273A
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United States
Prior art keywords
blank
roll
forming
engagement
rolls
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Expired - Lifetime
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US393500A
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English (en)
Inventor
Irven H Culver
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.)
RICHARD LEONHARD Inc A CORP OF CA
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Southwestern Industries Inc
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Application filed by Southwestern Industries Inc filed Critical Southwestern Industries Inc
Priority to US393500A priority Critical patent/US3877273A/en
Priority to CA206,870A priority patent/CA1031994A/fr
Priority to CH634376A priority patent/CH591293A5/xx
Priority to CH1109674A priority patent/CH583074A5/xx
Priority to CH634276A priority patent/CH590699A5/xx
Priority to DE2439420A priority patent/DE2439420A1/de
Priority to GB36687/74A priority patent/GB1485391A/en
Priority to GB30940/75A priority patent/GB1485392A/en
Priority to FR7429541A priority patent/FR2242174B1/fr
Priority to JP49099054A priority patent/JPS5051455A/ja
Application granted granted Critical
Publication of US3877273A publication Critical patent/US3877273A/en
Assigned to RICHARD LEONHARD, INC., A CORP. OF CA. reassignment RICHARD LEONHARD, INC., A CORP. OF CA. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: SOUTHWESTERN INDUSTRIES, INC.
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21H—MAKING PARTICULAR METAL OBJECTS BY ROLLING, e.g. SCREWS, WHEELS, RINGS, BARRELS, BALLS
    • B21H5/00—Making gear wheels, racks, spline shafts or worms
    • B21H5/02—Making gear wheels, racks, spline shafts or worms with cylindrical outline, e.g. by means of die rolls
    • 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
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49462—Gear making
    • Y10T29/49467—Gear shaping
    • Y10T29/49471—Roll forming

Definitions

  • This invention relates to gear forming and, more particularly, to the cold rolling of finished gear teeth in a virgin. i.e., substantially smooth, surface of a gear blank by the use of a forming roll in which all of the teeth on the roll are identical and are profiled along the entire length thereof to be substantially' conjugate to the teeth to be formed in the gear blank.
  • variable profile teeth may be provided either as plural sets of teeth on a single roll, or by identical teeth on a roll but in which the teeth are of variable profile axially of the roll. See, for example, US. Pat. Nos. 2,886,990, 3,580,027 and 3,611,772.
  • the United States standard pressure angle for power transmission gears and the like is The pressure angle is the slope of the gear tooth at the pitch diameter relative to a line radially 0f the gear, i.e., parallel to the tooth height.
  • the standard pressure angle in the United States was 14.5 percent.
  • Many gears of English manufacture have pressure angles of 28 or so.
  • the pressure angle increases, the force applied to a driven tooth by a driving tooth is applied more radially of the driven gear so that, for driven torque levels, bearing loads increase.
  • the pressure angle of the gear tooth is not a significant'factor.
  • the principal concerns are usually over backlash and continuity of motion transfer from gear to gear in the train.
  • the pressure angle of the individual gear teeth can be large.
  • a given metal may have good cold rollability for one usage, such as motion transmitting gears, but may have no or very little useful cold rollability characteristics for a different usage such as power transmission gears required to transmit cyclic torque loads of high magnitude.
  • gear teeth may be fully cold rolled from a virgin surface to a fully finished state by use of forming rolls in which all teeth are identical and are profiled substantially conjugate to the teeth to be rolled, if the teeth to be formed have pressure angles of about 28 or greater.
  • Another aspect of this invention in the context of fully cold rolled gear teeth, concerns the rate at which the metal deforming forces are applied to the gear blank by a forming roll.
  • This aspect of the invention is referred to herein as the soft start.”
  • the soft start features are especially useful where the gear rolling apparatus is of a centerless nature, or where the gear blank is mounted for rotation about a fixed axis but one of either the gear blank or the forming roll is undriven, in a positive sense, relative to the other.
  • the centerless rolling and idling blank features are still other aspects of this invention.
  • the gear blanks and forming roll or rolls are inter-geared so that the blank and rolls are all positively driven at predetermined relative rpms. See for example, U.S. Pat. Nos. 2,883,894, 2,886,990, and 3,580,027.
  • the forming rolls and the gear blank can be brought together under full forging force without significant adverse effect in terms of the number of teeth to be formed on the gear. Where centerless or idling blank procedures are followed.
  • This invention provides improvements in apparatus and procedures for the cold rolling of gear teeth in a virgin surface of gear blank to a finished state.
  • Such cold rolling of gear teeth is accomplished by the use of forming rolls in which the forming teeth are all identical and are of constant profile along their length on the forming roll.
  • the forming roll teeth have profiles which are essentially conjugate to the teeth to be formed.
  • This invention thus broadly summarized, includes method and apparatus in which only one of the gear blank and the forming roll are positively driven, the other of the blank and the roll being rotated in response to engagement with the positively driven element.
  • centerless rolling procedures and apparatus described herein are a form of the idling blank aspect of this invention. These features of this invention result in the ability to fully cold roll gear teeth by the use of apparatus which is substantially simplified over and less expensive than the gear rolling machines previously described and presently commercially available.
  • This invention is applicable to the cold rolling of gears for use in power transmissions gear trains or motion transmitting gear trains from the smallest pinion gear to relatively large gears such as are used in automotive transmissions and the like.
  • a principle claimed aspect of this invention pertains to the cold rolling of finished gear teeth in the smooth peripheral surface of a rotatable metal gear blank.
  • the periphery of the gear blank is forcefully engaged by the circumference of an appropriately arranged and profiled rotatable forming roll.
  • the improvement comprises establishing the desired tooth forming forceful engagement of the roll with the blank progressively from an initial engagement force over several rotations of the blank.
  • the initial engagement force is sufficient, in view of the initial contact area provided between the roll and the blank, to produce inelastic (i.e., plastic) deformation of the blank material.
  • the initial engagement force is of a magnitude which is substantially less than the ultimately desired engagement force.
  • virgin blank, virgin surface, smooth surface or unprepared surface
  • a virgin surface may be formed or machined, as by turning in a chucking machine or lathe. to a specified diameter. These terms are used to distinguish over gear blank surfaces which carry some preformed indicia or indications of desired gear tooth spacing. These terms are used to distinguish from gear blanks which have been prehobbed or the like to incorporate rudimentary teeth or tooth spacing grooves prior to commencement of the cold rolling process.
  • constant profile is used with reference to teeth on gear forming rolls in which each tooth on the forming roll is of constant profile along its length on the forming roll.
  • finished state means that the rolled teeth are not further formed or shaped after completion of the cold rolling process.
  • finished state does contemplate that the cold rolled gear may be subjected to other fabrication processes, such as hardening or polishing, which do not intentionally or significantly affect the shape or profile of the rolled tooth.
  • conjugate is used with reference to the teeth on the gear forming rolls and means that the forming roll teeth are so profiled and shaped to be effective during the last stages of the cold rolling process to form gear teeth of the desired profile in the gear blank.
  • Conjugate forming roll teeth may not exactly correspond to the profile of the inter-tooth space in the completed gear because of considerations of elasticity of the material of the gear blank and because of considerations of curvature of the forming roll.
  • Other terms of similar import which have been used previously in this technology are reciprocal" and "mirror image.”
  • FIG. 1 is a side elevation view of a soft start gear rolling tool
  • FIG. 2 is a view taken along line 2-2 of FIG. 1;
  • FIG. 3 is an elevation view, partly in section, of apparatus for holding a gear blank in a lathe, for example, for gear rolling by the tool shown in FIG. 1;
  • FIG. 4 is a side elevation view, partially in crosssection of a centerless gear rolling machine
  • FIG. 5 is a view, partly in section, taken along line 55 of FIG. 4;
  • FIG. 6 is a cross-section view taken along line 6-6 in FIG. 4; I
  • FIG. 7 is a side elevation view of a workpiece holder useful with the centerless gear rolling machine shown in FIG. 4;
  • FIG. 8 is a top plan view of the workpiece holder shown in FIG. 7;
  • FIG. 9 is an enlarged fragmentary plan view of a portion of the workpiece holder shown in FIG. 8;
  • FIG. 10 is an enlarged cross-sectional elevation view of a portion of the mechanism shown in FIG. 7;
  • FIG. II is a simplified schematic cross-section view of an aspect of the operation of the centerless rolling machine shown in FIG. 4;
  • FIG. 12 is a simplified schematic view of the rolling of a gear using the centerless rolling machine shown in FIG. 4;
  • FIG. 13 is a Table of the constraints imposed upon a workpiece during operation of the centerless rolling machine in FIG. 4 in conjunction with the workpiece holder shown in FIG. 7.
  • a gear rolling tool 10 shown in FIGS. I and 2 is usable in a lathe, for example, to cold roll gear teeth to appropriate configuration and profile in the smooth peripheral surface II of a cylindrical gear blank workpiece 12.
  • the workpiece may be held in position for rolling by a holder assembly 13 which includes a male member 14 and a female member 15.
  • the male and female members are so configured that, when they are engaged as shown in FIG. 3, they have coaxially aligned cylindrical shanks l6 and 17, respectively, adapted to be securely engaged in lathe headstock and tailstock chucks. In this manner, the holder assembly and the workpiece engaged therein may be positively driven relative to rolling tool by rotation of the headstock.
  • Male holder member I4 includes a coaxial projection 18 which extends coaxially of the holder member away from a workpiece engaging surface 19.
  • Surface 19 preferably is disposed perpendicular to the axis of shank l6 and is defined by an enlarged circumferential boss 20 of the male holder member.
  • the female holder member 17 has a similar enlarged circumferential boss 21 which defines a workpiece engaging surface 22 similar to surface l9.
  • the female holder member is coaxially recessed at 23 through surface 22 to provide snug mating engagement with the end of projection 18.
  • Projection I8 is a centering projection for workpiece 12 which preferably is formed to have a coaxial hole 24 sized to make snug mating engagement with the exterior of projection 18.
  • a dog pin 25 projects from surface 19 in spaced parallel to projection 18 for cooperation with a hold 26 in workpiece 12. Dog pin 25 and hole 26 cooperate to transfer angular motion applied to shank 16 to workpiece l2.
  • workpiece circumferential surface 11 is a virgin surface as defined above.
  • Cold rolling tool 10 includes an elongate solid barlike body 28 which preferably is proportioned and dimensioned to closely resemble the bar-like body of a tool holder of the type which is commonly used in machine shops to securely hold a high-speed steel or carbide cutting tool, and which is in turn usually clamped in a suitable holder assembly carried by the cross-slide of a lathe.
  • a forming roll 29 is rotatably supported by coaxial trunions 30 in a mount portion 31 of tool 10.
  • Forming roll 29 preferably is made ofa metal which has an intrinsic hardness and surface hardness substantially greater than the intrinsic and surface hardness of the metal defining a workpiece with which the forming roll is to be used.
  • Trunions 30 are rotatably received in corresponding coaxially aligned holes 32 formed in respective ones of parallel legs 33 of mount 31.
  • the end of the tool in which the forming roll is mounted is referred to herein for convenience as the front end of the tool.
  • Legs 33 are rigidly connected adjacent the rear of the forming roll by a bridge 34 shown best in FIG. 2.
  • the axis of the forming roll is perpendicular to and either intersects or is disposed closely adjacent to the elongate axis of body 28.
  • Bridge 34 has a rear surface 35 which normally is spaced forwardly from the front surface 36 of a stop projection 37 extended from the forward portion of body 28.
  • the upper extents of legs 33 are interconnected by a bridge 38.
  • An elongate resilient bendable beam portion 39 has its forward end securely connected to bridge 38 and has its rear extent securely connected to body 28 via an upwardly extending projection 40 carried by the body at its forward end.
  • roll mount portion 31 including legs 33 and bridges 34 and 38, beam 39 and lug 40 are all integral with each other and preferably are cut or otherwise formed from a common piece of metal.
  • beam 39 has a thickness perpendicular to its length and perpendicular to the axis of roll 29 which is substantially less than its length.
  • the beam provides cantilever support of forming roll 29 relative to a body 28'.
  • tool body 28 is engaged in a holder assembly carried by a lathe cross-slide, for example.
  • the forming roll is brought into engagement with the periphery 11 of gear blank workpiece 12, supported in chucks by the lathe headstock and tailstock, in response to infeed of the lathe cross-slide.
  • the initial contact force of the forming roll withthe workpiece circumference is relatively small and has a reaction in tool 10 which results in bending of beam 39.
  • the forming roll axis stays essentially stationary during further bending of beam 39 as further crossslide infeed occurs, until such time as bridge surface 35 engages stop surface 36 of the tool body. Thereafter.
  • beam 39 in combination with normally spaced stop surfaces 35 and 36 of the tool, constitutes a variableforce lost-motion means in the connection of roll mount 31 to tool body 28.
  • Tool body 28 constitutes means for supporting roll mount 31, and forming roll 29 carried thereby, for relative movement into and out of forceful engagement with the periphery of a gear blank workpiece.
  • the dimensioning, i.e., length, thickness, and width of beam 39 are selected in combination with the nature of the beam material so that the initial engagement force of the forming roll with the workpiece periphery is sufficient, in view of the initial contact area provided between the periphery of the forming roll and the periphery of the workpiece, to produce inelastic deformation of the material defining the workpiece.
  • This initial engagement force is substantially less than the ultimate engagement force desired between the forming roll and the workpiece to achieve cold rolling, by plastic deformation, of gear teeth of the desired profile and depth in the workpiece.
  • the periphery 41 of forming roll 29 defines a plurality of forming teeth 42 arranged so that the forming roll resembles a spur gear. It will be understood however, that the forming roll may be configured to resemble a helical gear .or a herringbone gear for the rolling of helical or herringbone teeth in workpiece l2.
  • Forming teeth 42 are profiled conjugate to the teeth desired to be formed in workpiece I2 by the cold rolling process. All of the forming teeth formed in the circumference of the forming roll are essentially identical. i.e.. are as identical as practically possible. and all have the same crosssectional profile or contour along their length. As shown in FIG. 3, it is preferred that the width of the forming roll be greater than the width. i.e.. axial dimen-' sion, of gear blank workpiece 12.
  • the diameter of forming roll 29 be substantially greater than the diameter of any gear blank workpiece with which the forming roll is to be used. In this manner. upon initial engagement of the forming roll with the gear blank workpiece. the location on the workpiece periphery which is engaged by the forming roll appears to be looking at, or be engaged by, a rack.
  • the headstock drive gearing be selected with respect to the cross-slide rate of infeed toward the workpiece so that the workpiece experiences several rotations in the period between initial engagement with the forming roll and positive engagement between tool stop surfaces 35 ad 36.
  • the ultimate desired forceful cold rolling engagement force of the forming roll with the workpiece is progressively established over several rotations of the workpiece from the initial engagement force described above.
  • cold rolling gear forming tool 10 shown in FIGS. 1 and 2 and described above, inherently provides the soft start feature referred to above.
  • forming roll 29 is passively rotatable in tool 10 and is not actively driven in the tool. Any rotation of the forming roll relative to the tool body which occurs during the use of the tool is rotation induced in the forming roll by reason of its engagement with a positively driven workpiece.
  • tool 10 also incorporates the idling blank feature mentioned above.
  • rolling tool 10 may be used to advantage in a cold-rolling gear forming process only where the gear blank workpiece and its holding assembly are of sufficient size and strength to accommodate the reaction forces associated with full forceful engagement between the forming roll and the workpiece. If desired, backup rolls may cooperate with holder assembly 13; for this reason it is preferred that the outer circumferential surfaces of bosses and 21 be cylindrical surfaces as shown at 43 in FIG. 3.
  • a centerless. soft start. cold rolling, gear forming machine 45 is shown in FIGS. 4, 5, and 6.
  • Machine 45 is particularly useful in the centerless cold rolling of finished gear teeth in the virgin surface of a pinion gear blank workpiece such as workpiece 46 shown in FIG. 9, for example. It should be understood, however, that with appropriate increases in its scantlings, the principles and features of machine 45 may be incorporated in a machine for rolling finished gear teeth in gear blank workpieces of a size like that contemplated by workpiece 12.
  • Centerless rolling machine 45 includes a base and carrier 47 for a fixed axis gear forming roll 48, and a carrier 49 for a movable axis gear forming roll 50 equal in diameter to roll 48.
  • Carrier 49 is hingeably connected to carrier 47 by hinge shaft 51 positioned parallel to and equidistantly from the axes of rotation 52 and 53 of forming rolls 48 and 50, respectively. Movement of carrier 49 about hinge shaft 51 toward carrier 47 is controlled by a soft start drive assembly 54 coupled between carrier 49 and an arm 55 secured to base and carrier 47. Retracting movement of carrier 49 about hinge shaft 51 away from carrier 47 is controlled by adjustable return drive assembly 56.
  • Carrier 47 is adapted to be secured to a suitable foundation 57 as by bolts 58.
  • forming rolls 48 and 50 are carried on respective drive shafts 59 and 60 adjacent the front end of carriers 47 and 49. respectively.
  • the drive shafts are passed parallel to each other through oversized bores 61 formed in the respective carriers to extend beyond the rear faces of the carriers.
  • Shafts 59 and 60 are rotatably supported adjacent the opposite ends of bores 61 by bearing assemblies 62, such as ball bearing assemblies.
  • Identical forming roll drive gears 63 and 64 are carried on the rear ends of shafts 59 and 60. respectively.
  • a drag brake assembly 65 such as a disk of high friction material, is engaged between the front face of each drive gear and the stationary rear faces of bearing assemblies 62, e.g.
  • the effective drag on each of the drive gears by the adjacent drag brake assembly is determined by the force of egagement between the gear and the drag brake assembly as set by a nut 66 engaged on the threaded rear end of the adjacent drive shaft for engagement with the rear face of the drive gear.
  • Each of the drive gears 63 and 64 is engaged with and driven by an intermediate gear 68 rotatably mounted on the rear end of hinge shaft 51 by a suitable bearing assembly 69.
  • a drag brake assembly 70 similar to drag brake assemblies 65, is engaged between the front face of intermediate gear 68 and the rear faces of carriers 47 and 49, as shown in FIG. 5.
  • the intermediate gear is engaged-with and driven by a drive gear 71 driven by a suitable drive motor 72 either directly or via speed reducing gears. as appropriate.
  • the gearing between forming rolls 48 and 50 and drive motor 72 is arranged so that the forming rolls rotate at about 60 rpm.
  • forming rolls 48 and 50 are rotated in the same direction at equal rates throughout motion of carrier 49 toward and away from carrier 47 during operation of motor 72.
  • a washer 73 is disposed between the rear face of each of forming rolls 48 and 50 and the inner race of forward drive shaft bearings assemblies 62, as shown in FIG. 6.
  • the forming rolls are fixed to the front end of the respective drive shafts in a keyless manner, as by friction washers 74 and nuts 75. If a friction connection of the forming rolls to the front ends of their drive shafts is used, the torque required to produce slippage of the forming rolls about their drive shafts is substan tially greater than the torque required to overcome the drag of drag brake assemblies upon drive gears 63 and 64.
  • Drag brake assemblies 65 and are provided in association with gears 63, 64 and 68 so that, during operation of machine 45, each of these gears is always backed up against its driving gear so as to overcome backlash which is always inherent in any gear drive arrangement.
  • backlash is always inherent in any gear drive arrangement.
  • the elimination of backlash from the drive gearing associated with forming rolls 48 and 50 is important in order that the forming teeth defined in the peripheries 76 and 77 of forming rolls 48 and 50, respectively, will not vary during the rolling of a single workpiece or from workpiece to workpiece once machine 45 and its workpiece holder 78 have been suitably adjusted.
  • Workpiece holder 78 is mounted to foundation 57 adjacent the front of centerless gear rolling machine 45 essentially parallel to the axes of forming rolls 48 and 50.
  • workpiece holder 78 includes a base 79 and a cover 80 which enclose and guide an elongage slide member 81 in reciprocal motion.
  • the slide member is constrained by the base and cover from rotation about its elongate extent.
  • the slide member is of rectangular crosssectional configuration to make a tight sliding fit with a correspondingly configured groove 82 formed along the length of the base and enclosed by cover 80.
  • the holder assembly is held against foundation 57 by a pair of elongate bolts 83 which are passed through oversized apertures 84, formed vertically in the holder assembly along its opposite sides intermediate its length, and into threaded engagement with foundation 57.
  • Stop means are provided in the workpiece holder for adjustably defining the extended position of the slide member toward the centerless gear rolling machine 45.
  • a pin 85 depends from the lower rear surface of slide member 81 for cooperation with the end of a bolt 86 threaded into base 79 below the slide member.
  • a lock nut 87 cooperates with bolt 86 for fixing bolt 86 in its adjusted position.
  • a lug 88 extends laterally from each corner of base 79 adjacent the lower surface of the base and is drilled and tapped to receive a vertically disposed adjustment screw 89, each of which has its lower end adapted for bearing against foundation 57.
  • the oversized holes 84 for tie-down bolts 83 facilitate fine adjustment of the position of the workpiece holder assembly on foundation 57, particularly the elevation of the front end, i.e., the end of the holder assembly disposed toward machine 45.
  • a knob 90 is secured to the rear end of slide member 81 for moving the slide member toward and away from its adjusted limiting position toward the centerless gear rolling machine.
  • the front end of slide member 81 extends from the front of base 79 and there carries on its upper extent a workpiece receiving and retaining assembly 92.
  • An upwardly opening recess 93 having a width less than the width of slide member 81, opens to the extreme front end 94 of the slide member and has its elongate extent centered with the elongate extent of the slide member.
  • a workpiece receiver member 95 is held in the appropriate position member into the slide member.
  • screw 96 is disposed adjacent the rear end of the receiver member. Screw 96 also mounts a leaf-type retainer spring 97 to the top of receiver member 95 via a shouldered washer 98 and an oversized hole 99 in the rear end of the retainer spring as shown best in FIG. 10.
  • Receiver member 95 and retainer spring 97 are defined and shaped with respect to a particular gear blank workpiece with which they are to be used. It will be understood, therefore, that receiver member 95 and retainer spring 97 as shown in FIGS. 7 through 10, for example, are defined with particular reference to pinion gear blank workpiece 46 and are shown and described for the purpose of example. It will be understood that where the gear blank workpiece has a configuration different from the configuration of workpiece 46, then the configuration and cooperation of the receiver member and retainer spring may be different from that shown in the accompanying drawings. It is because the receiver member and retainer spring are designed with respect to a particular workpiece geometry that these elements of holder 78 are removably mounted to the front end of slide member 81 by screw 96.
  • pinion gear blank workpiece 46 has a relatively large diameter elongate shank 100 on which a circumferential shoulder 101 is defined somewhat toward the rear end of the workpiece.
  • a pair of equal diameter pinion blank cylinders 102 are closely spaced adjacent each other coaxially on the front end of a pinion shaft 103 which is connected at its rear end to the front end of shank 100 via a transistion 104, shaft 103 being of smaller diameter than shank 100. All of these elements of workpiece 46 are coaxially aligned with each other and are concentric to the axis of the workpiece.
  • Pinion blank cylinders 102 are formed, as by turning or the like. to a predetermined diameter and their circumferential surfaces are virgin surfaces according to the definition set forth above.
  • workpiece 46 has the configuration described and shown because of its usage and function in the product in which it is used following rolling of gear teeth on pinion blank cylinders 102. That is. workpiece 46 is not configured to have the form described or shown because of any requirements of the gear rolling process.
  • workpiece 46 when fully finished. is used to define the output gear in a one-stage motion amplifying gear train in a friction wheel distance measuring device sold in the United States under the trademark TRAl(" by Southwestern Industries, Inc.. Los Angeles, Calif.
  • Two pinion blank cylinders are defined on workpiece 46 because of certain design features of the friction wheel measuring device which are not here pertinent, but it will be understood that, if desired. a single pinion blank cylinder having a total length equal to the aggregate length of cylinders 102 could be provided in workpiece 46 if desired.
  • Receiver member and spring 97 are configured to provide the desired receiving and positioning constraints for workpiece 46 during initial positioning of the workpiece in holder assembly 78 and during cold rolling of finished gear teeth in pinion blank cylinders 102 by use of centerless rolling machine 45. Accordingly, an upwardly opening elongate recess 105 is formed in the top of the receiver member so that the recess opens to the front end 106 of the receiver member. Recess 105 is approximately as deep as the diameter of work piece shank and has a width across the width of the receiver member which is substantially greater than the diameter of workpiece shank 100 but is less than the width of the receiver member.
  • a slot 107 is formed transversely of the entire width of the re DCver member and has a depth into the receiver member greater than the depth of recess 105. Slot 107 is of sufficient depth that when workpiece 46 is positioned in recess as shown in H0. 9, workpiece shoulder 101 is disposed in the slot but does not contact the bottom of the slot.
  • the slot has a width between its opposite side surfaces, i.e., those surfaces which extend transversely of the length of the receiver member 95 and of recess 105, which is somewhat greater than the extent of shoulder 101 along the length of shank 100.
  • Recess 105 and slot 107 are so disposed in receiver member 105 that when workpiece 46 is disposed in the recess with shoulder 101 positioned in slot 107, the workpiece projects beyond the front ends of receiver member 95 and slide member 81 so that pinion blank cylinders 102 may be moved into position between the adjacent portions of gear forming rolls 48 and 50.
  • retainer spring 97 at its end opposite from screw 96, has a hammerhead-like configuration 108 defined by a pair of tabs which extend laterally in opposite directions from the body of the spring.
  • the total transverse extent of spring 97 through the hammerhead configuration is greater than the width of retainer member recess 105.
  • Spring 97 preferably is defined by a piece of very thin sheet metal appropriately bent as illustrated in FIG. 7 so that, when workpieces 46 is disposed in recess 105 and spring 97 has its hammerhead configuration 108 engaged with the top of the workpiece, the spring exerts only sufficient downward force on the workpiece to keep the workpiece in recess 105. A retaining force of about one or two grams is sufficient.
  • spring 97 has very low stiffness such that, during the centerless rolling of gear teeth in workpiece 46, the workpiece can move upwardly out of recess 105 without causing the bias force exerted by spring 97 on the workpiece to increase appreciably.
  • the soft start drive assembly 54 of centerless gear rolling machine 45 includes an operating knob 110 which is connected to one end of an externally threaded shank 111 received in an internally threaded hole 112 formed in arm 55 adjacent movable carrier member 49.
  • Knob 110 and shank 111 preferably are integral and are coaxially bored along their length to define a hole which has (proceeding along the length of the bore from knob 110) a major diameter portion 113, an intermediate diameter portion 114 and a minor diameter portion 115.
  • a pin 116 is slidably disposed in bore minor diameter portion 115 and is fixed to movable carrier 49 by a lock nut 117, the outer surface of which defines a stop surface 118 for cooperation with the adjacent end surface of shank 111.
  • Pin 116 has an enlarged head 119 disposed in bore portion 114.
  • a compression spring 120 is disposed in the bore intermediate portion to have one end bear against pin head 119 and to have its other end bear against a plug 121 received in the bore enlarged diameter portion. Spring 120 is still relative to the bias spring 122 of return drive assembly 56.
  • the return drive assembly includes a knurled-head adjustment bolt 123 which has its shank engaged in a tapped hole formed through a finger 124 extended from carrier 49.
  • a lock nut 125 cooperates with the bolt shank between the bolt head and finger 124 for locking the bolt in its adjusted position relative to the finger.
  • the bolt shank extends through finger 124 toward the opposing stop surface of a stop pad 126 carried by base 47.
  • Spring 122 is a compression spring which is engaged circumferentially of the bolt shank between the stop pad and the adjacent surface of finger 124.
  • Bolt 123 is adjusted in carrier 49 to provide a desired limit of travel of forming roll 50 toward forming roll 48; this limit is defined in conjunction with the depth of the forming teeth on forming rolls 48 and 50,
  • FIG. 12 is a simplified illustration which. with FIG. 11, shows the engagement of a simplified workpiece 46' which has the essential characteristics of workpiece 46 (FIG. 9) but in which a single pinion blank cylinder 102' is illustrated.
  • the force of engagement of the retainer spring with the workpiece is sufficiently small that a workpiece can move laterally in recess and, within the limitations imposed by slot 107 on shoulder 101., can both rotate and move angularly in the recess. Axial movement of the workpiece in the receiver member is limited by the clearance afforded by the width of slot 107 to shoulder 101. It is assumed that when the workpiece is moved into position between the rotating forming rolls. the forming rolls are retracted from each other to provide sufficient clearance relative to the workpiece that the workpiece does not engage either forming roll.
  • the initial contact force is sufficient, in connection with the total contact area of the forming rolls with the virgin surface of the workpiece, to cause inelastic deformation of the workpiece material so that a faint trace of the forming teeth is impressed in the circumference of the workpiece gear blank cylinder.
  • initial engagement of the workpiece by the forming rolls produces a slight lifting of the workpiece out of engagement with recess 105 but not out of engagement with slot 107.
  • knob 110 produces further compression of spring 120 until such time as shank lll moves into physical contact with stop surface 118. During this interval, the force of engagement of the forming rolls with the workpiece is determined by compression forces developed in spring 120. On the other hand. once shank 111 has physically engaged stop surface 118, the force of engagement of the forming rolls with the workpiece is dependent upon the position of shank 111 in arm 55. Knob 110 is turned further to drive the forming rolls to their limiting position toward each other as defined by return drive assembly 56 and its adjustment. When the forming rolls reach their limiting position toward each other, gear teeth of the desired profile and depth will have been cold rolled from a virgin surface into the workpiece.
  • Knob 110 is then turned in the opposite direction to produce retraction of forming roll 50 sufficient to free the workpiece from the forming rolls.
  • Holder assembly slide member 81 is then retracted and the workpiece, with the desired gear teeth fully cold rolled in pinion blank cylinders 102, is then removed from the holder assembly and a new workpiece inserted in its place for rolling of gear teeth thereon.
  • the rolled pinion gears used in the aforementioned friction wheel measuring device have ten helical teeth rolled in the circumference of pinion blank cylinders 102.
  • the helix angle of these teeth is Prior to the commencement of the rolling process the pinion blank cylinders have an outer diameter of 0.0549 inches.
  • forming rolls 48 and 50 are 2 inches in diameter and have a rotational rate of about 60 rpm.
  • the holder assembly should be arranged to receive and support a workpiece so that the workpiece may move in the holder assembly in a desired manner after first being contacted by either one of the forming rolls, so that it can move in response to continued movement of the forming rolls toward each other into contact with both of the forming rolls, and so that, when engaged by both forming rolls, it can assume a position determined principally by the forming rolls themselves and the relationship of the forming teeth on the two forming rolls.
  • the presence of the drag brakes in the gearing of machine 45 keeps the gears backed up against their driving gears at all times during the gear rolling process.
  • the lack of this characteristic would allow the workpiece to pop up or down from its initial position between the forming rolls if that initial position were precisely on a line between the centers of the forming rolls and the forming rolls were forcefully applied against the workpiece at the time of initial contact.
  • the holder assembly 78 be so adjusted relative to rolling machine 45 that the workpiece is located slightly above (about 0.0002 of an inch or so) the line between the forming roll centers so that.
  • the workpiece would pop upwardly away from receiver member to pop downwardly from its position of initial contact between the forming rolls, the workpiece would move against the structure of the holder assembly, which event would generate constraints upon the workpiece redundant to the constraints imposed upon the workpiece by the forming rolls.
  • the forming rolls be of large diameter relative to the diameter of the workpiece to minimize, to the greatest extent possible. eccentric forces applied to the workpiece. ln other words, it is desirable that the forming rolls be sufficiently greater in diameter than the gear blank portion of the workpiece that the workpiece. as engaged with the forming rolls, appears to be contacted by a rack. 7
  • the first several rotations of the gear blank. after having been contacted by all forming rolls, are of particular significance. It is during these first several rotations that the basic spacing of the teeth to be formed in the blank are defined by the forming rolls.
  • the initial definition of the spacing should be very slight, i.e., the initial contact of the forming rolls with the gear blank should be sufficiently forceful to produce inelastic deformation of the workpiece material such that impressions of the forming rool teeth are left in the periphery of the gear blank.
  • impressions should be very shallow and sufficient in depth only to permit forming rolls 48 and 50 to begin to rotate the workpiece without slippage and to permit the forming rolls to move the workpiece into a satisfactory position between the forming rolls.
  • the first one or two revolutions of the workpiece after being engaged by both forming rolls is particularly important.
  • the correct number of teeth of the desired profile and depth will be rolled in the workpiece.
  • the diameter of the gear blank determines the basic number of teeth to be rolled in the workpiece, assuming that the height of holder assembly receiving member 95 is initially set consistent with the relative positioning of the forming teeth on the two forming rolls.
  • the height of receiver member 95 above foundation 57 should be adjusted so that when the workpiece is first contacted by both forming rolls, a line through the workpiece between the point of contact with a forming tooth on roll 48 to the point of contact by the first forming tooth on roll 50 passes through the axis of the workpiece.
  • the points of Contact with the workpiece by the first two forming teeth to engage the workpiece, one forming tooth being defined by roll 48 and the other by roll 50 should be at diametrically opposed locations on the workpiece. If this situation is produced. then the first impression made by forming roll 48 on the workpiece will exactly register with forming teeth on roll 50. and vice versa, after the workpiece has rotated 180 in response to being engaged between the two positively driven forming rolls.
  • the holder assembly should be adjusted on foundation 57 so that receiver member 95 is at such a height that when the workpiece is first contacted by both forming rolls, the initially contacting forming tooth on one forming roll is centered diametrically through the workpiece with the midpoint of the space between adjacent forming teeth on the other forming roll. ln this manner. the initial impressions made by one forming roll on the workpiece will register with the forming teeth on the other forming roll after the workpiece has been rotated 180 following its initial contact by both of the forming rolls.
  • the principal factor which determines a number of teeth to be formed in the workpiece is the diameter of the workpiece at its gear blank cylinder. lf the height of the receiver member relative to the forming roll axes is out of adjustment by precisely A tooth space, then the number of teeth generated in the workpiece by the cold rolling process will be twice the number of teeth actually desired and the generated teeth will have one-half the desired tooth height if, in fact, the generated teeth are recognizeable.
  • a change by A tooth space in the height of receiver member 95 relative to the forming roll axes is equivalent to a change in the angular position of one forming roll relative to the other by /2 tooth space.
  • the rolling machine is undecided and may roll the desired number of teeth on one workpiece and may roll twice the number of teeth desired on the next workpiece, all other things being equal, especially where the adjustment of the receiver member is off by /a tooth space.
  • the extent to which the cold rolling machine is, in effect, undecided as to the number of teeth it will roll in a workpiece depends upon the extent to which the adjustment of the receiver member height is in error. An error in receiver member adjustment from perfect adjustment. but different from an error equal to tooth space.
  • FIGS. 7, 8 and 9 Cartesian reference coordinates X, Y and Z are illustrated. These same coordinates are illustrated in FIGS. ll and 12 which constitute simplified schematic representations of the manner in which workpiece 46 (simplified in FIGS. 11 and 12 relative to FIG. 9) is ideally engaged during the cold rolling process by the holder assembly and by the forming rolls.
  • movement of the workpiece in the X direction is movement of the workpiece along its axis parallel to the axes of rotation of the forming rolls.
  • Movement of the workpiece in a Y direction is translation of a workpiece in a plane parallel to the plane of the forming roll axes.
  • Movement of the workpiece in a Z direction is translation of the workpiece in a plane perpendicular to the plane of the forming roll axes and parallel to the forming roll axes.
  • the other modes of movement which the workpiece may experience are angular movements of the workpiece about the same axes.
  • the table shown in FIG. 13 lists the preferred sources of constraint on the workpiece in the six modes of movement possible.
  • the constraints shown in FIG. 13 are the only constraints imposed on the workpiece as and after the trace of the forming roll forming teeth is generated in the workpiece. Accordingly, the workpiece is constrained from movement along its axis in an X direction by engagement of workpiece shoulder 101 in slot 107 of receiver member 95. This constraint on workpiece movement is particularly desirable where helical teeth are to be formed in a gear;
  • the receiver member imposes no other constraint upon movement of the workpiece such that the workpiece can move laterally in a Y direction in the holder assembly and can move upwardly in a Z direction out of the receiver member recess; downward movement of the workpiece toward the receiver member is not likely to occur where. as preferred. the workpiece is disposed slightly above the plane of the forming roll axes at the time it is initially contacted by both of the forming rolls. It will also be observed that neither the receiver member nor retainer spring 97 impose any significant constraints upon any angular modes of movement of the workpiece.
  • Forming rolls 48 and 50 per se constrain the workpiece from linear movement in a Y direction of from angular movement in a Z direction as and after the trace of forming teeth impressions are made in the workpiece.
  • the forming teeth themselves constrain the workpiece from movement linearly in a Z direction or angularly in a Y direction.
  • the only remaining mode of movement possible for the workpiece is angular motion about the X axis; there is no constraint imposed in this mode since angular motion of the workpiece about an X axis is in fact rotation of the workpiece about its own axis. which rotation obviously is desired.
  • the teeth cold rolled to a finished state in the virgin surface of the workpiece have a 30 pressure angle.
  • the only fabrication process to which these cold rolled pinion gears are subjected after the cold rolling process is a hardening process in which the tooth-form cold-formed into the workpiece is not deliberately or appreciably altered. Hardening of the cold rolled gears is done to improve the wear life of the gear in the product of which the pinion gears are components.
  • the gears with which these cold-formed pinion gears are meshed in the ultimate product are cold rolled in a continuous process from a virgin surface by use of rolling tool secured to the cross-slide ofa lathe.
  • the cold rolled gear teeth may be polished merely to improve the surface finish of the teeth. as opposed to changing or modifying the cross-sectional contour of the teeth.
  • the apparatus and procedures described above may be used to roll any tooth form desired in a cylindrical gear blank surface and not merely the helical or spur gear tooth forms mentioned specifically above. Also. the apparatus and procedures described above may be used to roll bevel gears. tapered gears or internal gears. if desired. Subject to the properties of the metals used to define the gear blank. this invention may be used to cold roll. in a single continuous process from a virgin surface. finished gears for power transmission or motion transmission gears if the generated tooth forms have pressure angles consistent with the characteristics of the blank metal.
  • Apparatus for cold rolling gear teeth into a smooth work surface of a rotatable metal gear blank by forceful engagement of the work surface with the appropriately arranged and profiled circumference of a rotatable forming roll comprising separate means for rotatably mounting a blank and a forming roll.
  • variable-force lost-motion means operatively associated with one of the mounting means and effective substantially in the direction of said relative movement for causing said'forceful engagement to be established progressively during operation of the relative movement means following initial engagement between the blank and the forming roll.
  • Apparatus according to claim 7 including means associated with only a first one of the mounting means for rotating the one of the blank and the forming roll engageable therein during operation of the supporting means to produce the relative movement and during engagement of the blank and the forming roll.
  • Apparatus according to claim 8 wherein the one of the blank and the roll engageable in the second mounting means rotates in response to said initial engagement. and the lost-motion means has a lost-motion accomodation capacity sufficient that the desired forceful engagement is established over plural rotations of the blank following the initial engagement.
  • Apparatus according to claim 8 wherein the first one mounting means is for rotatably mounting the forming roll. and the lost-motion means is operable for producing the relative movement between the mounting means.
  • Apparatus according to claim 11 including a second roll and mounting means therefor disposed in cooperation with the first one mounting means and the mounting means for the blank for engaging the blank essentially diametrically of the blank between the forming roll and the second roll.
  • Apparatus according to claim 12 wherein the second roll is a forming roll circumferentially profiled in cooperation with the first forming roll, and means associated with the mounting means for the second forming roll for rotating the second roll at a predetermined rate relative to the rotational rate of the first roll.
  • Apparatus according to claim 13 wherein the mounting means for the first and second rolls define definite axes of rotation of the respective rolls, and wherein the mounting means for the blank is defined to receive the blank for centerless rotation relative thereto.
  • Apparatus according to claim 14 wherein the blank mounting means is arranged to impose upon the blank during engagement of the blank between the rolls no significant constraint upon motion of the blank redundant to motion constraints imposed upon the blank by the rolls during engagement of the blank between the rolls.
  • Apparatus according to claim 5 wherein the apparatus is for cold rolling finished gear teeth in the blank work surface, and the forming roll circumference defines a plurality of forming teeth having constant profile conjugate to the teeth to be rolled in the blank.
  • a tool for cold rolling gear teeth in a metal gear blank comprising a forming roll of selected circumferential contour.
  • a carrier for the roll including a first part rotatably mounting the roll therein and a second part adapted to be engaged in ad supported by a tool holder and the like. and coupling means mounting the carrier first and second parts for movement of the forming roll substantially perpendicularly of its axis of rotation toward and away from a positive stop.
  • the coupling means including means resiliently biasing the carrier first part to a normal position spaced from the stop.
  • a tool for cold rolling gear teeth in a metal gear blank comprising a forming roll of selected circumferential contour.
  • a carrier for the roll including a first part mounting the roll therein for rotation about an axis fixed relative to the first part and a second part adapted to be engaged in and supported by a tool holder and the like. and coupling means mounting the carrier first and second parts for translatory movement of the forming roll substantially perpendicularly of its axis of rotation toward and away from a positive stop.
  • the coupling means including a beam spring coupled between the carrier first and second parts for resiliently biasing the carrier first part to a normal position spaced from the stop.
  • the improvement comprising positively driving only one of the gear blank and the forming roll during said engagement. and developing the forceful engagement progressively over several rotations of the blank.
  • the method of claim 22 including providing the forming roll of sufficiently great diameter relative to the blank that the portion of the blank work surface initially engaged by the roll appears to be engaged by substantially a rack.
  • the improvement comprising defining the forming teeth of such profile relative to the geometry of the blank to generate in the blank fully finished gear teeth having a pressure angle of at least substantially 28.
  • the method of claim 24 including defining the forming teeth to be of constant profile.
  • Apparatus for cold rolling finished gear teeth into a smooth work surface of a metal gear blank comprising means for rotatably mounting a forming roll having a circumference arranged and profile in combination with the geometry of the blank to form in the blank work surface gear teeth of predetermined profile when the roll is circumferentially forcefully engaged with the blank work surface.
  • means for mounting a gear blank for engagement of the work surface thereof by the forming roll. means operable for relatively moving the roll and the blank mounting means to produce engagement of the circumference of a roll engaged in the mounting means therefor with the work surface of a blank engaged in the mounting means therefor.
  • Apparatus for cold rolling finished gear teeth into a smooth peripheral surface of a metal gear blank comprising a plurality of essentially identical forming rolls each defining in the periphery thereof a plurality of forming teeth conjugate to teeth to be cold rolled in the blank. the forming teeth being of constant profile along their length.
  • Apparatus according to claim 27 wherein the blank receiving and supporting means is arranged to impose upon the blank during engagement thereof by the rolls no significant constraint upon motion of the blank which is redundant to motion constraints imposed upon the blank by the rolls during said engagement.
  • Apparatus according to claim 27 wherein the forming rolls are mounted for rotation about parallel axes disposed substantially symmetrically about the received and supported position of the blank.
  • Apparatus according to claim 30 wherein there are two forming rolls.
  • Apparatus according to claim 31 wherein the blank receiving and supporting means is arranged to support the blank substantially in a plane common to the roll axes upon engagement of the rolls with the blank.
  • Apparatus according to claim 31 wherein the means supporting the roll mounting means include a hinge connection between the roll mounting means. the hinge axis being equidistant from the two roll axes.
  • Apparatus according to claim 27 including means coupled to the roll mounting means for moving the rolls into forceful engagement with a blank disposed therebetween and including means for establishing said forceful engagement progressively over several rotations of the blank following initial engagement of all of the rolls with the blank.
  • the force establishing means includes variable-force lostmotion means defined to cause the rolls substantially on said initial engagement with the blank to apply to the blank a force which, in cooperation with the initial contact area of the rolls with the blank, is sufficient to produce inelastic deformation of the blank peripheral UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION PATENT NO. 1 3, 77,273

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Forging (AREA)
  • Gears, Cams (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
US393500A 1973-08-31 1973-08-31 Gear rolling method and apparatus Expired - Lifetime US3877273A (en)

Priority Applications (10)

Application Number Priority Date Filing Date Title
US393500A US3877273A (en) 1973-08-31 1973-08-31 Gear rolling method and apparatus
CA206,870A CA1031994A (fr) 1973-08-31 1974-08-13 Methode et materiel de laminage de pignons
CH634376A CH591293A5 (fr) 1973-08-31 1974-08-14
CH1109674A CH583074A5 (fr) 1973-08-31 1974-08-14
CH634276A CH590699A5 (fr) 1973-08-31 1974-08-14
DE2439420A DE2439420A1 (de) 1973-08-31 1974-08-16 Verfahren und vorrichtung zum rollen von verzahnungen
GB36687/74A GB1485391A (en) 1973-08-31 1974-08-21 Gear forming
GB30940/75A GB1485392A (en) 1973-08-31 1974-08-21 Gear forming
FR7429541A FR2242174B1 (fr) 1973-08-31 1974-08-29
JP49099054A JPS5051455A (fr) 1973-08-31 1974-08-30

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US393500A US3877273A (en) 1973-08-31 1973-08-31 Gear rolling method and apparatus

Publications (1)

Publication Number Publication Date
US3877273A true US3877273A (en) 1975-04-15

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ID=23554941

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Application Number Title Priority Date Filing Date
US393500A Expired - Lifetime US3877273A (en) 1973-08-31 1973-08-31 Gear rolling method and apparatus

Country Status (7)

Country Link
US (1) US3877273A (fr)
JP (1) JPS5051455A (fr)
CA (1) CA1031994A (fr)
CH (3) CH583074A5 (fr)
DE (1) DE2439420A1 (fr)
FR (1) FR2242174B1 (fr)
GB (2) GB1485392A (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4706483A (en) * 1982-08-03 1987-11-17 Equipements Automobiles Marchal Method and device for finishing by burnishing of a helical thread cut on a cylindrical component
US5711187A (en) * 1990-10-08 1998-01-27 Formflo Ltd. Gear wheels rolled from powder metal blanks and method of manufacture
US9597743B2 (en) 2014-01-17 2017-03-21 Sikorsky Aircraft Corporation Machine for machining gear teeth and gear teeth machining method
US20170314664A1 (en) * 2014-10-22 2017-11-02 Zf Friedrichshafen Ag Gear pair of a gearbox

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4022044A (en) * 1976-06-18 1977-05-10 Southwestern Industries, Inc. Machines for centerless cold rolling of gears

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2849904A (en) * 1955-09-23 1958-09-02 Louis G Hill Device for serrating a shaft
US3704612A (en) * 1968-04-08 1972-12-05 Hurth Masch Zahnrad Carl Toothed tool and device for chipless generation of gears
US3738140A (en) * 1971-07-06 1973-06-12 Lear Siegler Inc Gear rolling machine
US3745851A (en) * 1971-12-23 1973-07-17 North American Rockwell Power toothed transmission device

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3631704A (en) * 1970-01-12 1972-01-04 Teledyne Inc Apparatus for roll forming toothed workpieces

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2849904A (en) * 1955-09-23 1958-09-02 Louis G Hill Device for serrating a shaft
US3704612A (en) * 1968-04-08 1972-12-05 Hurth Masch Zahnrad Carl Toothed tool and device for chipless generation of gears
US3738140A (en) * 1971-07-06 1973-06-12 Lear Siegler Inc Gear rolling machine
US3745851A (en) * 1971-12-23 1973-07-17 North American Rockwell Power toothed transmission device

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4706483A (en) * 1982-08-03 1987-11-17 Equipements Automobiles Marchal Method and device for finishing by burnishing of a helical thread cut on a cylindrical component
US5711187A (en) * 1990-10-08 1998-01-27 Formflo Ltd. Gear wheels rolled from powder metal blanks and method of manufacture
US5884527A (en) * 1990-10-08 1999-03-23 Formflo Limited Gear wheels rolled from powder metal blanks
US9597743B2 (en) 2014-01-17 2017-03-21 Sikorsky Aircraft Corporation Machine for machining gear teeth and gear teeth machining method
US9956631B2 (en) 2014-01-17 2018-05-01 Sikorsky Aircraft Corporation Machine for machining gear teeth and gear teeth machining method
US20170314664A1 (en) * 2014-10-22 2017-11-02 Zf Friedrichshafen Ag Gear pair of a gearbox
US10612639B2 (en) * 2014-10-22 2020-04-07 Zf Friedrichshafen Ag Gear pair of a gearbox

Also Published As

Publication number Publication date
CA1031994A (fr) 1978-05-30
GB1485392A (en) 1977-09-08
DE2439420A1 (de) 1975-05-07
CH591293A5 (fr) 1977-09-15
CH583074A5 (fr) 1976-12-31
GB1485391A (en) 1977-09-08
CH590699A5 (fr) 1977-08-15
FR2242174A1 (fr) 1975-03-28
FR2242174B1 (fr) 1983-04-15
JPS5051455A (fr) 1975-05-08

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