US3807094A - High speed lapping machine and method - Google Patents

High speed lapping machine and method Download PDF

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Publication number
US3807094A
US3807094A US00266081A US26608172A US3807094A US 3807094 A US3807094 A US 3807094A US 00266081 A US00266081 A US 00266081A US 26608172 A US26608172 A US 26608172A US 3807094 A US3807094 A US 3807094A
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United States
Prior art keywords
gear
spindle
gears
chucking
dechucking
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US00266081A
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English (en)
Inventor
R Pigage
C Ellwanger
G Kimmet
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.)
Gleason Works
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Gleason Works
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gleason Works filed Critical Gleason Works
Priority to US00266081A priority Critical patent/US3807094A/en
Priority to GB2210073A priority patent/GB1393648A/en
Priority to IT24112/73A priority patent/IT987459B/it
Priority to FR7322291A priority patent/FR2190559B3/fr
Priority to JP48070411A priority patent/JPS4951694A/ja
Priority to CH911973A priority patent/CH574791A5/xx
Priority to DE7323671U priority patent/DE7323671U/de
Priority to DE2332410A priority patent/DE2332410A1/de
Application granted granted Critical
Publication of US3807094A publication Critical patent/US3807094A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23F—MAKING GEARS OR TOOTHED RACKS
    • B23F19/00—Finishing gear teeth by other tools than those used for manufacturing gear teeth
    • B23F19/02—Lapping gear teeth
    • 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
    • B23F23/1293—Workpiece heads

Definitions

  • a lapping type of machine is improved to reduce or eliminate unwanted periodic changes in driving moments between driving and driven gears being lapped by inserting dynamic system modifiers, in the form of energy storing or isolating devices, at critical points between the driven gear and the remaining driven elements of the machine.
  • Examples of this improvement include insertion of an elastomeric coupling in a portion of the drive train between a driven gear and a braking means of a lapping machine; provision for an arbor assembly for the driven gear which contains spring elements to permit limited rotational movements between the gear mounting elements of the arbor and the rest of the arbor assembly; and utilization of a pulley assembly which includes one or more spring devices between two major housing elements of the pulley assembly.
  • This invention relates to improvements in machines which are capable of running a pair of gears in meshing engagement for the purpose of carrying out an automatic finishing treatment of the pair of gears. More specifically, the invention is concerned with an improvement in a gear lapping machine which permits such machines to be adapted to relatively high speed lapping operations, in the range of 2,400 to 2,800 rpm (as compared to prior art lapping operations at about 1,200 rpm) without costly modification or redesign of the machines.
  • the two gears can be run together with a lapping compound applied to their surfaces to produce a matched gear set in which the two gears are highly compatible for applications requiring uniformity of motion transmission between tooth bearing surfaces when one gear is used to drive the other gear.
  • Examples of known lapping machines in this art are described in U. S. Pat. Nos. 2,691,250; 2,919,518; 2,947,120; 3,069,813; and 3,099,901.
  • the machine is improved upon by interposing a relatively simple and inexpensive storing or isolating means in its drive train at a selected critical point between the driven gear of a gear pair and the braking means which is operatively connected to the spindle carrying the driven gear.
  • the energy storing or isolating means acts to modify the dynamic system of the ma chine and may comprise an elastomeric coupling inserted in the aforesaid drive train or it may comprise improved arbor or pulley assemblies which include one or more spring devices for resisting relatively limited rotational movements between major components of such assemblies.
  • the discovery of the present invention is quite surprising in that it is the exact opposite of solutions traditionally utilized in precision machinery of this type in which stiffness is considered essential to accurate operation. That is, the use of a spring or elastomeric coupling would be expected to lead to a new problem of storing and releasing energy into a driven train in such a way as to create a new vibration or unwanted resonance.
  • the dynamic system modifiers of the present invention are completely workable because they reduce or eliminate unwanted periodic changes in driving moments, as initiated by imperfections in the driving spindle or other portions of the drive train of the machine, from developing and building up to such amplitude levels that tooth bearing patterns become non-uniform on the finished product.
  • the devices of the present invention function, in a very real sense, to prevent a magnification to significant values of periodic changes in driving moments between a pair of meshed gears running together, even though there may exist rotational deviations of a much lower, and insignificant, amplitude as a result of periodic energy storage and release into the system from the elastomeric or spring devices inserted therein.
  • Dynamic machine forces are known to increase in proportion to inertia as well as in proportion to the square of the rotational speed, and so research leading to the present invention considered the effect of inertia in a drive train system experiencing unwanted changes in the forces acting between the driving and driven gears of a pair being lapped. It was discovered that reduction of inertia in the driven portion of the drive train also functions to help dampen unwanted changes in driving moments which are created in a system and, thereby, also helps prevent a magnification or reinforcement of forces that would result in undesirable tooth contact pattern distortions in the gears being treated by the system. Therefore, the invention disclosed herein contemplate that certain components of the driven portion of the machine can be reduced in mass or weight to maintain good quality products at very high operational speeds.
  • One embodiment of the present invention provides for insertion of a dynamic system modifier in the form of spring devices in a special arbor assembly which carries the second or driven gear of a pair of gears, in a lapping machine.
  • This location for an energy storing or isolating means is theoretically desirable because it separates the gears being treated from the inertia of the substantial machine mass which comprises the driven portion of the drive train (i.e., the arbor itself, its spindle, and associated braking means for imparting a braking moment to the driven spindle.)
  • a second embodiment of the invention provides for an insertion of an elastomeric coupling in the second spindle of the machine which is operatively associated with a braking means and which carries the aforesaid arbor and second gear.
  • This embodiment offers certain practical advantages over the previously mentioned arbor modification because of certain factors relating to cost of manufacture and corrosiveness of working environment associated with the arbor assembly itself.
  • a third embodiment provides for insertion of an isolating or dynamic system modifying device in the pulley means which connects the driven spindle to the broke system thru a belt.
  • FIG. 1 is a diagrammatic illustration of a drive train system for a typical lapping machine of the type contemplated by the present invention
  • FIG. 2 is a side elevational view, in section, of an arbor assembly of a lapping machine which has been modified with the improvement of the present invention
  • FIG. 3 is a front elevational view of the arbor assembly shown in FIG. 2;
  • FIG. 4 is a back elevational view, in greatly enlarged scale, of a portion of the arbor assembly of FIG. 2 as seen generally on lines 44 of FIG. 2;
  • FIG. 5 is a side elevational view in cross section, and in greatly enlarged scale, of a detail of the arbor assembly of FIGS. 2 4, as seen on line 5-5 of FIG. 3;
  • FIG. 6 is a side elevational view, partly in cross section, of a spindle assembly associated with the arbor for the driven gears showing an installation of an elastomeric coupling therein in accordance with another embodiment of the present invention
  • FIG. 7 is an isometric view of a pair of mounting blocks used for securing the elastomeric coupling shown in FIG. 6;
  • FIG. 8 is an exploded view of a braking pulley assembly of the gear spindle provided with energy storing or isolating means in accordance with a further embodiment of the present invention, with one part of the assembly shown in enlarged scale for clarity of disclosure.
  • FIG. 1 illustrates a typical drive train system for a lapping machine of the type which can be improved upon by the discoveries of the present invention.
  • the basic arrangement of the illustrated drive train system is known in this art and does not constitute a separate invention.
  • the drive train system of FIG. 1 includes a first spindle means 10 for mounting a first gear 12 for rotation about a vertical axis.
  • the gear 12 is typically referred to as a pinion gear in the type of gear relationship illustrated in FIG. 1 and is releasably secured to the spindle 10 in any known manner.
  • the first spindle means 10 is operatively connected to a driving motor 14 through an output shaft 16 of the driving motor, a pair of pulleys and a drive belt 18, and an input shaft 20 of the first spindle means 10. In this way, the driving motor 14 functions to transmit a continuous driving moment to the first spindle means and the first gear 12 during a lapping operation.
  • a second spindle means is contained within a housing for rotation about a horizontal axis 22 and for mounting a second gear 24 in meshing engagement with the first gear 12.
  • An arbor assembly 26 functions to carry the second gear 24 on the second spindle means, and known chucking and dechucking devices are provided for securing and releasing the second gear 24 relative the second gear carried thereby during a gear lapping operation.
  • Braking moments are applied to the second spindle means through a drive belt 30 and a pair of pulleys which includes a braking pulley assembly 32.
  • the present invention provides for a reduction or elimination of unwanted periodic changes in driving moments between the first and second gears by inserting energy storing or isolating means in the drive train at one or more selected and preferred points in locations between the driven second gear 24 and its associated braking means 28.
  • FIGS. 2 5 relate to an embodiment of the present invention which provides for a modification of the arbor assembly 26 of FIG. 1 so as to isolate the substantial masses of the second spindle means and its associated structures from the second gear 24 as it is driven by the first gear 12.
  • FIG. 2 illustrates basic components of the improved arbor assembly 26 as including a first section 40 and a second section 42. These two basic sections of the arbor assembly are related to one another so that driving moments are imparted by the section 40 to the section 42 and braking moments are transmitted back from the section 42 to the section 40.
  • One or more spring means 44 which will be discussed in greater detail with reference to FIGS. 3 5, are interposed between the sections 40 and 42 so that driving and braking moments are actually transmitted through the spring means.
  • the spring means can function to minimize forces acting between the meshing teeth of the gears being lapped, since small periodic changes in driving moments received by second gear 24 are stored temporarily in the spring means 44 and are not transmitted to the remainder of the drive train, thereby apparently preventing the build up of any undesirable large changes in the driving moments as referred to above.
  • the first section 40 is formed from an inner backing ring 46 and an outer slinger ring 48 (also, see FIG. 5) secured together to define a component which can be mounted on an arbor sleeve 50.
  • the arbor sleeve 50 is carried on a centering unit 52.
  • the centering unit 52 is mounted on an actuating rod 53 of an expander unit 54 for chucking and duchucking the gear 24 relative to the arbor assembly.
  • the second section 42 of the arbor assembly is fastened to an end of a spindle section 55 mounted within a housing.
  • the spindle 55 is mounted for rotation relative to the housing, and braking moments are applied to an opposite end section of the spindle.
  • FIGS. 3 5 illustrate details of the spring means 44 and the manner in which they are mounted between the first section 40 and second section 42 of the arbor as sembly shown in FIG. 2.
  • FIG. 3 shows that the spring means 44 are carried in positions 180 apart to provide for an energy absorbing or isolating means which is effective for either direction of relative rotation between the two sections 40 and 42 of the arbor assembly.
  • the first section 40 of the arbor assembly carries a driving pin means 60 which is secured at a fixed point to the driving section 40 so as to intercept the central axis of the spring means 44.
  • the spring means 44 is carried within a bore 62 formed in the second section 42, and when compressed, the spring means 44 bears against a plunger and rod assembly 64 which makes actual contact with the drive pin means 60 of the driving section 40.
  • a spring retainer bolt 66 is threaded into a threaded end of the bore 62 to hold the spring 44 in place and to guide movement of the rod portion of the plunger and rod assembly 64.
  • FIGS. 2 5 Another feature of the arbor assembly illustrated in FIGS. 2 5 is to provide for a stop pin means 68 carried in a fixed location in the second section 42 of the arbor assembly.
  • the stop pin 68 (see phantom line illustration in FIG. 4) is positioned to normally maintain the plunger 64 out of contact with the drive pin means 60 when the arbor is at rest or when it is running in a neutral condition without any aberrations in driving moments between the two sections. This prevents a binding of the two sections 40 and 42, which might otherwise result from a continuous contact between the drive pin means 60 and the plunger head 64, and this improves speed and efficiency of operation of the energy storing or isolating devices of the arbor assembly.
  • a still further feature of the arbor assembly of FIGS. 2 5 is that the degree of compression of the springs 44 can be adjusted by adjusting the axial position of the retainer bolt 66. This is accomplished by threading the retainer bolt 66 inwardly or outwardly relative to the threaded bore into which it is received.
  • FIGS. 6 and 7 illustrate another embodiment of the present invention.
  • This embodiment provides for insertion of an energy absorbing or isolating means in the form of an elastomeric coupling 70 at some point along the length of the second spindle means of the machine illustrated in FIG. 1.
  • This embodiment provides for a reduction or elimination of unwanted periodic changes in driving moments between the gears 12 and 24 without a redesign and rebuilding of the arbor assembly 26.
  • the elastomeric coupling 70 comprises a known type of elastomeric element which is typically used in flexible coupling constructions for providing a range of torsional and axial deflection in a drive train. Such elements can be manufactured from rubber or synthetic elastomeric materials which offer resistance to lubricants and other corrosive environments in which they may be utilized. As shown in FIG. 7, the elastomeric coupling 70 is mounted between a pair of mounting blocks 72 and 74. Opposite end faces of the elastomeric coupling 70 are bolted and secured to respective end walls of the mounting blocks with the two mounting blocks being spaced apart to permit limited rotational deflection therebetween.
  • each mounting block 72 and 74 comprises a cupshaped element carrying axially extending finger portion 76 which is received within slot 78 formed between corresponding finger portion of an opposed mounting block.
  • the relationship between the finger portion 76 and slot 78 is such. that limited rotational movement can take place between the two mounting blocks 72 and 74, but extreme deflections will be stopped by a contact between edges of the extending portion 76 and slot 78.
  • a single stop limit means may be provided between the two mounting blocks if desired.
  • the mounting block 72 is secured to a cap element 80, which in turn is secured to a housing member 82.
  • the housing member 82 is keyed to a front spindle element 84 so that braking moments are transmitted through the flexible coupling 70 and to the arbor assembly 26.
  • the other mounting block 74 is keyed to a back spindle element 86, and the back spindle element carries a braking pulley 32 for receiving braking moments from the braking means 28. Any aberrations in rotational moments between the mounting blocks 72 and 74 of the elastomeric coupling 70 are absorbed by a twisting of the coupling element between the two mounting blocks.
  • FIG. 6 also illustrates a chucking and dechucking means for operating an expander element carried by the arbor assembly 26.
  • a control rod member 88 is spring urged to maintain the gear 24 in a secure mounted position on the arbor assembly 26.
  • FIG. 8 illustrates a third embodiment of the invention as applied to a modified pulley construction which can be substituted for the braking pulley 32 of the drive trainsystem illustrated in FIG. 1.
  • the modified pulley assembly includes two major housing elements 100 and 102 which are assembled so as to provide for a split pulley assembly offering limited rotation between its two housing elements.
  • element 100 is placed over the housing element 102 by insertion of a sleeve portion 104 of the housing element 102 into a cylindrical bearing ring 106 carried by the housing element 100.
  • a thrust bearing 108 is inserted over the sleeve portion 104 prior to assembly of the two major housing elements so that opposite faces of the thrust bearing 108 contact a face of the housing element 1-02 and a face of the cylindrical bearing ring 106 of the housing 100.
  • a pulley sleeve 110 is press fitted over the outside surface (not shown) of the cylindrical bearing carried by the cylindrical bearing ring 106.
  • Assembly of the elements shown in FIG. 8 places two energy absorbing devices on opposite sides of an axis of rotation 112 of the assembly.
  • One of the energy absorbing devices is shown removed from a bore into which it is secured in the assembly and is illustrated in enlarged scale for clarity of understanding.
  • This device includes a housing cylinder 114 having a bore therein for holding a spring 116.
  • a plunger and rod assembly 118 are inserted within an open end of the bore to contact the spring 116, and the housing cylinder 114 is screw threaded into a threaded bore 120 of the housing element 100.
  • a similar arrangement is provided on an opposite side of the housing element 100.
  • each of the plunger and rod assemblies contact fixed dowel elements 122 secured to the housing element 102.
  • the purpose in providing a curved surface of contact between the energy absorbing devices of the housing element 100 and fixed surfaces of the housing 102 is one of preventing a binding of the two separate housing elements as might be the case if flat surfaces were repeatedly impacted with one another.
  • the split pulley assembly of FIG. 8 offers a feature of adjustment of the degree of compression applied to the spring elements 116. This is accomplished by rotating each housing cylinder 1 14 inwardly or outwardly of its bore 120.
  • any of the above described embodiments can be further modified to reduce mass in the drive train system so as to reduce inertia magnifications in the system.
  • components of the improved arbor assembly of FIG. 2 can be formed from aluminum or other light weight materials to reduce inertia in the overall drive train system. Similar changes can be made with the arbor assembly used with the FIG. 6 embodiment of the invention. In fact a preferred utilization of the FIG. 6 concepts provides for a low inertia arbor assembly and a'reduced diameter (low inertia) spindle assembly for use with the flexible coupling 70.
  • An improved machine capable of running a pair of gears in meshing engagement at relatively high speeds for carrying out a finishing treatment, such as lapping, of the pair of gears, comprising a drive train having:
  • first spindle means for mounting a first gear for rotation, said first spindle means being operatively connected to a-driving motor which functions to transmit a driving moment to said first spindle means
  • a second spindle means for mounting a second gear in meshing engagement with said first gear, said second spindle means being operatively connected to a braking means which functions to apply a braking moment to said second spindle means during a gear treating operation, and
  • means including at least one dynamic system modifier for reducing or eliminating unwanted periodic changes in driving moments between said first and second gears during a running engagement of the two gears in a treating operation, said dynamic system modifier being interposed, in said drive train, between a driven gear of said two gears and its associated braking means.
  • the improved machine of claim 5 and including a chucking and dechucking means in said second spindle means for chucking and dechucking said second gear chucking and dechucking functions without compressing or tensioning said elastomeric coupling.
  • said means for reducing or eliminating said unwanted changes in driving moments includes low inertia assemblies interposed in said drive train between said second gear and its associated braking means.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Vibration Prevention Devices (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
US00266081A 1972-06-26 1972-06-26 High speed lapping machine and method Expired - Lifetime US3807094A (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
US00266081A US3807094A (en) 1972-06-26 1972-06-26 High speed lapping machine and method
GB2210073A GB1393648A (en) 1972-06-26 1973-05-09 Machines and methods for running pairs of gears together
IT24112/73A IT987459B (it) 1972-06-26 1973-05-15 Perfezionamento a macchina e metodo di lappatura ad alta velocita
FR7322291A FR2190559B3 (de) 1972-06-26 1973-06-19
JP48070411A JPS4951694A (de) 1972-06-26 1973-06-21
CH911973A CH574791A5 (de) 1972-06-26 1973-06-22
DE7323671U DE7323671U (de) 1972-06-26 1973-06-26 Antrieb einer Zahnradläppmaschine
DE2332410A DE2332410A1 (de) 1972-06-26 1973-06-26 Antrieb einer zahnradlaeppmaschine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US00266081A US3807094A (en) 1972-06-26 1972-06-26 High speed lapping machine and method

Publications (1)

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US3807094A true US3807094A (en) 1974-04-30

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US00266081A Expired - Lifetime US3807094A (en) 1972-06-26 1972-06-26 High speed lapping machine and method

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US (1) US3807094A (de)
JP (1) JPS4951694A (de)
CH (1) CH574791A5 (de)
DE (2) DE2332410A1 (de)
FR (1) FR2190559B3 (de)
GB (1) GB1393648A (de)
IT (1) IT987459B (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4788476A (en) * 1986-10-03 1988-11-29 Werkzeugmaschinenfabrik Oerlikon-Buhrle Ag Machine for lapping two curved-tooth bevel gears
US5090161A (en) * 1988-11-10 1992-02-25 Nissan Motor Company, Ltd. Method of producing curved-toothed bevel gear
WO2001043908A1 (en) * 1999-12-17 2001-06-21 The Gleason Works Spindle for machine tool
US20060073766A1 (en) * 2004-10-04 2006-04-06 The Gleason Works Magnetic spindle for machine tool

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4203258A (en) * 1978-12-22 1980-05-20 Held Gerhard R Gear finishing machine
AR228304A1 (es) * 1981-03-23 1983-02-15 Oerlikon Buehrle Ag Husillo de una maquina lapeadora de engranajes
JPH04165938A (ja) * 1990-10-26 1992-06-11 Matsushita Electric Ind Co Ltd モータの緩衝装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2691250A (en) * 1951-08-24 1954-10-12 Gleason Works Gear lapping machine
US2919518A (en) * 1957-03-06 1960-01-05 Gleason Works Machine for lapping or burnishing gears, or like operations
US2947120A (en) * 1957-08-10 1960-08-02 Gleason Works Machine and method for running gears together for testing and finishing
US3069813A (en) * 1961-06-26 1962-12-25 Gleason Works Testing or finishing machine for bevel or hypoid gears
US3099901A (en) * 1961-08-25 1963-08-06 Gleason Works Method and machine for finishing or testing gears
US3176512A (en) * 1961-06-26 1965-04-06 Gleason Works Machine for running gears for testing or finishing
US3293805A (en) * 1963-12-24 1966-12-27 Nat Broach & Mach Method of honing a gear

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2691250A (en) * 1951-08-24 1954-10-12 Gleason Works Gear lapping machine
US2919518A (en) * 1957-03-06 1960-01-05 Gleason Works Machine for lapping or burnishing gears, or like operations
US2947120A (en) * 1957-08-10 1960-08-02 Gleason Works Machine and method for running gears together for testing and finishing
US3069813A (en) * 1961-06-26 1962-12-25 Gleason Works Testing or finishing machine for bevel or hypoid gears
US3176512A (en) * 1961-06-26 1965-04-06 Gleason Works Machine for running gears for testing or finishing
US3099901A (en) * 1961-08-25 1963-08-06 Gleason Works Method and machine for finishing or testing gears
US3293805A (en) * 1963-12-24 1966-12-27 Nat Broach & Mach Method of honing a gear

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4788476A (en) * 1986-10-03 1988-11-29 Werkzeugmaschinenfabrik Oerlikon-Buhrle Ag Machine for lapping two curved-tooth bevel gears
US5090161A (en) * 1988-11-10 1992-02-25 Nissan Motor Company, Ltd. Method of producing curved-toothed bevel gear
WO2001043908A1 (en) * 1999-12-17 2001-06-21 The Gleason Works Spindle for machine tool
US6481508B2 (en) 1999-12-17 2002-11-19 The Gleason Works Spindle for machine tool
US20060073766A1 (en) * 2004-10-04 2006-04-06 The Gleason Works Magnetic spindle for machine tool
US8795028B2 (en) 2004-10-04 2014-08-05 The Gleason Works Magnetic spindle for machine tool

Also Published As

Publication number Publication date
FR2190559A1 (de) 1974-02-01
DE7323671U (de) 1974-01-31
IT987459B (it) 1975-02-20
DE2332410A1 (de) 1974-01-03
CH574791A5 (de) 1976-04-30
FR2190559B3 (de) 1976-06-18
JPS4951694A (de) 1974-05-20
GB1393648A (en) 1975-05-07

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