US2010965A - Precision grinding machine - Google Patents

Precision grinding machine Download PDF

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Publication number
US2010965A
US2010965A US701161A US70116133A US2010965A US 2010965 A US2010965 A US 2010965A US 701161 A US701161 A US 701161A US 70116133 A US70116133 A US 70116133A US 2010965 A US2010965 A US 2010965A
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Prior art keywords
brake shoe
stem
sleeve
block
bearings
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Expired - Lifetime
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US701161A
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Scrivener Arthur
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B41/00—Component parts such as frames, beds, carriages, headstocks
    • B24B41/04—Headstocks; Working-spindles; Features relating thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/527—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to vibration and noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2322/00—Apparatus used in shaping articles
    • F16C2322/39—General build up of machine tools, e.g. spindles, slides, actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/001—Integrated brakes or clutches for stopping or coupling the relatively movable parts

Definitions

  • the present improvements are designed with the object of neutralizing or damping-out these a predetermined braking load is applied to the minute vibrations, and of thereby/avoiding the consequent inconvenience referred to.
  • said spindle so as to operate in direct or indirect opposition to any load applied by the action of the grinding wheel, said braking load being controllable or adjustable to suit particular requirements, for example by means of an adjustable compression spring.
  • Figure 1 illustrates in transverse sectional elevation
  • Figure 2 inlongltudinal sectional elevation, vibration damper mechanism constructed according to the present invention.
  • the spindle a of the grinding machine is supported at axially spaced points within a suitable housing b by means of anti-friction bearings c and d, which may either be of ball or roller type or both, and the spindle a so mounted is fitted with a hardened steel sleeve or bush 6 concentric with the bearings and secured in a convenient position relative to the bearings, the
  • a predetermined braking load is applied to the spindle by means of a bronze brake shoe or equivalent friction pad I or brake band engageable with the outer surface of the sleeve or bush e, the braking load of this shoe or member ,1 being predetermined under control of a spiral compression spring I mounted upon the stem f carrying the shoe or member 1 and located within a barrel g disposed within the housing b in a position at nted Aug.
  • the normal bearing point of the brake shoe or 10 member f upon the sleeve or bush is preferably located for maximum efliciency on a radial line diametrically opposed to the normal line of the load applied to the spindle by the action of the grinding wheel during its working period, and it will be seen that on the predetermined load being applied to the brake shoe or band by a pre-setting of its control spring I and screw f an effective damping-out of all vibration of the antifriction bearings is obtained, resulting in the desired enhancement of the accuracy and finish of the work being ground, and ensuring also a longer working life of the bearings, as due to the absence of vibration the spindle is constrained to rotate in a true path about its axis, thereby reducing shock on the component members of the bearings.
  • a rotary shaft and means for dampening vibration thereof comprising a brake shoe operatively engaging the shaft, a stem rigid with and extending outwardly from said brake jshoe, a fixedly mounted sleeve into which said stem extends and in which said stem, adjacent to the brake shoe, has closely fitting slidable bearing engagement, a bored block threaded within said sleeve, the outer end of said stem being disposed within the bore of said block and having closely fitting slidable bearing engagement therewith, and
  • a rotary shaft and means for dampening vibration thereof comprising a brake shoe operatively engaging the shaft, a stem rigid with said brake shoe and extending outwardly therefrom, a fixedly mounted sleeve into which said stem extends and in which said stem, adjacent to the brake shoe, has closely fitting slidable bearing engagement, a block threaded within said sleeve, the outer end of the stemhaving closely fitting bearing engagement with said block, and means whereby rotation of the block varies the pressure of the brake shoe against the shaft.
  • a rotary shaft and means for dampening vibration thereof comprising a brake shoe operatively engaging the shaft, a stem rigid with said brake shoe and extending outwardly therefrom, a fixedly mounted sleeve into which said stem extends and in which said stem, adjacent to the brake shoe, has closely fitting slidable bearing engagement, a block threaded within said sleeve, the outer end of the stem having closely fitting slidable bearing engagement with said block, a shoulder on said stern, and yieldable means interposed between said shoulder and said block to be compressed by inward screwing of said block within said sleeve to maintain the brake shoe engaged under pressure with the shaft.
  • a grinding wheel shaft journaled in said bearings, a brake shoe operatively engaging said shaft between said bearings, a stem rigid with said brake shoe and extending outwardly therefrom, the housing having a bore, a sleeve closely fitted within said bore and fastened securely to the housing, the stem extending into said sleeve and having closely fitting slidable bearing engagement therewith adjacent to the brake shoe, a block threaded within said sleeve, the outer end of the stem having closely fitting slidable bearing engagement with said block, a shoulder on the stem, and yieldable means interposed between said shoulder and said block to be compressed by inward threading of the block to maintain the brake shoe engaged under constant pressure with said shaft.

Description

Aug. 13, 1935. A. SCRIVENER 2,010,965
PRECISION GRINDING MACHINE Filed Dec. 6, 1933 Pate This invention has reference to improvements in connection with precision grinding machines of the type in which the spindle is equipped with anti-friction bearings.
In grinding machines of this type it is found that minute vibrations are produced by the com- 1 ponent members of the anti-friction bearings within which the spindle is housed, and that this vibration is detrimentalboth to the accuracy and finish of the work being ground and also to the life of the bearings.
The present improvements are designed with the object of neutralizing or damping-out these a predetermined braking load is applied to the minute vibrations, and of thereby/avoiding the consequent inconvenience referred to.
According to the present invention, in a precision grinding machine of the type referred to,
spindle so as to operate in direct or indirect opposition to any load applied by the action of the grinding wheel, said braking load being controllable or adjustable to suit particular requirements, for example by means of an adjustable compression spring.
In order that the invention may be clearly understood and readily carried into practice,
reference may be had to the appended explanatory sheet of drawing, in which:-
Figure 1 illustrates in transverse sectional elevation, and Figure 2 inlongltudinal sectional elevation, vibration damper mechanism constructed according to the present invention.
In a convenient method of carrying the invention into effect, the spindle a of the grinding machine is supported at axially spaced points within a suitable housing b by means of anti-friction bearings c and d, which may either be of ball or roller type or both, and the spindle a so mounted is fitted with a hardened steel sleeve or bush 6 concentric with the bearings and secured in a convenient position relative to the bearings, the
sleeve or bush being fixed for example in an intermediate position on the spindle, between the two annular sets of bearings c and d which abut on I opposite ends of the sleeve or bush'as shown. A predetermined braking load is applied to the spindle by means of a bronze brake shoe or equivalent friction pad I or brake band engageable with the outer surface of the sleeve or bush e, the braking load of this shoe or member ,1 being predetermined under control of a spiral compression spring I mounted upon the stem f carrying the shoe or member 1 and located within a barrel g disposed within the housing b in a position at nted Aug. 13, 1935 I J a P aorsroNcmNpmG .mt n ei e t' m ham sa a 1f 3 A pplication December s, 1933; Serial No. 401,161 I 1 1 In Great BritainAhril281933 r i right angles to the axis of the spindle, the spring f being set by means of a retaining and adjusting screw block also fitted into the barrel under the protection of a terminal screw cap 9 and. the
barrel being fixed in position by means of a series 5 of screwed studs 9 passing through an apertured terminal flange of the barrel into engagement with internally screw-threaded sockets in the housing as shown.
The normal bearing point of the brake shoe or 10 member f upon the sleeve or bush is preferably located for maximum efliciency on a radial line diametrically opposed to the normal line of the load applied to the spindle by the action of the grinding wheel during its working period, and it will be seen that on the predetermined load being applied to the brake shoe or band by a pre-setting of its control spring I and screw f an effective damping-out of all vibration of the antifriction bearings is obtained, resulting in the desired enhancement of the accuracy and finish of the work being ground, and ensuring also a longer working life of the bearings, as due to the absence of vibration the spindle is constrained to rotate in a true path about its axis, thereby reducing shock on the component members of the bearings.
What I claim as my invention and desire to secure by Letters Patent is:
1. A rotary shaft and means for dampening vibration thereof, said means comprising a brake shoe operatively engaging the shaft, a stem rigid with and extending outwardly from said brake jshoe, a fixedly mounted sleeve into which said stem extends and in which said stem, adjacent to the brake shoe, has closely fitting slidable bearing engagement, a bored block threaded within said sleeve, the outer end of said stem being disposed within the bore of said block and having closely fitting slidable bearing engagement therewith, and
a spring interposed between said block and said brake shoeto be adjustably compressed by rotation of said block to maintain a constant pressure of the brake shoe against the'shaft.
2. A rotary shaft and means for dampening vibration thereof, said means comprising a brake shoe operatively engaging the shaft, a stem rigid with said brake shoe and extending outwardly therefrom, a fixedly mounted sleeve into which said stem extends and in which said stem, adjacent to the brake shoe, has closely fitting slidable bearing engagement, a block threaded within said sleeve, the outer end of the stemhaving closely fitting bearing engagement with said block, and means whereby rotation of the block varies the pressure of the brake shoe against the shaft.
3. A rotary shaft and means for dampening vibration thereof, said means comprising a brake shoe operatively engaging the shaft, a stem rigid with said brake shoe and extending outwardly therefrom, a fixedly mounted sleeve into which said stem extends and in which said stem, adjacent to the brake shoe, has closely fitting slidable bearing engagement, a block threaded within said sleeve, the outer end of the stem having closely fitting slidable bearing engagement with said block, a shoulder on said stern, and yieldable means interposed between said shoulder and said block to be compressed by inward screwing of said block within said sleeve to maintain the brake shoe engaged under pressure with the shaft.
4. In a precision grinding machine, a housing,
spaced bearings within said housing, a grinding wheel shaft journaled in said bearings, a brake shoe operatively engaging said shaft between said bearings, a stem rigid with said brake shoe and extending outwardly therefrom, the housing having a bore, a sleeve closely fitted within said bore and fastened securely to the housing, the stem extending into said sleeve and having closely fitting slidable bearing engagement therewith adjacent to the brake shoe, a block threaded within said sleeve, the outer end of the stem having closely fitting slidable bearing engagement with said block, a shoulder on the stem, and yieldable means interposed between said shoulder and said block to be compressed by inward threading of the block to maintain the brake shoe engaged under constant pressure with said shaft.
ARTHUR SCRIVENER.
US701161A 1933-04-28 1933-12-06 Precision grinding machine Expired - Lifetime US2010965A (en)

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2448341A (en) * 1944-06-30 1948-08-31 Lucien I Yeomans Inc Bearing for rotary shafts
US2909014A (en) * 1958-01-16 1959-10-20 Schumag Schumacher Metallwerke Tool-spindle journal, particularly in centerless grinding machines
US3209720A (en) * 1963-11-29 1965-10-05 Algonquin Shipping & Trading Vessel stern gear systems
US3385009A (en) * 1964-02-03 1968-05-28 Landis Tool Co Spindle bearings
US4248487A (en) * 1976-12-01 1981-02-03 Skf Nova Ab Rolling bearing
US6036371A (en) * 1997-09-22 2000-03-14 Nsk Ltd. Rolling bearing unit for vehicle wheel
US6331691B1 (en) 1999-09-20 2001-12-18 Automated Laser Corporation Precision guiding apparatus for laser marking system
US20070211976A1 (en) * 2004-05-07 2007-09-13 Fox Gerald P Locating Bearing Assembly for Wind Turbine Gearbox Shaft

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2448341A (en) * 1944-06-30 1948-08-31 Lucien I Yeomans Inc Bearing for rotary shafts
US2909014A (en) * 1958-01-16 1959-10-20 Schumag Schumacher Metallwerke Tool-spindle journal, particularly in centerless grinding machines
US3209720A (en) * 1963-11-29 1965-10-05 Algonquin Shipping & Trading Vessel stern gear systems
US3385009A (en) * 1964-02-03 1968-05-28 Landis Tool Co Spindle bearings
US4248487A (en) * 1976-12-01 1981-02-03 Skf Nova Ab Rolling bearing
US6036371A (en) * 1997-09-22 2000-03-14 Nsk Ltd. Rolling bearing unit for vehicle wheel
US6331691B1 (en) 1999-09-20 2001-12-18 Automated Laser Corporation Precision guiding apparatus for laser marking system
US20070211976A1 (en) * 2004-05-07 2007-09-13 Fox Gerald P Locating Bearing Assembly for Wind Turbine Gearbox Shaft
US7572061B2 (en) * 2004-05-07 2009-08-11 The Timken Company Locating bearing assembly for wind turbine gearbox shaft

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