US2192486A - Lens grinding and polishing machine - Google Patents

Description

March 5, 1940.-.. Y w, A, LOCKHART l 1 2,192,486 v I LENS GxIND-ING AND POLISH'ING MACHINE Filed sept. 1, 1937 Ve 'sheets-sheet 1 V l /4 1 *|l\o`s [38 As' A mgm - ATrnRnEY w.I A. LocYKHAR-r l l2,192,486 LENS lGRINDING AND PLIsHING MACHINE Maurch 5, 1940.

Filed Sept. l, 1937 l 6 Sheets-Sheet 4 mi( @M ATT URNEY March 5, 1940. w, AQ LOCKHART LENS GRINDING AND POLISHING MACHINE Filed Sept. l1, 1957 6 Sheets-Sheet 5 l ATTEIHHEY March 5,-1940. w. A. LocKHAR-r LENS GRINDINGAND POLISHING MACHINE Filed Sept. 1, 1957 6 Sheets-Sheet 6 lNvl-:NT DR Jmf @www ATTDRNEY Patented Mar. 5, v11940 Y y lauren` STATES LENS GRINDING AND POLISHING MACHINE William A. Lockhart, Waterloo, N. Y., assigner tc Shuron Optical Company, Inc., Geneva, N. Y., a corporation of New York Application September 1, 1937, Serial No. 161,985

14 Claims.

This invention relates to improvements in a -surface or lens grinding and polishing machine, in which a plurality of (in this instance two) grinding and polishing couples. each consisting of a lens holder and grinding lap, are operated in synchronism by a combination of two reciprocative movements and two variations or break-up movements. The two reciprocative movements operate in different directions, preferably at'right angles to each other, and the two continuous variation or break-up movements operate in conjunction with the reciprocative movements; whereby the paths of travel of the movable elements of the grinding and polishing couples are changed during successive strokes so that each lens will be moved relative to the grinding surface of the couple through a series of curvilinear strokes to thereby produce surfaces which are free from deformations and waves. This invention is an improvement on the structure shown in Patent No. 1,709,943, issued to E. M. Long, April 23, 1929, and also on my co-pending application, now Patent No. 2,168,343, issued- August 8, 1939.

An object of this invention is to provide a machine, which is of improved simplified construction, for grinding and polishing the surfaces of lenses or analogous objects; that is, a machine ywherein the various movable parts thereof will operate more eiiicaciously than heretofore, and thereby more Vexpeditiously and accurately grind or polish such surfaces to the desired contour and nish.

A more specific object of the invention is to provide a grinding and polishing machine of the above mentioned class with improved mechanisms associated with the two major ,or reciprocative movements for producing a break-up in the strokes thereof whereby the path of transversing A0 movement of the movable elements of each grinding and polishing couple will be caused to vary throughout successive strokes of a cycle of operation, and particularly to produce alterations in the positions of reversal at the ends of successive strokes of the relative movement of the lens, or other object, and the grinding surface or lap, and thereby to greatly increase the duration of each cycle of operation or the period between r the operation of the lens, or other object,a second time through a given path; so that the lens or object will not be moved twice through the same path or a portion thereof during the time ordinarily required to grind or polish a surface there- 5 of, and therefore any minutev inaccuracies 0ccurring in the surface of the lap will not be reproduced on the surface being ground.

`Other specic objects of the invention are: First, to provide a connecting rod associated with one of the major or reciprocative movements of 5 the grinding and polishing couples which is of improved, simplified construction and which is arranged to operate in an improved, more direct manner than the corresponding connecting .rod shown in the above mentioned patent; second, 10 to provide an improved structure connecting the main drive element or shaft with the reciprocating members or rock frame 3, associated with the two reciprocative movements to break up or alter the normall movements thereof, so that a slow, 15 continuous change in the path of the relative Y movement of a lens and the grinding orpolishing surface, and particularly in the reversing points thereof throughout successive strokes of the cycle of operation over an extendedbr indefinite period 20 and thus eliminate the formation of lines, waves or other defects in the lens surface which may cause a zone or aberration; third, to provide the drive mechanism with a simply constructed clutch means whereby the movable elements of the 25 grindingp and polishing couples may be selectively operated at either of two speeds,-a relatively slow speed for wax polishing and when grinding high or complex curved surfaces, or a relatively high speed for'grinding surfaces of relatively low 30 pitcher curves, -depending upon the operation -to be performed; fourth, to provide a removable rouge feed whereby the same may be used only when a surface is being polished; fth, to provide the drive elements or arms for transmitting mo- 35 tion from the reciprocating members or rock frames to the work or lens holders which are of improved structure. In' carrying out this object, the drive arms or elements are so constructed that the weight thereof is arranged as close to 40 the axis of movement or rotation of the elements as possible, whereby saidv elements will operate with a minimum amount of vibration and power and the pressure between the works and grinding lap or surface will be maintained more nearly '45 uniform, particularly at the point of reversal of the drive elements or arms at the end of one stroke and the beginning of the next stroke; sixth,

Ato provide an improved selective tension means whereby the work may be readily. moved into and maintained in operative relation with the grindingand polishing surface under a predetermined pressure, that is, a pressure most advantageous'to the form or type of the worksurface being ground.

or polished; seventh, to so construct this machine that the various moving parts thereof will be adequately lubricated for an extended or indciinite period so that the machine will successfully operate without a continuous iiow of lubricating iiuid to the various bearing members thereof and the mechanism for producing such iiow.

Other objects and advantages relating to the speciiic construction of the parts of the machine will more fully appear from the following description taken in conjunction with the accompanying drawings in which:

Figure 1-is a front elevation of a lens grinding and polishing machine embodying the various features of thisinvention.

Figure 2 is a top plan, partly broken away and in sections, of the machine shown in Figure 1 witlthe top removed to illustrate the interior construction.

Figure 3 is a detail longitudinal vertical sectional view taken substantially on line 3 3, Figure 2.

Figure 4 is a detail vertical sectional view taken on line 4 1, Figure 3.

Figure 5 is a detail horizontal sectional view taken substantially on line 5 5, Figure 3, illustrating the greater portion of the gear case or housing and the bearing bracket in elevation.

Figure 6 is a detail horizontal sectional view on an enlarged scale, taken substantially online 6 6, Figure 3.

Figure '7 is a vertical sectional View taken on line 1 1, Figure 3.

Figure 8 is a longitudinal vertical sectional view taken on line 8 8, Figure 2.

Figure 9 is a detail vertical sectional view taken substantially inv the plane of the line 9 9, Figure 8, anouter end portion of the lens driving member or arm and the lens holder connected thereto being broken away.

Figure 10 is a longitudinal vertical sectional view, partly in elevation, taken substantially in the plane of the line I Il I Il, Figure 2.

Figure 11 is a detail sectional view taken on line II II, Figure 10.

Figure 12 is a detail horizontal sectional View taken on line I 2 I 2, Figure 10.

Figure i3 is a detail vertical sectional view of the upper portion of the supporting frame illustrating my novel mechanism for producing a predetermined pressure between the lens and the grinding surface or lap. in side elevation, as

viewed from line I3 I3. Figure l.

Figure 14 is a detail vertical sectional view through the pressure producing mechanism taken substantially on line I 4 I4. Figure l.

Figure 15 is a horizontal sectional view taken substantially on line I5 I5, Figure 13.

Figure 16 is a detail vertical sectional view of the upper end portion of the rn'essurev producing mechanism shown in Figure i3 taken substantially on line I6 I6. Figure 15.

Figure 17 is a horizontal sectional view through the guide post and sleeve taken substantially on line I1 I1. Figure 13.

Figure 18 is a sectional view taken on line I8 I8, Figure 6.

Figures 19 to 22 inclusive are diagrammatic views illustrating the operation of my novel motion break-up mechanism associated with the reciprocative movement operating substantially parallel with the base axis nf the lens.

Figure 23 is a.` diagrammatic plan View of one of the lens holder drive elements illustrating the reciprocative movement thereof operating substantially parallel with the cylinder axis of the lens being ground and which is usually called the cross stroke.

Figure24isavlewsimilartoFlgm-e23 illustrating the reclprocative movement of a lens holding drive element operating substantially parallel with the`base axis of the lens being ground and which is usually called the lengthwise stroke.

Figure 25 is a diagrammaticview illustrating the action of the drive element upon the lens holder when' grinding or polishing a convex surface.

Figure 26 is a view similar to Figure 25 illustrating the action of the drive element upon the lens holder when grinding a concave surface.

Figure 27 is a diagrammatic view illustrating succeeding strokes of a lens over the grinding surface of a lap produced either by the cross stroke or the lengthwise stroke of the drive element.

Figures 28, 29, 30 and 31 are diagrammatic views illustrating the path of travel of a given point on the lens, for instance the center, over the grinding surface of the lap, each gure showing the movement of the lens through ten consecutive revolutions of the drive shaft.

I'he construction illustrated in the drawings comprises a main supporting frame I consisting of a substantially rectangular housing section 2 and a top section or cover 3 removably secured to the housing 2 by any suitable means. I'he housing 2 in this instance has the lower side thereof open and is provided with a pair of ribs 4 extending transversely therethrough adjacent the bottom or lower edge in spaced relation to each other. The top section 3 may, as indicate in Figures 1 and 3, have an opening 3' in the upper side thereof which is closed by a lid 5. A main drive shaft 6 is journaled in suitable bearings l and I to revolve about a horizontal axis. The bearing 'I is mounted in one of the end walls of the housing section 2, while the bearing 1I is mounted in a bracket 8 secured to the rear side wall of said housing intermediate the ends thereof. One end of the shaft 6 extends some distance outwardly beyond the adjacent end wall of the housing 2 and has secured thereto a hand wheel 9 by which the shaft may be manually rotated.

Mounted upon the shaft 6 intermediate the hand wheel 9 and housing 2 is a simple drive mechanism adapted to be connected with any suitable source of power, not shown, as by a belt I 0 whereby the shaft may be rotated at either of two speeds. This drive mechanism comprises a pair of grooved pulleys II and I2 mounted upon the shaft 6 in axial spaced relation to each other and a pair of fiat faced pulleys I3 and I4 positioned intermediate the pulleys IIJ and II. The grooved pulley II is fixed to the shaft 6 by any suitable means, as a pin I5. while the other grooved pulley I2 is loosely mounted on said shaft to rotate relatively thereto. The pulleys II and I2 are connected by belts I 6 andkI'I to similar pulleys I8 and I9 rotatably mounted upon a shaft 20 secured to the housing 2 in front of the shaft 6. pulleys I8 and I9 being connected to each other. as shown in Figure 2. to rotate in unison. The pulley II is preferably of greater diameter than the pulley I2, while the pulley I8. connected by the belt IB to pulley I I is of smaller diameter than the pulley I9 which is connected by belt II to pulley I2, as clearly illustrated in Fig-ure 2. The pulleys I3 and I4, which are adapted to be operated by the belt I0 are loosely mounted upon the shaft Il to rotate relative thereto. The pulley I4 is an idler pulley and, as shown, is mounted upon a roller bearing 2| mounted upon the hub portions l2' and I3' of pulleys I2 and I3 respectively.

The pulley I3 is adapted to be connected with either pulley II or I2 by a simple clutch mechanism which, as shown, consists of clutch pins 22 mounted in the hub portions II' and I2' of pulleys I I and I2 respectively and a clutch pin 23 mounted in the hub portion I3' of the pulley I3. The clutch pins 22 are flxedly secured to the respective hub portions II' and I2' to extend inwardly toward each other beyond the adjacent surfaces Aof said hub portions into corresponding -recesses 24 provided between the pulleys I3 and pulleys II. and I2, as shown in Figure 3. The clutch pin 23 is slidably mounted in thehub portion I3' of pulley I3 for movement into and out of engagement with the pins 22. 'I'he clutch pin 23 is moved axially relative to the pulley I3 by a cam rod 25 which extends inwardly from the outer face of the pulley I3 through a suitable hole provided in the pulley and has the inner end thereof provided with an eccentric portion or extension 25' received in a suitable aperture provided in the pin 23 intermediate the ends thereof. The cam rod 25 is maintained against outward axial movementby a, pin 26 which extends diametrically through the rod adjacent the outer wall of a slot 21 formed in thev web portion of the pulley I3.

It will now be observed thatv when the belt I 0 is shifted from the idle pulley I4 onto the drive pulley I3, motion from the pulley I3-may be transmitted either directly tothe'pulley II and shaft 6 through the medium of clutch pin 23 and one of the clutch pins 22 connected with pulley II so that the shaft 6 will be operated at the same speed as the pulley I3. If, on the other hand, it is desired to operate the shaft at a slower rate of speed than that of the pulley I3, the clutch pin 23 may be moved by rotating the cam rod 25 out of engagement with the clutchv pins 22 associated with the pulley II into operative engagement with clutchv pins 22 associated with the pulley I2. Rotation of the pulley I3 will now transmit motion through the pulley I2 and belt I1 to pulleys I9 and I8 and then through belt I6 to pulley II and shaft 6.

The shaft 6 is adapted to operate the movable elements of the two lens surface grinding and polishing couples which comprise a grinding lap 28 mounted `on a relatively stationary lap supporting element 29 and-a work or lens supporting block 30 operatively connected to a lens driving element for moving the work or lens as L, Figures 10, 13, 14, across and upon the upper surface of a lap 28. The laps 28 are of course of various contours and must be interchanged from time to time upon the supporting element 29. For this reason each lap is releasably held in operative position on a support 29 by a plate 33 arranged at the front side of a supporting block 34 and a second plate 35 positioned at the rear side of said block, as illustrated in Figure 9, said plates being clamped to the supporting block by a screw 36. The blocks 34 are each provided with a pendant hollow hub 34' which is adapted to removably receive the upper end portion of a bolt 31 mounted on a, boss 38 provided in the bottom wall 38 of a catch basin 39, see Figure 10.

`The supporting -elements 29 are removably mounted on the bolts 31, and in order that these elements may be releasably maintained in operative position, the upper end portion of each bolt l 31 isprovided with'a pin 40 which is adapted to be received in an elongated slot 4I extending upwardly from the lower end of each -hub portion -34' as shown in Figure 10. The supporting elements 23 are constructed with hubs 34' of dif-- ferent lengths so as to adapt them for maintaining the grinding lap 28 at different elevations with respect to the driving elements 31,50 as to adapt is a relatively long member, as illustrated at the left hand side of Figure 10. If,on the other hand, a minus or concave lens is being ground or polished, the same is maintained at a relatively low level and the hub 34 is a relatively short member, as illustrated at the right hand side of Figure 10. Also, if a substantially fiat lens is to be ground or polished, the lap 28 will be maintained at an intermediate position and the hub 34 will be of intermediate length.

The catch basin 39 is removably secured to the housing 2 by a pair of bolts 43 extending through corresponding holes or apertures at opposite ends of the catch basin 33, and are screwthreaded in the front wall of the housing 2. Each of these bolts 43, as shown more particularly in Figure 11, are of substantially uniform diameter throughout the length thereof, and is provided with an annular recess or groove, 43 in the periphery thereof a short distance from the outerl end, A slotted washer 44 extends into the groove 43' for maintaining the catch basin against outward 4movement axially from the screws `43. The washers 44 are clamped in the grooves 43' when the screws 43 are tightly screw-threaded in the housing 2; and when it is desired-to remove the catch basin, it is only necessary to rotate the screws 43 to move them axially outwardly a short distance relatively to the housing 2 to release the washers 44. Then by removing the washers from their respective grooves 43', the catch basinl may be drawn outwardly over the screws and thus removed from the housing 2. Likewise, the catch basin may be readily mounted on the housing 2 by sliding them onto the screws 43, inserting the washers 44 in the grooves 43' and then tightening the screws. I

Lens drive element The lens driving elements 3| are of novel construction and, as shown in Figures 2 and 14, each comprises a spindle 46 journaled in suitable ball bearings 41 mounted in theouter end portions 48 of a D-shaped -frame 49 which is rotatably supported by stub shafts or studs 50 carried by a. substantially horizontally disposed floating member or beam 5| mounted in the housing 2 in front of shaft 6. Each spindle 46 extends outwardly from the interior of the housing 2 through an opening 52 provided in -the front wall of the housing 2 and has connected to the outer end thereof a drive frame 53 for the lens holder or supporting block 3l. Each drive frame 53 compr'ses a substantially U-shaped-bracket 54 and a saddle memberI 55. The bracket member 54 has the center thereof provided with a hollow hub 54 which is adapted to removably receive the outer end of the spindle 46 therein. The bracket 54 is secured to the spindle 46 by means of a pin 56 which extends through the hub 54 and said spindle. The outer ends of 'the arms 54" of the bracket 54 are provided with hardened bearings 51 adapted to be engaged' by pointed pins 58 mounted on the opposite ends of the saddle member 55 which, in turn, is adapted to receive a supporting lens'block holder 59 which is secured to the central portion of the saddle 55 by a screw 60, as shown in Figures 2 and 14.

The lens block holder 59 comprises a body portion 6| provided with a shoulder 6| at the lower, inner or rear edge thereof. A clamp plate 62 is secured by a screw 63 to the outer face of the body portion 6| for firmly clamping the rib 64 of the lens holder 30 between the lower edge thereof and the shoulder 6 I The bearing members 51 are tightly secured in the opposite ends of the bracket member 54 and are provided with conical sockets in their lower faces for receiving the upper tapered ends of the pins 58 which engage the sockets in about the horizontal plane of the axis of rotation of the corresponding spindle 46, as illustrated in Figures 10 and 13. As shown in Figure l0, the central portion of each saddle member 55 extends across and some distance above the upper surface of the lap 28 and with the opposite side portions 55" of the saddle extending downwardly in diverging planes to a position below the adjacent ends of the bracket 54 to support the bearing pins 58 and to allow free lateral rocking movement of the saddle and its lens block holder 59 without liability of contact with the lap or its supporting means.

In order that lenses of various curvatures, whether concave or convex, may move across the surface of the lap 28 with a minimum. amount of power and with a substantially uniform pressure maintained between the lens and the grinding surface of the lap, the side portions 55 may vary materially in length in different saddle members 55. The reason for this is to maintain the lens at one or the other side of the horizontal plane passing through the axis of rotation of the spindle 46, depending upon the curvature of the surface being ground. That is, when the surface to be ground is of convex curvature, the side portions 55' are of relatively long length so as to hold the lens above the horizontal plane passing through the axis of rotation of the spindle 46, as shown at the left hand side of Figure 10.

On the other hand, if the surface to be ground is of concave form, then the side portions 55 of the saddle are of relatively short length so as to maintain the lens, and particularly the surface thereof to be ground, below the horizontal plane passing through said spindle 46, as illustrated at the right hand side of Figure 10. Again, if the surface of the lens, or other object to be ground, is substantially fiat the side portions 55 of the saddle are of medium length so as to maintain said surface to be ground in substantially a horizontal plane passing through the axis of rotation of the spindle 46.

To explain more explicitly, the co-action of the various members of a lens drive element 3i and the lap 28 when polishing lenses or other objects with surfaces of different curvatures, let it be assumed, first, that a plus or convex lens as illustrated at the left hand side of Figure 10 and in Figure 25 is to be ground. This lens L is positioned, as shown, with the surface thereof to be ground above the axis X-X of rotation of the spindle 46 by the selection of a saddle member 55 having relatively long side portions 55 and a lap support having Va relatively long hub 34'.

It will now be apparent that inasmuch as the longitudinal thrust of the spindle 46 upon the lens holder 30 is applied at the points of contact of the pins 58 with bearings 51 below the connection of the lens with the surface of the lap 26, the frictional resistance to the movement of the lens over the lap will tend to rotate the holder 30 and saddle 55 in a direction opposite to that of the movement of the spindle 46, as indicated by arrows N and N', Figure 25. The forward edge of the lens will therefore tend to move away from the curved portion of the lap surface coincident therewith at the beginning of each stroke of the drive element 3|, so that the lens will tend to rock about the center of curvature of the grinding surface of the lap and thus prevent excessive or uneven friction between the lap and lens.

If, on the other hand, a minus or concave lens is to beground, a saddle 55 and lap support will be chosen having relatively short side portions 55' and a relatively short hub 34' respectively, as illustrated on the right hand side of Figure 10 and in Figure 26 so as to position the lens surface to be ground below the axis X--X of rotation of spindle 46 and therefore below the point of contact of pins 58 with bearings 51. In this arrangement ofthe parts, the thrust of the spindle 46 during the axial movement thereof upon the lens holder 30 will be applied-to said holder'at the same side of said lens surface as the connection of the lens with the lens holder. It therefore follows that the force produced by the thrust of the lens upon the upwardly inclined central portion of the said lap at the beginning of each stroke will be applied to the lens holder radially outward from the surface of the lens contacting with the lap. This will tend to rock the lens holder forwardly or in the direction of movement of the spindle'46 as indicated by arrows N and N', Figure 26 and thereby tend to rock the lens holder 20 and'the lens carried thereby about the center of curvature of the lap surface or in the direction of curvature of the grinding surface of the lap, so that the lens will move smoothly along said surface of the lap in substantially coincidental contact therewith and therefore with a minimum amount of lateral thrust upon the surface of the lap, particularly at the beginning of each stroke.

`When a lens with a substantially at surface is to be ground, a saddle member 55 and lap holderv 29 will be chosen which will maintain such surface of the lens substantially in the plane of the axis X-X of rotation of the spindle 46. When the surface to be ground is in this position, the line of thrust of the spindle 46 during an axial movement thereof upon the lens holder is substantially coincident to the line of thrust of lens upon the grinding surface of the lap so that the tendency of the lens holder to be rotated upon the axis extending through the points of the pin 58 is reduced to a minimum, and the surface of the lens will be maintained in substantially coincidental contact with the grinding surface of the lap.

It will therefore be seen that it will be necessary to frequently change the saddle members in order to successfully grind surfaces of different curvatures, and this is readily accomplished due to the fact that the pins 58 have merely a bearing engagement with the bearings 51 so that the saddle members may be readily removed from the corresponding bracket 54 by merely separating the bearing members 51 from the pins 58.

The term "coincidental contact is used in the specifications and claims to designate that rela- Y gular relation with respect to each other.

The hereinbefore mentioned stub shafts 50 and 50' which rotatably support the-D frames 49 have the outer end portions and the central portion thereof respectivelyv secured to the oat,

ing beam or member while the opposite end portions of the shaft 50 and the outer end portions of the shaft 50' are each journaled in a respective roller bearing 66 secured in enlargedhousing portions 61 formed ineach D framev49 at opposite endsv thereof. The stub shafts 50 and 50' are arranged in cog-axial alignment with each other and with the common axis thereof intersecting the axes of rotation of the spindles 46. It will therefore be understood that inasmuch as'the bracket members .54 are arranged substantially in a diametrical plane passing through the axis of the corresponding spindle 46 each lens driving element 3| will be in nearly a balanced condition and will therefore rotate with a minimum amount of power and vibration about the axis of the spindle 46 as the lens is moved back and forth across 'the grinding surface of the lap.

Reciprocating rock frames or carriers The axial movement of spindle 4.6 for moving the lens carried thereby through the cross strokes, that is, transversely of the grinding surface of a lap, and the lateral movements of the spindle for producing the lengthwise strokes of the lens longitudinally of the grinding surface of the lap are produced by the operation of the floating beam 5| which has secured thereto a pair of studs or pivot shafts 69 extending'transversely of the beam intermediate shafts 50 and shaft 50', as illustrated in Figure 8. 'Ihe shafts 69 are arranged with the axes thereof intersecting the common axis of the shafts 50 and 50'. The shafts 69 have the ends thereof extending outwardly from the opposite sides of the beam 5| and journaled in corresponding` bearings 66 mounted in the upper end portions of a pair of supporting inverted V-frames 'l0 at opposite sides thereof and through which the beam 5l extends, as shown in Figures 8 and 9. 'I'hese frames 10 extend downwardly from the beam 5| to near the bottom of the housing 2 and have securedto opposite sides of the lower ends thereof a pair of stub shafts 1| arranged in co-axial alignment with each other. wardly from adjacent sides of the corresponding frame 10 and have their ends mounted in bear--l ings 66 secured in the opposite sides of anoscillating frame 12 mounted in a vertical plane beneath the floating beam 5I and in spaced revlation thereto.

This oscillating frame 12 is provided with a pair of bearing members 66 arranged in the ends thereof, as shown in Figure 8, and which receive the respective ends of a pair of stub shafts 13 which are secured to the hereinbefore mentioned ribs 4 provided in the housing 2. The

shafts 13 are arranged in axial alignment with each other'with the common axis thereof intersecting the common axes of each pair of stub' shafts -`1|. It will therefore be obvious that the These shafts 1| extend inf frame'12, the beam 5| and the lens driving elements 8| connected thereto are free to rock about the common axis of the shafts 13 extending longitudinally of the housing 2 in substantially parallel relation with the minor or lateral axes of the laps 28. Furthermore, it will be obvious that the `beam 5| and the lens driving elements 3l connected thereto may reciprocate in a direction longitudinal of the housing 2 and in substantially parallel relation with the major or longitudinal axes of the laps 28, due to the rocking action of the frames 10 about theaxes of tht? shafts 1| extending transversely of the housing 2. The mechanism for producing these rocking or oscillating movements of the frame 12 an beam 5| will now bedescribed.

. L engthwise reciprocating movement Mounted upon the drive shaft 6 intermediate the bearings 1 and 1' is a spiral gear 15 which is positioned within a gear housing or case 16 having bearings 11 arranged in opposite ends thereof, as shown 'in Figure, for receiving the shaft 6 therethrough and supporting a case 16 on said shaft. Thefcase 16 is maintained against rotation during the rotation of shaft 6 by a pin 18 secured in the hereinbefore mentioned bearing neath the shaft 6 and is journaled in bearings 83 mounted in the case 16 to'rotate about an axis extending in right angular relation to the axis of rotation of shaft 6, as shown in Figure 4. Thev shaft 82 extends beyond the outer side of the case 16 and has secured to the outer end thereof a grooved pulley 84 which is connected by a belt 85 toa grooved pulley 86 secured to one end of a drive shaft 81 comprising a portion of one of my novel power transmission and motion breakup mechanism 88.

This mechanism 88 comprises a case 89 which is secured to one end wall of the housing 2 as by screws 90 or their equivalent. The upper side of the case 89 is provided with a cover 89 removably secured thereto by screws 9|, as indicated in` Figures 2 and 3. The case 89 is provided with a pair of bearings 93 and 93' arranged in axial spaced relation to each other in one side thereof, which rotatably supports the shaft 81, as shown in Figure 6, whereby said shaft may be rotated about a fixed axis extending at substantially right angles to the axis of rotation of the drive shaft 6. The case 89 also has' a pair of axially spaced bearing members 94 mounted therein at one side of the bearings 93 and 93' for rotatably supporting an eccentric sleeve 95 arranged-in parallel spaced relation to the shaft 81. A shaft 96 .is journaled in the sleeve 95 to rotate about an axis arranged in spaced substantially parallel relation with the-axis of rotation of said sleeve. The sleeve 95 has secured to the one end thereof 'a gear 91 which is in meshing engagement with a similar gear 98 splined or otherwise secured to the shaft 81 to rotate in unison with said shaft. The

gears 91 and 98 are of the same pitch diameter so that the sleeve will be rotated at the same rate of speed as the shaft 81.

The shaft 96 has one end thereof extending v forwardly beyond the case 89 and supports an parallel with the axis of rotation of said shaft 96. 'I'he crank pin 00 is held in different positions of angular adjustment by means of a clamping screw engaged in a diametrically extending threaded aperture in the crank pin |00 and which extends outwardly from the crank pin through an elongated slot |02 provided in the adjacent end portion 96 of the shaft 96 which is enlarged to receive the pin 00 therein. The crank pin |00 is provided with an eccentric extension |00 which is arranged at one side of the axis of the crank pin.

Mounted upon the extension |00' is a ball bearing member |02 which rotatably supports one end of my novel connecting rod |03. 'Ihis rod |03 comprises a head |04 and a flexible shaft or rod |05. The head |04 is provided with a bore |04 extending transversely therethrough for the reception of the bearing |02 and outer endportion of the crank pin extension |00'. The rod |05 is comprised of a flexible metal core |06 which in this instance is in the form of a coil spring having one end thereof secured in a bore |04" provided in the head |04 in right angular relation to the bore |04. The head |04 may, as shown in Figures 2, 6 and 8, be slotted to form opposed sections at opposite sides of the bore |04" and which are provided with screws or bolts |01 whereby the sections may be clamped to the core |06 for securing the core to the head 04. The core |06 is provided with a flexible cover |08 composed of rubber, or the like, for providing the rod with a smooth outer surface and for maintaining the core free from dirt, grease or other foreign elements. from the head |04 to within a short distance of the opposite end of the core which is clamped in a split hollow boss |09 by a screw H0, said boss being shown integral with the end of the floating beam opposite the transmission mechanism 88, as illustrated in Figures 2 and 8.

The boss |09 is arranged, when the beam 5| `is substantially midway between the extreme to an eccentric sleeve ends of the transverse stroke thereof, in a plane extending substantiallyat right angles to the end portion |00 of thecrank pin 00 to which the connecting rod |03 is attached. It will, therefore, be seen that the connecting rod |03, during the rotation ofthe crank pin, will extend in substantially a straight line from the crank pin portion |00' to the boss |09 and will therefore have substantially a direct thrust upon the oating beam 5|. It will also be observed by referring to Figure 8 that owing to the particular construction of the beam 5| and rock frames 10 and 12 the connecting rod |03 may freely extend between the floating beam and rock frame 12 and through the interior of the rock frame 1 0. It is, therefore,-evident that this structure is an improvement over the structure shown in the hereinbefore mentioned Patent 1,709,943 wherein the connecting rod corresponding to applicants -connecting rod |03 is necessarily a more or less arcuate member to enable the same to extend around the rock frames associated therewith.

The read end of shaft 96 extends a short distance beyond the sleeve 95 and has secured thereto a gear member |2 which is ln meshing en-`A sagement with a similar gear member ||3 keyed ||4 which in turn is keyed to the shaft 81 adjacent the gear 98, as shown in Figure 6. As hereinbefore mentioned and as illustrated diagrammatically in Figure '19, the gears 91 and 90 are of substantially the same size while The sleeve |08 extends the gears ||2 and IIS, as illustrated diagrammatically in Figure 20, are of unequal pitch diameter. The gear I9, which is the smaller of the two, is mounted concentrically upon the sleeve ||4 and is therefore eccentric to the shaft 81 as indicated in Figures 6 and 20.

It will now be evident that when the crank pin |00 is adjusted relative to the shaft 96 to obtain the maximum degree of travel of the crank pin extension |00' about the axis of the shaft 96, as shown in Figure 6, any point on the lens, as the center thereof, will be moved a maximum distance over the grinding surface of the lap 28 as the crank pin 00 revolves with the shaft 96 during the rotation of said shaft as produced by the gears H3 and ||2.

It will also be obvious that inasmuch as the eccentric sleeve 95 is being continuously rotated at the same rate of speed as the shaft 81, the shaft 96, which is eccentrically mounted in said sleeve, will be revolved about the longitudinal center or axis of rotation of the sleeve at the same rate of speed that the shaft 81 is operated, while the speed of rotation of the shaft 96 about its own axis will be slightly slower than the speed of rotation of the sleeve 95 and shaft 81.

It therefore follows that the distance between the axis of the crank pin extension |00' and the axis of rotation of sleeve 95 changing during -the operation of the machine and, therefore, the effective throw of the crank are constantly pin will be constantly varying and causing the t beam 5| and each lens driving element 3| to' move through gradually varying distances within certain limits. In other words, each driving element 3| willmove between the positions 0btained by the maximum degree of throw produced by the combined action of the crank pin |00, shaft 96 and sleeve 95 and the minimum degree of throw produced by the combined action of these members.

To explain more explicitly, in Figures 19 to 22 inclusive of the drawings, circles 91 and 98 represent the gears 91 and 98 and circles ||2 and ||3 represent the corresponding gears. The lines A-A and B-B represent the axis of rotation of eccentric Ysleeve 95 and shaft 81 respectively. These axes, it will be observed, are in xed relation with each other and lines C-C and-D-D representing the axes of shaft 96 and eccentric sleeve ||4 which are mounted eccentrically to and adapted to be revolved around the xed axes A-A and B-B respectively. As hereinbefore stated, Figure 19 illustrates the shaft 81 and eccentric sleeve 95 with the gears 98 and 91 mounted thereon in cooperative relation with each other. Figure 20 illustrates the shaft 81 and shaft 98 and the gears H3 and ||2 associated therewith mounted in cooperative relation with each other. The teeth of the gears ||2 and ||3 engaging each other are illustrated by the line a-a, while the side of the shaft 96 adjacent the line a-a is represented by the lineb. Figures 21 and 22 are each ures 19,and 20.

It will now be readily understood that during a revolution of the shaft 81 the eccentric sleeve 95 will operate through a complete revolution due to the gears 98 and 91 being of the same pitch diameter. Furthermore, it will be observed that inasmuch as the eccentric sleeve ||4 `is keyed to the shaft 81 and gear ||9 is keyed to the sleeve ||4, the gear ||3 will rotate one complete revolution during each revolution of the shaft 81. The gear H2, however, will be rotated slightly a combination of Fig-- less than a revolution during each revolution of the shaft 81 and gear 'H3 inasmuch as the gear ||3 is of smaller pitch vdiameter than the gear ||2. It therefore follows that during each rotation of the shaft 81 the shaft 88 will be rotated slightly less than one complete revolution.

In other words, let it be considered that gears 98 and' 31 are each provided with twenty-four teeth, that gear ||3 is provided with twentythree teeth andgear 2 is provided with twentyve teeth, and also that the eccentric sleeves 95 and ||4 are arranged so that the axes C-C and D-D of the shaft 08 and gear ||3 are at one and the same side of the axes A--A and B-B respectively of eccentric sleeve 95 and shaft 81, as indicated in Figure 21. It will now be obvious that during one-half revolution of the shaft 81 and gears 98 and 3 connected therewith from the position shown in Figure 21 to the posiytion shown in Figure 22, the eccentric sleeve 95 will be driven one-half revolution while the shaft $6 will be driven slightly less than one-half revolution or to position b and, therefore, the crank pin will be rotated slightly less than onehalf revolution. It `therefore follows that the throw of the crank pin |00 will be slightly less than the maximum, which will produce a corresponding shortening in the stroke of reciprocation of the iioating'beam 5| connected to said crank pin by the connecting rod |03. This shortening in the length of succeeding strokes of the iioating beam will continue during the rotation of the shafts 81 and 96 until the minimum length stroke has beenv reduced, and then these strokes will gradually increase in length until the maximum length stroke is again4 reached. V

During continued rotation of the shafts 81 and 96 the axes of rotation/of gears ||3 and ||2 will be constantly varied with respect to each other in synchronism with the operation of said gears due tothe rotation of the eccentric sleeve 95 at the same rate of speed as the shaft 81 for maintaining the gears ||3 and ||2 in constant mesh with each other, as illustrated in Figures 2l and 22.

The setting of the crank pin |00 to a maximum degree of movement of the lens driving element 29 longitudinally of the grinding surface of the lap is utilized with a lens having a substantially flat surface or one in which the curve of the surface being ground has a relatively long radius. When the surface of the lens being ground has a relatively short radius, the crank pin |00 is adjusted relative to the end of the shaft 96 to bring the axis of the extension |00 thereof into relatively close relation with the axis of the shaft 06. When the crank pin |00 is thus adjusted to obtain the minimum degree of action produced by the crank pin, the lens driving element 3| will obviously have a much less degree of movement than with the previously described adjustment ofthe crank pin.

It will be observed, however, that owing to the particular driving connection shown between the drive shaft 6 and the crank pin |00 the lens driving element will not only be caused to travel through continuously changing paths or iields of action, but the ends of succeeding strokes thereof are continuously changing positions which reduces to a minimum the liability of scoring or otherwise injuring the lens, as. the lens is moved longitudinally of the base curve of the lap 28, by any errors or imperfections in the grinding surface of the lap. This is due not only to ,the positive action of thetransmission mechanism 88 above described, but also to the more or less indefinite action of the belt 85 connecting the shaft 6 with the transmission mechanisn 88 due to the creeping action of said belt with respect tothe pulleys 84 and 86.

'Transverse or cross recprocative movement The mechanism producing reciprocative movement of the beam 5| at substantially right angles to the reciprocative movement thereof produced by the driving mechanism 88 abote described for reciprocating the lens driving element 3| through the cross strokes, that is to say, in strokes substantially parallel withthe cylinder axis of the lens is shown more particularly in Figures 2, 3, 7, 8, and 9. This construction comprises an eccentric collar ||6 which is secured to the inner end of the drive shaft 6 adjacent the bearing members 1'. In this collar 'H6 isadjustably mounted an eccentric crank pin ||1. 'I'he pin ||1 issecured in the adjusted position 'by a screw ||8 which extends through an elongated slot ||9 formed in the collar |16 and screw-threaded into the pin ||1 in the same mannerv as the screw |0| shown in Figure 18 for the crank pin |00. The crank pin ||1 is provided with an extension H1 arranged in eccentric substantially parallel-relation with the axis of the crankv pin. Mounted on the extension H1' is a bearing which is also mounted in one,

end of a connecting rod |2| extending downwardly from the crank pin. The connecting rod has the lower end thereof provided with a bearing l|20' in which is mounted one portion of an eccentric crank pin |22 which is maintained in xed spaced relationto crank pin extension H1' by said connecting' rod, as shown in Figure 3.v The crank pin |22 is provided with anextension |22 arranged in eccentric substantially parallel relation to the axis of the crank pin |22. Upon extension |22' is mounted a bearing |20" which is also mounted in one end of a drive link |23 having the opposite end thereof secured, as by a pin |24 or other suitable means, to one end of a tubular sleeve |25. The sleeve |25 is secured by a screw |26 in the boss 12' connected with the rock frame 12 to extend outwardly from one end of the frame in a plane over the adjacent stub shaft 13, as illustrated in Figure 8.

It will now be observed that when the crank pin ||1 is secured in the collar HS, rotation of the shaft 5 will produce a vertical reciprocating movement of the connecting rod |21 and the rear end'of the drive link |23 which in turnwill produce a corresponding rocking or oscillating movement of the frame 12. This rocking of the frame 12k will produce a similar rocking or reciprocating movement of the floating beam 5| through the mediumI of the supporting rock 'frames 10, which in turnv produces reciprocative movement of the lens driving elements 3| connested therewith in a direction substantially parallel with the minor or cylinder axis of the lap 28.

In order that --the transverse or cross strokes of the lens driving elements 3| thus produced may be varied so that a variation in the point of reversal of the lens driving elements, and therefore of the lens carried thereby, at the ends of the strokes maybe produced, I have provided a simple mechanism for" rotating the eccentric crank pin |22 about the axis of bearing |20 mounted in the lower end of connecting rod |2|.

This mechanism 'comprises a drive pulley |28 secured, as shown in Figure 3, to the outer end of the extension of the crank pin I 1. The pulley |28 may be secured to said extension in any suitable manner so as to rotate in unisonn therewith. The pulley |28 is connected by a belt |29 to a similar pulley |30 secured to the crank pin |22, so that said pulley and crank pin will rotate in unison. Pulleys |28 and |30 are thus maintained in fixed spaced relation with respect to each other and the pulley |30, as shown, is of slightly greater diameter than 'the pulley |28 so that the crank pin |22 will be rotated at a slightly slower rate of speed than the crank pin ||1.

It will now be seen that this continuous rotation of the crank pin |22 will vary the distance between the axis of the extension |22' of said pin and the axis of rotation of the crank pin ||1, that is, of shaft 6, and will therefore vary the effective length of the connecting rod |2|. It therefore follows that a continual change will be produced in the cross stroke of each lens driving element dueA to a continual change in the lengths of succeeding strokes of the beam and that the movement of the lens across the grinding surface of the lap will be correspondingly affected thereby. It will be seen from the foregoing description that the two reciprocative movements when combined with the two break-up movements will be synchronous and simultaneous, resulting in the travel of the lens across the face of the lapin serpentine paths and also in the gradual and continuous changing of these paths during successive lengthwise and transverse `strokes of the lens driving elements, as clearly illustrated in Figures 28, 29, 30 and 31.

It will now be noted that inasmuch as all the co-acting relatively movable members of the mechanism mounted within the frame are supported by bearings of the roller bearing type arranged in suitable housings to protect them from dust and other foreign material, the machine may be successfully operated without the use of an oil pump or aliquid lubricant being supplied to said bearings.

PTeSSuTe means Each lens is yieldingly held against the surface of a lap 28 partially by the Weight of the front end of the lens driving element 3| and saddle 55 and partly by means of an upright pressure rod |32 and a coil spring |33 mounted in said rod. The rod |32 is composed of two telescoping tubular sections |32 and |32 and the spring. |33 is mounted within said sections between opposite ends thereof. The inner section, as |32", has the lower end thereof provided with a ball |34 which is adapted to releasably engage a seat |35 connected with'the spindle 46 and which is formed by extending a portion of the outer end of said spindle, as shown in Figure 14. The upper end of the outer tubular section |32 is provided with a ball |34 which is seated in a socket |36 provided in the lower end of a stem |31 of a pressure gauge |38. The ball |34' is preferably secured in the socket |36 so that the pressure rod 32 will be secured to the pressure gauge |38. The pressure gauge is'mounted upon an outwardly extending arm |39 formed integral with a supporting slide or bracket |40 mounted on a standard |4| secured to or made integral with the upper section 3 of the frame The stem |31 is yieldingly urged downwardly to its lowermost position by a spring |42 coiled about said stem between the lower end thereof and a nut |43 engaging the threaded sleeve connected to the gauge |38 and which servestfo clamp the gauge to the arm |39.

The bracket 40 is a tubular member which is mounted for vertical `reclprocative movement upon the standard 4|. The bracket |40 is maintained with the arm |39 in predetermined aligned relation with the corresponding spindle 46 of the respective lens driving element 3| by means of a screw |45 screw-threaded in the side of the bracket and which has the inner end thereof slidably received in a vertically disposed slot |46 provided in a guide post or a stud |41 secured to' the upper end of the standard |4|, as shown in Figure 14.

The vertical movement of the slide or bracket |40, and therefore the gauge |38, is controlled by a lever |50 which is rotatably mounted intermediate the ends upon a pin |5| secured to the upper end of the bracket |40. 'I'he upper or rear end of the lever |50 extends a short distance beyond the pin |5| and is pivotally connected, as at |52, to one end of a link |53 which has the other end pivotally connected at |54 to the upper section 3 of the frame as shown in Figure13. Mounted upon the pin |5| intermediate the lever |50 and bracket |40 is a ratchet wheel |55 which is secured by pins |56 to the bracket 40 to maintain said ratchet wheel against rotation. A ratchet pawl |51 is pivotally connected at |58 to the lever |50 at the lower or forward side of the pin |5|. 'I'he pawl |51 is provided with a finger piece |51' which extends outwardly therefrom in close cooperative relation with the outer end of the lever |50 which is curved, as shown in Figure 13, to provide a finger piece |50. The pawl |51 is urged into engagement with the ratchet wheel by a spring |59 mounted in the lever |50 and which isadapted to engage the finger piece |51', as shown in Figure 16. 'I'he teeth, as |55', and the ratchet wheel |55 are ar ranged in one side portion thereof only so as to be engaged by the pawl |51 when pressure is being exerted by the spring |33 upon the lens driving element,'or, in other words, when the bracket |40 is inv a lowered position. When the action of the spring |33 upon the spindle 46 is to be discontinued, the bracket 40 and rod |32 are raised to an upper inoperative position by swinging the lever |50 about the pin |5| until the pivot |52 has passed downwardly and'through the -straight line extending between the pivot |5| and the pivot |54, whereupon the weight of the bracket |40, gauge |38 and rod |32V will counter-balance the action of the upper or inner end of the lever |50 and link 53 for releasably4 securing said bracket, gauge and rod in the upper position.

'I'he rod |32 is maintained in cooperative engagement with the spindle 46 during the upward movement of the bracket |40 by a rod |60 which has the upper end portion extending through an aperture |39 formed in the arm |39 intermediate the bracket |40 and the gauge |38. 'I'he lower end of the rod |60 is secured in a ring |6| mounted upon the boss or hub portion 54' of the bracket 54 as shown in Figures 2 and 14. This ring |6| is removably mounted on the hub so that the bracket 54 may readily be removed from the spindle 46 and from said ring during the substitution of one bracket 54 for another. 'I'he upper end of the rod |60 is provided with a pair of nuts |62 so related to the ring |6| and arm |39 that prior to the rod 32 being moved out of engagement with the seat |35 as the bracket' |40 is moved upwardly, said nuts will engage the arm |39 and subsequently cause the outer end of the spindle 46 to move upwardly in unison with the bracket |40. This upward movement of the spindle 46 is permitted by rotation oi' said spindle 6 about the axes of the stub shafts 50 and 50' associated with the D-frame 48 with which said spindle is connected. A y

It will be understood that there is one of these pressure devices foreach of the lens driving ele- 10 ments, and the operation Yoi each of these pressure devices will now be understood to be substantially as follows: After a lens secured to one .of the saddles 55 has been placed upon a lap 28 the lens driving element 3| will be moved from 1l the upper inoperative position downwardly by the operator swinging the lever |50 about the Vpin |5| to move the bracket |40 downwardly. It

will be obvious that during this downward movement of the bracket thespindle 46 will move in unison with the arm |39 until the downward movement of the spindle is limited by the engagement of the pins 58 with the bearing members-51 provided on the saddle 55. During this downward movement of the bracket and spindle there will be no appreciable pressure inserted by the spring |33 upon the spindle. In other words, the pressure gauge |38 will have a zero reading. As soon, however, as the spindle 46 is maintained against downward movement by the engagement of the pins 58 with the bearings 51 when the saddle is supported by the engagement of the lens with the lap, any further downward movement of the arm |39 will tension the spring |33 by decreasing the over-all length of the rod |32.

85 This pressure tension of the spring |33 will be registered in the gauge |38, so that the operator may readily determine the pressure being exerted by the spring upon the spindle 46 which will more or less accurately indicate the pressure 40 between the lens and the grinding surface of the lap. When the downward movement of the bracket |40 is sufhcient to produce the required tension of the spring, the bracket may be secured in that position by the engagement of the ratchet pawl |51 with the` ratchet wheel |55. When the lens is again to be released from the lens driving element, this may be readily accomplished by the operator using the nger pieces and |51 to move the pawl |51 out of engagement with the 50 ratchet wheel |55 against the action of the spring |59, after which the lever |50 may be readily moved to its uppermost position and thus move and maintain the lens driving element in its uppermost inoperative position. 55 Rouge pump In order that rouge may be applied to the\ grinding surface of the lap during the polishing of` lenses, I have 'provided a simply constructed pump attached to the catch basin 39. This pump comprises a pump case which is secured to one end of the catch basin 39 by one or'more `screws |66. This pump case is provided with a pump chamber |61 in which is rotatably mounted 65 a rotary pump |68 which is secured to the lower end of a motor shaft |69 as shown in Figures 10 and 12. The shaft |69 extends upwardly from the pump chamber and case |65 through a verti` cally disposed standard |10 connected at its 70 lower end to the case |65. The upper end of the standard is connected with and supports an electric motor |1| connected with the opposite or upper end of the shaft |69. The standard |10 is.

provided with suitable bearings |12 in which t shaft |69 is journaled.

'rne intake side erthe pump chamber |61 is connected by an inlet passage |14 provided in 1 the case |65 withv the adjacent end of the interior of the catch basin 39-which has the bottom wall 38 thereof inclined upwardly -from the inlet 5 opening |14 to the opposite end of the catch basin, as illustrated in Figure 10. The case |65 is also provided with an outlet or discharge passage |15 which has Vthe outer end thereof registering 'with the interior of the catch basin |39 10 adjacent the outer or front wall thereof, as illustrated in Figure 12. 'Ihe end wall of the catch basin adjacent the pump case |65 is pro- ,vided with an opening |14' registered with the inlet opening |14 in said case and a second open- 15 ing |15 in registration with'the exhaust passage A distribution tube |16A is positioned in the catch basin |39 to extend from within the opening |15' along the front side wall ofthe catch 20 basin and then inwardly along the end 4wall ofA said basin opposite the pump case, as illustrated in Figure 2. The tube |16 has the outer end thereof adjacent the rear wall of the catch basin closed and is provided with a pair of laterally 25 projecting tubes |11, one for each lap 30. These lateral tubes |11 extend upwardly and inwardly fromrthe distribution tube |16 to a. position adjacent to and slightly above the corresponding lap 28 for continually supplying said lap and the lens 30 surface being ground thereon with rouge. The excess rouge deposited upon the lens and lap flows downwardly to the inclined wall 38 of the catch basin and then down said wall to the opening |14 and inlet passage |14 back to the pun'ip` 35 Y |68. The distribution tube |16 merely rests upon the bottom wall 38 of the catch basin when the inlet end thereof is inserted in the discharge opening |15' of the catch basin, so that said. tube may be readily removed for the purpose of 40 cleaning or for any other reason, by simply lifting the tube out of the catch basin. It is obvious that the tube may as readily be placed in operative position within the catch basin by inserting the inlet end thereof in the opening |14 and 45 positioning the laterally disposed opposite end of the tube along the end of the catch basin opposite the pump.

As hereinbefore stated, the rouge pump |68 and distribution tube |16 are usedto supply 50 rouge to the grinding surface of the laps when polishing lenses. When it is desired to use a grinding compound such as emery dust or the like, in grinding a lens, the catch basin 39 together with the pump |68 and motor |1| are re- 55 moved from the supporting frame by the manipulation of the bolts 43 and washers 44 inthe manner hereinbefore described, and another catch basin of suitable structure and design' for collecting the dust and excess grinding compound 50 may be secured to the supporting frame by the screws43 and washers 44 in the same manner in which the catch basin 39 is secured to said frame.

Although I have shown and particularly-dee5 scribed the preferred embodiment of my invention, I do not wish to be limited to the exact construction shown, as various changes, both in the form' and relation of the parts thereof, may. readily be made without departing from the l70 spiritof the invention as set forth in the appended claims.

I claim:

1. In a surface grinding and polishing machine having a grinding member and a work 75 35 to the driven shaft, means operatively connecting.

holding member. operating mechanism for producing relative movement of said members oomprising a rotary drive shaft having an eccentric, a connecting rod journaled on said eccentric, a driven element journaled on the connecting rod having an eccentric operatively connected with one of said membersl for producing reciprocative movement thereof, means for transmitting rotary movement from the drive shaft to the driven element comprising a pulley secured to the eccentric of the drive shaft, a second pulley connected to the driven element to rotate therewith, and a flexible friction belt connecting `said pulleys.

2. In combination, an actuating member mounted for reciprocative movement in two directions, means for reciprocating the member in one of said directions, and additional means for reciprocating the member in a secmd of said directions comprising a drive element mounted to revolve about a fixed axis, means including a head Journaled on the drive element and a connecting rod fixedly secured to said head and to. the actuating member operatively connecting the drive element with the actuating member, said connecting .rod being adapted to flex laterally during the reciprocative movement of the actuating member in the rst of said directions.

3. The combination with an actuating member mounted for reciprocative movement, of a drive mechanism for producing reciprocation of the actuating member through strokes of varying lengths comprising a driven shaft mounted to rotate about a fixed axis, a second shaft having an eccentric and mounted in spaced relation the eccentric with the actuating member, means including a pair -of gears one secured to the second shaft and the other secured to' the driven shaft and meshing with said rst mentioned gear operatively connecting the second' shaft with the driven shaft whereby the second shaft will be rotated by the driven shaft at a different rate of speed than that of said driven shaft, and'separate means connecting said shafts whereby the second shaft will be revolved by the driven shaft about an axis arranged in eccentric relation with the axes of rotation of both of said shafts'including a rotatable sleeve rotatably supporting 'said second shaft in eccentric relation with the axis of rotation of said sleeve, and a second pair of intermeshing gears secured to said sleeve and driven shaft respectively.

4. The combination with a rotary drive shaft and anV actuating member mounted for reciprocative movement, of two drive mechanisms operatively connecting the shaft with the actuating member for producing two reciprocative movements thereof operating in directions at substantially right' angles to each other and through strokes of varying lengths, one of said drive mechanisms comprising a driven shaft mounted to rotate about a fixed axis, a second shaft having an eccentric and mounted in spaced relation to the driven shaft, means operatively connecting the eccentric with the actuating member, means operatively connecting the second shaft with the driven shaft whereby the second shaft will be rotated by the driven shaft at a different rate of speed than .that of the driven shaft, separate means connecting said shafts whereby the second shaft will be revolved by the driven shaft about an axis arranged in eccentric relation with the axes of rotation of both of said shafts, and means including a belt operatively connecting the driven shaft with said drive shaft independently of the other one of said drive mechanisms.

5. The combination with an actuating member mounted for reciprocative movement, of a drive mechanism for producing reciprocation ofA eratively connecting said shaft eccentric with the actuating member for producing reciprocation of said member, and means including two pairs of intermeshing gears rotatably connecting the driven shaft with the sleeve and with said second shaft, one pair of said gears being secured to the driven shaft and to the second shaft respectively. the gear on said driven shaft being eccentrically mounted with respect thereto, and the other pair of said gears being secured to the driven shaft and to the eccentric sleeverrespectively, two of the gears of said pairs of gears being of different pitch diameter than the other two gears so that said second shaft and sleeve will be simultaneously rotated at different speeds.

6. The combination ,with an actuating member mounted for reciprocative movement, of a drive mechanism for producing reciprocation of said member through strokes of varying lengths com-' prising a driven shaft mounted to rotate about a nxed axis. an eccentric sleeve mounted to rotate about a xed axis arranged in predetermined spaced relation to said axis of rotation of said' tuating member for producing reciprocative movement thereof in directions at substantially right angles to the direction of the first mentioned reciprocating movement, and means in- -cluding a belt operatively connecting the ldrive shaft with said driven shaft.

7. In a surface grinding and polishing machine having a grinding element and a work holding element arranged in cooperative relation with each' other, operating mechanism for producing relative movement of said elements comprising a rock frame mounted to swing about a fixed axis, a supporting floating member mounted in a plane above the rock frame, means including hollow frame members pivotally connecting the floating member tothe rock frame whereby said floating member may be reciprocated in a direction extending substantially parallel with the axis 4of rotation of the rock frame, means connected with the rock frame for producing swinging movement thereof and` the floating member about said axis. means 'operatively connecting the floating member with one of said elements, means for producing reciprocative movement of the floating member independently of said swinging movement thereof including a flexible substantially straight connecting rod extending through the hollow frame intermediate the rock frame and said floating member and fixedly connected with the floating member, and means connected with the connecting rod for producing reciprocative movement thereof in a direction substantially parallel with said axis of the rock frame. y

8. In a surface grinding and polishing machine having a grinding member and a work holding member, in combination, operating mechanism for producing reciprocative movement of oneof said members with respect to the other member including a supporting floating element pivotally mounted to reciprocate in two directions substantially at right angles to each other, a D-frame arranged in substantially parallel relation with the floating element and -pivotally connected to said element in coaxial relation therewith and to rotate about an axis extending substantially parallel With'one of said directions of reciprocation of said iioating element, a spindle journaled inv said D-frame with the longitudinal axis thereof intersecting said axis of rotation of said D-frame substantially normal thereto, a saddle connected with said one of the members to extend to opposite sides thereof, means including a forked bracket connected with the spindle, and

of rotation pivotal bearing means associated with the bracket and saddle arranged substantially in a plane extending diametrically through said spindle for operatively connecting the spindle with the ends of said saddle.

9. A structure as in claim 8 having means operatively engaging the spindle for maintaining the work carried by the work. holding member in pressure engagement with the grinding member.

10. In a surface grinding and polishingma.- chine having a grinding member and a work holding member mounted in cooperative rela.

y tion with each other, means'including a driving element operatively .connected with one of said members for producing relative movement of i the members with respect to each other, and means for maintaining the work carried by the work holding member in pressure engagement with the surface of the grinding member including a. spring, a support for said spring having engagement with the driving -element, manually operated means connected with said'drivi'ng element and spring support for moving the same and the member connected therewith toward and from the other member, means connected with the manually operated means and spring support for tensioning the spring carried by said support after the Work is brought into engagement with the grinding member, and a pressure gauge carried by the manually operated means and connected with the spring for indicating the amount o f pressure between. the work and the grinding member.` A

11. A structure as in claim 10 having means including a ratchet wheel and p'awl associated with the manually operated means and springber mounted on said frame, a work holding member arranged in cooperative relation with said grinding member, and operating means including a driving element connected with the work holding member for producing movement thereof with respect to the grinding member to effect grinding of the surface of the Work carried by said work holding member, the combination with said frame and operating means of means for maintaining the work in predetermined pressure y engagement with the grinding member comprising a pressure rod composed of telescoping sections, having engagement at one end with the driving element, means including a supporting -member connectedwith the frame for movement toward and from the driving element and supportably engaging said pressure rod, additional means connected with the driving element and engaging the supporting member at a predetermined position of said member for causing the driving element to move toward and from the grinding member during a portion of the movement of the supporting element, and means including a spring mounted in the pressure rod rendered effective after the work carried by the work holding member is brought into engagement with the grinding member for producing a predetermined pressure between said work and grinding members.

13. In a surface grinding and polishing machine having a grinding member and aworx supporting member arranged in cooperative re lation with each other, a catch basin mounted' beneath said members and provided 'with a pair of fluid passages in communication with the interior thereof, a pump secured to the-catch basin with the inlet port in communication with one of said fluid passages and the exhaust port thereof in communication with the other one of said ud passages, and a conduit removably connected with the catch basin in communication with the last mentioned fluid passage adapted to supply rouge between the work carried by the Work supporting member and the grinding member.

14. In a precision surface grinding and polishing machine of the character described wherein a grinding member and a work holding member kare mounted in cooperative relation with each tric, said connecting rod having a bearing member mounted in spaced relation to the shaft eccentric, a rotary driven element rotatably mounted in said bearing member lto be carried by the connectingrod, means for transmitting rotary motion from the drive shaft to said driven element including a pulley secured to the-eccentric of the drive shaft, a second pulley secured to the driven element in coaxial relation with the bearing member, a flexible belt connecting said pulleys, anda second connecting rod rotatably connected with the driven element in eccentric relation to said bearing member operatively connecting the driven element with one of said members.

i' WILLIAM A. LOCKHART.

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