Grinding machinery

Application filed October 16,1929. Serial No. 400,136.

This invention relates to improvements in grinding machinery and has particular refrence to a machine especially adapted for use in the grinding of relatively long work ⁸ pieces.

One of the- principal objects of the present . invention is the provision of a machine which may be satisfactorily employed in the formation by grinding of tapered surfaces and par^{3 3} ticularly. tapered surfaces on work pieces of . appreciable length such as· rifle barrels, golf club shafts or the like.

An additional object of the present invention is the provision of mechanisms which -³ may be utilized to produce a controlled variable taper longitudinally of the work piece together- if desired with a reverse taper or configuration at the terminal portion thereof.

A further object of the invention is the pro²³ vision of an improved control mechanism readily applicable to standard forms of machines such as centerless grinders for example which will satisfactorily coordinate and . control the rate of movement of a work piece ²⁵ past the grinding member with respect to the rate of relative feeding movement determining the stock removal and in which one of said rates may be automatically varied, in recurrent cycle during successive grinding ²³ operations.

Further objects of the invention include the provisions of automatic means for controll’iig the rate and direction of movement _ of the several associated shiftable parts of ^2j the machine during grinding, the provision of means permitting variation in the relative rate of movement of the parts as well as the rate of movement of the mechanisms as an entirety, as should be readily apparent by -³ reference to the following specification considered in conjunction with the accompanying drawings illustrative of certain embodiments of the invention, and it will be understood that I may make any modifications in -^J the specific details hereinafter described, within the scope of the appended claims, without departing from' or exceeding the spirit of the invention.

Figure 1 is a. front elevation of a machine ³ embodying the invention.

Figure 2 is a fragmentary plan view thereof.

Figure 3 is a transverse section through themachine, with the work movement controlling mechanism illustrated in elevation. 55

Figure 4 is a vertical section on the line 4— of Figure 2.

Figure 5 is a vertical section, as on the line 5—5 of Figure 3, of the control valve and operating piston, the hydraulic circuit being 60. diagrammatically indicated.

Figure 5A is a fragmentary plan view of the operating lever .and parts associated therewith illustrating the relative positions thereof when the valve is shifted to the posi- 65 tion shown in Figure 5.

Figure 6 is a view similar to Figure 5 illustrating a different valve position.

Figure 6A is a view similar to Figure 5A showing, the relative positions of the parts 70. when the valve is in the position of Figure 6.

Figure 7 is a section through the valve lever detent and associate keeper member.

Figure 8 is a section through the feed screw gear box mechanism with associate parts 75 shown in elevation, taken as on the line 8—8 of Figure 1.

Figure 9 is a view similar to Figure 3, illustrating a variable work traverse control mechanism. .80

Figure 10 is a transverse section through the . work feed control mechanism, taken as on the line 10—10 of Figure 3.

Figure 11 is a sectional view on line 11—11 of Figure 6. ⁸³

The present invention contemplates the automatic production of tapered articles of appreciable length. It has been illustrated in its most approved form as applied to a machine of the general centerless grinder ⁹⁰type.

The machine illustrated comprises a bed 15 having the journal 16 for the spindle of the grinding wheel 17 rotatable at a high . grinding rate of speed in a clockwise direc- ⁹⁵tion, the bed 15 further serving as a support for a slide member 18 on which is mounted for movement therewith and relative thereto the regulating wheel unit designated as an entirety by the numeral 19. This unit has ¹⁰⁰

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53' communicating respectively with the upper and lower ends of the cylinder. The bracket is also formed with a chamber 54' having a ported bushing 55 containing the control valve 56. The bushing has an inlet 73 as at 57 coupled through conduit 43 with pump 42 for reception of actuating fluid and has the discharge outlet 58 coupled direct by conduit 44 with the reservoir and a second discharge outlet 59 coupled through conduit 75 45 and adjustable choke valve 60 with the reservoir.

In addition, the bushing has outlet port 61 coupled through passage 52' with the upper end of the cylinder and ports 63 and 64 cou- ³³pled by passage 53' with the lower end of the cylinder.

Disposed within the bushing is a plunger valve member designated as an entirety by the numeral 65 having cannelures as at 66, ⁸³67, 68 and 69 adapted to selectively join or couple certain of the inlet and outlet ports of the bushing to determine the rate and direction of flow of the actuating medium into and out of the piston controlling cylinder. ⁹³The valve 65 is adapted to occupy three different positions. In its depressed position as indicated in Figure 5 the flow is from the pump through conduit 43 port 57, cannelure 67, port 61 and passage 52' through the upper ⁹³end of the cylinder urging the piston downward. At this time the hydraulic actuating medium contained in the lower portion of the cylinder will be discharged through port 64, cannelure 68, port 58 and conduit 44 to ^19:the tank. It will be noted that this will be an un-restricted flow of the exhaust fluid and that consequently the piston may move at a rapid rate.

A second position of the valve is illustrated ¹ in Figure 6. In this position the flow from the pump as before passes out through port 61 to the upper end of the cylinder. The valve has been raised however, from a position where the flow from port 64 passes around ¹¹cannelure 68 and in its place the flow is around cannelure 69, discharge port 59 and conduit 45 including the choke valve 60. Adjustment of this choke valve serves to variably determine the rate of discharge of the ¹⁹compressed or exhaust fluid and thus slows down the movement of the piston producing a feeding as distinguished from quick traverse movement of the parts.

It will be understood that but two valve ^Jpositions have been shown which in connection one with the other serve to effect variable rates of movement of the piston according to the setting of the valve, but should additional rates of movement be desired it is merely *necessary to provide additional portings in connection with suitable valve positions for variably connecting selected ports with suitable choke or control of the additional circnits thus utilized.

swiveled thereto the bracket 20 bearing the regulating wheel 21 rotatable at a slow work controlling speed in a clockwise direction and angleable to any position to effect the desired 5 feed component or retardance thrust depending upon the particular method of operation of machine being utilized. Swiveled in a bracket 22 carried by the bed is an adjusting screw 23 fitting within a sleeve nut 24 ro10 tatably supported by the regulating wheel unit 19.

Rotation of screw 23 will therefore impart an in and out adjusting movement to the regulating wheel unit 19 while similarly a ¹⁵ rotation of sleeve nut 24 about the screw will effect a corresponding adjustment. The sleeve nut is provided with a pinion portion 25 meshing with gear 26 of the change gear series 26, 27, and 28 for effecting a suitable ²⁰ actuation of nut 24 for in and out movement of the regulating wheel unit.

Slide 18 supports what may be termed as a work rest assembly including a bracket portion 29 having mounted thereon a work ²³ rest blade 30 projecting into the space between the wheels 17 and 21. Member 29 also carries the V-shaped supports 32 and 33 for the work guide plates 34 and 35 forming troughs for reception of an elongated work ³⁰ piece such as the golf club shaft 36. Tlie member 29 is additionally provided with a guide passage as at 37 for slide rod 38 carrying the end stop ejector member 39 and the the work feeding member 40, these members ³⁵ riding respectively in slots 41 between the pairs of guide .plates 35 and 34 respectively, as it will be best understood by reference to Figure 10.

In the production of long, tapered articles ⁴⁰ it is desirable if the article be fed longitudinally or axially through the grinding throat between the grinding and regulating wheels and that at the same time the space between the wheels be varied to determine the diam⁴⁵ eter of the produced work. The said movements being effected in suitable timing one with respect to the other dependent on whether a uniform taper, variable taper or prescribed irregular contouring is to be effected on the ⁵⁰ Work, In the present instance there has been illustrated a semi-automatic manually controllable mechanism for effecting these movements. This mechanism comprises primarily a source of hydraulic power as indicated ³⁵ at 42 a suitable series of conduits 43, 44, 45 and 46, and a reservoir 47 for the hydraulic actuating medium.

Secured to the bed of the machine is a bracket 48 including a cylinder 49 having re⁶³ ci procable therein a piston 50 having a projecting rod 51 provided with a rack 52 for operation of pinion 53 mounted on spline shaft 54.

Formed in the bracket member 48 adjacent ⁹³ the cylinder 49 are a pair of passages 52' and

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Adjustment of the effective position of the valve is attained by a substantially automatic mechanism including a setting handle and a control cam therefor. Secured to the plunger ⁵ rod 51 are supports 70 carrying a bracket 71 on the face of which are adjustably mounted as by bolts 72 the cam plate 73 having the respective portions 74, 75 and 76. Bracket 48 has a lateral extension 77 to which is ¹⁰ pivoted the control lever 78 having an integral depending arm 79 provided with a spring pressed latch 80. Depression of the handle portion of lever 78 to the position shown in Figure' 5A causes the latch 80 to ¹⁵ snap over the cam plate and engage with the contoured side 74 thereof securing the lever in depressed position against the tension of its actuating spring 80'. Suitable adjustable stops 81 and 82 are disposed to terminally en²⁰ gage the lever and limit its oscillations. The lever itself has suitable pivotal connections as at 83 with the upper end of valve stem rod 84 with the result that when the lever is depressed the valve will be shifted to its lower²³ most position as shown in Figure 5 initiating a rapid downward movement of piston 50. On this downward movement power is imparted through rack 52 and the change gear train to sleeve nut 24 causing a relatively rapid roV* tating movement of the nut moving the regulating wheel unit, inward to narrow the throat between grinding and regulating wheels. At the same time rod 38 is given a corresponding rapid movement to bring the ³ work piece 36 in proper grinding position within the throat. As member 51 moves downward the cam is correspondingly shifted moving portion 74 thereof past the keeper 80 which will thus ride along the incline 75 ³ of the cam allowing lever 78 to rise or snap up to portion 76 of the cam to the position shown in Figure 6A. In this movement, the yalve will be shifted to its second position as indicated in Figure 6 when there will be a ⁴⁵ slow or gradual movement of the piston with a corresponding gradual narrowing of the grinding throat and timed transverse movement of the work engaging carriage.

By reference to Figure 2 it will be noted ^1,0 that the grinding wheel is illustrated as formed with a contoured face comprising a rounded forward portion as at 85 and a reversely tapered portion as at 86, The regulating wheel preferably bears a contoured ° forward portion at 87 and tapered rear section at 88. The regulating wheel may either be set with its axis parallel to that of the grinding wheel so that no feed component is introduced or may have its axis tilted to in^υ troduce a feed component urging the work into the throat in correspondence with the movement of the work carriage or holding the work back against the pusher member 40 _ according to preference or the particular type ⁶⁵ of work being ground.

It will be understood the mechanism in question is adapted for grinding various articles of varying materials such as long steel . fish poles, wooden golf club shafts or the like. In the grinding of metal members ⁴® where considerable stock removal is necessary and wheel wear must be taken into consideration. the angled taper between grinding and regulating wheels is preferably that to be reproduced on the work as the truing of the ^,5wheel is thereby reduced- to a minimum.

The operation is such that the rate of diminution of the throat and the rate of traverse movement of the work in a direction through the throat maintain a. constant en- ⁸® gagement of the grinding. and regulating wheels throughout the extent of their tapered portion with'the work as the same progresses from large to small end or from ..small to large depending on whether the screw and ⁸³nut effect narrowing or widening of the throat during the grinding operation. Ultimately downward movement of piston rod 51 and cam 73 carried thereby will move the cam past the keeper allowing the lever to snap ⁹® upward to a' position limited by engagement of stop 81 therewith. This upward movement further shifts. the valve causing a reversal of the direction of actuation of piston 50 at a rapid rate separating the grinding ⁹⁵and regulating wheels in the form illustrated and at the same time causing a rapid reversal of movement of the work carriage members when the end stop ejector 39 will carry the work back to a loading position when the ¹⁰⁰machine will come to rest ready for removal of a completed work piece and insertion of a new one. Depression of lever 78 will then initiate a new automatic cycle.

It will be understood that the forward and ¹⁰⁵back movement of rod 38 is effected by a carrier belt, chain, or the like 89 passing from the drive member 90 secured on spline shaft ..· 54.and the idlers 91 provided with suitable guiding and tension therefor. Member 89 ^J1® is shown as connected by collars 92 with the rod for this shifting which, if member 90 be circular in form will be at a rate constant as respects the rate of rotation of shaft 54.

In Figure 9 there has been illustrated a ¹¹⁵mechanism by which a variable rate of movement may be effected. In this instance there, is shown as secured on shaft 54 the spiral cam member 93 coupled with the slide bar or rod 38 for controlling the rate. of movement of ⁱ²® belt 89.

In .this instance, the rate of .movement of the work piece will be a variable one. This is particularly advantageous in the grinding of non-metallic articles where wear of the *²⁵grinding wheel may be substantially disregarded and the taper determined by the rela- . tive rates of infeeding and traversing movements. . The faster the rate of traverse of the work as respects a given rate of infeed move- ^u

1,891,663 ment the more gradual the taper produced on the work while the slower the travel of the work the greater the taper thereon.

Mention has been made of the fact that 5 the grinding and regulating wheels have.the forward portions thereof contoured as at 85 and 87. As a result when the work moves toward its position the contour of the grinding wheel at this point will be reproduced To giving an outward curve or tapered swell such as the lower end of a golf club shaft has where it joins the exterior of the socket on the head. This is the particular form of work illustrated and is therefore specifically 16 referred to although it will be understood the mechanism in question has the capacity of producing many different tapers and contours of articles for different purposes.

Attention is also invited to the fact that 20 the rate of infeed with respect to through feed is determinable by variation in the pick off or change gear series 26, 27 and 28 which determine the rate and extent of rotation of nut 24 for a stroke of the actuating piston.

It will be further understood that by varying the position or the length of the cam 73 that the reversal of piston 50 may be effected at any desired point in its stroke according to whether long or short work pieces are be30 ing operated upon.