US2345930A - Cylinder grinding tool - Google Patents

Description

April 4, 1944. c, A, FULMER- 2,345,930

CYLINDER GRINDING TOOL Filed Feb. 18, 1942 4 Sheets-Sheet 1 I INVENTOR/ 4 Charles A. Fuimei' flaw, I

Ap c. A. :FULMER 2,345,930

CYLINDER GRINDING TOOL Filed Feb. 18, 1942 4 Shegis-She'et 2 INVENTOR.

BY Charles A Fulmer M,

April 4, 1944. c A, FULMER 2,345,930

CYLINDER GRINDING TOOL "1196. Feb. 18, 1942 4 Sheets-Sheet 3 INVENT OR.

Charles A. Fulmer April 4, 1944. c. A. FULMER CYLINDER GRINDING TOOL Filed Feb. 18, 1942 4 Sheets-Sheet 4 in. I IIHI I' II/)1 IIIIIIIIIIIIIIIIIIIH I INV ENT OR.

Charles .Fulmer M,1*!%@ Patented Apr. 4, 1944 UNITED STATES PATENT OFFICE CYLINDER GRINDING TOOL Charles A. 'Fulmer, Waukegan, Ill., assignor to Automotive Maintenance Machinery 00., North Chicago, 111., a corporation of Illinois Application February 18, 1942, Serial No. 431,348

17 Claims.-

My invention relates -to cylinder grinding tools and it has to do particularly with a tool of the foregoing character well adapted for factory production use.

One of the objects of my invention is to provide an improved cylinder grinding tool which is of simple and rugged construction, is inexpensive to manufacture, is durable, is highly accurate in performance, and is adapted to greatly increase efficiency in the grinding of cylinders.

Another object is to provide improved means for quickly and easily grinding cylinders to predetermined size under a substantially constant and predetermined pressure.

Still another object is to provide an expansible and contractible cylinder grinding tool which is adapted to be automatically expanded during the grinding operation and which is so constructed and arranged as to reduce the chance of error to a minimum. In other words, my invention contemplates a cylinder grinding tool adapted for An additional object is to provide pressure ad.- '1

justing mechanism of the foregoing character which embodies a compression spring adapted to bev loaded to variable extents for applying variable unit stone pressures, which spring loading is effected positively and accurately by an adjust able element movable to and latchable in a plurality of positions in each of which the spring is placed under a predetermined load for effecting a predetermined unit stone pressure.

A further object is to provide a cylinder grindl ing tool having an improved form of rigid, cage- .like frame structure supporting abrasive carriers for movement toward and from a cylinder wall to be ground.

A more specific object is to provide a cylinder grinding tool of the foregoing character wherein the abrasive carriers are supported against distortion during the grinding operation, thereby materially increasing the life of the carriers, and abrasive members supported thereby.

Still another object is to provide improved means for determining the extent and range of the grinding operation, the arrangement being such that a single cylinder may be ground autotool shown in Fig.

of cylinders may be ground to the same size with a minimum of attention on the part of the operator. 7

A more specific object is to provide a tool of the foregoing character wherein the desired working load for the expanding spring is selectively effected by a cam device adjustable to a plurality of positions in each of which the expanding spring is compressed to a different extent for effecting a different and predetermined unit stone pressure.

Other objects and advantages will become apparent as this description progresses and by reference to the drawings, wherein- Figure 1 is an elevational View of one form of cylinder grinding tool embodying my invention, the tool being illustrated in position in a cylinder before the tool has been fully expanded into engagement with the cylinder wall;

Fig. 2 is a top plan view of the tool shown in Fig. 1;

Fig. 3 is a central vertical sectional view of the Fig. 3 is a section taken substantially on line 3* 3 of Fig. 3;

Fig. 3 is a fragmental view of a portion of the spring loading cam device shown in Figs. 1 and 3;

Fig. 4 is a bottom plan'view of the structure shown in Figs. 1 and 3;

Fig. 5 is a section taken substantially on line 5-5 of Fig. 3;

Fig. 6 is an assembly view of the spring loading cam device shown in Figs. 1 and 3;

Fig. 7 is a fragmental view of the structure shown in Fig. 3 illustrating the spring loading cam device in a position such as may be employed for initially grinding a cylinder to remove tool marks and high points;

Fig. 8 is a top plan view of the rotatable part of the cam device in the position illustrated in Fig. '7;

Fig. 9 is a view similar to Fig. '7 illustrating the cam device in a position for loading the expanding spring to a greater extent such as may be maximum spring loading;

Fig. 12 is a top plan view of the rotatable part of the cam device in the position shown in Fig.

Fig. 13 is a vertical sectional view of a modimatically to predetermined size and a plurality fled form of tool embodying my invention;

Fig. 14 is a partial elevational view of the structure shown in Fig. 13 illustrating the tool driving means; and

Fig. 15 is a bottom plan view of the tool shown in Fig. 13, certain portions thereof being cut away to better illustrate the structure.

Although the tool shown in the drawings is well adapted for the grinding .of cylinders in the so-called production field, it is to be understood that it may also be used for grinding tools in the so-called service field. In use, the tool shown in Figs. 1 to 12, inclusive, is driven by a so-called honing or grinding machine (not shown) having a spindle (not shown) connected to a ball head on the tool forming part of a universal joint. The ball head 20 is carried by a yoke member 21 connected to the tool body, which will now be described.

The tool body (Figs. 1-4) is of a rigid, framelike construction including a pair of end plates 22 and 2-3 axially spaced apart and rigidly secured together by an annular series of posts 24 forming radial passages which are mounted abrasive carriers 25. The lower ends of the posts 24 are riveted in the bottom plate 23, and their u e t eaded upper ends a c e in t e p P at 2 by nuts 25, The note 2 are leea e n coun unk openin s termed. in th up r fac o t e en plate 32 fer a eason which W111 become obvious hereina er.

Each of the senior members is of identical construction and only one will be described in detail. Each c rrier comprise .a rectaneularly shaped body :21 3 and i) having end tongueelike portions 1Z1 slidab'ly mounte n radially directed grooves 2.8 and 2:9 formed in the facing surfaces of the end plates 23 and 23. Each carrier "body 21 is provided at its .outer edge with an enlarged head-like portion having therein a longitudinally extending channel which receives an abrastive unit including a channeled support 31 and a grinding stone 32 secured therein. The abrasive unit is secured in the carrier channel by a longitudinally extending clamp block 33 held in place by screw studs 34.

The tool shown in Figs. 1 and 3 is adapted for the grinding of so-called blind bores and, to this end, each carrier body 21 is provided with an overhanging portion 21 which extends downwardly past the peripheral edge of the lower end plate 23 which is shaped as shown in Fig. 4. That is to say, the periphery of the bottom plate 23 is provided with alternating humps and depressions and the carrier body portions 21 overhang the peripheral edge of the depressed portions thereof. The hump portions of the bottom plate 23 receive the ends of the posts 24 whereby the posts are located in close proximity to the periphery of the end plates 22 and 23 making the tool frame much more rigid so that it will transmit a greater torque without material distortion.

The carriers 25 are retained in the end plate grooves 23 and 29 by a garter spring 35 (Figs. 3 and 4) seated in grooves formed in the outer edge of the upper carrier tongue 21*- and by a garter spring 36 engaging hooks 31 secured by screws 38 to the overhanging carrier portions 2 he ar e s 2 a e sup or ed at their er ed e by a central exp nd n ee e un t comprising a stem 39 supporting a pair of cone elements 4t, 41 which en ge in e mp em nt y aped notc s 42 formed the i ner edg s o the carrier bodies 21. A sleeve 43 is fixed in an opening i the bottom plate 23 and it slidably receives and supports the lower end of the cone stem 39. The cones 40, 4| are prevented from rotating by a post 3% (Fig. 4) carried by the end plates 22 and 23 and received in notches 39 in the cones. The stem 39 extends upwardly through and beyond an enlarged opening 45 (Fig. 3) in the top end plate 22 for cooperation with means for automatically expanding the carriers 25 toward the cylinder wall, which is diagrammatically illustrated at 46 (Figs. 1 and 3). The carriers are expanded by movement of the stem 39 and. cones 40, 4| axially upward against the slight pressure ofiered by the garter springs 35 and 36. When the stem 39 is moved downwardly the carriers are contracted or moved away from the cylinder wall 43 through the action of the garter springs 35 and 36. The mechanism for. moving the cone unit to automatically expand the tool will ow be described.

The to l ex and n me s c des a two-part cam device comprising an upper annular and tubular cam element 41 having a depending socketelike portion 48 with an opening 4,8 in its bottom through which the cone unit stem 39 slidably passes. The depending portion 48 of this cam element is also ,slidably received in the opening 45 in the top end plate 22 so that it is positively guided for axial slide movement along the stem 39 by both the stem 39 and end plate 22. Rotation of cam element 41 is prevented by a key 49 carried in a slot formed in the upper I end plate 22 and engaging a longitudinally ex.- tendin d o gat d keyw y .59 fo med n t adjacent exterior wall of the tubular porti n 48 of the cam element 41 (Figs. 3, 7, 9 and 11).

:By f rm h c m emen a Just n'bed, it is p ov ded th a ce t al x al elon a d socket 41 (Fi 3 in wh ch is re ive a c il d compression spr n 5. th ou h which the eeri stem 9 p she stem 39 extends outwardly beyond e pring 51 (Fi and its outer e is externally threaded at 333 to receive an adjusting nut 52. The spring 51, which extends outwardly beyond the upper end of the socket 41 is confined between the lower face of the adjusting nut .52 and the bottom of the socket 41. This arrangement is such that, byscrewi-ng the nut 52 downwardly on the cone stem 39,

the spring 51 is compressed slightly due to the resistance offered by the garter springs 35 and 33. This causes the cone stem 39 to move upwardly and expand the carriers 25. More particularly, in the use of this tool, it may be inserted in the cylinder 43, as shown in Fig. 3, and

the nut 52 adjusted downwardly. This adjustment of the nut 52 pulls cones 43 upwardly to expand the stonecarriers 25 to initially engage the stones 32 with the cylinder wall. After the grinding stones 32 are engaged with the cylinder wall, the spring 5| is loaded by the cam 41. As soon as the carriers engage the cylinder wall no further expansion occurs until grinding takes place. However, after the carriers 25 have engaged the cylinder wall one may, in using my invention, cause the tool to be automatically expanded during the grinding operation and the grinding operation to be carried on under a predetermined unit stone pressure by further compressing the spring 51. By unit stone pressure, I mean the pressure applied over each square inch of grinding stone area in contact with the cylinder wall.

It is highly desirable, in order that best grinding results be obtained, that materials of difierent hardness be ground with varying unit stone pressures and that, in the grinding of a single cylinder of predetermined hardness, the tool marks and high points be initially removed by rinding under a preliminary and much reduced stone pressure. If the full grinding pressure for the particular material being ground were employed in removing tool marks and high points, the grinding stones would be rapidly broken down or injured to an extentv requiring replacement thereof. For example, in the grinding of newly bored or formed cast iron and mild steel cylinders, I have found that a unit stone pressure of approximately five pounds may best be employed in removing tool marks and high points and that the unit stone pressure employed in finally grinding the cylinder should, preferably, vary from twenty to thirty pounds; whereas, in the grinding of cylinders formed from extremely. hard materials which require considerable pressure in order that the abrasive grains may penetrate the surface being ground, the initial unit stone pressure may vary from five to ten pounds while the final pressure may vary from fifty to sixty pounds. In carrying out my invention, the compression spring is so constructed that predetermined extents of compression of the same produce predetermined spring loadings for causing the stone carriers to engage the cylinder wall under predetermined unit stone pressures. These spring loadings and unit stone pressures might be obtained in the tool so far described (Figs. 1 and 3) by adjusting the nut 52 downwardly on the cone stem 39 to predetermined extents after the carriers have been adjusted into engagement with the cylinder wall. However, the accuracy of such an adjustment would depend upon the care and skill of the operator and, in order that the human element may be avoided and positive accuracy in adjustment may be insured, I provide an arrangement wherein the cam element 41' may be accurately shifted axially predeter mined extents, after the stone carriers have been set up initially against the cylinder wall. More specifically, a second annular cam element 53 (Figs. 1-3 and 5-12) is mounted between the cam element 4'! and the upper face of the top end plate 22, which lower cam element is mounted upon and guided rotatably by the depending tubular portion 48 of the upper cam element 41. The lower face of the upper cam element 41 (Fig. 6) is provided with a plurality of notches 54, each "ofwhich has an inclined camway 55 and a vertical end wall 55 The lower cam element 53 is provided, on its upper face, with a similar number of notches 56 shaped complementally to the notches 54, being provided with inclined camways 57 and vertical end walls 51 The cam elements 41 and 53, in the normal, contracted condition of the tool (Figs. 1 and 3), are disposed in a closed or fully nested relation with their cam faces 55and 5! engaged throughout and their vertical notch walls 55 and 5! abutting.

The cam elements .41 and 53 are so constructed that by rotating the lower cam element 53 in a clockwise direction, as viewed in Figs. 1 and 3,

the high points of the camways 51 of the lower cam element 53 are moved toward the high points of the camways 55 of the upper cam element 41, and the upper cam element 41 is shifted axially upward, in turn, compressing the spring 5|.

It will be seen from the foregoing that a predetermined compression of the spring 5! effecting a predetermined spring loading and unit stone pressure may be accomplished by a predetermined rotation of the lower cam element 53. Therefore, having determined the desirable spring loading for preliminary grinding to remove high points, etc., and having determined the desirable loading for finally grinding either a cast iron or mild steel or a harder cylinder, the lower cam element 53 may be rotated to a predetermined position and held there so that the tool will not only be automatically expanded during the grinding operation, but such operation will be carried on under a selected unit stone pressure.

The lower cam element is held in its selected rotary position by latching means. Specifically, the upper end plate 22 is provided with an opening 58 in which is received a ball 59 constantly urged upwardly by a spring 69. The underface of the lower cam element 53 is provided with four notches or depressions 6|, 62, 63 and 64 located at spaced points in an arcuate path around the bottom of such element in alignment with ball 59 so that, when the lower cam element is in its normal or home position (Figs. 1 and 3) the ball 59 is seated in the notch 6| yieldably retaining the cam element 53 in that position. When the cam element 53 is rotated clockwise from the position of Fig. 3, as will be permitted by the latch ball 60, and the notch 52 thereof comes into alignment with and receives the ball 59, the cam element 53 (Figs. 7 and 8) is yieldably latched and held in that position wherein the spring 5i is compressed to an extent sufiicient to apply, for example, five pounds unit stone pressure. Then, by further rotating the cam element 53 until the ball 59 engages in the notch 53 (Figs, 9 and 10), the spring 5| is further compressed to exert a unit stone pressure of, for example, twenty pounds; and by rotating the cam element 53 to a position wherein the ball 59 engages the notch 54 (Figs. 11 and 12), the spring is set for exerting a unit stone pressure of, for example, sixty pounds. It is highly desirable that the clockwise rotation of the lower cam element be limited so as to not pass beyond the maximum pressure notch 64 and, to that end (Figs. 3 3 5, 8, 10 and 12), the upper end plate is provided with an upwardly projecting pin 65 in the rotary path of and received in an arcuate notch 65 formed. in the lower face of the lower cam element 53. As will be seen from Fig. 5, when the lower cam element 53 is in its normal at home position, the pin is at one end of the notch 55. As the cam element 53 is rotated clockwise, the

. pin moves along the notch 66, as indicated in Figs. 8 and 10, and, by the time the cam element is rotated to its maximum pressure position, the pin 55 has reached the opposite end of the notch 66, as shown in Fig. 12, preventing further rotation of the cam element.

In order that a single cylinder or successive cylinders may be ground to predetermined size with precision accuracy and with a minimum of attention on the part of the operator, I provide means for limiting the expansion of the tool, in turn, determining the amount or thickness of material to be removed from the cylinder wall. Specifically, the universal tool driving head 2!) is provided with an axial threaded opening w (Fig. 3) which receives a threaded shaft 6! having an adjusting head 89 on the lower depending end thereof. This head 59 is provided on its upper inclined surface ill with a scale graduated in thousandths of an inch, and it also has a lower knurled portion H which permits ready adjust ment of the same. The head 6-9 is in axial alignment with the upper end of the cone stem 39 and the bottom of such head has a small rounded head or nose 12 adapted to abut the upper end of the stem 38. The ball head 20 supports an indicating element 13 having a lower pointed end which registers with the scale F on the adjusting nut or head 69. It will be seen that by adjusting the nut 69 toward and from the stem 39 the extent of axial movement of such stem is controlled or limited, in turn, controlling the extent of expansion of the abrasive carriers and the extent of grinding a cylinder.

In the use, assuming that .010" material is to be removed from a newly bored cast iron cylinder, the tool is placed in the cylinder as illustrated in Fig. l, and the adjusting nut 52 is screwed downwardly causing the spring to move the cone unit to expand the abrasive carriers into firm engagement with the cylinder wall as. The adjustment limiting or stop nut 69 is then screwed downwardly until it engages the end of the cone stem 39, after which the operator notes the position of the scale 19 relative to the indicating element l3 and then backs off the. nut 69 .910 as indicated on the scale Hi. It will be appreciated that in the grinding of a cylinder the grinding stone wears away to a certain extent, say .095. Knowing this, the operator, in order to grind .010 from the cylinder wall 46, backs off the adjustment limiting nut 59 an additional .005. The lower pressure cam element 53 is next adjusted clockwise to its first position wherein the ball 59 seats in the notch 62 in the lower cam element. When this is done the cone unit does not shift or expand the tool until grinding takes place, but the spring 5% is placed under a load causing the grinding stones 32 to engage the cyl inder wall with, for example, a five pound unit stone pressure. The tool is now rotated, reciprocated and expanded in the bore for a short time until the high points and tool marks are removed, whereupon the tool is stopped and the cam element 53 is adjusted to its second position wherein the ball 59 engages the notch 63 in the lower face of the cam element. The grinding operation is then continued and, as grinding takes place, the spring 51 moves the cone unit upwardly and expands the carriers 25. During this operation, the spring 5| is under a substantial constant load exerting a substantial constant unit stone pressure. The cone stem 39 is eventually shifted to an extent wherein its upper end engages the nose l2 on the adjustment limiting nut (ill, preventing further expansion of the tool so that no further material is removed from the cylinder wall. When this has been done the cylinder has been ground .010".

To facilitate rotational movement of the lower cam element 53 against the action of the spring 5!, it is provided with a plurality of openings 1 which are adapted to receive a suitable tool through which pressure may be applied for rotating the cam element. As soon as the grinding operation is completed, the tool may be collapsed by rotating the cam element in a counterclockwise direction back to its normal position of Figs. 1 and 3. The tool in this condition is collapsed for ready removal from the cylinder. If it is desired to grind a plurality of cylinders to the same size, all that the operator need do is to make a further adjustment in the adjustment lmiiting nut 69 to compensate for stone wear. The tool is then placed in the next cylinder, the lower cam element 53 set up to its different positions, and the cylinder ground as above explained. In the event that a cylinder formed of a harder material than cast iron or mild steel is to be ground, the cam element 53 may be set up to the first position above explained for removing tool marks and high points and then finally set up to its maximum position wherein the ball 59 engages the notch E l in the lower face of thecam element 53. In grinding such harder cylinders, the operation is otherwise the same as explained in connection with cast iron and mild steel cylinders, except that in some cases grinding stones of different character may be substituted.

It will be appreciated that in the use of the foregoing tool a very great amount of torque must be absorbed through the stone carriers, 'particularly when the tool is adjusted for final grinding pressures of twenty pounds or more. In this type tool this torque is transmitted into the stone carriers through the tongue-and-groove construction at the end thereof. Consequently, there is a constant tendency for the carriers to deflect during the grinding operation'and, in some cases, unless guarded against, this deflection may be sufficient to permanently distort or bind the carriers in their grooves and render them useless. In carrying out my invention, I utilize the end plate supporting parts 24 for preventing any motional deflection of the carriers or deflection which would tend to permanently distort and injure the carriers.

More particularly, with the tool rotating in a clockwise direction, as viewed in Fig. 1, the drag imposed on the carriers by the cylinder wall tends to deflect the carriers in a counterclockwise di rection. I therefore mount each carrier 25 counterclockwise of one of the posts 24 (Figs. 1 and 4) and in close proximity thereto. Each carrier body 21 is provided with a central, elongated pad 15 disposed in alignment with the adjacent post 24 and long enough to remain in alignment with the post throughout the range of adjustment of the carrier. The pads I5 are of such thickness and the carrier bodies are so located that the outer faces of the pads are spaced from the posts a distance of, for example, two to five thousandths of an inch. Deflection of the carrier bodies 2'! is greatest at the central part where the pads 15 are located and when the car rier bodies are deflected sufficiently for the pads 15 to engage the posts 24, further deflection cannot take place. In this way, injurious deflection is prevented and the tool :body as a whole is rendered more rigid during the grinding operation.

While I have found that a tool of the foregoing construction well serves the purposes of my invention, it will be understood that my invention may be embodied in tools of different formsfor example, the form shown in Figs. 13 to 15, inclusive. Referring particularly to Fig. 13, this modified tool is quite similar to the tool previously described except for the particular manner of driving the tool and the particular means for determining the extent of adjustment, the grinding pressure and the extent of the grinding operation.

More particularly, this modified tool comprises a cage-like frame having end plates 80, 8| with radially directed grooves 82 in their facing surfaces supporting end tongues 83* of abrasive carriers 83. Each of the abrasive carriers supports a grinding stone unit 84 similar to the abrasive unit of the first-described form, except that ad ditional means is employed for positively preventing longitudinal displacement of the abrasive unit. Specifically, lugs are struck from the channel member 84 (Figs. 13 and 15), which supports the grinding stone 84 at spaced points along the length thereof. These lugs are rolled to form bead-like elements 84 which seat in notches 8 1 formed in the adjacent wall of the abrasive unit supporting channel 94 and the block 84 which clamps the unit in place against outward displacement.

The carriers 89 (Figs. 13 and 15) are yieldably urged in contracting direction by garter springs 85 applied to the opposite end portions of the carriers 83. The inner edges of the carriers are supported by a tubular cone unit 86 having I thereon cone members 81, 88 and an upwardly extending tubular shank portion 89 slidably supported ina central opening 99 in the upper end plate 99. The cone unit 86 is further supported .and guided for axial expansion movement by a central tubular member 9| rigidly secured at its lower end to the bottom plate 8|. The cone unit 89 is of such diameter as tosnugly receive the tubular member 9i, the lower end of the tubular member 95 being of enlarged diameter and having a laterally extending flange 92 received in a recess 93 in the outer face of the lower end plate 9i, where it is secured by an annular series of screw studs 99. r

The tool of Fig. 13 is driven'from the lower end plate 8|. Specifically, I provide a spindle 95, the upper end of which is provided with a ball head 96 forming part of a universaljoint 91 connected to a head 98 on a spindle of the so-called honing machine (not shown). The spindle 95 is of lesser diameter than and extends downwardly through the tubular member 91, its lower end being provided with a ball 99. This ball end 99 is provided with a diametrical pin lililwith oppositely extending ends received in diametrically opposed elongated slots lill formed in the lower end of the tubular member 9|. By enlarging the lower end of the tubular member 9| as above mentioned, there is provided a shoulder [02 against which seats the shoulder 193 of a two-part thrust bearing ring ltd having an annular arcuate bearing surface 495 against which the ball head 99 seats. The ball head and spindle are retained in the tubular member 9| by a nut I06 mounted in the lower, internally threaded end of the tubu lar member 9l'and having an annular bearing surface 19] against which the lower endof the ball 99 seats. When the nut 106 is 'securedin place, the ball head 99 is confined between it and the upper ring I94. 'Theends of the'universal drive pin I99 are free to rock in one direction due to the-length of the sljotslflhand they are also free to rotate in a right-angular direction about the bearing surfaces I95 and I01, thereby providing a universal drive connection which, together with the universal joint 91 at the other end of thespindleftlii, fully accommodates disalignmentbetween the grinding tool and its operating machine. r

The means for automatically expanding the abrasive carriers 83 is quite similar to that previously described. In this case (Figs. 13- and l4), I' provide an upper camielement I08 similar-to the cam elemental, except thatit is not pro vided with a depending tubular portion, but is merely mounted upon the cone unit 86 foraxial slide movement. To this latter end, the upper extending tubularpart 89 of the cone unit isprovided with an elongated slot I99 in which is received the-end of a pin H0 carried by the m element I08. Between the cam element I08 and the upper end plate 89, I mount a lower cam element F I l which is similar to the lower cam element of the first-described form, which cam element is mounted rotatably upon the tubular portion 89 of the cone unit 96 and is adapted to be located in its normal home position and in its various pressure-determining positions in the same manner as in the form previously described.

The adjusting mechanism of Figs. 13 and 14 furtherinciudes a pressure spring H2 confined between the upper cam element I98 and a pressure adjusting nut H3 threaded upon the upper exteriorly threaded end of the tubular portion 89 of the cone unit. 111 the use of this tool, the nut MS may be initially adjusted downwardly to expand the stone carriers 83 into engagement with the cylinder wall, after which the lower cam element HE is rotated, as described in connection with the first form, to get the desired unit stone pressure. If desired, the unit stone pressure may be varied by screwing downwardly to a further extent the adjusting nut US after the abrasive carriers have been set against the cylinder wall. The extent to which the nut may be adjusted in this instance may be determined by the operator in any suitable manner.

In this modified form of tool (Figs. 13-15) I also provide an adjustment limiting means which includes an adjusting nut H5 threadedly engaged with the upper end of the tubular member 9| and having a bead H6 on its bottom face adapted to engage the upper end of the tubular portion 9| of the cone unit. This nut serves the same purpose in the same way as th nut 69 of the first form, the same being set after the abrasive members have engaged the cylinder wall by moving it first into engagement with the upper end of the cone unit 9! and then backing it away to an extent equal to the thickness of material to be removed from the cylinder wall plus stone wear. The extent of adjustment of this nut H5 may be determined by a scale II! on the lower part thereof which registers with an indicating element I [9 carried by a ring-like member I [9 secured to the upper portion of the adjusting nut H3. Otherwise the construction and operation of this form of my invention are similar to the construction and operation of the form previously described.

It is believed that the operation and advantages of my invention will be well understood-from the foregoing description. My invention not only provides a simple and inexpensive tool but one which is quite rugged and durable. It is well suited for heavy duty work with precision results. The work to be done by the operator is reduced to the Very minimum. Accurate grinding pressures are obtainable without guesswork merely by setting the adjustable cam device to different positions representing selected pressures. This arrangement greatly facilitates not only the grinding of a single cylinder but successive cylinders. In the grinding of successive cylinders the only adjustment required is adjustment of the grinding limit stop to compensate for stone wear, after the grinding of the first cylinder. The grinding operation is further greatly facilitated by the readiness in which the tool may be applied to and removed from a cylinder. After the grinding operation the only adjustment required to remove the toolis movement of the cam device to its home position. This can be done easily and quickly and when it is done the-tool is conditioned for immediate insertion in a new cylinder.

I claim:

1. A cylinder grinding tool comprising a body, abrasive carriers mounted in said body for movement toward and from a cylinder wall to be ground, means for moving said abrasive carriers toward the cylinder wall including a member shiitable in a direction to so move said carriers, a spring compressible for shifting said member, an element carried by said member and adjustable therealong in one axial direction to initially compress said spring and shift said member to cause said carriers to initially engage the cylinder wall, another element on said member adjustable independently of said first element to compress and hold compressed said spring to difierent selected extents after said carriers are initiallyengaged with the cylinder wall for effecting movement of said carriers toward the cylinder wall under different selected pressures during the grinding operation.

2 A cylinder grinding tool comprising a body, abrasive carriers supported by said body for expansion and contraction movements, and means for automatically expanding said carriers prior to and during the grinding operation which includes a member engaging said carriers and movable in one direction to expand said carriers, compressible spring means for urging said member in said one direction, and means for compressing said spring means to variable extents for applying predetermined grinding pressures which includes devices at the opposite ends of said spring means, each of said devices being carried by said carrier-engaging member and being adjustable axially of said spring means in opposite directions and independently of each other to effect independent compression of said spring, and means for holding one of said devices in any one of a plurality of predetermined positions for applying predetermined grinding pressures.

3. A cylinder grinding tool comprising a body, abrasive carriers mounted in said body for movement toward and from a cylinder wall to be ground, means engaging said carriers and move able to move said carriers toward the cylinder wall, and means for moving said carrier-moving means to automatically move said carriers t9? Ward the cylinder wall including an element car.- ried by and axially adjustable therealong and forming part of said carrier-moving meaILS, a Com v e, and a comp es ion sp in s d cam device having; two parts, one of which is adjust,- able rotatably to move the other part aXially of said spring and having a plurality of positions, to compress the latter to different selected extents for exerting a predetermined grinding pressure.

A y inder r nding tool co p ising a body, abrasive carriers supported by said body for movement toward a cylinder wall to be ground, and means for moving said carriers toward the cylinder wall which includes a member engaging said carriers and movable axially of said body in one direction, an adjustable element on said mem-v ber, a second element mounted for adjustable slide movement only along said member, a compression spring adapted to be compressed :by adjustment of said elements, and a third element mounted for rotation only and having cam means engaging said second element and so constructed that as said third element is rotated in one direction said second element is shifted axially of said spring to compress the latter to variable extents, and means for releasably latching said third ele ment in any one of a plurality of selected rotary positions to cause said spring to exert any one of a plurality of selected grinding pressures.

5. A cylinder grinding tool comprising a body, abrasive carriers mounted in said body for movement toward and from the cylinder to be ground, means for moving said abrasive carriers toward the cylinder wall including shiftable expanding elements engaging said abrasive carriers, a member supporting said elements and movable to shift the latter, a compression spring for moving said supporting member in one direction, an element on said supporting member slidably movable in one direction relative to said supporting member tov compress said spring,. means having a I plus rality of predetermined positions for sliding said slida le element to predetermined selected extents to compress said spring for moving said supporting member under predetermined pressures, a d means. for limiting movement of said supportin m mber in one direction to limit the extents? the. grinding operation.

6- A cyli der rinding tool comprising a body, abrasive carriers mounted in said body for move ment teward and from the cylinder to be ground, means fer moving said abrasive carriers toward he cylind r W ll nclu n e panding elements enga ng said a rasi e ca rier-s, a movable member supporting said expanding elements and mova e o. shi he a ter to expand saidcarriers, a ompr ssion spr n tending to. move said suppor ing member o hi t id expandin el m n s, moons adjus able o compress s d. spring to vary e p ssure unde wh ch s id suppor ing mem ber i mo od s i t sa d ex and n elements, moans movable to. ny one o a plura ity oi position o adj s n said, d usta e means to compr s aid. sp ing t prede rmined select d exten s, and me ns. o e ea b y ho d n said ad.- iustine m ns. n any o e oi its adiu ted. positions o ma t ng any on a p u a ity of selected grinding pressures, i 7, cyl e g ing o oomp isins a ody, abrasiv a iers mou ted. in sa d b dy o movement o rd and f om he y ind r to b ground, means for'moving said abrasive carriers toward the cylinder wall including expanding elements ng in saidabrasive carriers, a movable mom-s ber supporting said expanding elements and movable to shii the latter to expa a d ar iers, a compre sio spr n tending to o e said s portins. mem er h ft s d e pan i g ements, means, adiustable to compress said spring to vary the pressure under which said supporting member s, moved, to sh f said expanding ments, m ans movable to any one of a plurality of positions, for adj ing said adjustable mean o, compre s id spring to predetermined selected extents, means o r leasa'b'ly h ld nslsaid adjusti mo siin any one of its adjusted positions for'maintai'nin g any onev of a plurality of selected grinding press sures, and means for variably limiting'the-extent o ovom nt of sa mem e and; in. turn, "the extent ofv the grinding operation, j A

8. A cylinder grinding tool cg'rnprising'aj body', abrasive carriers mounted in said bqdyfiorfexpan i n and ontr n; mo mo tsjm nsj for expanding saidabrasive carriers including a,

shiftabledevi ce having elements engaging; said carriers-to expand the latter when said device'i's shifted-in one direction-, a compression spring tending to shift saidf device, a first adjustable mean-ea second adjustable means, one of said adjustable means beingadj-ustable to preliminarily compress-said spring to expand said carriersto initially engage acylinder wall, and the other e! said adjustable means including a part adjustable to shift said other adjustable means and compress said spring to predetermined extents to cause the grinding operation to take place under selected grinding pressures, and means for releasably holding said adjustable part in any one of a plurality of adjusted positions.

9. A cylinder grinding tool comprising a body, abrasive carriers mounted in said body for movement toward and from a cylinder wall to be ground, spring means engaging said carriers and yieldably urging the same inwardly away from the cylinder wall, a stem member passing through said body, expanding elements on said stem member engaging said carriers and moving the latter toward the cylinder wall in opposition to, said spring means when said stem member is moved in one direction, means for moving said stem mem ber in said one direction which includes a member mounted on said stem member and adjustable axially thereof, a member slidably carried by said stem member for axial shift movement only along said stem member, a rotatable member having cam means which, upon rotation of said rotatable member, shifts said slidable member axially of said stem member, a compression spring adapted to be compressed by adjustment of either of said adjustable members and which, when placed under compression, tends to move said stem member in a direction to move said carriers toward the cylinder wall, and means for latching said rotatable memberin a plurality of rotary positions wherein said spring is compressed to predetermined and variable extents for exerting selected grinding pressures during the grinding operation. V

10. A cylinder grinding tool comprising a body, abrasive carriers mounted in said body for movement toward and from a cylinder to be ground, means for moving said carriers toward the cylinder wall which includes a stem member passing through said body, elements on said stem engaging said carrier and expanding the latter when said stem is shifted in one direction, an adjusting member on said stem, a two-part cam device, one part of said device being slidably supported by said stem and the other part being rotatable about said one part and held against longitudinal displacement, said two parts of said cam device having engaged cam faces so shaped that rotation of said rotatable part shifts said slidable part axially along said stem, a spring adapted to be compressed by adjustment of said adjusting member or said one part of said cam device, means for releasably holding said rotatable cam part in certain ones of a plurality of rotatable positions for holding said spring compressed to predetermined extents, the cam faces of said cam parts being also shaped to limit rotation of said rotatable cam. part in a direction toward its normal non-spring-compressing condition, and stop means limiting the extent of rotation of said rotatable cam part in a spring compressing direction.

11. A cylinder grindin tool comprising a body, abrasive carriers mounted in said body for movement toward and from the wall of a cylinder to be ground, a tubular member rigidly secured at its lower end to and passing centrally through and beyond one end of said body, a carrier expanding device slidably mounted upon said tubular member and engaging said carriers to move them toward the cylinder wall, and means moving said device to so move said carriers which includes a, member adjustably mounted on said device, a two-part member on said device, one part of said two-part member being supported to shift axially only and the other part being supported to rotate only to shift said one part axially, and a compression spring carried by said expanding device, the arrangement being such that said first adjustable member is adjustable to compress said spring to shift said device to cause said carriers to initially engage the cylinder wall, and said two-part member is independently adjustable by rotation of said rotatable part thereof to further compress said spring to effect a predetermined grinding pressure.

12. A cylinder grinding tool comprising a body, abrasive carriers mounted in said body for movement toward and from the Wall of a cylinder to be ground, a tubular member rigidly secured to and passing centrally through and beyond one end ofsaid body, a carrier expanding device slidably mounted upon said tubular member and engaging said carriers to move them toward the cylinder wall, and means moving said device to so move said carriers which includes a member adjustably mounted on said device, a two-part member on said device, one part of said twopart member being shiftable axially only and the other part being rotatable only to shift said one part axially, and a compression sprin carried by said expanding device, said first adjustable member being adjustable to compress said spring to shift said device to cause said carriers to initially engage the cylinder wall, and said twopart member being independently adjustable by rotation of said rotatable part thereof to further compress said spring to effect a predetermined grinding pressure, and a member mounted on said tubular member in axial alignment with said expanding device and adjustable toward and from said expanding device to limit the extent of movement of the latter and in turn the extent of the grinding operation.

13. A cylinder grinding tool comprising a body, abrasive carrier mounted in said body for movement toward and from the wall of a cylinder to be ground, a tubular member rigidly secured to one end of said body, a second tubular member mounted upon and slidable along said first tubular member, expander elements on said second tubular member engaging said carriers to expand the latter as said second tubular member is shifted in one direction, and means for shiftin said second tubular member in said one direction which includes a first member mounted on said second tubular member and adjustable therealong, a second member rotatable upon said sec ond tubular member, a third member slidable along said second tubular member and seated against said second member, said second and third members having complemental abutting camways whereby rotation of said second member moves said third member axially along said second tubular member toward said first member, and a compression spring mounted upon said second tubular member and compressed by adjustment of said adjustable members to shift said second tubular member to expand said carriers and to exert a selected grinding pressure through said carriers.

14. A cylinder grinding tool comprising a body, abrasive carriers mounted in said body for expansion and contraction movements, shiftable means engaging said carriers to expand and contract the same as it is shifted, and means for shifting said shiftable means to expand said carriers which includes a compression spring which when compressed tends to move said shiftable means in carrier expanding direction, a device carried by said shiftable means and supporting one end of said spring and adjustable to compress said spring and effect initial engagement arse-id carriers with the cylinder wall, and another device carried by said shiftable means and seated upon said body for supporting the other end of said spring and adjustable aftersaid carriers have been engaged with. the cylinder wall to. further compress said spring to establish a range of expansion of said carriers as the grinding operation is carried on and to cause said carriers to move toward the cylinder wall under a predetermined pressure, and means located in the axial path of said shiftable: means and adjustable axially toward. and from the latter to engage said shiftable means with said axially adjustable means sooner or later to limit the extent of shift of said shiftable means and the expansion of said carriers.

15. A rotatable cylinder grinding tool comprising end plates having radially extendin grooves in their facing surfaces, a plurality of annularly disposed posts rigidly joining together said end plates in. spaced relation and defining radial passageways, abrasive carriers mounted in said passageways and having end portions slidably mounted in said end plate grooves,- and means for limiting the extent of deflection of saidcarriers during the grinding operation including: elements on said carriers disposed in close proximity to said posts and adapted to engage the latter upon a predetermined deflection of said carriers in a direction opposite the direction of rotation of the tool.

16. A rotatable cylinder grinding tool comprising end plates having radially extending grooves in their facing surfaces, a plurality of annularly disposed posts rigidly joining together said end plates in spaced relation and defining radial passageways, abrasive carriers mounted in said passageways each of said carriers having: a rectangularly-shaped body portion and end portions slidably mounted in said end plate grooves, abrasive stones carried by the outer edges of said carrier bodies, carrier-expanding means engag ing the inner edges of saidcarri'er bodies, means by which the tool may be rotatably driven, and means limiting the extent of deflection of said carrier bodies including an abutment element on the rear side, with respect to direction of tool rotation, of each said carrier body adapted to abut said posts, respectively, upon a' s'lig-ht deflection of said carrier bodies in a direction opposite the direction of tool rotation.

17. A rotatable cylinder grinding tool comprising end plates having radially extending grooves in their facing surfaces, a plurality of annularly disposed posts rigidly joining together said end plates in spaced relation and defining radial passageways, abrasive carriers mounted in said passageways, each of said carriers having a rectangularly shaped body portion and end portions slidably mounted in said end plate grooves, abrasive stones carried by the outer edges of said earrier bodies, carrier-expanding means engaging the inner edges of said carrier bodies, means by which the tool may be rotatably driven, and means limitin the extent of deflection of each of said carrier bodies including an elongated pad element on the central part of the rear side,- with respect to direction of tool rotation, of each said carrier body, said pad element being aligned with the adjacent one of said posts, being thick enough to abuttingly engag said post upon slight deflection of the central portion of said carrier body, and being long enough to so engage said post throughout the operating range of expansion of said carrier body.

CHARLES A. FULMER.

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