US3498004A

US3498004A - Grinding machines

Info

Publication number: US3498004A
Application number: US474058A
Authority: US
Inventors: James L Hensley
Original assignee: Carborundum Co
Current assignee: Unifrax 1 LLC
Priority date: 1965-07-22
Filing date: 1965-07-22
Publication date: 1970-03-03
Anticipated expiration: 1987-03-03
Also published as: ES329385A1; DE1577316A1; GB1118414A; AT270425B; BE684466A; SE327925B

Description

March 3,1910 J. 1.. HENSLEY 3,498,004

GRINDING MACHINES Filed July 22, 1965 12 Sheets-Sheet 1 JAMES L. HENSLEY BY M, M,MAM{M ATTORNEY S Manila 3,1970 J. L. HENSLEY I I 3,498,004

GRINDING MACHINES Filed July 22, 1965 I 12 Sheets-Sheet 2 INVENT OR JAMES L. HENSLEY M au w M {nu-A44 ATTORNEYS March 3, 1970 J. L. HENSLEY 3,498,004

- GRINDING MACHINES Filed July 22, 1965 12 Sheets-Sheet 5 INVENTOR JAMES L. HENSLEY ATTORNEYS J. L. HENSLEY GRINDING MACHINES March 3, 1910 12 Sheets-Sheet 4 Filed July 22, 1965 INVENTOR JAMES L. HENSLEY ATTORNEY March 3,1970 J. L. HENSLEY 3,498,004

GRINDING mcnmns Filed July 22, 1965 12 Sheets-Sheet 5 JAMES L. HENSLEY M AM, M {flaw/4 ATTORNEYS Mar ch 3,1970 J. L. HENSLEY 3,

GRINDING MACHINES Filed July 22, 1965 12 Sheets-Sheet 6 ATTORNEYS March 3, 1970 J. L. HENSLEY GRINDING MACHINES 12 Sheets-Sheet 7 Filed July 22, 1965 INVENTOR JAMES L. HENSLEY ATTORNEYS ,1. L. HENSLEY GRINDING MACHINES March 3, 1970 12 Sheets-Sheet 8 Filed July 22, 1965 FIG."

FIGJZ ATTORNEYS BY M W Mlwedirf J. L HENSLEY GRINDING MACHINES March 3, 1970 Filed July 22, 1965' '12 Sheets-Sheet 9 INVENTOR JAMES L. HENSLEY ATTORNEY 12 Sheets-Sheet 10 Filed July 22, 1965 INVENTOR JAMES L. HENSLEY BY M, @M,WM4MM;

ATTORNEYS March 3, 1970 .1. L. HENS LEY 3,498,004

GRINDING MACHINES Filed July 22, 1965 I2 Sheets-Sheet 11 INVENT OR 2 JAMES L. HENSLEY Li Z 14 n m yw-A,

ATTORNEY- March 3, 1970 J. L. HEN SLEY GRINDING MACHINES 12 Sheets-Sheet 12 Filed July 22, 1965 use FIGZO INVENTOR JAMES L. HENSLEY ATTORNEYS United States Patent 3,498,004 GRINDING MACHINES James L. Hensley, Knoxville, Tenn., assignor, by mesne assignments, to The Carborundum Company, Niagara Falls, N.Y., a corporation of Delaware Filed July 22, 1965, Ser. No. 474,058 Int. Cl. B24b 7/00, 9/00, 55/04 US. Cl. 5199 13 Claims ABSTRACT THE DISCLOSURE A grinding machine having a grinding wheel supported on a boom for relative movement with respect to a movable body and with the power driving unit also mounted on the boom to move therewith. The output shaft of the power unit is in axial alignment with the axis of bodily movement of the grinding wheel, which latter is suspended below the axis for operating on the work and is capable of bodily movement transversely relative thereto. Means is provided for effecting driving connection from the output shaft of the power unit to the drive shaft of the wheel to drive the latter and to maintain the driving connection in the different transverse positions of the wheel. The bodily shifting movement of the wheel is effected by power means acting transversely of a line extending from the axis of swinging movement of the center of the wheel.

This invention relates to improvements in grinding machines and, more particularly, to grinders of the character used for the preparation of grinding surfaces of semi-finished steel slabs or billets in preparation for rolling these into plates.

Grinding machines of this character, as used heretofore, have been materially limited in their operating speeds and cost of operation. It has been highly desirable to effect materially increased operating surface speeds and improved conditioning practices, but the machines available heretofore have not been adequate to accomplish these results.

One object of this invention is to improve the construction of grinding machines to enable these to be operated at materially greater surface speeds and at lower cost of operation.

Another object of the invention is to provide for positive control of the grinding pressure.

Still another object of the invention is to provide for the operation of the grinding wheel around a pivot point which is directly in line with the power output shaft that drives the wheel, thus to effect a very sensitive control eliminating all positive side chatter. The are of swinging movement from the high pivot point provides the operator with a sensitive wide sweep and smoother blending of deep defects in the work. Thus, a constant pressure can be obtained which is directly related to the topography of the slab or billet surface.

A further object of the invention is to provide a constant contact at controlled depths of cut at various track speeds in the operation of the grinding wheel.

These objects may be accomplished, according to one embodiment of the invention, by mounting the wheel for bodily swinging movement through an arc with respect to the work about a pivot point or center axis which is directly over the center line of the wheel. With such a support an actuating cylinder can be connected to the wheel support at one side thereof so as to provide in effect a three-point suspension of the wheel by means of which a very sensitive control can be obtained, eliminating all possible side chatter.

The long wheel radius afforded by this arrangement produces a flatter wheel face, wider contact and, of

3,498,004 Patented Mar. 3, 1970 course, a finer finish. The are of swinging movement from the overhead or higher pivot point provides a sensitive wide sweep and smoother blending of deep defects in surfaces of the work. The sudden stress on the corner of the grinding wheel is considerably relieve from the arc generated on the high pivot point.

The spindle and guard assembly are pivotally mounted on a shaft in line with the output shaft of the speed reducer or gear box. This enables the grinding wheel to be oscillated through the are mentioned without twisting the V-belts or other drive means and maintains a positive driving connection therewith in all positions of swinging movement. A double acting hydraulic cylinder effects the swinging movement.

The wheel is preferably supported on one end of a pivoted boom, which is pivotally mounted on and suspended from a carriage adapted to travel lengthwise of tracks by means of which the carriage is guided in its back and forth movements so as to traverse with respect to the work. The swinging movement of the pivoted boom not only moves the wheel into and out of operating positions with respect to the billets or slabs, but also enables the wheel to follow the topography of the work surfaces.

Hydraulic cylinders are provided for swinging the boom vertically on its pivot with respect to the carriage and additional cylinders or other means may be used for moving the carriage lengthwise with respect to the body on which it is mounted. The body, in turn, is preferably adapted for traversing movement along the billets or slabs and may be mounted on track rails to effect this traverse. All of these controls are under the supervision of an operator who may be located, if desired, in a convenient relation to the machine such, for example, as in a cab attached thereto. In this way he can get close to the work surface for full visibility thereof.

This embodiment of the invention is illustrated in the accompanying drawings, in which:

FIG. 1 is a perspective view of the machine, with the machine, with the wheel in operating position;

FIG. 2 is a side elevation of the machine, with the wheel extended and raised;

FIG. 3 is an elevation of the wheel end of the machine;

FIG. 4 is a similar view of the rear end of the machine;

FIG. 5 is a disassembled perspective view of the pivoted boom and carriage, with the main parts separated from each other;

FIG. 6 is a partial side elevation of the body of the machine, with parts removed and showing the traverse means thereof;

FIG. 7 is a side elevation, showing the side opposite from FIG. 2;

FIG. 8 is a detail cross section through the grinding wheel assembly, taken on the line 88 in FIG. 11;

FIG. 9 is a top plan view of the machine, with the wheel retracted;

FIG. 10 is a detail section through the drive assembly for the grinding wheel when mounted at a 45 angle;

FIG. 11 is a side elevation of the grinding wheel and guard assembly;

FIG. 12 is a top plan view thereof;

FIG. 13 is an elevation at right angles to FIG. 12, with parts in section;

FIG. 14 is a diagrammatic view illustrating the swinging movements of the grinding wheel;

FIG. 15 is a detail side elevation showing the wheel at a 45 angle;

FIG. 16 is a detail elevation, partly in section, showing the body drive means;

FIG. 17 is a detail side elevation showing a further modification in the wheel drive;

FIG. 18 is a top plan view thereof;

FIG. 19 is an end elevation thereof; and

FIG. 20 is a detail section therethrough.

The embodiment of the invention illustrated in the drawings has the grinder mounted on a suitable body, generally indicated by the numeral 2, capable of movement along the surface on which billets or slabs are supported for effecting surfacing operations thereon. Accordingly, the body 2 is provided with wheels 4 mounted on suitable rails 6 along which the machine may be propelled. Any suitable drive means may be used as desired for propelling the machine along the rails 6.

In the embodiment of the invention illustrated particularly in FIGS. 4 and 16, the wheels 4 on one side of the car 2 are mounted on stub shafts and each provided with a sprocket 7 on the stub shaft thereof. A sprocket chain 9 extends over the sprockets 7 and over a sprocket on the drive shaft of a motor 11, which may be a hydraulic motor mounted on the car 2. An adjustable takeup sprocket 13 intermediate the chain 9 may be used for varying the tension of the chain. Upon operation of the motor 11, the chain is driven to operate the traction wheels 4 and propel the body 2 along the tracks 6.

The body 2 is provided with opposite upstanding walls, generally indicated at 8 and 10, shown particularly in FIGS. 2 and 7, respectively, and which provide supports for the operating mechanism of the grinder. Supported upon the

walls

8 and 10 are rails 12 which extend, respectively, throughout the width of the machine and project laterally from the grinding wheel side thereof in cantilever fashion. These projecting portions are adapted to extend toward or to overlap the work support on which the billets and slabs may be mounted for surface operations.

Each of the rails 12 is preferably formed of honeycomb structure which provides the advantages of strength and dissipation of heat during operation of the machine. The honeycomb structure is formed with an upstanding plate 14 forming the inner surface of each rail 12 and having a plate 16 extending edgewise with respect to the plate 14 intermediate the width of the latter.

The plate 16 is braced at opposite sides by plate sections or gussets 18 extending vertically in longitudinally spaced relation from the plate 16 downwardly to a base plate 20 that is seated on the top surface of each of the

walls

8 and 10 and upwardly to a top plate 22. These parts may be welded or otherwise secured rigidly together to form a fabricated honyecomb structure of great strength relative to the weight thereof and with heat dissipating properties. Track members 24 are mounted on the top plates 22 of the rails 12 and extending lengthwise thereof substantially throughout the length of the respective rails.

Mounted on the track rails 12 is a carriage, generally indicated at 26. As shown in FIGS. 3 to 5, the carriage 26 extends in bridging relation between the opposite rails 12 and is mounted thereon by rollers 28 which ride upon the track members 24.

The carriage 26 comprises a bridge member 30 of fabricated structure that extends across from side to side of the machine between the rails 12. At opposite ends of the bridge member 30 and depending therefrom are side support members 32, both of which are located between the spaced rails 12 at the inner faces of the respective rails and adjacent thereto. The rollers 28 are mounted on the outer faces of the side support members 32 adjacent the upper edges of said side support members in riding relation upon the track members 24 of the rails.

The rails 12 are also provided along their inner faces thereof with guiding track members 34, as shown in FIG. 6. Rollers 36, mounted on the side support members 32, bear laterally against the track members 34, thereby guiding the carriage 26 along and between the rails 12 from a. position substantially as shown in dotted lines in FIG. 6 to a position at the opposite ends of the rails fully extended with respect thereto, as shown in FIGS. 1 and 2.

The movement of the carriage 26 is accomplished by a hydraulic power device, generally indicated at 38 in FIG. 6, pivotally connected at one end at 40 with an end portion of the rail 12 and at 42 to one of the side support members 32 of the carriage 12. The power device 38 is shown in the form of a hydraulic cylinder and piston assembly with the piston rod thereof connected at one of the pivot points mentioned and the cylinder connected at the other of the pivot points mentioned, and may be lengthened or shortened to effect the movements of the carriage as described.

Extending lengthwise between the side rails 12 and beneath the carriage 26, is a boom 44. The boom 44 is of fabricated structure for mounting and supporting the operating parts of the machine. It extends beneath the carriage 26 throughout the length of the rails 12 and projects laterally at the grinding wheel end beyond the ends of the rails, as shown in FIGS. 1 and 2.

The boom 44 has opposite side plates 46 in relatively close relation to the inner faces of the side support members 32 between the latter (see FIGS. 3 and 4). These side support plates 46 have mounted thereon a supporting shaft 47 extending continuously from side to side of the boom 44 through a spacer tube 49 which extends in bridging relation between the side plates 46. The opposite ends of the shaft 47 project outwardly from the plates forming supporting trunnions 48 journaled in bearings 50 mounted on the lower portions of the side support members 32 of the carriage. These

parts

48 and 50 thus form a pivotal support for the boom 44 on the carriage 26 and mount the boom for rocking movement on the axis of the pivot 48-50, upwardly and downwardly with respect to the carriage.

The boom 44 supports a drive motor 52 seated on a shelf plate 54 (FIGS. 4 and 5) extending between the side plates 46 of the boom at the rear end of the latter. The boom also supports a gear box or assembly 56 seated upon a shelf plate 58 extending between the side plates 46 of the boom. The motor 52 is connected with the operating parts in the gear box 56 by a drive shaft 60. The output from the gear box 56 is provided by a shaft 62.

The boom 44 is mounted for rocking movement on the pivotal support 485tl by a pair of hydraulic power devices 51 located on opposite sides of the boom. Each of these power devices is shown in the form of a double acting hydraulic cylinder and piston assembly (FIG. 5), pivotally connected at one end, at 53, with the respective side support member 32 and at the other end, at 55, with a bracket support 57 on the outer face of the side support plate 46 of the boom.

By means of the double acting hydraulic power devices 51, the boom 44 can be lifted to raise its operating end portion or lowered to apply downward pressure to the Work, as will be explained more fully hereinafter. The output shaft 62 is provided with a pulley 64 thereon connected by belts 66 with a pulley 68 to effect driving movement of the latter.

One form of spindle assembly is shown in detail in FIG. 8. This assembly includes a driving shaft 70 on one end of which the pulley 68 is mounted. The driving shaft 70 is mounted in bearings 72 in a sleeve 74. Thus, the operation of the driving shaft 70 is effected by the belt drive 66 from the motor 52. A spindle 76 is connected by gearing 78 with an adjacent end of the driving shaft 70. The spindle 76 is counted in a house 80, being journaled in

bearings

82 and 84 therein. The spindle 76, therefore, is driven by the belts 66 from the axis of the output shaft 62.

Mounted on the outer end of the spindle 76 is a driving flange 86 having a cooperating loose flange 88 connected together by pins 90. A grinding wheel is shown at 92 clamped between the

flanges

86 and 88. These parts are held in locked relation upon the grinding wheel 92 by a spacer nut 94 threaded on the projecting portion of the driving flange 86.

A guard 96 extends over the wheel 92 and around the upper portion of the wheel, as illustrated particularly in FIGS. 8, 11 and 13. This guard 96 is provided with a back wall 98 which overlaps a flange 100 at the forward end of the

spindle housing

80 or 77. Ribs 102 formed on the back face of the wall 98 slidably receive the flange 100 therebetween as illustrated in FIGS. 11 and 12. Vertically extending slots 104 are formed in the flange 100 through which mounting screws 106 extend and are threaded into the wall 98 of the guard 96. This forms an adjustable support for the spindle housing and the spindle of the guard 96. as well as providing for vertical adjustment relative thereto to compensate for stretch or length of the belt drive 66.

The guard 96 is supported by a pair of arms 108 connected together in rigid relation by a casting assembly 110. The arms 108 and the assembly 110 are pivotally supported on a shaft 112 mounted in a housing 114 on the forward end of the boom 44.

The guard 96 is provided with a cover plate 116 closing the outer side of the guard. The cover plate 116 is also provided with arms 118 supported upon the shaft 112 on which these arms 118 are journaled. The cover plate 116 is held in close relation over the guard 96 by eyebolts 120 connected at one end with the guard and engaging slotted flanges 122 at the opposite end of the eye-bolts. Thus, the cover 116 can be raised with respect to the guard 96 to allow access to the interior of the guard as, for example, to replace the wheel 92 or for other purposes.

The grinding assembly, including not only the wheel 92, but also the spindle, spindle housing, etc., are capable of adjusting around the axis of the shaft 112. This adjustment is accomplished in the manner illustrated in FIGS. 13 and 14.

According to the embodiment illustrated in the drawings, a double acting hydraulic cylinder 124 is preferably used for this purpose. The hydraulic cylinder 124 is in the form of a piston and cylinder assembly pivotally connected at one end by trunnions 126 with one side of the housing 114 and at 128 with a bearing bracket 130 mounted on the spindle housing 80.

It will be apparent from FIGS. 13 and 14 that the grinding wheel assembly is thus mounted on the outer end of the boom 44 for swinging movement of the Wheel 92 bodily with respect to the Work W about the axis of the shaft 112, which axis is located directly over the wheel in a vertical plane through the diameter of the wheel and normal to the axis of rotation thereof. This provides, in effect, a three-point suspension of the wheel, one of which is a double acting cylinder which provides a very sensitive control eliminating all possible side chatter.

The long wheel radius from the axis of the shaft 112 to the working face of the wheel at the work provides a flat wheel face, wider contact and, of course, a finer finish. The wheel can oscillate about this axis through a substantial arc which may be of the order of 15 (see FIG. 14), and which provides the operator with a sensitive wide sweep and smoother blending of deep defects. The sudden stress on the corners of the griding wheel is considerably relieved by the arc generated from the high pivot point provided by the axis of the shaft 112 over the wheel.

The driving spindle for operating the wheel, being suspended from the guard 96, is also pivoted about the axis of the shaft 112. This axis is located in line with the axis of the output shaft 62 from the gear box. This enables the grinding wheel 92 to swing through an arc of the order of 15 without twisting the V-belt drive.

The grinding wheel is locked in any position of operation with respect to this arc by the double-acting hydraulic cylinder 124 which can be moved in either direction to swing the grinding wheel, as desired, through the arc of movement mentioned. The upward and horizontal forces exerted by the grinding wheel are contained in the pivot shaft 112 directly over the wheel, but in widely spaced bearings 113 where the shaft is mounted in opposite sides of the housing 114.

This machine provides a positive control of the grinding pressure which is obtained by utilizing the two cylinders 51 to handle the heavy mass of the boom assembly and the parts supported thereby. These cylinders may be operated either downward or upward or in both directions by applying variable pressure to both sides of the cylinders.

The differential downward force can be set at the desired working pressure which provides a very rigid grinding head and insures constant contact. The degree of so-called constant pressure to be obtained from such a system is related to the track speed and the topography of the slab or billet surface. By utilizing certain servo controls operated by a signal from the main motor load, constant Wheel pressure can be simulated to some degree.

It will also be apparent that the spindle 76 can be used to mount a centerless grinding wheel, if desired by appropriate and conventional mounting means for securing the wheel to the outer face of a driving flange on the spindle. Such a centerless mounting is provided for in the modification shown in FIG. 10.

FIGS. 10 and 15 also illustrate a 45 angular disposition of the grinding wheel 92 instead of at 90, as illustrated in FIG. 8. Thus, in FIG. 10 a driving shaft 71 has the axis thereof at 135 to the axis of the spindle 73. The driving shaft 71 is located in a position comparable to the location of the driving shaft 70 with respect to the boom 44 and is driven, as described above, from the motor 52 on the boom on the axis of the output shaft 62.

The driving shaft 71 is operatively connected through gearing 75 with the spindle 73, which latter is journaled in a spindle housing 77 corresponding otherwise with the housing 80 in FIG. 8. The outer end of the spindle 73 is provided with a flange 87 to which the grinding wheel 92 is secured in the usual manner of supporting a centerless thereon.

The 45 angular disposition of the grinding wheel 92 can be provided on the machine easily and simply by replacing the spindle shaft assembly, as illustrated in FIG. 8, with the spindle shaft assembly, as illustrated in FIG. 10, and suspending the latter from a guard assembly, generally indicated at 79 in FIG. 15. The guard assembly 79 is journaled on and suspended from the shaft 112, re placing the arms 108 and guard 96 as described above. The wheel swings about the axis of the shaft 112 in the manner described above.

In this form of the invention the cover plate is shown at -81 hinged at 83 on a vertical axis to the guard assembly 79, as illustrated in FIG. 15. At the opposite side of the wheel 92 the cover plate 81 is secured by a tie bolt 83 permitting the opening of the cover plate for access to or replacement of the wheel 92. In all other respects this assembly functions in the manner described herein except that the wheel 92 operates on an axis of 45 relative to the length of the boo-m 44 rather than at with respect thereto.

I have not illustrated in detail the operating systems, either electrical or hydraulic, but suitable conventional controls can be employed under control of an operator. The operator may be located in a cab, generally indicated at 132, mounted on one side of the body 2, as illustrated FIG. 1. The starter switches and controls may be located in a separate box 133 also mounted on the body 2 beside the cab 132.

The grinding wheel 92 is positioned in proper relation to the work W such as billets, or slabs, or the like, by projecting or retracting the boom 44 relative to the body 2. This is accomplished by the hydraulic cylinder 38 (FIG. 6). The boom 44 is also tilted about the axis of the pivot 4850 by manipulation of the hydraulic cylinders 51 to raise or lower the wheel 92 with respect to the surface of the work.

This machine involves few main parts, with the entire Structure of the machine made of heavy fabricated steel' 17,000 surface feet per minute can be attained with this.

machine.

The boom is arranged to afford maximum ease of wheel change, when retracted to the position shown in FIG. 3 and lowered to its bottom position. The

wheel guard

96 or 79 is hinged and its

cover plate

116 or 81 may be readily opened for changing the wheel.

The car 2 is shown as having a storage channel 134 extending along the upstanding wall 8 and may extend from end to end thereof, of a size and dimensions so as to receive a plurality of grinding wheels in upstanding relation in this channel 134. These may be rolled through the channel and out of the open end of the channel adjacent the grinding wheel end of the machine. The lastmentioned end of the channel has a shelf plate 136 extending outwardly therefrom and with an upturned outer end portion, as shown in FIGS. 1, 3 and 6 so as to permit one of the grinding wheels to be rolled out of the channel 134 onto the shelf plate 136 and to be held in such position for mounting on the boom. With the boom 44 lowered to the dotted line position illustrated in FIG. 2 and retracted to the full limit of its retracted position, the grinding wheel will be disposed directly beside the dotted line position of the new wheel supported on the shelf 136. This permits easy assembly of a new wheel on the spindle of the machine without requiring any considerable lifting thereof and holding the wheel during the assembling operation.

In the modification shown in FIGS. 17 to 20, an alter nate mounting arrangement is provided here for a spindle to drive a ring-type grinding wheel which operates on a horizontal grinding plane. This modification also operates by direct connection with the output shaft 62 of the gear box 56.

In this modification the abrasive wheel is indicated at 138 and is of the ring type, supported on a mounting plate 140 to which it is secured by bolts 142. The mounting plate 140 is secured to a spindle 144 extending vertically through an upright housing 146 and journaled in

bearings

148 and 150.

The upper end of the spindle 144 is connected through spiral bevel gears 152 with a transmission shaft 154 that is in direct axial alignment with the output shaft 62 to which it is connected by a coupling 156. This forms a direct drive from the driving means to the grinding wheel spindle on the axis of the output shaft and without requiring the use of a belt drive in the form described above.

The transmission shaft 154 is journaled in a sleeve 158 at one side of the spindle housing 146 and from which a sleeve 160 extends in the opposite direction and is axially aligned therewith, coaxial with the shaft 154.

The

sleeves

158 and 160 are provided with

tapered end bearings

162 and 164, respectively, the former of which has the transmission shaft 154 extending therethrough. These

end bearings

162 and 164 serve to connect the adapter assembly for the head 138 with the outer end of the boom 44 in mountings in opposite sides of the housing 114 secured to the outer end of said boom.

End plates

166 and 168 are secured by bolts 170 to the housing 114 for mounting the adapter assembly in proper relation to the boom 44 and suspending the wheel 138 therefrom in position to operate on a horizontal grinding p ane.

The assembly comprising the housing 146 with the

sleeves

158 and 160 is mounted in the

end plates

166 and 168 so as to swing horizontally relative thereto about refthe axis of the transmission haft 154. This is permitted by the journaled connections between the

end bearing members

162 and 164 and the

end plates

166 and 168. This swinging movement may be used to swing the grinding wheel 138 around the axis of the shaft 154 if it be desired to change the plane of operation of the wheel 138 or to permit it to operate radially against an upright surface.

This horizontal swinging movement of the assembly and wheel may be accomplished in the manner illustrated in FIG. 19. Thus, a double-acting hydraulic cylinder 172 is connected between one side of the spindle housing 146 and the adjacent side of the boxing 1'14. Upon expansion or contraction of the hydraulic cylinder 172, the spindle housing 146, and with it the wheel 138, may swing horizontally about the axis of the transmission shaft 154. The housing assembly moves'ab'out the axis of the bearing

members

162 and 164 in the

end plates

166 and 168.

"This one grinding machine will condition an infinite variety of steels and do it more economically than has been possible with machines available heretofore. The spindle boom 44 can handle billets orslabs up to sixty inches wide. It is of rugged construction and permits grinding with either regular wheels or? arborless wheels and in different angular positions.

By operating the grinding wheel under hydraulic control many variations in controls can be utilized which permits conditioning of any type of steel, carbon, stainless or any of the new exotic hard steels. The grinding wheel can be set to operate at variable conditions and to maintain continuous contact pressure at its set height.

The spindle and guard assembly are pivoted over the center plane ofthe wheel on a shaft in line with the output shaft of the driving gearing. This allows a wide sweep oscillation through an arc which may be of the order of 15, but with no twisting of the V-belt drive or interference with the driving operation.

While the invention has been illustrated and described in one embodiment, it is recognized that variations and changes may be made therein without departing from the invention set forth in the claims.

I claim:

1. A grinding machine comprising means for mounting a grinding wheel for rotary movement about an axis, means supporting said wheel mounting means for bodily movement about a supporting axis spaced from the grinding wheel axis, said wheel axis being substantially perpendicular to said supporting axis, rotary power output shaft means in axial alignment with said supporting axis, and means for transmitting rotary power from said output shaft means to said wheel, said bodily movement of said mounting means being independent of movement of said output shaft means.

2. A grinding machine comprising means for mounting a grinding wheel for rotary movement about an axis, means supporting'said wheel mounting means for bodily movement about a supporting axis spaced from the grinding wheel axis, power means for swinging the wheel mounting means bodily from side to side about said supporting axis, said wheel axis being substantially perpendicular to said supporting axis, rotary power output shaft means in axial alignment with said supporting axis, and means for transmitting rotary power from said output shaft means to said wheel, said bodily movement of said mounting means being independent of movement of said output shaft means.

3. A grinding machine comprising means for mounting a grinding wheel for rotary movement about an axis, means for supporting said wheel mounting means for bodily movement of the wheel about a supporting axis spaced over and perpendicular to the grinding wheel axis, fluid power means connected with the wheel mounting means and extending laterally from the wheel mounting means for oscillating said wheel mounting means about said supporting axis, and means extending-in axial alignment with the supporting axis for driving said wheel.

4. A grinding machine comprising means mounting a grinding wheel for rotary movement about an axis, means for supporting said wheel mounting means for bodily movement of the wheel about a supporting axis spaced over and perpendicular to the grinding wheel axis, power driving means having an output axis extending substantially in longitudinal alignment with the supporting axis, and means operatively connecting the power driving means with the wheel, said connecting means including a wheel pulley shaft mounted on said supporting means for rotation about an axis substantially parallel to said supporting axis, said wheel pulley shaft being in driving connection with said wheel, said power driving means including a pulley mounted for rotation about said output axis, and belt means for transmitting rotary power from said power driving pulley to said wheel pulley shaft.v

5. A grinding machine comprising a boom, a shaft extending lengthwise of the boom and mounted thereon, a guard device, means supported by the guard device for mounting a grinding wheel for rotary movement about an axis, means pivotally suspended from the shaft for mounting the guard device thereon, means extending between said boom and said wheel mounting means for swinging the grinding wheel about said shaft, and means mounted on the boom and extending in axial alignment with the shaft for driving said grinding wheel.

6. A grinding machine comprising a boom, a shaft extending lengthwise of the boom and mounted thereon, a guard device, means supported by the guard device for mounting a grinding wheel for rotary movemen about an axis, means pivotally suspended from the shaft for mounting the guard device thereon with the axis of the grinding wheel below the shaft and at an angle thereto, and means operating on the axis of the shaft and having operative driving connection with the grinding wheel for driving said wheel.

7. A grinding machine, comprising a boom, a housing on one end portion of the boom, a shaft exending lengthwise of the boom and mounted in opposite sides of the housing, a wheel guard, means supported by the wheel guard and fixed relative thereo for mounting a grinding wheel for rotary movement, means pivotally suspended from the shaft for mounting the wheel guard thereon with the grinding wheel directly beneath the shaft, and means operating on the axis of the shaft and having operatively driving connection with the grinding wheel for driving said wheel.

8. A grinding machine, comprising a boom, a housing on one end portion of the boom, a shaft extending lengthwise of the boom and mounted in opposite sides of the housing, a wheel guard, means supported by the wheel guard and fixed relative thereto for mounting a grinding wheel for rotary movement, means pivotally suspended from the shaft for mounting the wheel guard thereon with the grinding wheel directly beneath the shaft, means operating on the axis of the shaft and having operative driving connection with the grinding wheel for driving said wheel, and fluid power means within the housing and operatively connected with the wheel mounting means for moving the grinding wheel laterally on either side of an upright longitudinal plane through the shaft.

9. A grinding machine comprising a body, a pair of rails mounted on said body and extending in parallel relation, a carriage mounted on the rails and extending in bridging relation therebetween for movement lengthwise of the rails, a boom pivotally mounted on said carriage for vertical swinging movement between the rails, means for tilting the boom in a vertical direction relative to the body, said boom including a pivot shaft adjacent one end thereof and extending longitudinally of the boom, means for supporting a roary grinding wheel for rotation about an axis substantially perpendicular to said pivot shaft, said supporting means being mounted on said pivot shaft for swinging movement, rotary power means on said boom, means for transmitting rotary power to said grinding wheel, and power means for swinging said supporting means about said pivot shaft.

10. The grinding machine according to claim 9, including power means between said grinding wheel supporting means and said boom for selectively swinging said grinding wheel about said pivot shaft, said power swinging means including a double acting hydraulic ram journaled at one end on said boom and journaled at the opposite end of said supporting means.

11. A grinding machine comprising frame structure, an elongated boom, means mounting a grinding wheel on one end portion of the boom, means pivotally supporting the boom on the frame structure for vertically swinging movement of the grinding wheel and for bodily movement of the grinding wheel on the boom from a retracted position adjacent the frame structure to a position spaced therefrom, means forming a wheel receptacle in the frame structure having an access opening beside the grinding wheel in said retracted position, and a wheel support at the outer side of said opening for holding a grinding wheel in position for mounting on the boom.

12. A grinding machine comprising supporting means, a grinding wheel, means mounting the grinding wheel on the supporting means for swinging movement about a pivot axis, driving means for the wheel including a drive shaft operating on said pivot axis, means operatively connecting said drive shaft with the wheel for rotating the wheel about an axis perpendicular to said pivot axis, and power means for swinging said grinding wheel about said pivot axis, said power means being connected at one end with said supporting means and at the other end with said grinding wheel, each end of said power means being journaled in bearings for swinging about a bearing axis, both of said bearing axes being in a common plane substantially parallel to and spaced from said pivot axis.

13. A grinding wheel comprising supporting means, a pivot shaft mounted on the supporting means, a grinding Wheel having a central axis of rotation and a peripheral grinding surface and opposite radial faces, said pivot shaft being spaced from said wheel and extending perpendicular to said wheel axis and being intersected by a plane extending parallel to said radial faces, said plane being positioned between said radial faces, a housing having means mounting the grinding wheel and a driving shaft therefor and locating the wheel spaced below the axis of the pivot shaft, means for driving the wheel including a drive shaft in axial alignment with said pivot axis and operatively connected with the driving shaft, and power means operatively connected between said housing and said supporting means and acting on a line at an acute angle to said radial wheel plane for moving the wheel bodily about said pivot axis.

References Cited UNITED STATES PATENTS 3,081,581 3/1963 Hensley 51-99 3,099,902 8/1963 Carlson n 51-99 X 2,073,400 3/ 1937 Cumming 51-126 2,358,880 9/1944 Robinson 51-98 2,763,967 9/ 1956 Hardy 51-98 2,982,056 5/1961 Edgvist 51-99 X 3,052,067 9/1962 Dilks 51-99 X 3,245,176 4/1966 Muehling 51-47 X OTHER REFERENCES 1,125,803 3/1962 Germany.

ROBERT C. RIORDON, Primary Examiner D. G. KELLY, Assistant Examiner US. Cl. X.R. 51-126, 269