US1924588A - Grinding machine - Google Patents

Description

Aug. 29, 1933. T. ADDISON- 1,924,583

GRINDING MACHINE Filed Feb. 29, 1932 7 Sheet-Sheet 1 7&7 429/507 T. ADDISON GRINDING MACHINE 7 Sheets-Sheet 2' Filed Feb. 29, 1932 Aug. 29, 1933. T. ADDISON 1,924,588

GRINDING MACHINE Filed Feb. 29. 1952 7 Sheets-Sheet 3 WW 32 5 A Aug. 29, 1933. T. ADDISON GRINDING MACHINE Filed Feb. 29, 1932 7 Sheets-Sheet 5 Guam;

Aug. 29, 1933. "r. ADDISON GRINDING MACHINE Filed Feb. 29, 1932 7 Sheets-Sheet 6 Aug. 29, 1933. T. ADDISON GRINDING MACHINE Filed Feb. 29, 1932 7 Sheets-Sheet 7 Patented Aug. 29, 1933 UNITED STATES GRINDING MACHINE Tom Addison, Cincinnati, Ohio, assignor to Cincinnati Grinders Incorporated, Cincinnati, Ohio, a corporation of Ohio Application February 29, 1932. Serial No. 595,789

25 Claims. (Cl. 51-48) This invention relates to improvements in machine tools and especially to improvements in centerless grinders.

An object of the invention is the provision of an improved centerless grinder mechanism for semiautomatically, expeditiously producing work pieces of an irregular form.

Another object of the invention is the provision of an improved work supporting mechanism for use with centerless grinders.

A further object of the invention is the provision of an improved spindle centralizing mechanism which co-operates with a feeding device whereby the said structures are synchronized while in operation.

A further object of the invention is the provision of a grinding machine of the nature described in which the axis of thework is at all times maintained parallel with the face of the :0 grinding wheel for insuring the production of cylindrical surfaces.

A still further object of the invention is the provision of improved work loading and ejecting means, feeding mechanism, and improved means establishing a tie or interlock between the said mechanisms.

Other objects and advantages of the present invention should be readily apparent by reference to the following specification considered in i0 conjunction with the accompanying drawings, forming a part thereof, and it is to be understood that any modifications may be made in the exact structural details there shown and described within the scope of the appended claims without exceeding or departing from the spirit of the invention.

In the drawings:

Figure 1 is a front elevation of a centerless grinder embodying the improvements of this invention.

Figure 2 is a top plan view of the device shown in Figure 1.

Figure 3 is a fragmentary elevational sectional view of the parts within the grinder throat as seen particularly from line 3-3 of Figure 1.

Figure 4 is a fragmentary'elevational view of the parts shown in Figure 3 as seen from the left hand end thereof, certain of the details being shown in cross section.

Figure 5 is a fragmentary sectional view taken on line 5-5 of Figure 1.

Figure 6 is a fragmentary sectional view taken on line 66 of Figure 2.

Figure 7 is a top plan view of the structure 55 shown in Figure 6, certain parts being broken away to more clearly illustrate the internal structure. c

Figure 8 is a sectional view taken on line 8-8 of Figure 1.

Figure 9 is a sectional view taken on line 99 of Figure 1.

Figure 10 is a sectional view taken on line 10--10 01 Figure 1.

Figure 11 is an elevational view of certain of the mechanism shown in Figure 9 and as seen particularly from line 11--11 thereon.

Figure 12 is a sectional view taken on line 12-12 of Figure 11.

Figure 13 is a diagrammatic illustration of the several hydraulic and electrical circuits involved in the invention.

Figure 14 is a longitudinal sectional view through the centers of the grinding wheels, regulating wheels and work illustrating a modification of the said parts for operation on a different type of work piece.

Figure 15 is a fragmentary sectional view taken on line 15-15 of Figure 7.

Throughout the several views of the drawings similar reference characters are employed to denote-the same or similar parts.

A machine embodying this invention may comprise a bed or support 15 having rising therefrom at one end thereof a pedestal bearing 16 in which is rotatably mounted a spindle 17. As shown in Figures 1 and 2, the spindle 17 has secured thereto a pair of grinding wheels 18 and 19 being suitably clamped to the spindle and from which spindle the reduced bearing portion 20 projects. This bearing portion 20 is journaled in anti-friction bearings 21 mounted in the upper or journal portion of outboard support 22 suitably secured to a bracket 23 carried by the forward face of the bed 15. The grinding wheels and spindle are adapted to be rotated at a high grinding rate of speed in a clockwise direction as indicated by the arrow associated with the said grinding wheels in Figure 1.

Opposed to the grinding wheels 18 and 19 is a pair of regulating wheels 24 and 25 secured to a spindle 26 rotatably journaled in a housing or head 2'7. The spindle 26 and regulating wheels secured thereto are adapted to be rotated at a relatively slow rate of speed in a clockwise direction as indicated by the arrow associated therewith in Figure 1. Thus the wheels frictionally engage and control the rate of rotation of the work while it is being operated upon by the grinding wheels 18 and 19.

The housing or head 27 is in turn secured to a bracket or upper slide 28, which terminates in a slide 29 hereinafter referred-to as the upper slide. This slide 29 is formed with suitable guideways engaging the guide 30' formed on the upper surface of a lower slide 31 which in turn is provided with a dovetailed guideway 32 engaging the guide 33 projecting upwardly from the oscillatable plate 34, see Figure 5. The upper and lower slides 29 and 31 are adapted to be actuated relative to one another and relative to the oscillatable plate 34 by means of an adjusting screw 35 journaled against relative axial movement in a bearing 36 projecting upwardly from the oscillatable plate 34. The threaded portion of the screw 35 is threadedly engaged with a nut 37 carried by the bracket or housing portion 28 of the slide 29. Secured to the screw 35 beyond the bearing 36 is a pilot or hand wheel 38 whereby the screw may be rotated for eflecting the adjustments above described.

In actual practice the operative faces of the wheels 18, 19, 24 and 25 are spaced from one another as shown in Figure 1 to form a grinding throat therebetween. Secured to the lower slide 31 and sub-tending the grinding throat is a block 39 for a work rest blade 40, which has an operative supporting face 41 inclined in the direction of the operative faces of the regulating wheels 24 and 25. The operative surface 41 of the blade is adapted to properly engage the work while it is being reduced to the desired size. As shown in Figure 3, the work is of such a length that it extends well beyond the grinding throat having the portions 43 and 44 within the throat and adapted to be operated upon by the grinding wheels 18 and 19. The portions 43 and 44 of the work 42 are spaced by an enlarged flange 45 which projects into the area between the said grinding wheels. The work 42 is further provided with a finished portion 46 at its extreme left hand end as seen in Figure 3 which must be supported to prevent the work from tipping about the work rest blade as respects the grinding throat. For this reason the 'block 39 has secured thereto a bracket 47 to which is adjustably secured as by means of the bolt and slot connection 48 an arm 49 having rotatably mounted at its upper end the anti-friction roller 50. Spaced from the roller 50 is a second roller 51 likewise carried by an arm 52 which is adjustable through the bolt and slot connection 53 to a lever 54 which will be de.-

scribed in detail later. From the foregoing it will be noted that there has been provided a centerless grinding machine in which work of a considerable length may be appropriately supported within and without the grinding throat.

The work 42 is adapted to be lowered into the grinding throat and removed therefrom by an hydraulic loading and ejecting mechanism illustrated in Figure 1. As shown therein, this mechanism comprises a supporting bracket 55 mounted in the upper end of the grinding wheel housing 56. The bracket 55 is adapted to be adjusted relative to the housing 56 by means of suitable mechanism controlled by the hand wheel 57. At its forward end the bracket 55 carries a cylinder 58 containing a piston from which projects the piston rod 59. The piston rod is connected to the carrying frame 60 for vertically actuating said frame and carrying the work from the grinding throat to the loading position as shown in Figure 1. This mechanism is adapted to be actuated by hydraulic pressure, which will be described in. detail later.

In order to lower the work into the grinding throat without endangering either the grinding wheels or the flange 45 of the work, the said wheels must be centralized. Also the grinding wheels and their spindle must be axially shifted relative to the work to properly remove the grinding lines from the portions 43 and 44 of the work and to cause engagement between the side faces of the wheels and the shoulders 61 and 62 on the work. For this reason the pedestal bearing 16 has secured to it a housing 63 into which a stub shaft 64 projects. The stub shaft 64 has on one end thereof a flange 65 through which cap screws or the like 66 extend for securing the stub shaft 64 to the grinding wheel spindle 17. This stub shaft rotates with the spindle 17 and in turn drives a worm 67 secured thereto. The worm 67 meshes with a worm wheel 68 secured to or formed integral with a shaft 69 having the eccentric pin 70. The pin 70 is received in a block 71 slidable in the upper channel 72 of a curved or arcuate actuating arm 73. At the other end of the channel 72 the arm 73 has secured thereto a second block 74 in which is journaled one .end of a pin 75 carried by a link 76. This link '76 is in'turn keyed or otherwise secured to a hollow shaft 77 journaled at one end in the housing 63 and at the other end in a cap 78. Secured to the shaft I 77 exteriorly of the cap 78 is a lever 79 having formed in one end thereof a slot 80. Received in the slot- 80 is a pin 81 depending from cross head 82 secured to the piston rod 83. The piston rod 83 is carried by a piston 84 mounted in and reciprocable through 'a cylinder 85 secured to the cover plate 78. The outer end of the piston rod 83 passes through a guide formed in lug 86 integral with the. cylinder 85 and projecting therefrom. Carried by the lug 86 .at a point below the piston rod 83 is an adjustable stop screw 87 threaded through the lug 86 and receiving a lock nut 88 whereby the screw 87 may be locked in adjusted positions. The inner end of 'the screw 87 is positioned in the path of movement of lever 79 and forms a limit stop for limiting the oscillation of the lever 79, and the linear travel of the piston 84. The piston 84 is adapted to be actuated relative to its cylinder by an hydraulic medium under pressure which is introduced to the cylinder at opposite ends thereof by pipes 89 and 90. The flow of the pressure medium through the pipes is adapted to be reversed through a valve which will be I described in detail later.

The arm 73, see Figure 6, is provided with a channel 91 on its under surface in which is received a block 92 for a pin 93 which projects upwardly from an arm 94. The other end of the arm 94 is secured to or formed integral with a sleeve 95 which contains anti-friction thrust bearings 96 in which is journaled the end of the stub shaft 64;

As shown in Figures 6 and 7, the axis of the pin 75 carried by the link '76 and the axis of the pin 93 carried by the arm 94 are superimposed on one another so that any oscillations imparted to the arcuate arm 73 take place about the axes of said pins. Now if the piston 84 is actuated to the right, as seen in Figure 6, it will oscillate the link 76 in a clockwise direction, as seen in Figure 7, thereby placing the axis of the pin 93 in between the axis of the pin 75 and the axis of the shaft 69 which carries the eccentric pin 70 so that the oscillatory movement of the arm 73 about the axis of pin 75 would tend to shift the axis of the pin 93 first to one side of the position illustrated in Figure 6 and then to the other side thereof. This movement of the pin 93 carries with it the arm 94 and consequently the sleeve 95, which being securely connected to the spindle 17 reciprocates the said spindle through the pedestal bearing 16. As the piston 84 is actuated to the left or returned to the position shown in Figure til) 6 the pins 93 and again have their axes placed in co-incidental relation and further reciprocation of the spindle 17 stops. In order to vary the length of stroke of reciprocation of the spindle 17 the position of the stop screw 87 is varied. This will limit the extent to which the lever 79 may be oscillated and consequently the extent to which the link 76 is shifted and thereby controls the distance to which the axis of pins 75 and 93 are separated and consequently the length of stroke of the arcuate arm 73.

In the event it is not desired to use the oscillating mechanism the hollow shaft 77 has extending therefrom a post 97 having at one end the tapered nose 98 and at the other an actuating knob 99. The rod 97 is further provided adjacent the knob 99 with a threaded portion 100 through which it is vertically adjusted as respects its operative position. The lever 79 has formed therein a pocket 101 in which is placed a coiled spring 102 surrounding the reduced portion 103 of a pin 104 which has its enlarged head portion guided by the pocket 101 and abutting the under surface of the actuating knob 99; The sliding sleeve 95 has formed therein a tapered socket 105 receiving the tapered nose 98 of the rod 97. This mechanism operates as follows. The piston 84 is actuated to its extreme left hand position, as shown in Figure 6, thereby aligning the socket 105 with the nose 98 whereupon the rod 97 is actuated downwardly to insert its nose within the socket and at the same time shift the pin 104 through pocket 101 causing the reduced portion 103 of the pin to enter a counter-bore in the cover plate 78 and thereby prevent any oscillatory movements of the lever 79 relative to the housing cap 78.

After the work piece has been mounted on the work rest blade the oscillatable plate and parts carried thereby are actuated about the axis of the plate pivot toward the grinding wheel to feed the work into the wheel. For this purpose, the bed has secured thereto a bed plate 106 which has rising therefrom bearing bosses 107 in which the pivot pins 108 are journaled. The pins 108 are secured in lugs or ears 109 depending from the under surface of the oscillatable plate 34. A ball socket member 110 is secured to the forward face of the plate 34 and has mounted therein the ball end 111 of an adjusting screw 112 which is threaded into the nut member 113 secured to the forward face of the bed 15. The screw 112 is formed on its outer end with a wrench portion 114 whereby the screw is rotated. This mechanism is provided so that the oscillatable plate 34 may be laterally adjusted relative to the bed plate 106 to align the regulating wheels with the grinding wheels and to establish thedesired or proper relation between the said wheels.

In order to effect this oscillation of the plate it is provided in its rear end with a cam follower 115 engaging the outer cam face of a rotatable cam 116, see Figures 9 and 10. As shown in Figure 10, the cam 116 is keyed or otherwise secured to a cam shaft 117 journaled in suitable antifriction bearings carried by a housing 118 secured to the rear end of the bed 15. Also journaled in the housing 118 below the cam shaft 117 is a driving shaft 119 having secured thereto a pinion 120 geared in any desirable manner, preferably by a sprocket chain to a prime mover or motor 121 secured to the rearmost face of the housing 118. This drive shaft 119 has secured to its one end a sprocket chainpinion 122 ge'ared as by gear chain 123 to a gear 124 on the end of a worm shaft 125, see Figure 1. The worm shaft 125 is also journaled in the housing 118 and has formed integral therewith or secured thereto a 'worm 126 meshing with a worm wheel 127 on one end of a longitudinal worm shaft 128. 'This shaft 128 is also provided with a worm 129 which in turn drives a worm wheel 130 keyed or otherwise secured to the cam shaft 117. From this it will and surrounding the valve stem 137 is an expansion coiled. spring 138 which abuts on one end with a valve casing 139 and on the other end with a shoulder 140 formed on the stem 137, the sleeve 136 being also adapted to engage the valve stem shoulder 140 for shifting the valve stem against the yielding resistance of the spring 138 when the roller 135 engages with the lug 134. The valve stem 137 is secured to a spool type valve 141 mounted within the valve casing 131 and being provided with a cannelure 142 for connecting the hydraulic medium with either of 3 the spindle reciprocatory conduits 89 and 90. The hydraulic medium is conveyed to the valve casing 139 by a pipe or conduit 143. When the pressure is passing into and through either of the conduits 89 or 90 the remaining conduit is an exhaust line for conveying the hydraulic medium on the other side of the piston to the valve casing where it is connected by the valve with the exhaust pipe 144.

From this it will be seen that the valve 141 is 1'" actuated to stop further reciprocation of the spindle when the cam is in a given position, namely for retracting the regulating wheels from the grinding wheels while permitting a replacement of the work within the grinding throat and at the same time will permit a reciprocation of the spindle during the actual grinding operation.

The cam 116 is provided on its other face with a cam track 145 which has formed therein a notch or depression 146. The cam track 145 is adapted to be engaged by means of a roller 147 carried in the forward end of a shiftable rack 148 slidable through a bearing formed in the housing 118. The rack 148 has projecting from it the clevice 149 through which is formed a slot 150 receiving a pin 151 projecting laterally from a pivoted arm 152. This arm 152 is pivoted at 153 to the housing 118 and is pivoted at its upper end at 154 to one end of a link 155 which extends transversely along the rear of the bed 15. The

outer or forward end of the link 155 is pivoted at 156 to an arm 157 carried by a rock shaft 158 lying along the front wall of the bed 15. The

outer end of the shaft 158 is journaled in a housing or bearing 159 secured to the forward face through the valve casing 171.

of the bed 15. The rock shaft 158 has secured to it interiorly of the housing 159 a bevel pinion 160 meshing with a complementary bevel pinion 161 keyed or otherwise secured to stub shaft 162 likewise journaled in the housing or bearing 159. The hand lever 163 is secured to the stub shaft 162 exteriorly of the housing 159 whereby the said shaft is oscillated for correspondingly actuating the pinion 161.

The rack 148 has its teeth meshing with a rack pinion "164 secured to a shaft 165 journaled in the housing 118. This shaft also carries a gear 166. meshing with'a complementary gear .167 secured to a valve actuating shaft 168.- The rack pinion 169 is also carried by the shaft168 meshing with suitable rack teeth formed onthe adjacent side of a valve stem 170. As will be noted in Figure 12, the valve stem 170 is vertically disposed for movement in a vertical direction The valve casing 171 has secured therein the sleeve 172 through which the spool type valve 173 integral. with the stem 170 is adapted to be actuated upon movement of the rack pinion 169. This valve 173 is provided with cannelures 174 and 175 for respectively alternately comiecting the hydraulic medium under pressure from the conduit or pipe 176 with the conduits 177 and 178 which respectively terminate at the lower and upper ends of the cylinder 58. The hydraulic medium on the other side of the piston within the cylinder 58 is conveyedto the valve 173 through the pipe not being used for the pressure, where it is connected with the port 179 controlled at opposite ends by adjustable needle valves 180 and 181 terminating in the exhaust line or pipe 182. Also secured to the shaft 165 is a plate-like lever 183 to the outer end of which is secured one end of a spring 184 which has its other end' secured or anchored at 185 to a bracket 186 carried by the housing 118. The spring 184 tends to rotate the shaft 165 in a counterclockwise direction, as seen in Figure 9, against the rotation thereof through the actuation of the rack- 148. I

Carried by the bed 15 adjacent the limit switch 133 is a second limit switch 187 adapted to be closed by means of a'cam 188 carried by and movable with the link 155; The bracket or housing has mounted thereon an electrical limit switch 189 adapted to be closed by switch actuator 190 secured to and movable with the frame 60. The

actuator 190 closes the switch 189 when the work is in the desired position on the work rest blade.

The limit switches 133, 187 and 189 are so inter-connected as to start the rotation of the motor 121 only after the work is properly posi-. tioned within the grinding throat and to stop said rotation after the work has been reduced to the desired size and the regulating wheels retracted to the limit of their retractable move-- ment. As shown diagrammatically in Figure 13, the main electrical leads 191 and 192 have each extending therefrom an electric wire or line 193 and 194, the former terminating in one pole of the motor 121 and the latter terminating in the limit switch 189. An electric wire or lead. 196 extends from the switch 189 to the second limit switch 187 of Figures 9 and 10. An electric wire or lead 198 extends from the switch 187 to a magnetic switch 133. From this switch 133 a further electric wire or lead 200 extends terminating in the other pole of the motor 121. 4 In addition, the switch 133 includes an electrical solenoid 201 which draws the switch blade 133 to its seat when the electric circuit is complete.

From the foregoing it will be noted that the electricmotor 121 is not rotated until the work is properly placed on the work rest blade at which time the switch 189 is closed for completing the electrical circuit since the switch 187 was closed at the time of shifting the valve for eifecting the descent of the loading mechanism.

Shown also in Figure 13, is the hydraulic circuit which includes a tank or sump 202 containing the hydraulic medium, preferably oil, which is drawn therefrom through the pipe or conduit 203 by the pump 204 and discharged under pressure into pressure line 205. This pressure line 205 has extending from it the branch pressure line 176 which terminates in the valve casing 171 where it is directed to either of the conduits 177 or 178. The return medium from the other of these conduits is connected with the discharge conduit 182 which is in turn connected with the.

' which terminates at the valve casing 139. The

hydraulic medium from the casing 139 passes through the conduit 144 to. the branch main return conduit 208 terminating in the sump or tank 202.

The oscillation of the oscillatable plate 34 about the axis of the pins 108 feeds the work into the grinding wheel thereby causing the portions 43 and 44 to be reduced in diameter. The reduction of these portions of the work causes the axis thereof to descend to fall further into the grinding throat thereby tending to dispose the axis of the work at an angle to the horizontal plane through the grinding and regulating wheels with the outboard supporting rollers as the point of pivotance and would result in the production of. tapered work pieces. In order to overcome this condition, the arm 54 which carries the outboard supporting roller 51 is carried by a shaft 209 secured in bearings 210 and 211 carried by the inner surface of the front wall of the, bed. The arm 541s provided with a sleeve-like bearing 212 into which is pressed a sleeve 213 surrounding the shaft 209. The arm is further provided with 9. lug or ear 214 extending outwardly therefrom in which is adjustably mounted a stop screw 215 adapted to abut a cam face 216 of a lug 217. The arm 54 is further provided with a pin 218 to which is anchored oneend of a'spring 219, the other end of which is anchored to a similar pin 220 projecting from a bracket 221 that is in turn secured to for movement with the oscillatable plate 34. This spring is employed for maintaining contact between the adjustable stop screw or cam follower 215-and the cam face 216. In order to prevent any lateral movement of the arm it is provided near its upper end with a slot 222 receiving a guide pin 223 extending laterally from the bracket 47 of outboard support roller 50.

As the plate 34 is oscillated to feed the work into the grinding wheel the roller 50 moves therewith while the roller 51 is also moved but in a rectilinear direction and at a slower rate than the movement of roller 50 to thereby gradually open up the distance between the said rollers and permit the dropping of the work down between them as the diameter of the portions 43 and 44 is being reduced. This opening up of the rollers 50 and 51 is controlled by the cam 216 and takes place at the same rate as the work is reduced to thereby effect the shifting of the axis of the work into the grinding throat while held parallel construction work pieces of a length considerably greaterthan the width of grinding face of the grinding wheel and the work rest blade can .be accurately produced without danger of the work having a final form of conical contour and for maintaining line contact'between the work and work rest blade.

The modified structure disclosed in Figure 14 includes four grinding wheels 224a, 224b, 2240,

- and 224d and but three regulating wheels 225a,

225b, and 2250 being respectively opposed to the grinding wheels 224b, 2240, and 224d. The work piece illustrated in Figure 14 is a cam shaft as used in connection with internal combustion engines adapted to have the main bearings ground between the grinding and regulating wheels and the timing gear bearing 227 ground by the wheel 224a. By this construction an overhanging piece of the work may be ground while the work is being rotated between another grinding wheel and its opposed regulating wheel and all of the bearings ground concentric to one another.

The complete operation of the machine is as follows: Awork piece is mounted on the frame 60 and the handle 163 actuated in a counterclockwise direction as seen in Figure 1. This movement of the lever 163 rocks the shaft 158 which through the arm 157 and link 155 actuates the rack 147 to the left, as seen in Figure 9, thereby withdrawing the roller 14'] carriedby the rack from the notch or depression 146 in the cam 116. The movement of the rack 148 rotates the shaft 165 for rotating the pinion 169 and elevating the valve 173. The vertical shifting of the valve 173 connects the hydraulic medium in the line 176 with the conduit 178 for directing the same to the upper end of the cylinder 58 and actuating fportions of the grinding and regulating wheels the piston therein downwardly to lower the work carried by the frame 60 onto the work rest blade. The shifting of the link 155 also closed the limit switch 187 for partially completing the electrical circuit including the infeed motor 121. The lever 163 is held in its forward position until the work is deposited on the work rest blade whereupon the switch 189 is closed for completing the electrical circuit to the motor 121 thereby effecting the energization of the said motor and. the rotation of the cam 116. As soon as the cam 116 is rotated and the notch or recess 146 is actuated out of line with the roller 147, the lever 163 may be released because the roller is then riding on the cam track 145, which holds the rack 148 in its outward position.

The rotation of the cam 116 causes the cam lug 134 on its one side to release the roller 135 thereby permitting the spring 138 to expand for shifting the valve 141 and permitting the hydraulic medium in the conduit 143 to be conveyed by means of pipe 89 to the cylinder shifting the piston 84 therein for oscillating the, arm 76 whereupon the reciprocation of the spindle 64 takes place. At the same time the oscillatable plate 34 is being actuated to feed the work into the grinding wheel and effect the desired stockremoval therefrom. The cam 116 is so ,constructed that the slides and work are first actuated at a rapid rate toward the grinding wheel until contact is had between the work and wheels whereupon the rate of movement is' reduced to the desired proper feed of a work piece' against the grinding wheel. Near the end of the rotation of the cam a concentric portion comes into play for cleaning up'oi the work and allowing the wheel and work to spark out.

After the work has been properly cleaned up, the cam 131 actuates the limit switch 133 for breaking the electrical circuit to the motor'1'21. This breaking of the circuit de-energizes the solenoid 201 whereupon the switch 187 is broken thereby cutting off the electrical current from the motor and causing it to stop. The coasting of the motor after the current has been cut off therefrom causes the cam '131 to pass the limit switch 138 allowing it to close and at the same time aligns the notch or recess with the roller 147 so that the spring 184 previously compressed may rotate the shaft 165 causing the valve 170 to be lowered to the position shown in Figure 12 for connecting the pressure in the line 176 with the conduit 177 and directing the medium to the lower end of the cylinder 58 causing elevation of the frame 60 carrying with it the finished .work piece. Just prior to the completion of the revolution of the cam 116 the cam lug 134 engages the roller 135 for shifting the valve 141 to the right, as seen in Figure 10, thereby oscillating the arm 76 to its normal position and stopping reciprocation of the grinding wheel spindles with the grinding wheels centralized as respects the work carrying frame 60. The parts are now in their normal positions preparatory to a re-initiation of the cycle by actuating the lever 163 in a counterclockwise direction as above described.

What is claimed is:

1. In a centerless grinder for grinding spaced portions of a work piece having said portions separated by an enlarged flange, the combination of a plurality of grinding wheels, a regulating wheel opposed to each grinding wheel, a work rest blade disposed in the space between the opposed and adapted to support the work with the flange thereof disposed between adjacent grinding wheels, and power operated means for axially adjusting the position of the grinding wheels to align the space therebetween with the flange of the work to facilitate loading and unloading of the work relative to the work rest blade.

2. In a centerless grinder for grinding spaced portions of a work piece having said portions separated by an enlarged flange, the combination of a plurality of grinding wheels, a regulating wheel opposed to each grinding wheel, a work rest blade disposed in the space between the opposed portions of the grinding and regulating wheels and adapted to support the work with the flange thereof disposed between adjacent grinding wheels, power actuated means for axially adjusting the position of the grinding wheels to align the space therebetween with the flange of the work to facilitate loading and unloading of the work relative to the work rest blade, and power operated means for placing the work on the work rest blade and removing same therefrom.

3. In a grinding machine of the class described for grinding portions of a work piece on opposite sides of an enlarged flange. the combination of a grinding wheel for each portion of the work, a work support adjacent the grinding wheels for supporting a work piece with the flange disposed within the space between the the actual grinding operation but stopping said' wheel reciprocation upon conclusion of the grinding operation and disposing said wheels with the space therebetween centrally of the flange. 4

4. In a grinding machine of the class described for grinding portions of a work piece on opposite sides of an enlarged flange, the combination of a grinding wheel for each portion of the work, a work support adjacent the grinding wheels for supporting a work piece with the flange disposed within the space between the grinding wheels, means for reciprocating the grinding wheels relative to the work during the actual grinding operation but stopping said wheel reciprocation upon conclusion of the grinding operation and disposing said wheels with the space therebetween centrally of the flange, said means comprising a spindle for the wheels, an axially shiftable member operatively coupled with the.

spindle, means driven from the spindle for reciprocating the member, a connection between the reciprocating member and the reciprocating means variable from zero to maximum whereby the reciprocations of the member and spindle may be adjusted, and means for operating said adjustable means for eflfecting the reciprocation of the spindle during the grinding operation but holding same inoperative at other times.

5. In a grinding machine of the class described for grinding portions of a work piece on opposite sides of an enlarged flange, the combination of a grinding wheel for each portion of the work, a work support adjacent the grinding wheels for supporting a work piece with the flange disposed withinwthe space between the grinding wheels, means for reciprocating the grinding wheels relative to the work during the actual grinding operation but stopping said wheel reciprocation upon conclusion of the grinding operation and disposing said wheels with the space therebetween centrally of the flange, said means comprising a spindle for the wheels, an axially shiftable member operatively coupled with the spindle, means driven from the spindle for reciprocating the member, a connection between the reciprocating member and the reciprocating means variable from zero to maximum whereby the reciprocations of the member and spindle may be adjusted, and means for operating said adjustable means for effecting the reciprocation of the spindle during the grinding operation but holding same inoperative at other times, including an hydraulically actuated piston, and an adjustable stop arying the limit of movement of the piston for thereby varying the length of stroke of the spindle.

6. In a grinding machine of the class described the combination of a bed, a grinding wheel spindle rotatably mounted on the bed for axial movement relative thereto, a grinding wheel secured to the spindle, a work support adjacent the operative face of the grinding wheel, means for feeding the work supported by the support into the grinding wheel, and means energized upon actuation of the feeding means for effecting reciprocation of the spindle.

7. In a centerless grinder the combination of a bed, opposed grinding and regulating wheels carried thereby and forming a grinding throat therebetween, a work rest blade disposed within the grinding throat, one of said wheels being mounted for axial reciprocation relative to the work rest blade to break up grinding lines on the work, one of said wheels being movable toward the other for feeding the work into the grinding throat, and a common member for effecting the relative movement of said wheel toward the other and for axially reciprocating the said wheel relative to the blade.

8. In a centerless grinder the combination of a bed, opposed grinding and regulating wheels carried thereby and forming a grinding throat therebetween, a work rest blade disposed within the grinding throat, one of said wheels being mounted for axial reciprocation relative to the work rest blade to break up grinding lines on the work, one of said wheels being movabletoward the other for feeding the workinto the grinding throat, and a common member for effecting the relative movement of said wheel toward the other and for axially reciprocating the said wheel relative to the blade, said member taking the form of a cam for actuating a feed ing mechanism and for shifting a valve for energizing the reciprocating mechanism.

9. In a centerless grinder of the class described the combination of a bed supporting a pair of opposed grinding and regulating wheels forming a grinding throat therebetween, a work rest blade disposed within the grinding throat, a spindle supporting the grinding wheel for axial reciprocation relative to the work, means for supporting the regulating wheel for oscillatory move-' ment toward and from the grinding wheel to feed the work controlled thereby into the grinding wheel, means operable by the work feeding means for efiecting the reciprocation of the grinding wheel and its spindle, the work rest blade having an outboard support for supporting an overhanging portion of the Work on the blade, and means for varying the supporting action of the outboard support as the regulating wheel is fed.

for grinding work pieces having an overall length 11 greater than the portion to be ground thereon, the combination of opposed grinding and regulating wheels forming a grinding throat between them, a work rest blade within the grinding throat peripherally engaging the portion of the work in contact with the grinding and regulating wheels, an outboard support for engaging and supporting the portion of the work extending beyond the grinding throat, means for actuating one of the wheels toward the other to reduce the portion of the work to be operated upon thereby changing the position of its axis as respects the work rest blade, and means simultaneously operable for varying the supporting action of the outboard support to vary the position of the axis of said overhanging portion of the work.

11. In a grinding machine of the class described the combination of a work rest blade peripherally supporting a work piece, a grinding wheel on one side of said blade operable at a high grinding rate of speed for engaging the portion of the work being operated upon, a regulating wheel on the other side of said blade and opposed to the grinding wheel, means remote from the portion of the work being operated upon for supporting the work at a point remote from the grinding and regulating wheels, means for actuating one of said wheels toward the other to reduce the Work and thereby alter the position of its axis as respects the work rest blade, and means simultaneously varying the position of the axis of the work remote from the grinding point to maintain the axis thereof parallel with the axis of the portion being ground.

12. In a grinding machine of the class described the combination of a work rest blade peripherally supporting a work piece, a grinding wheel on one side of said blade operable at a high grinding rate of speed for engaging the portion of the work to be operated upon, a regulating wheel on the other side of said blade and opposed to the grinding wheel,-means remote from the portion of the work being operated upon for supporting the work at a point remote from the grinding and regulatingwheels, means for actuating one of said wheels toward the other to reduce the work and thereby alter the position of its axis as respects the work rest blade, and means simultaneously varying the position of the axis of the work remote from the grinding point to maintain the axis thereof parallel with the axis of the portion being ground, said remote supporting means comprising a pair of rollers positioned as respects one another to co-operate with the work rest blade for holding the axis of the work parallel and adapted to be adjusted relative to one another to lower the axis of the work supported thereby as the axis of the work is lowered upon being reduced.

13. In a grinding machine of the class described, the combination of a pair of opposed grinding and regulating wheels forming a grinding throat, a work rest blade withinsaid grinding throat for peripherally supporting the work, an additional work support exterior of the grinding throat for supporting an overhanging portion of the work and maintaining the axis of the work on the blade with the overhanging portion parallel, means for effecting a relative feed between the work and grinding wheel thereby reducing the work and varying the position of the axis of the portion being ground, means for varying the supporting action of the outboard work support for maintaining the axis of the overhanging portion of the work parallel with the portion being reduced during the grinding operation, and; hydraulically actuated means for depositing the" work on the work rest blade and outboard support.

14. In a grinding machine of the class described the combination of a pair of opposed grinding and regulating wheels forming a grinding throat, a work rest blade within said grinding throat for peripherally supporting the work, an additional work support exterior of the grinding throat for supporting an overhanging portion of the work and maintaining the axis of the work.

on the blade with the overhanging portion parallel, means for effecting a relative feed between the work and grinding wheel thereby reducing the work and varying the position of the axis. of

the portion being ground, means for varying the supporting action of the outboard work support for maintaining the axis of the overhanging portion of the work parallel with the portion being reduced during the grinding operation, hydraulically actuated means for depositing the work on the work rest blade and outboard support, an hydraulic medium for actuating the work loading mechanism, a valve controlling the flow of the medium, and means connecting the feeding mechanism and valve for operating the said mechanisms in timed sequential order.

15. In a grinding machine of the class described the combination of a grinding wheel, a work support adjacent the grinding wheel for supporting the work while being operated upon, an additional outboard work support for supporting an overhanging portion of the work remote from the grinding wheel, said work support and outboard work support disposing the axis .of the work in a plane definitely related to the operative face of the grinding wheel, means for feeding the work into the grinding wheel to effect a stock removal therefrom and thereby change the relation of the plane of the axis of the work to the operative face of the wheel, means for adjusting the outboard work support to rectify the relation of the plane of the axis of the work as respects the operative face of the wheel, a cam associated with the feeding mechanism, means for rotating the cam through one revolution and stop, an hydraulic mechanism for placing a work piece on the supports and removing it therefrom, a valve controlling the hydraulic loading and ejecting mechanism, and an operative connection between the loading and ejecting mechanism and the cam actuating mechanism whereby the work is placed on the supports prior to the actuation of the feed and ejected at the conclusion of the feeding operation.

16. In a grinding machine of the class described, the combination of a grinding wheel, a worksupport adjacent the grinding wheel for supporting the work while being operated upon, an additional outboard work support for supporting an overhanging portion of the work remote from the grinding wheel, said work support and outboard work support disposing the axis of the work in a plane definitely related to the operative face of the grinding wheel, means for feeding the work into the grinding wheel to effect a stock removal therefrom and thereby change the relation of the plane of the axis of the work to the operative face of the wheel, means for ad justing the outboard work support to rectify the relation of the plane of the axis of the work as respects the operative face of the wheel, a cam the cam actuating mechanism whereby the work is placed on the supports prior to the actuation of the feed and ejected at the conclusion of the feeding operation, hydraulic means for reciprocating the grinding wheel during the grinding operation, and means associated with the feed cam for rendering the reciprocating means inoperative at the conclusion of the grinding operation.

17. In a centerless grinder the combination of a bed, a pair of opposed grinding and regulating wheels mounted thereon, supporting means for pivotally securing one of said wheels to the bed for oscillation toward and from the other, a work support between the wheels, additional supporting I means in line with the work support for supporting an overhanging portion of the work, means for oscillating said pivotally supported wheel to feed the work into the grinding wheel thereby reducing its size, and means simultaneously operable with the oscillation of said wheel for varying the action of the outboard support to maintain the axis of the work at all times parallel with the face of the grinding wheel.

18. In a centerless grinder of the class described for grinding portions of a work piece remote from one end thereof the combination of a pair of opposed grinding and regulating wheels forming a grinding throat in which the portion of the work to be ground is disposed, a work rest blade subtending the grinding throat and peripherally sup- 'porting' the portion of the work being ground,

wheel, and additional means operable simultaneouslywith the oscillation of said wheel for varying the supporting efiect of the work support remote from the grinding throat.

19. In a centerless grinder of the class described for grinding portions of a work piece remote from one end thereof the combination of a pair of opposed grinding and regulating wheels forming a grinding .throat in which the portion of the work to be ground is disposed, a work rest blade" subtending the grinding throat and peripherally supporting the portion of the work being ground, means exterior of the grinding throat for supporting the work at a point remote from the work rest blade, means pivotally mounting one of said wheels for oscillation toward and from the other wheel, and additional means operable simultaneously with the oscillation of said wheel for varying the supporting effect of the work support remote from the grinding throat, said remote supporting means including a pair of rollers which are separated to permit the lowering of the work at the same rate that the diameter thereof is reduced.

20. In a centerless grinder of the class described the combination of a bed, a pair of opposed grinding and regulating wheels mounted thereon and forming a grinding throat therebetween, a work rest blade sub-tending the grinding throat for peripherally supporting the work within the grinding throat, means mounting one of said wheels and the work rest blade for oscillation toward and from the other wheel to effect a stock removal from the work, an outboard support for supporting the work at a point remote from the grinding throat and comprising a pair of supporting rollers, said rollers co-operating with the work rest blade to support the work piece with its axis parallel with the face of the grinding wheel, means for effecting the oscillation of the work rest blade and said one wheel, and means simultaneously separating the supporting rollers to permit the portion of the work supported thereby to be lowered at the same rate as the stock is removed from the work and maintain the axis of said work parallel with the wheel.

21. In a centerless grinder of the class described the combination of a bed, a pair of opposed grinding and regulating wheels mounted thereon and forming a grinding throat therebetween, a work rest blade sub-tending the grinding throat for peripherally supporting the work within the grinding throat, means mounting one of said wheels and the work rest blade for oscillation toward and from the other wheel to effect a stock removal from the work, an outboard support for supporting the work at a point remote from the grinding throat and comprising a pair of supporting rollers, said rollers co-operating with the work rest blade to support the work piece with its axis parallel with the face of the grinding wheel, means for efiecting the oscillation of the work rest blade and said one wheel, and means simultaneously separating the supporting rollers to permit the portion of the work supported thereby to be, lowered at the same .rate as the stock is removed from the work and maintain'the axis of the work parallel with the wheel, said means comprising a cam, a separate support for each-roller, and a connection between the cam and one of said roller supports for shifting it during the oscillation of and work rest blade.

22. An outboard support for use with centerless grinders for maintaining the axis of the work throughout its length parallel with the face of the grinding wheel comprising a pair of supporting rollers, one of said rollers being supported for movement with one of the wheels, a support for the second roller, and means for shifting said second roller and its support at a rate less than the rate of movement of the roller associated with the wheel whereby said rollers are separated at the rate of stock removal from the work.

23. In a centerless grinder of the class described the combination of a bed, a pair of opposed grinding and regulating wheels mounted thereon and forming a grinding throat therebetween, a work rest blade within the grinding throat peripherally supporting the work during the grinding operation, power actuated means for placing the work on the blade and removing same therefrom, power actuated means for feeding the wheels relative to one another to feed the work into the grinding wheel, and means energizing the feed power means operable by the power loading and ejecting means after the work is placed on the work rest blade. .7

24. In a centerless grinder of the class described the combination of a bed, a pair of opposed grinding and regulating wheels mounted thereon and forming a grinding throat therebetween, a work rest blade within the grinding throat peripherally supporting the work during the grinding operation, power actuated means the wheel for placing the work on the blade and removing same therefrom, power actuated means for feeding the wheels relative to one another to feed the work into the grinding wheel, means energizing the feed power means operable by the power loading and ejecting means after the work is placed on the work rest blade, and means for stopping said feeding means at the conclusion of a definite cycle of operation.

25. In a centerless grinder of the class described the combination of a bed, a pair of opposed grinding and regulating wheels mounted thereon and forming a grinding throat therebetween, a work rest blade within the grinding throat peripherally supporting the work during the grinding operation, power actuated means for placing the work on the blade and removing same therefrom, power actuated means for feeding the wheels relative to one another to feed the work into the grinding wheel, means energizing the feed power means operable by the power loading and ejecting means after the work is placed on the work rest blade, means for stopping said feeding means at the conclusion of

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