US2601277A - Road machine - Google Patents

Description

G. P. GREEN June 24, 1952 ROAD MACHINE 6 Sheets-Sheet 1 Filed March 5, 1945 INVENTOR ATTORN EY G. P. GREEN ROAD MACHINE June 24, 1952 Filed March 3, 1945 6 Sheets-Sheet 3 L MM WIIIIHIIIIJNW I87 F/lg. I0 /8 /52 /85 MQM INVENTOR ATTORNEY G. P. GREEN ROAD MACHINE 6 Sheets-Sheet 4 Filed March 5, 1945 Fly.

Z+ 1 2 M "W4 3 q k 7 a 4 u a m 5 z m a m 6 4 mm a 0 a e a as n a w a aw w 4 7 o 2 u 3 W a 6 aw 2, 2 2 2 M 2 2 7 9 l 6 7 2 6 2 6m 22 MM 1 2 9 0 w 6 2 "1 IL .l 30/ INVENTOR A'ITORNEY G. P. GREEN ROAD MACHINE June 24, 1952 6 Sheets-Sheet 5 Filed March 5, 1945 INVE'NTOR III;

lllllllllfll rlllfl ATTORNEY G. P. GREEN June 24, 1952 ROAD MACHINE Filed March 3, 1945 6 Sheets-Sheet 6 0 w 2 m a l INVENTOR ATTORNEY Patented June 24, 1952 UNITED STATES star FFICE 14 Claims.

This invention relates to an improvement in road machines, and the principal object is to provide a machine of this class which may be advantageously applied in construction operations relative to road subgrades, base courses, surface courses and other work of similar nature such as tel-racing, leveling, compacting and miscellaneous construction of this nature. These and other objects are hereinafter more fully described, illustrated in the drawings, and specifically pointed out in the appended claims; it being understood that construction deviations may be made so long as they fall within the scope of the claims.

Figure l is an elevation of the right side of the machine.

Fig. 2 is a rear elevation of the left end of the machine (Fig. 1).

Fig. 3 is a rear elevation of the center portion of the machine.

Fig. 4 is an enlarged plan view of the portion of the machine shown in Fig. 2..

5 is a plan view of the portion of the machine shown in Fig. 3.

Fig.6 is a sectional elevation of a front portion of the carriage assembly.

Fig. 7 is a transverse section along lines i= and l- -T' of Fig. 6.

Fig. 8 is a sectional view of a mixer claw along line 8 8, Fi '7.

Fig. 9 is a section through the mixer shaft along line 99, Fig. 6.

Fig. 10 is a section through the mixer shaft along line 10-40,, Fig. 6.

Fig. 11 is an elevation, partly in section, through the rear part of the carriage assembly.

Fig. 12 is an elevation, partly in section, taken transversely of the portion shown in Fig. 11 along line 12-12 .(Fig. 11).

Fig. 13 is a section of a portion of the rail rollers of carriage Support member 31 of Fig. 11.

Fig. 14 is a plan view of the scarifier along line I l-+14, Fig. 6.

Fig. 15 is an elevation, partly in section, through blade assembly taken along line I S-15, Fig. 6.

Fig. 16 is a section of the reel member, shown in Fig. 1.

Fig. 17 is a sectional elevation through the transmission taken along line 11-41, Fig. 5.

Fig. 18 is a section through the shift control, along line It-i8, Fig. 17.

Fig.19 is an elevational view of an hydraulic control for the steering arrangement.

FiggZO is a vertical section along line 20-40, Fig. 19.

Fig. 21 is a front elevation, partly in section, of a portion at the front wheel of the machine.

Fig. 22 is a section through an hydraulic grade control mechanism, along line 'Z2-22, Fig. 21.

Fig. 23 is an elevational view of an hydraulic grade'control mechanism, along line 23-23, Fig. 22; and

Fig. 24 is an elevational view, partly in section, of a clutch for driving and steering the machine, shown in Fig. 2.

Similar numerals refer to similar parts throughout the several views.

In general, the machine comprises a horizontal frame provided with supporting wheels at each end, to travel along a strip of Work, with the roadworking structure spanned transversely thereto; and a carriage frame roller mounted on the structure and supporting certain members such as a mixer, blades and rollers adapted to perform a sequence of road construction operations as the carriage is propelled back and forth across the work. The travel rate of the entire machine along the strip of work is coordinated with the carriage travel, so that the operations lap to produce a uniformly worked section.

The structure which spans the work comprises two I beams, l and 2, Figs. 1 to 5, which are hinged at the middle on hinges 3, Figs. 1 and 5. The I beams are spaced and secured horizontally by the braces 4, Figs. 4 and 5. The I beams are pivoted about hinges 3 by means of shaft 5, Figs. 1 and 5, with eccentric portions connecting integral truss portions 5 of the beams through links 1, Figs. 3 and 5. A crank 8 with a worm gear cooperates with gear 9 which is adapted to rotate shaft 5 and thus enable adjustment of the angle at which beams l and 2 meet at hinges 3. This is for the purpose of predetermining the crown of the road section under construction or repair.

The span structure is detachably fixed to girders l0, and braces 15, Figs. 1 and 4, by bolts (not shown) passing through holes in the contacting flanges of the members, the bolt holes being arranged along the I beams to permit fixing the girders It at optional positions to thus adapt the wheel tread to various widths, as well as to facilitate knock-down for transportation. Girders H] are supported by a wheel arrangement on each end adapted to support the entire machine.

The rear wheels ll, Figs. 1, 2 and l, are relatively wide for hearing and traction purposes. Axle 12 for wheel I l is rotatably mounted in bearings I3 on frame members I 4, Figs. 1 and 2, which are fixed to girders ll]. Braces l5 connect frame members M to beam 2 and are fixed to girders ill by means of webs l6, Fig. 2. A sprocket ll, Fig. 1, is fixed to each wheel ll and cooperates with chain l8 to which power is transmitted to propel the machine.

Pneumatic front wheels I9, Figs. 1 and 21, are rotatably fixed to respective forks 29 from which a piston 21 extends into a cooperating hydraulic cylinder 22 (Fig. 21). A link 23, Fig. 1, fixed to front wheel fork is adapted to be fixed at option to a bracket 2 which is rigidly fixed to cylinder 22 so that piston 2! is free for longitudinal motion and restrained from rotation in the cylinder 22.

The carriage which supports the various road operation performing members comprises a frame consisting of main members 25, Fig. 1, with cross braces 26, 21 and 28, Fig. 11. Strap-like cross braces 29, Fig. 11, may be placed diagonally on the frame. The carriage frame is pivotally fixed to an intermediate frame by bearing member 30, Fig. 11, on the carriage frame connected to bearing member 3! of the intermediate frame by pin 32.

The intermediate frame consists of cros members 33 (Fig; 11), longitudinal members 34 (Fig. 1), and diagonal members 35 (Figs. 11 and 12). The intermediate frame has two roller supporting members 36 (Figs. 1 and 11) fixed to the back, and two members 31 fixed to the front as shown in Figs. 11 and 12. Rail roller 38 are arranged on supports 36 and 31 in a manner to roll on beams l and 2 with fixed rail portions 39 as shown in Figs. 11 and 13. The pivoting of the carriage frame about pin 32 is maintained in a plane with the intermediate frame by means of cross member 28 of the carriage frame being slidably retained between intermediate frame member 33 and plates 46 which are secured to support members 31 by bolts 4|, Figs. 11 and 12.

The range of the sliding motion and related pivoting of the carriage frame relative to the intermediate frame is limited by stop screws 62 and 43, Fig. 12, which are oppositely threaded through the respective support members 31, and operated by a nut and spline member 36. Rubber cushioned pads 45, Fig. 12, fixed on members at each side of the carriage frame serve as stop contacts for screws 3-2 and 63. The purpose of this arrangement, whereby the angle at which the carriage frame may pivot relative to the intermediate frame may be predetermined by adjusting screws 42 and 43, is to position the carriage frame at right angles to its path of travel over the work, for reasons hereinafter set forth.

The carriage frame, members 25 etc., with the attached operation members and the intermediate frame are propelled back and forth along beams l and 2 of the span structure, by means of cable 46 which is attached to each support member 31 by means of eye bolts 67, Fig. 11. Cable 46 passes over a sheave 58 (Figs. 1, 4 and 5) at each end of the span structure and over drum 49 (Figs. 1 and 17) which actuates the cable. Preferably the cable is fixed to the drum to prevent slippage and sufficient raps are made over the drum each side of the fixed point to permit sufficient drum rotation either way for the back and forth travel of the cable. Drum 49 is actuated by a power plant 59, Figs. 1 and 5, through a transmission 5| adapted to automatically reverse the direction of rotation of drum 49 at a predetermined instant.

Details of the transmission 5! and drum 49 are shown in Figs. 1'7 and 18. An end member 52 is fixed to drum 49 by bolts 53 and rotatably supported by a ball bearing on spindle 54 which is supported by member 55, Figs. 17 and 1. End member 52 has a cam shaped section which fits concentrically along the interior cylindrical section of a piston member 56 (Fig. 17). Piston 56 is arranged to rotate with shaft 5! by means of a slidable splined section, and is adapted for longitudinal and rotary motion in the cylindrical portion of drum 59 which maintains therewith a fiuidtight contact. Piston 56 is yieldably maintained in contact with the cam portion of end 52 by means of spring 58 which is maintained and adjusted in compression by a member 59 threaded into a portion of drum i9 and adapted to serve as a bearing and packing on shaft 5?. A valve 69 is adapted to permit unobstructed passage of fluid from the top to the bottom of piston 56. A passage 6! is provided through piston 56 of correct size to permit return of fiuid to the top of the piston 56 at a rate to prevent rapid downward movement of the piston.

The mechanism is operated with piston 56 submerged in a suitable fluid. The purpose of this arrangement within drum 49 is to provide a cushion between the rotation of shaft 51 and the drum 49 when a sudden impact load is applied. Spring 58 applies suificient force on piston 56 to cause the piston to return to its lowermost position with the cam sections meshed, i. e., when the overload due to impact is reduced to a normal load, the rate of return being restricted by the rate at which fiuid passes from the bottom to the top of piston 56. The restriction on the rate of fluid fiow through passage 6| is in amount that is necessary to prevent harmonic variation in the rotation rate. Under normal operating conditions, including the rotation reversal of drum 49, the rotative displacement of the drum 49 relative to shaft 5'1 is small, the impact being absorbed by the rubber cushioned pad 45 on the carriage frame.

In the transmission (Fig. 17) a shaft 62 is rotatably supported by bearings 63 and 64 which are fixed to transmission box 5|, and transmits power from plant 58 through gears 65 and 66 which are splined to rotate with shaft 62. A shift control 83A (similar to 833 shown in Fig. 18) may be of the usual thrust and collar arrangement, and cooperates with gears 65 and 66 to shift and maintain their position on shaft 62. The gears are shown in a neutral position in Fig. 17. When they are shifted to the left, Fig. 17, gear 65 meshes with a reverse gear 6! which cooperates with gear 68 fixed to a shaft 69 with gears 16, TI and i2. Shaft 69 is rotatably supported by bearings 73 and M which are fixed to the transmission box 51. Gear 65 may be shifted to mesh with gear 16, or gear 66 to mesh with gear H to actuate shaft 69 at two respective speed ratios. Gear 12 cooperates with gear 15 to actuate shaft 16 which is rotatably supported by bearings 71 and 18. Gears [9 and are rotatably supported on shaft 16 and each mesh with gear 8| which is fixed to shaft 57. A clutch member 82 is splined to rotate with shaft 16 to engage matching clutch portions of either gear 19 or 80 at option.

Clutch member 82 is shifted by a control as shown in Fig. 18. An arm 83, fixed to shaft 84 which is rotatably supported by box 5|, is actuated by lever 85. Lugs 86 are provided to engage a grooved section of clutch member 82 in a manner to control its position longitudinally along shaft 76. Spring 87 is arranged in compression between a portion of arm 83B and box 5| with dead center at neutral shift position, and serves to facilitate engaging the clutch. A wing screw 88 is provided to fix lever 85 in neutral or other positions. A roller bearing 89 and packing 90, Fig. 17, are provided for drum shaft 51.

The remainder of the transmission mechanism relates to means for'propelling the entire machine alongthe work by wheels II, Fig. 1. Gear 9I (Fig. 1'?) which is an integral portion of shaft I0, cooperates with gear 92 to rotate shaft 93 and gear 94. Shaft 93 is rotatably supported by bearings'at each end which are fixed to portions of transmission box 5|. Shaft 95 is rotatably supported by gear 9i and bearing 96 (Fig. 17). Gear 97 is arranged to rotate shaft 95 by means of splines adapted to permit shifting the gear along the shaft to mesh gear 97 with either gear 9-I or 94 at option to thus provide two different speeds. A control arm 830 similar to arm 833 in Fig. 18, cooperates with gear 91 to control its position along shaft 95. Gear 91 is shown in a neutral position in Fig. 17. Worm gear 08 is fixed to shaft 95 and cooperates with gear 99 to rotate shaft I09. Shaft I is rotatably supported by transmission box and extends exterior thereof and through beam 2 of the span structure where it is rotatably supported by bearing IllI as shown in Fig. 1.

Gear I02 is fixed to the end of shaft I00 and operates with gear I03 to rotate shaft I04 as shown in Figs. '1 and 3. Shaft I05 is connected to shaft I04 (Fig. 3) by a universal joint I06. Shafts I04 and I05 are rotatably supported by brackets I01 along beam 2, and connect to a clutch at each side of the machine (indicated :1

H3, Fig. 2).

The purpose of the clutches H3 is to provide a means by which to steer and turn the machine by disengaging actuation on one side while the other side continues actuation. Details of the clutch are shown in Fig. 24, in which member I08 is secured to shaft I04 by set screw I09. Member H0 is arranged to rotate with member I08 by means of key III which is adapted to permit longitudinal motion of member H0 relative to I08. A lining H2 suitable for frictional contact is fixed to member III]. Member II3 which is adapted to cooperate with lining I I2 is rotatably journaled on shaft I04 and, maintained in position by collar II4. Spring H5 is arranged in compression between members III) and I08 to maintain frictional contact between members I I2 and H3 except when control is disengaged by application of force through control yoke III; to compress spring I I5. Rollers II! are provided on each side of control I I6 to cooperate with the flange portion of member IIO when the force is applied. Control yoke H0 is operated by a diaphragm power device IIB which is actuated by pressurized fluid introduced at passage II9. Sprocket I26, an integral portion of member H3, is provided to actuate drive chain I8, Fig. 2. Support I22 is fixed to brace member I5, and part I23 is secured to support I22 by bolts I24 to form a split bearing and rotatably support memher 4.

Hydraulic fluid is supplied under pressure for operating device IIB of the clutches, Fig. 24, and to maintain front wheel piston 2|, Fig. 21, in a predetermined position. No hydraulic fluid supply facilities are shown by the drawings, however any arrangement of conventional type may be applied.

An hydraulic fluid control valve for clutch members I08 is shown in Figs. 19, and 21. A

casing I 25 is provided with an inlet fluid passage I26, a return passage I21, and passage 128 which is connected to passage H9 of one clutch, Fig. 24, by a suitable fluid conduit, and passage I29 which is similarly connected to the other clutch. An oscillatory valve member I30 (Fig. 19), isflxed to shaft I3I which is journalcd in cover member I32 and easing I25 which latter v is provided with packing I33. Passages I34, I35 and I35 in valve I30 are arranged so that when the valve is oscillated counter clockwise, Fig. 19, pressurized fluid flows through passage I26, I35 and I28 to passage II9 (Fig. 24) of the clutch on the left side of the machine, while passage I'Iil on the other clutch is connected to the return line through passages I29, I34 and I2]. When valve I30 is oscillated clockwise (Fig. 19) passages I243 and I29 are reverse in function, I 28 being in the return circuit and I29 thepressurized circuit.

An arm I31, Figs. 20 and 21, is fixed to shaft I31 and connected by control link I33 to guide arm I39 which is fulcrumed to one end of mem ber I40 which is fixed to the machine at the other end, as shown in Fig. 21. The purpose of this arrangement is to provide a means to steer the machine automatically by guide wheel I l-I of guide arm I38, following a guide line arranged along the work, and thus causing valve 139 to function as the machine deviates from the course determined by the guide line to disengage the clutch and drive wheel II on the applicable side so that the other drive wheel ll propels the machine about the disengaged wheel II as a pivot until the machine is brought to a true course. It is advantageous to adapt this control valve to operate on either side of the machine, at option, and also to provide a manual means of control. Guide arm I39 and member Mt also serve to maintain the machine on a predetermined grade as described hereinafter.

The extent of travel of the carriage member actuated by cable along the span structure is controlled by means adapted to shift clutch member 82, Fig. 17, and thus reverse the travel direction of the carriage frame at a predetermined point on each side of the machine. This is accomplished by lever I42, Fig. 1, fulcrumed on supports I43, Fig. 5, which are fixed to cross members I44, Fig. 1, of the span structure. Lever I42 is connected at its upper end to control lever 8E3, Figs. 1 and 18, and to a rod indicated at I46, in Figs. 3 and 5 at its lower end by coupling I41 as shown in Figs. 1 and 3. Rod I40 is supported on the span structure by supports I40 adapted .to permit free longitudinal motion of the rod. A contact member I49 is fixed at some predetermined point on each end of rod I46 by screw I50- and is adapted to shift clutch member 02 (Fig. 18) through red I46, arm I42 and lever when actuated by contact of carriage frame member 34 with member I49v The members supported by the carriage frame for the purpose of performing construction operations, as shown in Fig. 1, from the front to the back, are: a combined leveling and mixer member, a scarifler member, a blade member, a vibrating roller and associated leveling member, and a roller member. These members are proportioned in size such that each covers about the same width of work. The travel of the memhers is practically transverse to the general strip of work. In the usual procedure of operation, the machine travels along the work a distance equal to the width of the work covered by the individual operational member while the carriage frame passes from and returns to one side of the machine. Gears I02 and I03 (Fig. 1) are replaceable by sets of gears in various transmission ratios which in conjunction with the gear box ratios are applied to coordinate the rate of speed of the carriage frame with that of the entire machine for various specific operating conditions. The operational members of the machine are designed so that any of them may be prevented from operation while the others function, and any combination of the members may be used as are applicable.

The patentable features of the various operational members will be made the subject matter of separate patent applications and therefore the members will be described in only sufiicient detail to reveal the general nature of some of the members which may be advantageously used with the machine set forth.

The combination leveling and mixer member is shown in Figs. 6 and 7. The mixing rotor II, Fig. 6, is secured to shaft I52 by nut I53 for horizontal rotation. The mixer is adapted to discharge a fluid to material through openings I54. Mixer shaft I52 is rotatably supported by bearing ['56 in housing I51 which is disposed in a housing I58 to permit vertical motion of I51 to adjust the depth of operation. Packings I59 and I60 are provided to seal the lubricant. A cover comprised of parts IGI and I62 are secured by bolts I63 (Fig. '7) to protect the parts from abrasive materials. A bracket I64 is attached to cover I6I and threaded to crank operated screw I65 with anti-thrust collar I66 to control depth setting. A gear I61 supported by bearings I68 is slidably fitted to mixer shaft I52 to rotate the mixer. A cover I69 is secured to casing I58 by bolts III] and is adapted with packing I1I to seal mixer shaft I52. Fitting I12 for connection of a fluid supply line comprises non-rotating packing members I13 and I14, and retaining flanges I and I16 with packing "I which rotates with shaft I52. A fluid line support I18 is provided.

A material retaining hood over the mixer comprises side members I19 and I8!) fixed to supports IBI from the carriage frame by bolts I82, and top I83 being secured by bolts I84, Figs. 6 and 7. Leveling members I85 (Fig. '7) are pivotally supported by brackets I85 secured to the hood by bolts I81 positioned by stop screws II8, fixed to the hood. The mixer is actuated by power plant I 96 through clutch I9I, through gear I92 and shaft I93 supported by case I94 and bearing I95, cooperating with gear I96 and shaft I91 supported by bearings I98 and I99. Gears 208, 28I, 282 and control lever 263, control shaft 294, arm 295, yoke bearing 286 (Figs. 6 and '7) and are arranged to permit two different transmission drive speed ratios for the mixer.

A two speed power take off for actuating a vibrating roller is shown in Figs. 6 and '1, comprising shaft 251, gears 288 and 299, control lever 2I0, with shaft 2II and arm 2I2.

Fluid cement, asphalt or other agent is conveyed to the mixer through flexible conduit 2I3 (Fig. 1) connected to fitting I12 and supported by link 2 I4 and clamp 2 I5. To support the other end of the fluid conduit a reel is provided (Fig. 16) in which drum 2I1 is rotatably supported by hollow shaft 2I8 journaled upon the span structure by bracket 2I6. Fitting 2I9 provided with packing 229 about shaft 2 I 8 is secured to drum 2I1 by bolts 22I and 222 and serves to convey fluid from shaft 2I8 to flexible conduit 2I3. Slack of conduit 2I3 is maintained wound upon drum 2I1 by torque applied by spring 223 (Fig. 16) fixed to shaft H8 and bearing part 225 by pin 224 at one end, and to drum 2" by bolt 22I at the other end. A fluid supply source may be mounted on the machine and connected by fitting 226 to hollow shaft 2 I8.

The scarifier member is shown in Figs. 1, 6, '7 and 14. Scarifier teeth 221 are secured to frame 228 by pins 229 (Fig. 7). Guide members 239 (Figs. 6 and 14) extended from the carriage frame, cooperate with lugs 23I of frame 228 to permit vertical movement of the frame on members 238. Four control screws 232 (Figs. 7 and 14) rotatably supported on the carriage frame by parts 233 cooperate with lugs 23I by threads to permit vertical control of the scarifier.

The blade member comprises two blades pivotally supported in opposed relation as illustrated in Figs. 1, 6, 11 and 15. Mold board 234 (Fig. 15) with affixed bits 235 is pivotally supported by shaft 236 upon bearings 231 secured to side plates 238 and 239 provided with stiffeners 248 secured by bolts 24L Side plates 238 and 239 for the purpose of retaining material on the blades are fixed to frame members 242 and 243 (Fig. 15) which are provided with stop screws 245 adapted to limit the pivot arc and angle of the blade members by contact with parts 246. Fixed to the end of frame members 241, (Fig. 15) 'are lugs 248 threaded for cooperation with vertical adjustment screws 249. Guide members 258 fixed to frame members 242, 243 and 248 extend vertically and slidably through guides 25I fixed to carriage members 25. Screws 249 are rotatably supported on the carriage frame 25 by screw housings 252 and brackets 253 (Fig. 15).

The vibrating roller and associated leveling members are shown in Figs. 11 and 12. Roller cylinder 254 (Fig. 11) is fixed to end 255 rotatably supported on hollow shaft 256, and end 251 secured to cylinder 254 by bolts 258 is rotatably supported on shaft 259 (Fig. 11). A shaft 268 with eccentrically attached weight 26I is rotatably supported by hollow shaft 256 and bearing 282 and is provided with gear 263 adapted to cooperate with a similar gear 264 fixed to a shaft 285 with eccentrically attached weight 266. Shaft 265 is rotatably supported by bearing 261 mounted in member 268 fixed to a non-rotating shaft 259. A screw 269 secures thrust bearing 21!) to shaft 265. Three frame members 21I (Fig. 11) fixed to member 268 extended radially within the roller to join three similar frame members 213 which are fixed to hollow shaft 256 (Fig. 11). Shaft 268 is connected through universal joint 216 and shaft 291 (Fig. 6) for rotative actuation. Roller support shafts 256 and 259 are fixed to roller frame members 211 and 218 by parts 219 and 288 (Fig. 11). These frame members are joined by end members 28I and 282; and the frame unit is pivotally supported about shaft 283 (Fig. 12) which is secured to carriage member 25 by brackets 284 (Fig. 11).

Compression spring 285 (Fig. 12) is arranged between roller frame member 28I and cap 286, threaded to adjusting screw 281 which bears on bracket 288 through thrust washer 288 at the upper end of the screw. The lower end of screw 281 is retained by support 290 secured to carriage member 25 by bolts 29I (Fig. 12). An adjusting screw eye 292 is provided for turning, and a stop nut 293 is provided on the screw to set the roller frame supported upwardly out of operative position.

The pressure of the roller 254 is predetermined by setting the compression spring 285. Vibration is provided by the centrifugal force of weights 26! and 266, (Fig. 11) occurring in unison at the upper and lower points of the respective rotation orbits.

The leveling member associated with the roller 254 is illustrated in Fig. 12, and comprises a rectangular frame 294, vertical supports 295, diagonal braces 296 and 291, and end cross braces 208 (Figs. 1 and 12). Vertical supports 295 are slidably retained by guide brackets 299 fixed to carriage members 25, and frame 294 is set in a predetermined position by cooperative control screws 300 rotatably fixed to carriage members 25 by parts 30!. Similar and opposed leveling mold boards 302 are pivotally supported to each end of frame 294 by bearings 303, and have blades 304 fixed thereto by brackets 305. Screws 305 (Fig. 12) of frame 294 function to limit and predetermine the pivotal arc of mold board 302. End plates 30'! secured to frame 294 by bolts 308 are provided to retain material. Leveling is accomplished by blade 304 of the mold board 302, which trails in operation travel, functioning to loosen material which is leveled by passing under the mold board.

The final roller member 309 is similar to the roller hereinabove described except it is not arranged for vibration.

An automatic hydraulic means, for controlling the grade at which the machine operates by regulating the height of girders above front wheels !9 through piston 2! (Figs. 1 and 21), is provided. Rear wheels travel on the completed surface in most applications.

An hydraulic control valve for elevation con trol comprises casing 3l0 with a detachable top 3!! (Figs. 21, 22 and 23) contains float 3!2 connected by arm 3!3 to shaft 3!4 which is connected by arm 3!5 (Fig. 22) which cooperates with pin 3l6 (Fig. 23). Through pin 3 3 (Fig. 22) and arm 3!'!, a rotary valve 3!8, fixed to shaft 3I9, is pivoted in operative range. Passage 320 is connected by a fluid line to a pressurized fluid source, passage 32! to wheel cylinder 22, and passage 322 to a low pressure return line as i1- lustrated in Fig. 23. The above valve functions to introduce or to return hydraulic fluid from wheel cylinder 22. The control valves are slidable vertically on guide 325 by cooperation with screws 325 which bears on girder !0 by part 326 (Figs. 1 and 21). Screw 325 is operated by pulleys 321 and 328 coupled by cable 329 (Fig. 1). The control valve casings 3! 0 are connected at passages 330 (Fig. 23) of a fluid line, a portion of which is shown as 33! (Fig. 5) and a fluid reservoir 332 is connected to line 33! by flexible fluid conveying line 333 through valve 334 (Figs. 1 and 5). Fluid reservoir 332 is shifted vertically on guide 335 fixed to span structure portion 6, by screws 336 (Figs. 1 and 5). Grade control is accomplished by the fluid maintaining a common level in the valve casings and reservoir 332 by gravity flow through the interconnecting fluid conveying lines, the valve being actuated by a change in fluid level to cause hydraulic shifting of piston 2! (Fig. 1) in a direction to tend to maintain a predetermined level of fluid in the valve casings.

The machine may be controlled by a wire or other suitable means placed on a predetermined grade line to guide wheel !4! (Fig. 21) and thus actuate valve 3!8 through arm !39, member I40, and link 338 connected to pin 3l6 (Fig. 23).

- To arrange the machine for convenient transportation, the span structure is constructed with splice joints in beams I and 2 about eightfeet from one end adapted so that the structure may be separated at the joints. The carriage frame assembly and both sets of wheels with girders !0 are arranged in usual orientation on the short part of the span structure and the remaining longer part of the structure is placed on top of and parallel with wheel girders !0. Rear wheels (Figs. 2 and 4) are provided with lugs 339 adapted to secure an auxiliary wheel with a pneumatic tire of sufiicient diameter to keep wheel off of roadsurfaces while the machine is in transit. The front wheels are made free for turns by disengaging link 23 and bracket 24 (Fig. 1).

The splices for the knock-down joints in the span structure referred to above are shown in Fig. 11. Beams and 2 and rails 39 have right angle butt joints secured by splice plates 3140 and 34! fixed to the webs and flanges of the beams by bolts 342, and dowels are placed through rail joints 39. Span structure braces 4 at the splice may be made detachable, but preferably are arranged such that none connect between the two parts of the span structure, as separated by the joints.

The foregoing description and related drawings have illustrated one embodiment of my invention. Modifications in the construction of the machine may be made within the scope of the claims.

The operation of the machine is as follows:

The construction of a flexible base, sub grade, of courses stabilized with cement, bitumen, salt, or the like, and other courses which require mixing, addition of water or stabilizing material, leveling and compacting to a defined section, are all handled in the same general manner.

The material to be worked is uniformly windrowed in the middle, or evenly distributed over the work strip. The wheels which support the machine are set to travel on the outer parts of the work strip, and the machine is adjusted to operate to the desired width. Leveling members I are adjusted in elevation to level the material and above any surplus to the edges; and mixed rotor I5! is set to operate at a predetermined depth; and the required quantity of moisture or stabilizing material in fluid condition is introduced through the rotor !5! as set forth. The scarifier 22! need not be operated unless additional mixing is desired.

Blade members 235 (Figs. 1 and 15) are set at proper elevations and pitch angles by means previously described so that an appreciable quantity of material is carried back and forth across the work between the two blade members. The leading blade revolves to the extent that the material does not accumulate in front of it, but. accumulates in front of the trailing blade. This evenly distributes the material and compacts it to an extent, depending on the quantity of material shifted between the blades.

The vibrating roller 254 (Fig. 11) is set at the desired pressure by spring 285 (Fig. 12) and appropriate centrifugal . weights 266 and 26! are rotated at a rateto obtain the desired amplitude and frequency in the roller vibration. The leveling members 302, 304, etc. Fig. 12, which are associated with the vibrating roller, in the case of most materials, are adjusted so that they loosen the material only to the depth necessary to include the lower spots left by the roller, and maintain sufficient surplus on the mold board of the functioning member to leave the material in a 11 uniform condition by means set forth suitable for final rolling.

When the carriage travel is reversed, direction at the edge of the work, the surplus material is crossed by the roller and 'pickedup by the other leveling member.

Minor modifications in the construction of the vibrating roller and associated leveling member may be made to most effectively adapt the machine to the material under operation. The final roller is generally set at a predetermined pressure controlled by the spring as described.

The machine is obviously more applicable to construction with materials which may be compacted immediately after mixing. However, when a curing period is desired before compaction the rolling operations maybe omitted from the first passage and performed during the second passage.

When the machine is applied to construction of ready mixed materials such as concrete, bituminous concrete, or any material not requiring mixing, the operations are substantially the same as described above, except that the mixer rotor is inactive and raised in position.

To cut trench subgrade, to terrace and grade, the scarifier member maybe operated to loosen the material to the desired depth, The blades may be set to shove the surplus material to the edges, one member shoving part of it to one side and the other member shoving the balance to the other side, or both blade members may be set to shove it to the same side. The vibrating roller, associated leveling member and final roller may be operated as described above in connection with these operations.

As mentioned hereinbefore, the usual operative speed of the machine as a whole, relative to the crosswise travel speed of the carriage assembly, is such that the carriage travels from one side of the work to the other and returns while the machine travels a distance equal to the width of work covered by one of the individual operation members. When operated at this ratio the Work is covered twice by the same operation and the passes overlap one another, which is very advantageous in obtaining a uniform and thoroughly worked section. In case of some materials which are difficult to handle the forward travel rate may be relatively reduced to. give additional passes of the same operations over the material.

It is possible to operate the machine on material against a curb, or along the trimmed edge of other work as applicable in construction of a wider section than can be covered in one work strip. In such application the various operation members lap over the edge of the curb or work being joined, and the surplus material deposited thereon ahead of the vibrating roller serves to protect the curb or work being joined from direct impact of the roller. Surplus material is removed from the curb or work surface by the leveling member following the vibrating roller. The application just described is without use of the mixer rotor and the scarifier member which would obviously interfere with the curb or work being joined in most cases, if lowered for operation.

The above description and drawings are merely an illustration of my invention in one of many possible forms of application, and the scope of protection contemplated is to be taken from the appended claims interpreted as broadly as is consistent with the prior art.

said frame structure transversely of the longitudinal axis thereof; a carriage supported by rollers on said trackway for back-and-forth movement thereacross; road working elements supported by said carriage; power means mounted on said frame to propel the machine; means operated by said power means to actuate the carriage back-and-forth on said trackway; said trackway comprising hinged sections; and means to adjust said hinged sections relative to each other to conform with a desired road crown curvature whereby movement of the carriage will conform therewith. v

2. In a machine as set forth in claim 1, said hinge section adjusting means comprising a shaft offset from and journaled parallel with said hinge of the sections; said shaft being provided with eccentric portions cooperating with bearing members connected to the respective sections to pivot the sections about said hinge when the shaft is rotated; and means for rotating said shaft into, and locking said shaft in adjusted positions. V

3. In a machine as set forthin claim 1,'said carriage actuating means comprising a drum; a cable coiled around said drum and having its ends secured to oppositeends of the carriage; reversible means operated by said power means for rotating the drum; and means adapted to be engaged by the carriage when nearing the limits of its movement in either direction to cause reversal of rotation of the drum.

l. A road machine, comprising a wheel sup ported frame structure; a trackway supported by said frame structure transversely of the longitudinal axis thereof; a carriage supported by means of rollers on said trackway for back-andforth movement; said carriage comprising a main frame pivotally supported about a vertical axis on an intermediate'frame which is supported by said rollers on the trackway; road working elements supported by said carriage; power means mounted on said frame to propel the machine; means operated by said power means to actuate the carriage back-and-forth on said trackway; said trackway comprising hinged sections; means to, adjust said hinged sections relative to each other to conform with a desired crown curvature, whereby movement of the carriage will conform therewith.

5. In a machine as set forth in claim 4, said hinge section adjusting means comprising a shaft offset from and journaled parallel with said hinge of the sections, said shaft being provided with eccentric portions cooperating with bearing members connected to the respective sections to pivot the sections about said hinge when the shaft is rotated; and means for rotating said shaft into, andlocking said shaft in adjusted positions.

6. In a machine as set forth in claim l, said carriage actuating means comprising a drum; a cable coiled around said drum and having its ends secured to opposite ends of the carriage; reversible means operated by said power means for rotating the drum; and means adapted to be engaged by the carriage when nearing the limits of its movement in either direction to cause reversal of rotation of the drum.

7. In a machine as set forth in claim 4, means on the carriage main frame and intermediate frame for predetermining the extent of the arc 13 within which the carriage main frame may swing on the intermediate frame.

8. In a machine as set forth in claim 4, means on the carriage main frame and intermediate frame for predetermining the extent of the are within which the carriage main frame may swing on the intermediate frame; and means for causing the carriage main frame to retain a position at one extreme of said are by a drag force while the carriage is moving in one direction across the trackway, and means whereby when the direction of travel of the carriage is reversed the carriage main frame will swing to the opposite extreme of said are.

9. A road machine, comprising a wheel sup ported frame structure; a trackway supported by said frame structure transversely of the longitudinal axis thereof; a carriage supported by means of rollers on said trackway for back-and-forth movement thereacross; road working elements supported by said carriage; power means mounted on said frame to propel the machine; means operated by said power means to actuate the carriage back-and-forth on said trackway; said trackway comprising hinged sections; and means to adjust said hinged sections relative to each other to con form with a desired road crown curvature, whereby movement of the carriage will conform therewith; said trackway having a short section supported on said frame structure, and a long section adapted to be swung into superimposed position on said short section parallel with the longitudinal axis of the machine to facilitate transportation of the machine.

10. In a machine as set forth in claim 9, said bers connected to the respective sections to pivot the sections about said hinge when the shaft is rotated; and means for rotating said shaft into. and locking said shaft in adjusted positions.

11. In a machine as set forth in claim 9, said carriage actuating means comprising a drum; a

cable coiled around said drum and having its ends secured to opposite ends of the carriage; reversible means operated by said power means for rotating the drum; and means adapted to be engaged by the carriage when nearing the limits of its movement in either direction to cause reversal of rotation of the drum.

12. In a machine as set forth in claim 9, said carriage comprising a main frame pivotally supported about a vertical axis on an intermediate frame which is supported by said roller on the trackway.

13. In a machine as set forth in claim 9, said carriage comprising a main frame pivotally supported about a vertical axis on an intermediate frame which is supported by said rollers on the trackway, and means on the carriage main frame and intermediate frame for predetermining the extent of the arc within which the carriage main frame may swing on the intermediate frame.

14. In a machine as set forth in claim 9, said carriage comprising a main frame pivotally supported about a vertical axis on an intermediate frame which is supported by said rollers on the trackway, and means on the carriage main frame and intermediate frame for predetermining the extent of the are within which the carriage main frame may swing on the intermediate frame, and means for causing the carriage main frame to retain a position at one extreme of said are by a drag force while the carriage is moving in one direction across the trackway, and means whereby when the direction of travel of the carriage is reversedthe carriage main frame will swing to the opposite extreme of said arc.

GEORGE P. GREEN.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 910,073 Lischke Jan. 19, 1909 1,410,114 Peterson Mar. 21, 1922 1,467,243 Fitzgerald Sept. 4, 1923 1,514,923 Parker Nov. 11, 1924 1,533,464 Robb Apr. 14, 1925 1,629,611 Carr May 24, 1927 1,673,298 OConnor June 12, 1928 1,677,877 Carr July 17, 1928 1,700,797 Hebden Feb. 5, 1929 1,736,412 Lichtenberg Nov. 19, 1929 2,025,703 Baily Dec. 31, 1935 2,043,413 Knox June 9, 1936 2,054,236 McCreary Sept. 15, 1936 2,059,205 Buffington Nov. 3, 1936 2,101,837 Blanchett Dec. 14, 1937 2,169,184 French Aug. 8, 1939 2,192,027 Crowder Feb. 27, 1940 2,223,024 Beierlein Nov. 26, 1940 2,229,530 South Jan. 21, 1941 2,261,491 Baily Nov. 4, 1941 2,287,723 Boyd H-. June 23, 1942 2,295,519 Millikin Sept. 8, 1942 2,324,412 Milster July 13, 1943 2,351,593 Barber June 20, 1944 2,438,159 Faber Mar. 23, 1948 FOREIGN PATENTS Number Country Date 24,547 Australia 1935

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