Linear moving irrigating apparatus

A self-propelled, linear-forwardly, relatively slow-moving irrigating apparatus has a main frame and master drive unit carrying a rotating, water-supplying, pipe-like, axle shaft that provides a side-extending wheel-line along which are spaced what may be termed power, booster and wheeled spray units that enable a large area of ground crop to be irrigated at one time. Longitudinally spaced-apart hydrants are provided along the length of the field that is to be irrigated to detachably receive a flexible water-supplying hose that is also detachably carried by the main frame. The apparatus has automatic means for maintaining the main frame and the wheel-line in an aligned forwardly advancing relation, for stopping forward movement when a serious obstruction is encountered and when the desired full extent of its advance along a side-extending anchored guide cable has been attained. Combustion engine and coupling means is provided for the main frame and a wheel-line power unit to drive the apparatus backwardly towards its starting position without the need for auxiliary drag-back tractor or other equipment.

FIELD OF THE INVENTION 
This invention pertains to an irrigating apparatus for linear movement 
along a field crop to effectively cover a maximum area thereof in a 
progressive, slowly advancing type of sprinkling operation in which the 
apparatus is self-energized in both its forwardly advancing sprinkling 
operation and in a reverse-return type of operation. A further aspect 
deals with operative features of the apparatus that enable it to function 
in a foolproof and positive manner, with a minimum of manual control and 
auxiliary equipment. 
DESCRIPTION OF THE PRIOR ART AND PROBLEMS INVOLVED 
Heretofore, there have been both rotary and linear types of field area 
irrigating equipment, but the present invention pertains particularly to a 
linear type and to problems which have heretofore been presented from the 
standpoint of presently known prior art apparatus. One characteristic of 
the prior art apparatus is that use has been made of hydraulic jack 
actuation in which the upper or forward movement of the piston rod of the 
jack represents the only positive actuation thereof and as employed to 
advance the equipment. The disadvantage of constructions of this type has 
been that the return of the piston and its rod is non-positive, in that it 
depends primarily on gravity and weight considerations, and this has given 
rise to various adverse factors, such as a total stoppage of return due to 
dirt or mud thrown up from the field, or uncertain and uneven movement due 
to frictional resistance encountered by the piston within its housings, 
etc. 
A further problem encountered in the prior art equipment has been the lack 
of full coordination between the drive of the main frame unit and the 
movement and drive of the wheel-line, side-extending portion of the 
apparatus, such as may be caused by the different nature and contour of 
the field transversely thereof as encountered by the apparatus, by an 
actual obstruction encountered, such as a stone or mound of dirt, all of 
which tend to present problems of misalignment or a tendency to bend or 
break wheel-line portions of the apparatus or to damage the equipment when 
an excess torque is engendered. The need has been for an apparatus that 
will give a maximum coverage in its forward linear advance, for example, 
about a quarter of a mile of field width, and which will do so without 
entailing any damage to the apparatus due to obstructions, stoppage, 
irregular contours or other factors that are encountered during forward 
movement. 
The need has been for a substantially fully coordinated and automated type 
of operation, such that stoppage of wheel-line drive may be effected when 
torque resistance above a present value is reached. Also, simplified 
self-aligning means should be provided that will enable the advance of the 
main frame to be slowed down, speeded up or stopped to coordinate its 
movement with that of the wheel-line. 
Another problem, as previously presented, has been the difficulty of 
returning apparatus, and especially apparatus having a considerable length 
of wheel-line, to an initial or starting position, once it has reached the 
end of its desired forward travel. In this connection, it has heretofore 
been necessary to utilize a heavy tractor, truck or other power equipment 
which tends to sink into the wet soil and cause excessive damage to the 
growing crops, and which increase costs from the standpoint of man hours 
and excessive auxiliary equipment required. 
OBJECTS OF THE INVENTION 
It has thus been an object of the invention to determine and evaluate the 
adverse factors that heretofore have been encountered in connection with 
the utilization of wide coverage, linear irrigating apparatus. 
Another object has been to devise linear moving irrigating apparatus which 
meets the adverse factors and which enables a solution to problems 
encountered in the design and use of prior art construction. 
A further object of the invention has been to devise an irrigating 
apparatus for effectively wetting a large crop planted field or area, and 
whose relatively slow speed can be accurately adjusted and set to 
accommodate an efficient, full forward irrigating action, and that is so 
constructed as to enable automatic alignment adjustment and protection 
from damage by reason of irregular ground contour or the presence of an 
equipment damaging type of obstruction. 
A still further object has been to devise a linear irrigating apparatus 
that may be both positively hydraulically advanced in a sprinkling 
operation, and that may then be self-operated in a reverse or return 
direction with a minimal or changeover involved and with minimal damage to 
the crop area. 
These and other objects of the invention will appear to those skilled in 
the art from the illustrated embodiment and the claims. 
BRIEF DESCRIPTION 
The illustrated embodiment utilizes a main frame that carries a lateral or 
side-extending wheel-line on a hollow, water-supplying, pipe-like shaft 
member that serves as a drive shaft and wheel axle for moving the 
apparatus in both forwardly advancing and retracting directions. The shaft 
serves to supply water under pressure to spray heads at spaced locations 
along the wheel-line; it utilizes spaced-apart supporting wheels and 
booster and power units that supplement movement that is effected by a 
positively reciprocated hydraulic jack on the main frame. A power unit 
carried midway of the wheel-line also cooperates with the master drive 
unit of the main frame in returning the apparatus to a starting area. 
Power units of the apparatus employ hydraulic jacks, stroking arms and 
bull gears for effecting forward movement and have adjustment means 
between the stroking arms and teeth of cooperating bull gears for 
selecting the number of teeth that will be engaged during each upward 
stroke of the jacks. 
The main frame unit utilizes a self-aligning means that is controlled in 
its operation by the relationship between a drive reel or capstan and a 
reeved guide cable which is to be anchored at its ends to extend along a 
full forward length of the field to be covered. 
Side-positioned booster drive and power units are each provided with 
torque-sensitive valve means that will slow down and stop the drive 
stroking movement of their associated jacks when an obstruction is 
encountered. The main frame as well as an intermediate power drive unit 
are provided with combustion engines for driving the equipment in a 
coordinated return direction after a flexible supply hose has been 
disconnected from a water supply hydrant at its one end and its other end 
has been connected in a dragging return relation to the then back end of 
the returning main frame.

DETAILED DESCRIPTION 
In FIG. 1 of the drawings, an apparatus of the invention is somewhat 
diagrammatically illustrated. In this layout, A and A' represent a group 
or series of spaced-apart hydrants whose intermediate spacing approximates 
a distance representing twice the length of a flexible hose G which is to 
be detachably utilized therewith for supplying water under pressure to the 
apparatus. As indicated, the irrigating apparatus is adapted to advance 
forwardly lengthwise in a direction along a field or crop area between two 
locations that are represented by ground anchors 42, 43 between which the 
guide cable 41 is adapted to extend. It will be noted that the back end of 
the cable 41 is secured to the anchor 43 through the agency of a heavy 
spring 44 which serves to provide it with a flexible, non-breakable 
mounting. 
The apparatus proper employs a master drive unit C that is represented by a 
main frame 10 (see FIG. 2) from which extends a rotating, pipe-like 
water-carrying axle shaft 17 that serves as a conduit to supply water 
under pressure along its length to sprinkling units 93 (see FIGS. 2, 3, 4, 
13 and 14). The shaft 17 defines a side or laterally extending wheel-line 
B that is supported at spaced locations along its length by wheels F that 
are keyed thereon. Also, a mid-located power mover unit D and 
lengthwise-space booster units E are shown as completing the wheel-line 
construction. 
Forward movement of the construction is accomplished in a substantially 
automatic manner by a four wheel master drive unit C, four wheel power 
unit D, and two wheel booster units E, all as driven by reciprocating 
hydraulic jacks 30, 30' and 30". The maximum or final forward position of 
the apparatus is controlled by a stop element of trip clamp 41a (see FIGS. 
6 and 12) that is to be clamped on the cable 41 to trip a lever mechanism 
shown in FIG. 12 of the drawings to completely shut-off the supply of 
water to the apparatus at the end of its forward movement through the 
agency of a main shut-off valve 45. As shown in FIG. 5, the valve 45 is 
mounted on frame 10 by an upwardly extending bracket 46. Suitable 
rotatable spray head assemblies (see FIGS. 13 and 14) apply water to the 
crop rows during the forward advance of the apparatus. The advance is 
effected at a relatively slow rate to assure a suitable depth of wetting 
of the field area with one movement. 
Referring to FIGS. 2, 5 and 6, the master drive unit C is shown as a 
four-wheeled unit whose pair of rear wheels 11 (the arrow a represents the 
direction of forward movement) are free-turning and mounted by their hubs 
12 on a cross-extending axle shaft 13 and secured in place by spacer 
collars 14. The shaft 13 is rigidly secured on a back end front portion of 
the main frame 10. 
A pair of front wheels 15 are provided with hubs 16 that are bolted on the 
front shaft 17 which, as noted in FIG. 2, is provided with enclosure caps 
18 at its opposite ends to provide a closed-end conduit for water supplied 
thereto. As shown in FIGS. 5 and 6, a dead end coupling 21 is securely 
fastened, as by weld metal, on a U-shaped mounting block 22 that extends 
upwardly from the main frame 10 to provide it with sufficient strength to 
drag flexible water supply hose G back when the apparatus has reached its 
final forward position. 
Water under suitable pressure is supplied by heavy duty flexible hose G to 
the main unit C through an end coupling 45a of a main butterfly, shut-off 
valve 45, see FIG. 5. Water passes from the valve 45 through an opposite 
end coupling 21a which serves as a one-end mounting for short length of 
flexible hose H (see FIG. 2). The other or front end of the hose H is 
adapted to be connected to a tee fitting 20 (see FIGS. 2 and 15) which is 
mounted in a fluid sealed-off positioning on the hollow shaft 17 to supply 
water under pressure through sidewise open ports in the shaft and provide 
a continuous flow therethrough during the forward movement of the 
apparatus. As shown in FIGS. 2, 5 and 6, and earlier mentioned, closed-off 
or dead end coupling 21 is mounted on the front end of the frame 10 to 
receive one end of the flexible hose G for dragging it backwardly along 
the field when the apparatus is to be returned to an initial or starting 
position. At this time, the forward end of the hose G is disconnected from 
an adjacent hydrant, such as A', which is turned-off, and from the back 
end coupling 45a of the main valve 45. 
A relatively slowly timed forward movement of the main frame 10 and its 
unit C is accomplished through the agency of a reciprocating, positively 
powered, double-acting hydraulic jack 30 (see particularly FIGS. 6 and 7). 
The hydraulic jack 30 is employed to forwardly advance the unit C through 
the agency of a stroking arm 28, an upper or power stroke actuated drive 
dog, pawl or spring-pressed latching finger element 24, a bull gear 25 and 
a capstan 40. As shown particularly in FIGS. 6 and 10, anchored cable 41 
is reeved about the grooved periphery of the capstan 40 in such a manner 
that rotation thereof will cause the capstan to advance the unit C 
forwardly along the cable 41 at a rate depending upon the number of teeth 
25a of the bull gear 15 that are engaged with each upward or outer power 
stroke of piston rod 31 of the jack 30. As shown in FIGS. 8 and 9, the 
upper or power stroke pawl 24 is pivotally mounted by a side-extending pin 
23a within and to extend from bifurcated bracket 23 that is secured at a 
mid location along the stroking arm 28. 
Adjustment of the number of teeth engaged with each upward power stroke of 
piston 32 and piston rod 31 of the jack 30 is controlled by adjustable, 
arcuate-shaped, sliding piece or element 26, see particularly FIG. 9. A 
support or bracket member 27 extends upwardy in a secured relation to the 
frame 10, and has an offset angle-shaped extension portion 27a that 
carries a wing nut and bolt assembly 27b for mounting the adjustment plate 
or element 26 in a secure, set position along its arcuate or sloped 
adjustment slot 26a. In this manner, as illustrated by the dot and dash 
lines of FIG. 8, the dog 24 may, for example, be adapted to advance the 
bull gear 25 by only one or two or three teeth engagement during the upper 
stroke of the jack. 
As shown in FIG. 9, the extending portion of the pin 23a of the pawl 24 is 
rounded to ride along the outer arcuate surface of the adjustment element 
26 for a distance which represents a distance of non-tooth engagement by 
the pawl 24. A tension spring 24b is connected at one end to a lug 24f on 
the pawl 24 and, at its other end, to a lug 24e on the mounting bracket 
assembly 23 to normally urge the pawl towards tooth engagement with 
respect to the bull gear 25, as well as into riding-over engagement with 
the adjustment plate or element 26. 
To prevent reverse (clockwise) movement of the bull gear 25, a second pawl 
24' is pivotally mounted by a pin 23a' on a lower bracket assembly 23' 
that is directly secured to the main frame 10. The pawl 24' is urged into 
tooth-engagement by a tension spring 24b' that is secured between a lug 
24f' on the pawl 24' and a lug 24e' on the mounting bracket 24'. It will 
be apparent that the pawl 24' rides over teeth 25a of the bull gear when 
rotation is being effected counterclockwise by the pawl 24, but that 
reverse (clockwise) rotation is prevented by latching engagement of the 
pawl 24' with the teeth 25a. 
The construction and mounting of the jack 30 for the master drive unit C, 
for the power drive unit D and for the booster units E is substantially 
the same. For this reason, to avoid duplication of description, like parts 
of the drive units have been given the same reference numerals, but with a 
single prime affix for the power unit and a double prime affix for the 
booster units. Where the parts are exactly the same, no prime affixes have 
been applied. 
Again referring to FIGS. 5, 6 and 7, the lower end of the housing of the 
jack 30 is shown pivotally mounted at 76 on an upright mounting bracket 
10d which is secured to extend upwardly from the main frame 10. Water 
under pressure is supplied alternately to opposite ends of the jack 30 and 
alternately exhausted therefrom through flexible, end-mounted hose lengths 
30a and 30b. Reciprocating movement or reversal of the direction of 
movement of the piston rod 31 is effected by a poppet valve 34 that is 
mounted on the side of the housing of the jack to exend sideways therefrom 
(see FIG. 7). The valve 34 has an upper plunger 34a that is adapted to be 
engaged and pressed inwardly by a laterally extending finger 35b which is 
secured on a vertically movable, side-positioned operating rod 35. The rod 
35 is secured, as by weld metal, to the side of a clevis 33 carried by the 
upper or outer end of piston rod 31. 
When the piston rod 31 is in its final, innermost, withdrawn position of 
FIG. 7, the poppet valve 34 is actuated by its plunger 34a to send a 
reversing signal through flexible hose lines 34d and 34e to a main control 
valve 36 to reverse the direction of positive forwardly and exhaust flows 
to the jack 30. At this time, there is a positive fluid flow through line 
30b and a negative or return flow through line 30a which is the direct 
opposite of the flow in accordance with which the piston 32 is moved 
positively to its "down" and innermost position within the jack housing. 
When the piston rod 31 has reached its uppermost position, a 
side-projecting, lower operating finger 35c contacts pressure plunger 34b 
of the poppet valve 34 to send a signal through lines 34d and 34e to again 
effect a reverse flow through the lines 30a and 30b, such that the power 
pressure flow is through line 30a and the exhaust flow is through line 
30b. Operating water under pressure is applied to the poppet valve 34 
through a flexible hose line 34c which, as shown in FIG. 6, is connected 
to a tee 56a, a line valve and a gauge to a main input water line 56 from 
the main water supply end coupling 20a that leads from the main valve 45. 
Operating water under pressure is applied to control valve 36 which effects 
a positive reciprocating movement of the jack 30, through line 57, an 
alignment flow control valve 55, and a line 56b from the tee 56a (see FIG. 
6). Water exhausts from the valve 36 through line 98 which may be 
connected to a spray nozzle 99 carried on the rear end of the main frame 
10 (see FIGS. 5 and 6) and mounted on spacer collar 14. With reference to 
FIGS. 6 and 8, a pressure gauge 37 is shown connected to the inside of the 
cylinder of the jack 30 through a manual line closing valve 38. 
Referring particularly to FIGS. 5, 6 and 12, main water supply shut-off 
valve 45 is controlled in its operation by a lever system which is 
pivotally mounted on the main frame 10 by a mounting bracket assembly 49 
that is secured thereto to project upwardly therefrom. The system has a 
pair of operating arms 47 and 51 that are secured in a pivotally connected 
operating relation on an upright, frame mounted bracket 49 by a connecting 
pin 47a. The pin 47a is rotatably mounted in a sleeve 53 that is secured 
by weld metal to extend crosswise through the upper end of the bracket 49. 
Latching arm 47 of the assembly has a down-projecting latching pin 47a 
which is adapted to engage within a hole in the end of a valve shut-off 
main lever arm 52 to hold the valve 45 through the agency of the arm 52 in 
fully open, left hand position of FIG. 5 against the tension of a spring 
48 that normally urges it to a closed, dot and dash position of the same 
Figure. 
Again referring to FIG. 12, a longitudinally extending push rod 50 has a 
pivoted, bifurcated mounting with the lever arm 51 and, at its front end, 
is slidably mounted within a guide collar 50c that is weld-secured to an 
upstanding, box-like mounting piece 74 that may be weld-secured to the 
main frame 10. The foremost front end portion of the operating push rod 50 
has a downwardly bent or right-angular extension portion 50a that, at its 
lower end, carries a bifurcated bracket or clevis 50b having a 
cross-extending, removable guide pin 50c to receive and bypass the anchor 
cable 41. During normal forward movement of the apparatus along a crop 
field, the somewhat thimble-like guide construction 50b will freely slide 
along the anchored cable 41 until it engages a stop or trip block 41a that 
is secured on the cable, see also FIG. 1. This engagement causes the rod 
50 to move in the direction of the arrow of FIG. 12 to thus raise the 
latch arm 47 to disengage its latching pin 47a from within a latching hole 
in the valve operating arm 52. At this time, the spring 48 will then be 
free to swing the arm 52 to its right hand position of FIG. 5 to fully 
shut-off flow of water from the valve 45 to all parts of the apparatus. 
As shown in FIG. 12, the stop or trip block 41a which is adapted to be 
mounted on the cable 41 may be of two-part construction secured together 
by a set screw in a clamping relation on the cable. This enables the stop 
41a to be located at any suitable desired position along the anchor cable 
41 for effecting an automatic stopping operation. 
Self-alignment of the forward movement of the master drive unit C is 
enabled through a mechanism or system particularly illustrated in FIGS. 10 
and 11 of the drawings. In this connection, the capstan 40 is mounted with 
respect to the shaft 17 in such a manner that any misalignment of the main 
frame 10 with respect to the cable 41 will be registered in the alignment 
system, but without any danger of the reeving being disturbed. With 
reference to FIG. 10, a pair of longitudinally spaced-apart support arms 
67 and 67' are rigidly secured by bolt and nut assemblies 70, 70' to 
brackets 10c and 10c' that are mounted on the frame 10 to project 
downwardly therefrom and carry a pair of pulley boxes 68 and 68' within 
which are rotatably mounted guide alignment pulleys 69 and 69'. This 
assures that any misalignment of the machine with respect to the anchored 
cable 41 does not influence the reeving of it with respect to the capstan 
40. 
To register off-alignment, a lengthwise-extending, angle-shaped member 72 
is shown pivotally mounted by a pivot bolt, nut and washer assembly 75 on 
a foot 74a of a bracket 74 that extends downwardly from the main frame 10 
and also extends upwardly therefrom as a stationary support for the 
rotating axle shaft 17. Each end of the alignment arm member 72 is 
connected through adjustable screw and nut means 73, 73' to pulley 
mounting housings or boxes 65, 65'. Each box is carried on a swing finger 
61, 61'; the upper end of each finger is pivotally mounted at 62, 62' in a 
side-extending bifurcated bracket 10b, 10b' that is secured to and mounted 
to the main frame 10. Each box 65, 65' carries a pair of cooperating 
pulleys 66 and 66' which, with their central grooves, define a pass 
therebetween for the anchor cable 41 (see FIG. 11). 
The right hand end of the alignment assembly in FIG. 10, see the detail of 
FIG. 11 and the enlarged detail of FIG. 11A, is provided with an 
adjustment screw 60a which is threadably adjustably mounted to extend 
through pivot finger 61 to support and adjustably carry a collar 58. The 
collar 58 at one end has a slot and pin mounting 58a on an extending end 
of the adjustment screw shaft 60a (see FIG. 11A). The collar 58 also has 
an integral, side-extending valve operating finger 59a that has a pivot 
pin 55b which swingably connects the finger 59a on a mounting finger 55a 
which extends integrally from the housing of an alignment flow control 
valve 55. Alignment control valve 55 is positioned in the water supply 
line 56b to adjust the flow of water under pressure through line 57 (see 
FIGS. 5 and 6) to the control valve 36 for the jack 30. As indicated in 
FIGS. 11 and 11A, swing of the pivot finger 59a about the pivot point 55b 
will control the operation of the valve 55 through its connection 59b to 
valve operating stem 59 to, in one direction, open it to more than its 
normal setting and in the other direction to move it towards a closed 
position, depending on whether the misalignment is caused by a lagging of 
the master drive unit C with respect to the wheel-line, or a more normal 
condition in which the master drive unit C tends to lead the wheel-line 
during advance of the apparatus over a crop field area. 
Referring particularly to FIGS. 3, 4 and 8, the drive mechanism for the 
power mover unit D and the booster units E operate in substantially the 
same manner as previously described in connection with the master drive 
unit C, except that no capstan is used and the bull gear 25', 25" is keyed 
to directly effect rotating movement of the saft 17. However, an 
additional feature is added to the mechanism of the power drive and 
booster units which is employed to provide protection to units of the 
wheel-line from the standpoint of obstructions encountered by it during 
its forward movement. Such means may be termed torque means, in the sense 
that it will automatically close-off water pressure application to the 
respective jacks 30 of such unit when torque resistance to forward advance 
of such units reaches a preset maximum limit. 
As shown particularly in FIG. 8, the jack 30, instead of being directly, 
pivotally mounted at the lower end of its housing on the main frame of the 
unit, is securely and non-pivotally mounted by a pin 77 to an upwardly 
extending foot portion of a fulcrum arm 78. The fulcrum arm 78 is, in 
turn, mounted on a fixed pivot 79 adjacent the jack on a frame mounted, 
upwardly projecting bracket 10d'. It will be noted that this bracket has a 
reinforcing rib 80 through which the pivot pin 79 extends. It will thus be 
apparent that when the housing of the jack 30 of unit D or E tends to 
swing during the reciprocating movement of its piston 32, this will cause 
a corresponding movement of the fulcrum arm 78. When the piston rod 31 of 
the jack 30 is moved outwardly or upwardly to advance its bull gear 25' or 
25", as effected by the upward swing of the stroking arm 28', see the dot 
and dash position thereof, this causes a corresponding forwardly, 
downwardly, tilted positioning of the fulcrum arm 78, as indicated by the 
solid line position of FIG. 8. 
An extension piece 81 is weld-secured to the fulcrum arm 78 and, at its 
foremost end, has a slide pin 78a projecting therefrom to operate within 
an elongated slot 84a in a valve operating finger 84. The finger 84 is 
adapted to move between the full line and dot and dash line positions at 
FIG. 8. The dot and dash line position represents a position in which a 
pressure cut-off valve 85 may be fully closed through the agency of its 
pin shaft 86 that securely, non-rotatably carries the forward end of the 
slotted finger 84 thereon. To adjust the amount of force or torque to 
which the finger 84 may be subjected before it completely closes the valve 
85, the extension piece 81 carries an adjustable screw and nut assembly 82 
that extends therethrough and that, at its lower end, is urged downwardly 
by a tension spring 83. The spring 83 is connected between the lower end 
of the screw of the assembly 82 and a mounting lug 83a on a downwardly 
projecting leg of bracket 10e that is bolt-secured to the frame 10' or 
10". 
The valve 85 has an in-line position the same as the alignment flow control 
valve 55 of the master unit C (see FIG. 6), in that it is connected 
between take-off line 56b and the main water pressure supply line 57 that 
leads to the jack-operating main control valve 36. Adjusting the tension 
of the spring 83, for example increasing it, will increase the required 
amount of torque as applied to the jack 30 through the stroking arm 28, 
before a complete cut-off pressure fluid is accomplished to thus stop 
forward movement of the particular unit in question. 
The pressure setting for the cut-off action may be noted from the pressure 
gauge 37 to which water may be supplied from the cylinder of the jack when 
the hand wheel 38 is moved from its normally closed to an open position. 
FIGS. 13 and 14 illustrate a typical sprinkler mount such as located along 
the rotating water supply and wheel-line defining shaft 17. Sprinkler 
heads 93 are located along suitable spaced-apart length portions of the 
member 17, usually in an equally spaced relation between the wheel units D 
and E and supplemental wheels F. Water is supplied to a central chamber 92 
through a hole 17a in the wall of the shaft 17. The chamber 92 is defined 
by a two-part, fluid sealed-off coupling collar or sleeve construction 90 
which, at its ends, has a rotatable mounting with respect to the member 17 
and is sealed-off by suitable gasket means 91. The central chamber 92, as 
defined by the sleeve 90, supplies water under pressure through a threaded 
exit pipe 94 to spray nozzle head 93 which is shown provided with an 
outwardly extending, upwardly projecting nozzle 93a. Each head 93 may be 
adapted to rotate on its stem 94 to provide a circular path of water spray 
in a conventional manner. 
To prevent rotatative movement of the sleeve 90 with the shaft 17 during 
its driving movement, a backwardly extending, angle-shaped, trailing 
ground-engaging sprag rod 97 is provided. 
As shown in FIGS. 13 and 14, the sleeve 90 may be of two-part, sealed-off 
construction bolted together for easy assembly and disassembly through the 
agency of bolt and nut assemblies 95, and associated resilient gaskets 
that extend along flanges of the two halves. The upper end of each 
trailing rod 97 has a sleeve 96 with a hole therethrough which fits over a 
pipe nipple 98 that is assembled into a threaded projection that extends 
from the bottom portion of the sleeve 90. The rod is secured in position 
with respect thereto by a pipe cap 98a. Sleeve 90 is retained in position 
on conduit 17 over hole 17a by two split clamps 99, 99' which are secured 
in position by bolt and nut assemblies 99a. 
With reference to FIG. 15, tee fitting 20 may be of somewhat similar 
construction to the sleeve 90 of FIGS. 13 and 14. It is, however, of 
one-piece construction and is provided with sealing gaskets 91' that 
permit rotation of the shaft 17 with respect to the collar. A fluid 
chamber 92' is defined by the wall of the collar 20 that enables water 
supplied by the short length hose H to be supplied to the shaft 17 through 
feed holes 17a' that may be of larger size and smaller in number than 
shown, if so desired. 
It will appear from the previously described construction of the apparatus 
illustrated in the drawings, the master drive unit C is positively 
advanced by its jack 30 at a relatively slow rate, dependent upon the 
number of teeth that are adjustably set to be engaged by the stroking arm 
28. Since the bull gear 25 and the capstan 40 of the unit C are integrally 
secured together, this will produce a corresponding turning movement of 
the capstan and thus a forward movement of the capstan in its reeving 
relation with respect to the cable 41. As to the power unit D and the 
booster units E, advancing movement is accomplished in a similar manner by 
their respective jacks 30, except that no capstan is provided and their 
bull gears 25' and 25" are keyed to or secured on the shaft 17 to directly 
actuate it. 
Adjustment of the member 26 of each unit is set by the wing nut 27b (see 
FIG. 9), in order to assure that each unit C, D and E has the same forward 
timing for coordinated, aligned advance. Since each jack 30 of the units 
will have a like return stroke or movement that is assured by positive 
fluid actuation, uncertain, erratic return action of the jack is obviated. 
Without such a positive return movement, it is impossible to coordinate 
the piston movement as is now assured in the present construction. 
It is believed to be apparent that the equipment or apparatus of the 
present invention is so constructed that once its forward operation is 
initiated, its operation will be substantially fully automatic and that it 
will not require an attendant to closely follow and become soaked with 
water. The only manual requirement for transversing the full length of the 
field in which an anchor cable 41 extends, is for an attendant to open and 
close valves of the hydrant A, A', etc. and detach the flexible hose G 
from a given hydrant, such as A of FIG. 1, when the apparatus has 
additionally reached the forward length extent of the hose, and to then 
attach the hose to the next hydrant A' and open its valve. At this time, 
the apparatus will resume its forward advancing movement. Stop 41a may be 
located at a suitable position along the anchor cable 41 to effect an 
automatic stoppage of the apparatus at the end of the run. This is 
accomplished by a fully automatic closing of the main supply valve 45 of 
the master drive unit C. 
The attendant, on noting such stoppage and desiring to return the machine 
to its starting location, may then approach the hydrant A', shut it off 
and uncouple the hose G therefrom. He then uncouples the other end of the 
hose G from the shut-off valve coupling 45a and connects it to the front, 
dead-end coupling 21. Next, the dogs or pawls 24 and 24' of the units C, D 
and E are moved back against the tension of their springs 24b and 24b' out 
of engagement with the bull gears 25, 25' and 25". They are locked in such 
a position by hooking each chain 24d, 24d' through an adjacent projecting 
lug 24c, 24c' so as to permit the bull gears to freely move in a clockwise 
direction. 
At this time, the atttendant may start up combustion engines I which are 
carried by the master unit C and the power drive unit D. It will be noted 
from FIGS. 5 and 6 that each engine has a gear and drive shaft assembly 
101 which is connected through a transmission, for example, in a 
hydrostatic gear box 102, to drive shaft 103 on which pinion 104 is 
mounted. As shown in FIG. 5, the pinion 104 is adapted to mesh with the 
teeth of a gear 105 that is keyed or secured on the conduit and drive 
shaft 17. A manual operating arm 106 is employed to operate an overriding 
clutch in the gear box 102 to drive the pinion 104. In this way, the 
apparatus may be moved backwardly, dragging the flexible hose G to the 
rear thereof and at a suitable speed, as governed by throttle on each 
engine I and the ratio of the running gears of the drive train. When the 
apparatus arrives at its starting position, then the operating lever 106 
may be swung to throw the shaft 103 out of operation. The engine I may 
then be stopped.