US2657011A

US2657011A - Means for controlling hoists and winches

Info

Publication number: US2657011A
Application number: US153319A
Authority: US
Inventors: John C Slonneger
Original assignee: CONTINENTAL SUPPLY Co
Current assignee: CONTINENTAL SUPPLY Co
Priority date: 1950-04-01
Filing date: 1950-04-01
Publication date: 1953-10-27
Anticipated expiration: 1970-10-27

Description

Oct. 27, 1953 J C SLONNEGER 2,657,011

MEANS FOR CONTROLLING HOISTS AND WINCHES Filed April 1, 1950 5 Sheets-Sheet 1 John C. S/onneger INVENTOR. 30

BY &%

Oct. 27, 1953 J. c. SLONNEGER 2,657,011

MEANS FOR CONTROLLING HOISTS AND WINCHES Filed April 1, 1950 5 Sheets-$heet 2 Jr r W R a: n J n m mm my 5. \8 C 3 n h 0 6 J m 3 0 9 6 8 4 5 5 5 3 2 & 9 5 J@ 6 4 o IIII uV IIII i. l 5 5 I I lllllllllll In 7 5 O 8 0 5 5 4 4 5 4 3 l= 3 v 4 5 5 MW IF; I [g C 4 Oct. 27, 1953 J. c. SLONNEGER MEANS FOR CONTROLLING HOISTS AND WINCHES 5 Sheets-Sheet 4 Filed April 1, 1950 John C S/onneger INVENTOR.

Patented Oct. 27, 1953 MEANS FOR CONTROLLING HOISTS AND WINCHES John C. Slonneger, Dallas, Tex., assignor to The Continental Supply Company, Dallas, Tex., a corporation of Delaware Application April 1, 1950, Serial No. 153,319

23 Claims. (Cl. 254-473) This invention relates to new and useful improvements in means for controlling hoists and winches.

The invention is particularly concerned with apparatus for controlling the rotation of the cable reels of well drilling rigs, and in provision for maintaining a constant rate of feed and a constant drilling load upon the drilling bit of such a rig.

One object of the invention is to provide a device of the character described includin a small motor which may be driven at various ascertainable speeds and which will regulate the paying-out of cable from a reel in accordance with such speed.

Yet another object of the invention is to provide a device of the character described which may be set to maintain a given drilling load upon a drill bit, and will maintain such load by regulating the paying-out from the cable drum of a drilling rig the cable which supports the drill bit and drill stem assembly.

A particular object of the invention is to provide an improved device of the character described having a novel anchor for the dead end of the supporting cable, in which compensation may be made for the size or diameter of the cable, and which aids in the accuracy of control effected by the entire apparatus.

A further object of the invention is to provide an improved device of the character described which is light and inexpensive in structure, but which adequately controls the heavy loads involved.

A still further object of the invention is to provide an improved device of the character described which properly controls a hoist or winch, but which allows manual or other types of control to be taken over immediately.

A construction designed to carry out the invention will be hereinafter described together with other features of the invention.

The invention will be more readily understood from a readin of the following specification and by reference to the accompanying drawings, wherein examples of theinvention are shown, and wherein:

Fig. l is a side elevational view showing schematically a drilling rig assembly having incorporated therein a control apparatus constructed in accordance with this invention,

Fig. 2 is an enlarged view of the cable reel controlling portion of the apparatus,

Fig. 3 is a schematic view of the assembly for controlling the flow of driving fluid to the control motor,

Fig. 4 is a view of a modified form of the brake lever couplin arrangement,

Fig. 5 is an enlarged view in elevation of a modified form of the driving fluid control mechanism,

Fig. 6 is a view of a modified form of the deadline anchor,

Fig. 7 is a view, partly in elevation and partly in section, of a modified form of the control motor driving connection,

Fig. 8 is a vertical, sectional view of a further modification of the driving arrangement shown in Fig. 7 and illustrating the clutch operating mechanism,

Fig. 9 is an enlarged sectional View of the hydraulic cylinder and piston coupling the control mechanism to the cable drum brake,

Fig. 10 is a vertical, sectional view taken upon the line Ill-Ill of Fig. 6,

Fig. 11 is a vertical, sectional view taken upon the line ll-l I of Fig. 6,

Fig. 12 is a plan view, partly broken away, of the dead line anchor, and

Fig. 13 is an enlarged, fragmentary, plan view of the driving arrangement shown in Fig. 8, illustrating the clutch actuating mechanism.

In the drawings, the numeral [0 designates in general a drilling rig of the type generally employed for the drilling of wells, such as oil wells. The rig is shown in a very simplified. and schematic manner for the purposes of illustration and for explanation of the mode of application or this invention.

The rig includes the usual upright derrick it having a crown block l2 at the upper end thereof, and a travelling block [3' suspended from the crown block by a plurality of strands of cable H, in the usual manner. One end of the cable I4 is secured to an anchor I 5, and the other end of the cable is reeled upon a drum I5. As the drum I6 is revolved forwardly or backwardly, the cable I4 is reeled in or payed out and the travelling block I 3 is caused to rise or fall within the derrick ll. Of course, the drill pipe (not shown) is supported from the travelling block l3 in the usual manner and carries a drilling bit upon its lower end.

In drilling operations, the cable drum It is revolved by a suitable engine or motor (not shown) to reel in the cable l4, raising the travelling block l3, and the drill pipe consequently being raised within the Well bore. The cable is payed out from the drum It simply through the action of the weight of the drill stem which pulls the travelling block l3 downwardly and draws the cable M from the drum. A suitable band brake I! is provided upon one flange of the drum l6 for controlling its movement, and the rate and degree of paying-out of the cable therefrom. This invention, in part, controls the operation of the brake IT, thereby stopping the paying-out of the cable M from the drum, or permitting unreeling of the cableat a rate which may be selected at will.

As shown in Fig. 2, a motive means such as an air motor 58, or any other suitable type of motor or engine adapted to be driven by fluid under pressure or other readily-controllable source of power, is provided adjacent the drum l6 and drives an operating shaft [9 through a suitable selective speed changer 28. The speed changer 20 may be any suitable or desirable type of device capable of varying the ratio between the speeds of rotation of the motor l8 and shaft l9,.and may be operated by a suitable gear shift or speed changer lever 2| for selecting various ratios of speeds. A telescoping splined coupling 22 is connected to the shaft i9 and couples a second operating shaft 23 to said shaft I9. This arrangement prevents rotation between the two shafts, but permits longitudinal movement of the shaft 23 with respect to the shaft l9.

A worm gear 26 or other rotatable element is mounted upon the shaft 23 and mesheswith a worm wheel 25 coupled to a suitable pulley 26. In turn, the pulley 2B is connected by a driving belt 21 to a pulley 28 mounted upon and rotating with the cable drum or reel IS; The worm wheel 25 is connected to the pulley 25 through a suitable ratchet mechanism 28', whereby rotation of the pulley 2c in a clockwise direction, as viewed in Fig. 2, is transmitted to the worm wheel 25, but rotation of the pulley in the opposite or counter-clockwise direction is unimpeded, Other rotatable elements and connections may be employed in this portion of the apparatus for accomplishing the same function. The described coupling has been found most desirable.

The shaft 23 is extended beyond the worm gear 24, being supported in a suitable bearing 29 and having its outer end 30 terminating adjacent an arm 3| or other actuating means secured to the brake-operating handle 32. With this arrangement, longitudinal movement of the shaft 23 to the left, as viewed in Fig. 2, causes the arm 3| to swing counter-clockwise and tighten the brake band I1 upon the periphery of the cable reel 16. Such tightening of the brake band slows or stops the revolution of the cable reel according to the degree of force applied to the lever 3| by said shaft 23.

In the operation of this portion of the invention, assuming that it is desired to take up or reel in cable onto the drum IS, the ordinary driving machinery is employed for this purpose to revolve the drum in a counter-clockwise direction, as viewed in Fig. 2. When this occurs, the

pulleys

28 and 26 are also driven in a counterclockwise direction, but the ratchet mechanism 28' permits the worm wheel 25 to remain at rest or to revolve slowly. When it is desiredto pay out or unreel cable from the drum, however, the latter is revolved in a clockwise direction, revolving the

pulleys

28 and 25 in a clockwise direction and resulting in clockwise revolution of the worm wheel 25. Such revolution of the worm wheel causes the wormgear 24 to move to the left, forcing the end 30 of the shaft 23 against the lever or arm 3|, tightening the brake I! and slowing or stopping the reel I6. In this condition of the apparatus, the motor l8 may be employed to regulate the speed of revolution of the drum It, in that the motor may be driven at a desired speed, and by means of the speed changer 2d, the shafts Is and 23 will also be driven at a selected or desired speed. This speed of revolution of the shaft 2% creates a selected speed of revolution of the worm wheel 25, and provides for a certain speed of revolution of the

pulleys

26 and 28 along with the drum it. If the drum tends to revolve too slowly, the worm gear 24 will be revolved too rapidly by the motor E8 in relation to the speed of revolution of the worm wheel 25, and will tend to move to the right, as viewed in Fig. 2. Such movement shifts the shaft 23 to the right and releases the brake i 1, thereby allowing the drum iii to increase its speed of revolution. Should the drum tend to overspeed and unreel cable too rapidly, the worm wheel 25 will be driven too rapidly in the relationship to the speed of revolution of the worm gear 24, and the worm gear along with the shaft 23 will be shifted to the left, tightening the brake band I? and slowing down the cable reel Hi. It is to be noted that the motor l8 does not drive or revolve the drum it, but merely serves as a means for revolving the shaft 23 and the worm gear 24, at a selected speed. The drum i6 is revolved by suitable engines or motors, or by the weight of the drill stem carried by the cable M, and in turn, drives the

pulleys

28 and 28 and the worm whee 25. According to whether the worm wheel 25 is being revolved too rapidly or too slowly, the worm 2d and shaft 23 will be shifted to the left or to the right to increase or decrease the tension upon the brake band H and bring the speed of revolution of the cable drum to the proper value. Of course, the longitudinal shifting of the shaft 23 is made possible by the splined coupling 22 without requiring corresponding shifting of the shaft i9, and at the same time, the coupling effectively transmits rotative motion between the two shafts.

It is obvious that the relative pitches of the worm 2d and the worm wheel 25 may be of any selected value, and, with proper design, will eliminate any possibility of the worm being driven by the worm wheel. Thus, no matter how great the load upon the cable l4 may be, the

a worm 2 may be driven with a small source of power and will control the feeding out of cable from the drum without being susceptible to driving by the drum. The maximum load placed upon the driving motor 38 does not exceed that necessary to overcome the friction of the system and to permit a braking force to be applied to the brake band IT. The actual braking is done by rotation of the cable drum, and the need for heavy or cumbersome equipment is therefore eliminated. This point is emphasized by the fact that rotation of the cable drum will apply the brake even when no energy is being supplied to the driving motor. Actually, the brake is applied by the cable drum and merely released by the motor.

Itv is not always possible or preferable to arrange the elements precisely as shown in Fig. 2, and it is sometimes not desirable to place the worm and worm wheel mechanism upon the same side of the cable drum as the brake band 17. A modification is shown in Fig. 4, in which the shaft 23 carries at its outer end a hydraulic piston 33 enclosed within a hydraulic cylinder 35. A similar hydraulic piston 35, enclosed in a hydraulic cylinder 36, is adapted to have its piston rod 37 engage the arm 3| of the cable reel brake band handle 32. A suitable hydraulic fluid conductor 38 extends between the

cylinders

34 and 36 so that longitudinal movement of the shaft 23 and piston 33 is reflected in similar longitudinal movement of the piston 35 and the piston rod 31. The utilization of the hydraulic fluid conductor 39 permits the location of the two cylinders at remote points, whereby the operating shaft 23 need not be alined with the brake handle arm3l, as shown in Fig. 2.

As hereinbefore stated, any suitable source of motive fluid under pressure or other power supply may be employed for driving the motor 18, and any suitable means may be employed for regulating the supply of power to the motor so as to control the speed of operation thereof. A preferred embodiment of the invention, however, includes a source of compressed air 39, as shown in Fig. 3, connected through a valve 46 to a header or manifold ii. A second header or manifold 42 is connected to the manifold 41 through a plurality of short conductors 43, each conductor having therein an orifice valve 4 1. The apertures of the valves 44 are of diifering values, and by opening different ones of said valves or different groups of said valves, fluid under pressure may be supplied at various rates to the header 42 from the header 4|. In this manner, an initial control of the volume of mo tive fluid is provided.

A first conductor 45 is connected into the manifold 42 and extends through a shut-off valve 46 to a supply pipe 41 leading to the motor [8. By opening the valve 46, driving fluid is supplied directly to the motor 18 through the valve 44, and the speed of revolution of the motor !8 will be controlled and regulated in accordance with the opening of one or more of the orifice valves 44. For automatic control of the motor I8, a second conductor 48 leads from the manifold 42 to a hydraulically operated valve 49. The valve includes a housing 59 having therein a sliding valve 5| of the piston type, and having a hy-- draulie piston 52 operatively connected to said valve. The conductor 43 is connected into one side wall of the housing 56, and a similar conductor 53 extends from the opposite wall of the housing to the pipe 4?. Longitudinal shifting of the valve 5! within the housing shuts oif, restricts, or regulates the flow of fluid from the conductor 48 to the conductor 53 in the manner customary in this type of valve. An adjustable spring 54 is provided within the housing for applying a load to the valve structure in opposition to the force exerted upon the piston 52 by the hydraulic fluid.

For applying pressure to the piston 52, the load upon the dead end of the cable I4 is employed. As illustrated in Fig. 1, the dead end of the cable carries a clevis 55 which is pivotally connected to the intermediate portion of an arm 56 anchored to the derrick structure and adapted to swing in a vertical arc thereabove. The outer end of the arm 56 bears upon the lower end of the piston rod 5'! of a piston 58 confined within a hydraulic cylinder 59. A suitable conductor 6!: extends between the cylinder 59 and the housing 58, and a body of hydraulic fluid or liquid 6! transmits force from the piston 58 to the piston 52.

With this arrangement, and when the valve 46 is closed, the operation of the motor 18 may be regulated in accordance with the load exerted upon the dead end portion of the cable l4, and it is possible to maintain a constant drilling load upon a drill bit suspended from the travelling block I3 by means of the drill stem. It is customary to support part of the weight of the drill stem from the travelling block, and to allow part of said weight to bear against the drill bit to urge the same into the formation being drilled. Obviously, as the drill is rotated and feeds downwardly into the formation, cable must be payed out from the drum IE to maintain the load upon the bit at a constant value. The present inven" tion accomplishes this function by regulating the speed of rotation of the motor I8 in accordance with the load exerted upon the dead end of the cable M.

In the event the drum I6 is paying out cable too rapidly so as to apply an excessive portion of the weight of the drill stem as a load upon the drill bit, the load upon the dead end of the cable it will be decreased, and the spring 54 will tend to move the valve 5i to the right, as viewed in Fig. 3, shifting the piston 52 to the right and moving the piston 58 downwardly. As this occurs, the valve moves from the wide open position, shown in Fig. 3, to a partially closed position wherein the outlet from the conductor 48 is restricted, and the flow of motive or driving fluid to the motor through the

conductors

53 and 41 is diminished. The motor is thus caused to revolve at a slower speed, and the overspeeding of the drum It shifts the worm 2t and the operating rod 23 to the left against the brake arm 3! so that the brake band 57 is tightened and the drum IE is slowed down. Similarly, if the drum I5 is rotating too slowly, the drill bit will dig faster than cable is payed out whereby the drilling load upon the bit will be reduced and the load upon the dead end of the cable 54 will be increased. This increasing of the load upon the cable swings the arm 55 upwardly, forcing the piston 58 upwardly and the piston 52 toward the left and reduces the restriction of the corn ductor 48 by thevalve 5!. The flow of motive fluid to the motor I 8 is therefore increased as the regulating valve 49 opens, whereby the motor will be speeded up, resulting in releasing of the brake band H to a point at which the drum l6 revolves at the proper speed and pays out the cable M at the proper rate.

It is obvious that the force exerted by the spring 54 may be adjusted by means of the screwthreaded follower 62 to compensate for the varying weight of the drill stem as sections of pipe are added thereto or removed therefrom, and that a substantially constant drilling load upon the drill bit may be obtained in the manner described. At any time, the valve 46 may be opened and the valves 44 regulated to provide any desired speed of revolution of t e drum l6. Similarly, the revolution of the drum it may be reversed at any time so as to reel in cable or to assume the weight of any sudden load placed upon the travelling bloc i3.

A more detailed and specific embodiment of the invention is shown in Figs. 5 through 10 of the drawings. In Fig. 5, is illustrated the preferred form of control mechanism for regulating the flow of motive fluid to the speed regulating motor. This control apparatus includes a rectangular housing 63 adapted to be mounted upon a suitable support or standard 64 and positioned at a convenient opera-ting height adjacent the floor of the derrick or drilling rig structure. The housing includes a longitudinal horizontal partition 65 carrying a pair of posts 66 upon which a weight or scale beam 61 is mounted by means of a suitable knife edge 08. The usual large and small weights 69 and I0, respectively, are longitudinally slidable upon individual arms II and I2, respectively, of the scale beam 61, and indicating scales I are provided for designating the weight or load being exerted by the scale beam. An indicating finger or tang I4 projects from the end of the scale beam and is confined between a pin I5 carried upon upright supports 10, and a moveable keeper TI pivoted upon the supports i6. At the opposite end of the scale beam, the customary counterbalance weight I8 is provided, along with an adjustable balancing or zeroing weight "IS.

A second pair of posts 330 project downwardly from the partition 65 adjacent its central portion, and an elongate weight lever BI has its fulcrum or knife edge 82 bearing upwardly against the posts 80. The long arm or" the weight lever 81 is operatively connected to the scale beam 61 by an adjustable link 83, and the short arm of the weight lever 85 is provided with knife edges 84 bearing against the upper end of a yoke 85 con nected to the upper end of a piston rod 86. The rod 06 extends into a diaphragm housing 87 and is connected therein to a suitable flexible diaphragm 83.

The weight and beam structure which has been described takes the place of the adjustable spring 54, previously described, and provides a means for placing a selected and exact load acting downwardly upon the diaphragm 88. For opposing this load, a suitable hydraulic fluid conductor 89 is connected into the lower portion of the housing El and places the housing into communication with a source of hydraulic fluid to be described hereinafter, and which exists under a pressure proportional to the load upon the dead end of the cable I4. With this arrangement, as the pressure exerted by the hydraulic fluid upon the under side of the diaphragm 38 is less than or is greater than the load exerted by means of the piston rod 88, the weight lever 0| will be caused to swing clockwise and counter-clockwise, and may be employed for controlling the rate of flow of iiuid to the previously-described fluid motor.

A control valve 9%, is mounted in one end of the housing 63 beneath the partition 65, substantially in vertical alinement with the adjustable link 83. The valve includes a cylindrical housing 9i having therein a cylindrical liner 92 provided with valve ports 93 and 04. A piston type valve core 95 has a sliding fit within the liner 92, and has its upper end secured to a flanged cap 95 which fits loosely over the open upper end of the housing St. A substantially L-shaped arm 97 is pivoted to the long arm of the weight lever 8i, and is constantly urged toward said lever by a suitable spring 92. A set or stop screw 99 limits the swinging of the arm 9'! and provides for radial adjustment of the spring. The arm is connected to the valve core 95 by means of a flexible wire I00 of sufficient strength as not to stretch when a tension is applied thereto, but which is sufficiently flexible as to bend under compression when the arm 9? is swung downwardly. Since the outer end of the lever 8i swings in an are rather than in a straight line, and since the valve 95 must move rectilinearly, the flexible wire I00 is employed to eliminate the need for guides and. pivoted joints in the connection between the weight lever and the valve core.

Motive fluid under pressure is supplied to the device through a pipe I0! connected through a plug valve I02 to a pipe T I03. One branch of 8. the T I03 is connected into the valve port 93, and a suitable conductor I04 leads from the other valve port 94 to a pipe T I05. A bypass pipe I06 is provided with a shut-off valve I01 and extends between the Ts I03 and I05 for bypassing the valve 90, when such is desired. A header I03, equivalent to the header 4l, is connected into the T I05, and is provided with a plurality of branch conductors i09 carrying drilled orifices H0 and shut-off valves III. The lower ends of the conductors I09 are connected into a header IIZ, equivalent to the header 42, and a conductor I I3 leads from the latter header or manifold to the fluid motor I8.

As stated hereinbefore, the pressure exerted upon the under side or" the diaphragm 88 will vary from time to time whereby the weight arm 8| will be allowed to swing clockwise or counterclockwise. When the pressure exerted on the underside of the diaphragm is low, as occurs when too much weight is being applied to the drilling bit, the lever 3i swings clockwise which raises the valves core 95, shutting off or restricting the port 94. When this occurs, the flow of fluid through the valve to the headers and the supply pipe H3 is restricted or reduced, with the result that the revolution of the cable drum I6 is slowed down, and a portion of the weight or load is removed from the drilling bit. Conversely, if the bit is underloaded and the pressure upon the diaphragm 8i) is high, the lever 81 swings counterclockwise, exposing the port 93 an additional amount and permitting a greater flow of fluid and faster revolution of the cable drum. For convenience in operation, the valves I07 and Iii are provided with suitable operating handles or levers H4, and a pressure gauge I I5 is connected into the conductor 89 for indicating the pressure being exerted therein. In accordance with the previous description of the invention, the orifice plates lit are of various and different sizes, and opening or one or more of the valves III results in varying rates of flow of the motive fluid to the motor it. When desired, the valve I0! may be opened to bypass the control valve t0 and permit the revolving of the cable drum It at any desired or selected speed.

A preferred embodiment of the cable anchor is shown in Figs. 6, 10, 11 and 12. The anchor includes a base plate or support lit, adapted to be anchored suitably adjacent the derrick floor or the ground surface, and having a pair of upstanding side plates I ii. The plates I i? are generally triangular in shape and having extensions lie of reduced cross-section extending outwardly of the base plate 5 it. A plate i i9 is connected between the extension lit and joins the two together. A pair of cheek plates I23 are pivoted adjacent one vertical edge or" the plates II! upon a transverse shaft H9 and have their free ends projecting beneath the extensions Iiii. Between the plates I2 l a relatively narrow flanged reel I2I is rotatably mounted and receives a number of turns of the dead end pcrtion of the cable It. A clamp I22 secures the projecting portion of the cable to the cheek plates, and provides an anchor for said cable.

In order to permit rotation of the reel I2! when such is desired, but to hold the reel immovable with respect to the cheek plates at other times, the reel carries a plurality of transverse openings I23 adapted to be alined with openings I2 5 in the cheek plates and to receive a cotter or looking pin I25 passed through the openings I24. Enlarged openings i261 in the side plates III facilitate insertion and removal of the pin. When the pin I25 is in place, the reel and cheek plates move together as a unit, but because of their small amplitude of movement, there is no engagement between the pin and the walls of the opening I25.

A hydraulic cylinder I28 is disposed vertically between the extensions II8 adjacent the plate I I9 and is adjustably secured thereto by bolts I29 engaging in slotted openings I35 formed in lateral ribs I3I projecting from said extensions. A hydraulic piston I32 is carried within the cylinder I28 and has a piston rod I32 projecting downwardly into engagement with a plate I20 carried upon the upper edges of the cheek plates In use, the dead end of the cable I4 is received tangentially by the reel 2I and is passed therearound several times, the projecting end of the cable being secured in the clamp I22. Any upward stress or load upon the cable I4 thus tends to swing the reel and the cheek plates upwardly, as viewed in Fig. 6, and to swing the plate I20 upwardly, forcing the piston I32 upwardly within the cylinder I28. In this manner, the load placed upon the cable is reflected as the pressure exerted by the piston I32 upon the hydraulic fluid within the cylinder I28, this pressure being communicated through the conductor 35, which is connected into the upper end of the cylinder, to the underside of the diaphragm 38 in the weight control structure shown in Fig. 5.

It is to be noted that the distance between the shaft II9, which is the center about which the cheek plates I20 are pivoted upon the side plates H1, and the center of the cable I4 is much less than the distance between the shaft and the point of engagement on the piston rod I32. With thi arrangement, a considerable mechanical advantage is had, and both the dimensions of the cylinder I28 and the pressures within the cylinder are kept within reasonable limits. At the same time, the cylinder may be adjusted toward or away from the shaft M9 by means of the bolts I29 and slotted openings I38, and compensation made for the use of cables of various diameters. Since the effective lever arm between the shaft H9 and the cable I4 is viewed as extending from the center of the shaft to the axial center of said cable, provision is desirably made for adjusting the anchor mechanism in accordance with the diameter of cable in use. With this structure described, as cables of various sizes are employed, the cylinder I 23 may be shifted toward or away from the shaft I I9 to make proper compensation for the difference in cable diameter.

A preferred embodiment of the worm wheel and worm gear structure is shown in Fig. 7, including a speed changing device I33, having a drive shaft I 34 to which is connected the fluid motor IB (not shown in this figure). A splined operating shaft I35 extends from the speed changer I33 into a gear housing I35 within which the worm wheel I31 and the worm gear I33 are mounted. The worm gear I351! is secured upon the splined shaft I 35, which is movable longitudinally with respect to the speed changer. The gear, therefore, may not revolve on the shaft, but the entire gear and shaft structure may shift longitudinally. A toothed ratchet wheel I 39 is disposed centrally of the worm wheel I31, and is provided with ratchets I45 having leaf or drag springs I4I thereon. An operating shaft I42 projects from the worm gear I38 and extends into a lateral housing I43 projecting from the housing I36. A hydraulic piston I44 is provided within the housing I43 upon the outer end of the shaft I42, an enlarged View of this structure being shown in Fig. 9 of the drawings. In the latter view, the piston I44 is shown as being hollow and substantially cylindrical, and as being connected to the shaft I42 by a suitable thrust bearing I 45. A cap I46 forms the outer end of the housing I43 and encloses the outer end of the piston I44. As shown, both the housing and the cap are flanged at their point of joining and a domed diaphragm member I41 has its outer marginal edge or periphery I48 clamped. and secured between the abutting faces of the cap and the housing. The central portion of the diaphragm is secured upon the face of the piston I44 by a plate I 49 and bolts I50. As shown, the clearance between the piston and the housing and cap is sufficient to permit doubling of the diaphragm structure, whereby an effective sealing is obtained without the employment of piston rings or similar structures which are subject to leakage. The diaphragm structure may roll upon itself as the piston moves from the position shown in Fig. 9 to the position shown in Fig. 7, and a complete seal is maintained at all times. The hydraulic fluid conductor 38 (shown in Fig. 4) is connected into the outer end of the cap I45 and leads to the cylinder 36 and the piston 35 for operating the brake band I1.

It is often desirable to disconnect thi entire control mechanism from the cable drum I5, and a structure for this purpose is shown in Fig. 8 of the drawings. In this modification, the worm gear I33 and the worm wheel I31 are mounted within the housing I36 in the manner illustrated in Fig. 7, and an operating shaft I 5| projects through the side walls of the housing. The worm wheel I3! is rotatably mounted upon the shaft I5I by means of bearings I52, the shaft, in turn, being journalled in the walls of the housing upon bearings I53. Suitable oil seals I54 are provided to prevent oil leakage through the side walls of the housing around the shaft. A spline clutch I55 is keyed upon the shaft I5I and is adapted to engage a splined collar I56 formed integrally with the ratchet wheel I39. In the position of the elements shown in Fig. 8, the clutch is disengaged and the shaft I5I may turn independently of the ratchet wheel I39 and of the worm wheel I3l. Upon shifting to the left, however, the clutch I55 engages the splined collar I56 and locks the elements against rotation with respect to one another.

A hydraulic or air pressure operated means is provided for shifting the clutch to and from its operating position, and includes a double-acting piston I51 engaging within a pair of opposed cylinders I58 carried upon the top wall of the housing I 36. A link I59 connects the piston to an arm I60 which revolves a shaft I6I extending down one face of the housing I35 and carrying a suitable gear wheel I62 at its lower end. The gear wheel I62 meshes with a gear rack I63 which is reciprocally mounted within the wall of the housing I36 and the inner end of which has engagement with the clutch I 55. Transverse shifting of the piston I54 in accordance with the admission of fluid under pressure to one of the cylinders I58 causes swinging of the arm I63, rotation of the shaft 55!, and reciprocal movement of the gear rack I 52. In this manner, the clutch I55 is moved into and out of engagement with the splined collar I56 so as to place the control de- 1 l vice in operative or inoperative connection with the cable drum Hi.

In the use of the peferred embodiment of the invention herein described, the cable drum may be run at any desired speed, or it may be set by adjustment of the weights 59 and "it to place any desired load on the drill bit and to maintain such loading at a constant value.

The advantages and benefits flowing from the invention herein disclosed are manifold and involve many important factors in safety and ease of operation. As pointed out hereinbefore, the operating and control mechanism is subjected only to light loads of a frictional nature, and. hence the elements of the system may be made quite small and relatively inexpensive. This permite the various elements of' the device to be fabricated with high safety factors without involving expensive and heavy parts, thereby considerably reducing the probability of mechanical failure within the device. Nevertheless, should some mechanical failure occur, so as to stop the motor it or interrupt the flow of motive fluid under pressure flowing thereto, the motor will simply stop, thereby applying the brake and terminating the feed-oil or payout of cable from the reel It. In some existing devices using direct electrical control, hydraulic control, or electrically actuated brakes, a power failure will permit the paying-out of cable and so increase the load upon the drill bit so quickly that the drill pipe is twisted off before the operator can seize control of the drilling mechanism. In the present invention, the customary cable reel brake is employed for control of the cable drum or reel, and since the brake is already present and is designed to handle in an adequate fashion the loads and forces involved, the present invention does not require the provision of additional braking or control devices of sufiicient massiveness and strength as to be capable of handling the heavy loads involved.

A further very important feature of the invention lies in the fact that the operator can instantly take over control of the drilling machine. It is only necessary to operate the brake lever by hand to take over the control, and there is no necessity of manipulating clutches, switches, valves, and the like to disengage the automatic control before taking over manual control. Indeed, if hoisting is required, the hoisting rig clutch may be engaged at once without stopping or altering the operation of the control device since the brake will be instantly released as soon as the cable drum begins to rotate to take in cable.

Under emergency conditions, a few seconds delay in operation or manipulation of the drilling machinery may cause heavy damage, and no delay is encountered through use of the present invention.

It is further to be noted that so long as the automatic control device is in operation, there will be established a maximum rate of cable payout. Thus, should the drill bit .or the drill stem suddenly break through into a void in the forma tion, dropping of the bit and the drill string will be prevented since the brake will instantly take hold and prevent such dropping. This is very important, especially in deep drilling where many tons of drill pipe are involved. Such large mass need only be dropped a small distance to do enormous damage. This control of maximum rate of feed-out is also important in reaming operations. In such cases, the entire load of the drill stem must be suspended from the drilling machinery, and the present device provides adequate control and regulation of such an operation.

Fhebwpass valves 45 and I9? are of great value when controlled rapid shifting from upward to downward movement of the drill stem and from downward to upward movement thereof, are required, such a in fishing operations. The hoisting mechanism cannot get out of control when the present device is being employed, and very rapid shifting is facilitated by the ease of engagement and disengagement of the control mechanism with the drilling machine.

As pointed out hereinbefore, the adjustable mounting of the hydraulic cylinder I28 provides for compensation of the control device in accord ance with the size cable being employed. This adjustableness of the cylinder also is of importance permitting exact calibration of the structure to permit direct reading from the scale 53 of the actual load upon the travelling block l3. In practice, the scale 13 is removable, and a plurality of such scales are provided in accordance with the number of lengths of cable from which the travelling block is suspended. After the proper scale has been attached, the empty travelling block hook may be balanced to zero upon the scale and then a known weight lifted by said hook. If the scale fails to balance at the setting of that known weight on the beam, the cylinder on the deadline anchor is shifted and adjusted by trial until the reading on the scale when balanced corresponds with the known weight. Accurate calibration of the'clevice and adjustment thereof to a proper reading is thereby permitted and facilitated.

The foregoing description of the invention is explanatory thereof and various changes in the size, shape and materials, as well as in the details of the illustrated construction may be made, within the scope of the appended claims, with out departing from the spirit of the invention.

What I claim and desire to secure by Letters Patent is:

1. Control apparatus for cable drums including, driving means, an element driven by said driving means, a second element adapted to be driven by the cable drum, a connection between the first and second elements, a support for the first element, the latter element being movable longitudinally of the support with respect to the second element, brake means for the cable drum, and a force-transmittmg connection between the brake means and the first element whereby force for tightening the brake means is supplied by the cable drum through the connection between the first and second elements and through the forcetransmitting connection to the brake means.

2. Control apparatus for cable drums inoluding, driving means, a longitudinall shiftable worm gear driven by the driving means, a second gear adapted to be driven by the cable drum meshing with the worm gear, brake means for the cable drum, and a force-transmitting connection between the brake means and the worm gear whereby force for tightening the brake means is supplied by the cable drum through the worm gear and the second gear and through the force-transmitting connection to the brake means.

3. Control apparatus for cable drums including, driving'means, an element driven by said driving means, a second element adapted to be driven b the cable drum, an operating connection between the elements, the first element being shiftable with respect to the second element,

brake means for the cable drum, and'a movement-transmitting connection between the brake means and the first element for transmitting movement of the first element to the brake means, whereby movement and force to tighten the brake means is supplied from the cable drum through the connection between the first and second elements and through the movement-transmitting connection to the brake means.

4:. A control apparatus for cable drums including, driving means, an element revolved by said driving means, a second element adapted to be revolved by the cable drum, 2, driving connection between the elements, a support for the first element permitting shifting of the latter with respect to the second element, brake means for the cable drum, and a movement-transmitting connection between the brake means and the first element for transmitting movement of the first element to the brake means, whereby movement and force to tighten the brake means is supplied from the cable drum through the connection between the first and second elements and through the movement-transmitting connection to the brake means.

5. Control apparatus as set forth in claim 4, and means for regulating the driving means.

5. Control apparatus as set forth in claim 4, and a splined connection between the driving means and the first element.

7. Control apparatus for drilling equipment having a hoisting cable carried by a cable drum and an anchor for the dead end of the cable, including, a driving motor adapted to be driven by fluid under pressure, a pressure fiuid conductor leading to the motor, a metering valve in said conductor, operating means for the valve connected to the anchor, a coupling between the motor and the cable drum, brake means for the cable drum, and actuating means for the brake means connected to said coupling.

8. Control apparatus for drilling equipment having a hoisting cable carried by a cable drum an anchor for the dead end of the cable, including, a driving motor adapted to be driven by fluid under pressure, a pressure fluid conductor leading to the motor, a metering valve in said conductor, operating means for the valve conneoted to the anchor, a coupling between the motor and the cable drum, brake means for the cable drum, and hydraulic actuating means for the brake means connected to said coupling.

9. Control apparatus as set forth in claim 7, wherein the coupling between the motor and the cable drum includes, an element revolved by the motor, a second element revolved by the cable a drivin connection between the elements, and a support for the first element permitting shifting of the latter with respect to the second element, the actuating means for the brake means being operated by the shifting of said first element.

19. Control apparatus as set forth in claim 7, wherein the coupling between the motor and the cable drum includes, a longitudinally-shiftable operating shaft driven by the motor and operating the brake actuating means, a worm gear on the shaft, and a worm wheel meshing with the worm gear adapted to be driven by the cable drum.

11. Control apparatus as set forth in claim 10, wherein. the coupling between the motor and the cable drum includes, a first shaft driven by the motor, a second longitudinally-shiftable shaft splined to the first shaft and operating the brake actuating means, a worm gear on the second shaft, and a worm wheel meshing with the worm gear adapted to be driven by the cable drum.

12. Control apparatus as set forth in claim 7, wherein the coupling between the motor and the cable drum includes, a speed changer driven by the motor, a first shaft driven by the speed changer, a worm gear, splines connecting the worm gear with the first shaft, a worm wheel meshing with the worm gear, a ratchet for connecting the worm wheel with the cable drum, and means connected with the worm gear for operating the brake actuating means.

13. Control apparatus as set forth in claim '7, wherein the anchor for the dead end of the cable includes, a support, a reel structure pivotally mounted on the support, means on the reel for securing the dead end of the cable thereto, a hydraulic cylinder carried by the support, and a piston in the cylinder having a piston rod, said rod being adapted to be actuated by the reel, and said cylinder being adjustable on the support toward and away from the pivotal center of the reel, the piston and cylinder comprising the op erating means for the metering valve.

14. Control apparatus as set forth in claim 7, wherein the anchor for the dead end of the cable includes, a support, a reel structure receiving the cable tangentially, means on the reel for securing the cable thereto, said reel being eccentrically mounted for revolution upon the support about a center closely adjacent the point of tangency of the cable to said reel, the reel and support forming the two main elements of the anchor, a hydraulic cylinder carried by one of said main elements, and a piston in the cylinder having a piston rod engaging the other of said main elements, the point of engagement of the piston rod being relatively remote from the center of revolution of the reel, the piston and cylinder con prising the operating means for the metering valve.

15. Control apparatus as set forth in claim '7, wherein the anchor for the dead end of the cable includes, a support, a reel structure pivotally mounted on the support, means on the reel for securing the dead end of the cable thereto, the reel and the support forming the two main elements of the anchor, a hydraulic cylinder carried by one of said main elements, and pressureexerting means in. the cylinder having an operating stem engaging the other of said main elements, said operating stem being adjustable toward and away from the pivotal center of the reel, the pressure exerting means and the cylinder comprising the operating means for the metering Valve.

16. Control apparatus as set forth in claim 7, wherein the anchor for the dead end of the cable includes, a fixed support, a movable support pivotally mounted upon the fixed support, a reel pivotally mounted upon the movable support, said reel receiving the cable tangentially, means for securing the reel against rotation with respect to the movable support, means on the movable support for securing the dead end of the cable, and pressure-indicating means associated with the movable and the fixed supports.

17. Control apparatus as set forth in claim 16, wherein the reel securing means includes a pin engageable with the movable support, the reel having a plurality of transverse openings adapted to receive said pin in a plurality of positions of the reel with respect to the movable support.

18. A control apparatus for cable drums ini5 cluding, driving means, an element revolved by said driving means, a second element adapted to be revolved by the cable drum, a' driving connection between the elements, a support for the first element permitting shifting of the latter with respect to the second element, brake means for the cable drum, actuating means for the brake means connected to the first element and operated by shifting thereof, and a ratchet connection between the cable drum and the second element.

19. A control apparatus for cable drums including, driving means, an element revolved by said driving means, a second element adapted to be revolved by the cable drum, a driving connection between the elements, a support for the first element permitting shifting of the latter with respect to the second element, brake means for the cable drum, actuating means for the brake means connected to the first. element and operated by shifting thereof, and control means for regulating the driving means including, a source of fiuid under pressure for operating the driving means, a pressure fluid conductor between said source and the driving means, and adjustable valve means in said conductor.

20. A control apparatus for cable drums including, driving means, an element revolved by said driving means, a second element adapted to be revolved by the cable drum, a driving connection between the elements, a support for the first element permitting shifting of the latter with respect to the second element, brake means for the cable drum, actuating means for the brake means connected to the first element and operated by shifting thereof, and control means for regulating the driving means including, a source of fluid under pressure for operating the driving means, a pressure fluid conductor between said source and the driving means, and a metering valve in said conductor.

21. Control apparatus for cable drums including, driving means operable at a selected speed, brake means for the cable drum arranged to be applied and released to maintain the speed of revolution of the drum at a predetermined ratio with respect to the speed of operation of the driving means, a motion-transmitting connection between the driving means and the cable drum, said connection including an element having a normal position occupied when the cable drum and the driving means are operating at the predetermined ratio, said element being mounted for shifting from its normal position when the relative speeds of operation of the cable drum and the driving means vary from said predetermined ratio, an actuating connection between said element and the brake for applying and releasing the brake means in accordance with the shifting of the element, and means for controlling the speed of operation of the driving means.

22. Control apparatus for cable drums including, brake means for the cable drum, driving means operable at a selected speed, a motion transm'tting connection between the driving means and the cable drum and having an element arranged to shift position when the speed of operation of the cable drum varies from a predetermined ratio with respect to the speed of operation of the driving means, the brake means being applied and released by the position shifting of said element, and means for controlling the speed of operation of the driving means.

23. A control apparatus as set forth in claim 22, a weight-responsive means responsive to the load sustained by the cable drum, and an operating connection between said weight-responsive means and the speed-controlling means for the driving means for maintaining a predetermined load on the cable drum.

JOHN C. SLONNEGER.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 1,779,480 Loomis Oct. 28, 1930 1,779,656 Brauer Oct. 28, 1930 1,954,176 Johnson Apr. 10, 1934 FOREIGN PATENTS Number Country Date 305,939 Great Britain Feb. 11, 1929 647,491 Germany July 6, 1937