US3592570A

US3592570A - Reversible fluid-driven motor

Info

Publication number: US3592570A
Application number: US52262A
Authority: US
Inventors: Josef Bartos
Original assignee: Abegg and Reinhold Co
Current assignee: Varco International Inc; Abegg and Reinhold Co
Priority date: 1970-07-06
Filing date: 1970-07-06
Publication date: 1971-07-13
Anticipated expiration: 1988-07-13

Abstract

A reversible fluid-driven motor having two selectively usable fluid inlet passages for introducing pressure fluid to the motor to drive it in two opposite directions, with each passage being vented to atmosphere during periods when fluid is being admitted to the motor through the other passage, and with two valve units being provided between a source of pressure fluid and the two passages respectively and each operable automatically when pressure fluid is supplied thereto to close off a vent to atmosphere from the associated passage.

Description

United States Patent |72, inventor Josef Blrt 389,328 Sleigh. 4 Iii/181 Auhein,n{. 468,198 Graham4 418/2411 121| Appl No. 52.262 2.360.430 Leur 4 n i 4 l B/i 11h [22| Film 10|! 6,1970 2.382,59l Warren .n Hl-164 1451 Paimed July 13. 1971 2,507,151 Gnbricl i. ils/1x@ |73] Assignee Abeggnnd Reinhoid Co. 3.381.584 Banus. i. 418/248 L AngekmCnHl. 3,461,974 Banus 173/3 'I Division of ber. \o. 787,! IJ. Der. -6. |968 Primary mmn" clmon R. Croyle Assistant Examiner-Wilbur J. Goodlin Attorney-William P. Green |541 REVERSIBLE FLUID-DRIVEN MOTOR 7 Claims, l5 Drawing Fig;

[S2] U.S.Cl i. 4l8/l86 9|464 H3/243 ABSTRACT: A reversible fluid-driven motor having twv lll. CL...................................................... Iegygly ugablc inlgi passages for inugducing Pfcggurc l I ddd sa@ H3/I8@ fluid to the motor to drive i1 in two opposite directions` wiih 243. 244. 24S. 246. 247, 24B. 249. 250, 25 l. 270; each passage being vented lo atmosphere during periods when 41713 I S. S18; 9U464. 469 nuid is being admitted to the motor through the other passage. and with two valve units being provided between a source of '56] keknnm cud pressure fluid and the two passages respcclivciy and cach UNITED STATES PATENTS operable automatically when pressure Huid is supplied therein 38 I ,287 411888 Snevely Y. 418/!86 to close offa vent lo atmosphere from lhe associated passage.

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PATENTEB JUL 1 3 |971 SHEET 3 UF 4 dom www o@ mm MQN PATENTED JUL 1 a lan SHEET 0F 4 J1 WOL INVENTUR. Josef: .Bae ros (/g L Toreuav REVERSIBLE FLUID-DRIVI'IN MOTOR CROSS REFERENCES TO RELATED APPLICATIONS This application is a division of my prior copending application U.S. Pat. Ser. No. 787,1 I3, filed Dec. 26, 1968 on Vane Type Rotary Fluid Handling Mechanism," which in turn was a division of and copending with my prior U.S. Pat. application Ser. No. 648,913, filed .lune 26, 1967 on Spinner Device For Turning Well Pipe or the Like, now U.S. Pat. No. 3,461,974. Certain features of thc apparatus ofthe present invention have been disclosed and claimed in my U.S. Pat. No. 3,381,584, issued May 7, 1968 on Vane Type Rotary Device."

BACKG ROU ND OF THE INVENTION This invention relates to fluid-driven motors ola reversible type adapted to be driven rotativcly in either of two opposite directions, and preferably also of the vane type in which one or more vanes define a compartment or compartments which change in size as the motor turns.

In devising a reversible rotary fluid-driven motor, it is frequently relatively difficult to provide completely effective and yet structurally simple valving means for controlling the flow of pressure fluid to and from the motor in its two different direction conditions, and also in a stopped condition. This is particularly true in situations where the motor is to be controlled remotely, and especially where the volume of air or other pressure fluid required to drive the motor is relatively large. Particularly difficult under those conditions is the maintenance of positive and reliable fluid seals in the valving structure under all conditions of the motor.

SUMMARY OF THE INVENTION The present invention teaches an improved valving arrangement for attaining the above discussed purpose of controlling the flow ofpressure fluid to and from a reversible fluid motor. For this purpose, l provide means which are capable of introducing pressure fluid selectively into either of two different inlets, to drive the motor in its two opposite directions respectively, with the inactive one ofthe inlets serving as an outlet passage. In each of the inlet lines, there is provided a unique valve unit which is automatically actuable from a fluid discharging condition to a position for closing off an associated outlet passage in response to the introduction of inlet pressure to that line. This valve unit may include a slide valve element which is actuable by the inlet pressure to a position closing off the discharge or outlet passage, and which carries a second valve element spring urged to a closed position and adapted to be automatically opened by the inlet pressure fluid to a position passing such pressure fluid to the motor. These two automatic valve units may then be controlled very effectively and positively but from a remote location by actuation ofa remote control valve or valves which act merely to admit pressure fluid to a pair of supply lines` leading to the two automatic valve units respectively.

BRIEF DESCRIPTION OF THE DRAWINGS The above and other features and objects of the invention will be better understood from the following detailed description of the typical embodiments illustrated in the accompanying drawings, in which the invention is typically illustrated as applied to a fluid motor utilized as the driving force in a well pipe spinner, and in which drawings:

FIG. l is a somewhat diagrammatic side view of a drill rig having a spinner which contains a motor embodying the invention;

FIG. 2 is an enlarged fragmentary representation of a portion of FIG. l;

FIG. 3 is a further enlarged view taken on line 3-3 of FIG. 2;

FIG. 4 is an enlarged view taken primarily on the vertical sectional line designated 4-4 in FIG. 3;

FIG. 4a is a fragmentary representation of one of the valve units of FIG. 4, in a changed position;

FIG. 5 is a horizontal section taken on line 5-5 ofFIG. 4.;

FIGS. Sa and 5b are fragmentary vertical sections taken on lines Sa-Sa and Sb-Sb respectively of FIG. 5;

FIG. 5c is an enlarged horizontal section through one of the varies of the device;

FIG. 6 is a fragmentary view representing a portion of FIG. 5, but with the clutch in itsl released condition;

FIG. 7 is a fragmentary vertical section taken primarily on line 7-7 of FIG. 6;

FIG. 8 is a fragmentary elevation, partially broken away in section, taken on line 8-8 of FIG. 7;

FIG. 9 is a view similar to FIG. 7, but showing a different form ofclutch mechanism;

FIG. I0 shows a portion of FIGv 9 in a position in which the clutch is released; and

FIG. Il is a fragmentary horizontal section taken on line lI-ll of FIG. 9.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Attention is first directed to FIG. l, in which there is shown a conventional well drilling rig Il) having a rotary table ll which turns about a vertical axis I2, and is adapted to drive rotatively about that axis the usual noncircular kelly' section I3 of the drill pipe. The rest of the drill string is of course connected to the kelly and extends downwardly into the well. The entire drill string is suspended by the usual elevator assembly designated 14 in FIG. 1, which includes a block and tackle assembly I4' driven by a motor l5, with the cable I6 of the block and tackle carrying a hook I7. The swivel is illustrated at I8, and has an upwardly projecting bail I9, which engages and is suspended by hook I7 ofthe elevator assembly. The swivel of course includes an outer body 20, having a tubular vertically extending spindle or stem 2l mounted in the body for rotation about the vertical axis l2, with drilling fluid or mud being fed to the upper end of the tubular spindle 2l from an appropriate supply hose 22 through the usual goose neck 23. The circulating fluid is pressurized by a pump represented at 24, which is in operation during rotation of the well string to produce circulation of drilling fluid downwardly therethrough, but which is stopped whenever a joint in the string is to be made or broken.

The spindle 2l of the swivel projects downwardly a short distance beneath the lower end of the nonrotating body 20, and has external threads 25 connectable to a spinner 26. This spinner includes a vertically extending short pipe section 27 (see FIGS. 2 and 4), containing a passage 28 through which drilling fluid passes downwardly from swivel stem 2l to the kelly. The upper end of pipe section 27 is internally threaded at 29, to form a box end into which the threads 2S of the swivel stern or spindle are connectable. Alternatively, there may be connected between the swivel stem and section 27 of the spinner an intermediate short pipe section or sub'. The lower end of pipe section 27 may have an externally threaded downwardly projecting end 30 which may be connected to the kelly through a conventional kelly cock section 3l having a kelly cock valve 32 for closing off the flow of fluid through the string when necessary. The kelly cock section in turn is connected to the upper end of the kelly I3 by an appropriate threaded connection, with section 3l of course containing a passage forming a continuation of the passage 28 in pipe section 27 of the spinner, so that fluid may flow downwardly through section 3l to the kelly and into the well. The joint between sections 27 and 3l, as well as the joint between section 3l and the kelly, may be locked against accidental detachment by appropriate external locking rings 33 and 34 suitably connected to the joined parts.

In addition to the central tubular pipe section 27 of the spinner, this device includes and forms, about section 27, a vane-type fluid driven motor 35, with whose construction the present invention is primarily concerned, this motor including an outer nonrotating housing or body 36, and a rotor 37 which in one condition of the apparatus acts to drive pipe section 27 and the connected parts rotatively about vertical axis l2. The rotor is capable of driving the well pipe in either rotary direction, and for this purpose two flexible liuid inlet hoses 38 5 and 39 may be provided, to lead actuating pressure fluid, typically compressed air, into housing 36, for driving the rotor in its opposite directions. The fluid may be delivered to

hoses

38 and 39 from a source 40 of compressed air or other pressurized fluid, through a three'way valve 4l, which is actuable to three positions, for admitting air selectively to either ofthe two hoses, or closing off all air to both hoses.

Housing 36 contains and forms an inner annular chamber 42 (FIGS. 4 and 5) within which rotor 37 is mounted to turn. The housing may be formed sectionally or several parts, including a generally annular main section 43, a generally annular top wall ,or section 44, and a series of radially outer cover plates 46. At a series of evenly circularly spaced locations (desirably live such locations), the

sections

43 and 44 have radially outwardly projecting portions or enlargements forming outwardly projecting portions 47 of the housing, within which a series of radially movable varies 48 are slidably received.

Sections

43 and 44 are secured rigidly together in any suitable manner, as by several sets of screws 49 extending ,5 downwardly through top section 44 and into bottom section 43 at the locations of the outwardly projecting enlargements 47, and by several similar screws 50 extending through section 44 and into section 43 at a number of circularly intermediate locations (FIG. 3). Outer cover plates 46 extend across the radially outer extremities of

sections

43 and 44 at the loca tions of outwardly projecting portions 47, and are secured thereto by bolts Sl.

The previously mentioned rotor chamber 42 in the housing is defined at its .top and bottom by two annular parallel horizontal surfaces-52 and 53, formed on the underside of section 44 and the upper side of section 43 respectively, and both disposed perpendicular to axis l2. The radially outer extremity of chamber 42 is defined by a generally annular wall 45 projecting upwardly from and desirably integral with section 43 of the housing, and having an inner cylindrical wall surface S4 centered about axis l2 and extending vertically from surface 52 to surface 53. Wall 45 is circularly continuous except at the locations of outwardly projecting enlargements 47 on the housing, at which locations wall 45 is interrupted to provide radially extending slots or guideways 247 within which varies 48 and their guiding parts are received.

Vanes 48 are rectangular flat elements of a height corresponding to the vertical distance between the two top and bottom wall surfaces 52 and 53 of chamber 42, to be slidably received therebetween. More specifically, as seen in FIG. 4, one of the varies is there illustrated as having a bottom horizontal edge 55 slidably engaging surface 53 of housing section 43, and a top horizontal edge 56 slidably engaging surface 52 of top section 44. The radially outer extremity ofthe vane may be defined by a vertical edge 57, while the radially inner extremity of the vane may be defined by a vertical edge 58, desirably containing a vertical groove S9 (see FIGS. 4 and S) within which there is retained by rivets or screws 259 a seal element 60 formed of nylon or other sealing material and extending vertically between surfaces 52 and S3. The vane 48 may be formed of any suitable preferably rigid material, such as an appropriate metal, and may be slidably confined between two bearing carrier plates 60' and 6l (FIG. 5), confined within one of the housing slots 247. Plates 60' and 6l may be formed of an appropriate metal, such as steel, and be welded to section 43 or otherwise permanently secured in the illustrated positions. Plates 60' and 6l have parallel opposed vertical

planar surfaces

260 and 261. extending substantially; 70 radially with respect to axis l2, and containing vertical grooves within which there are loosely received vertical bearing inserts 62 of an appropriate bearing material (such as nylon or aluminum bronze) for minimizing the frictional resistance to motion ofthe varies. The two elements 60' and 6l,

and their inserts 62, form together the opposed vertical sidewalls of a guideway within which the vane 48 is mounted for sliding movement directly radially with respect to the main axis l2 ofthe spinner.

Fach of thc varies is spring urged radially inwardly against the rotor by a coil spring 64, which may be received about a pin 65 projecting radially inwardly from the associated cover plate 46, with thc spring projecting into a suitable passage 66 in the vane (FIGS. 4 and S and bearing against a shoulder at the end of that passage` The radially outer end of the vane receiving guideway may be sealed by provision of an appropriate seal between each of the cover plates 46 and the other housing parts (sections 43 and 44), peripherally about the vane area, and more specifically by providing an endless typically rectangular gasket 67 (FIGS. 4 and 5) for preventing leakage of air from the housing. The radially innerextremities of the two bearing carrier plates 60' and 6l, at each of the vane locations, may have arcuate surfaces which form continuations ofthe cylindrical surface 54 of housing wall 4S.

The opposite side surfaces 68 of each ofthe varies are parallel to one another, and extend vertically, but are spaced apart a distance somewhat less than the space between the opposed parallel planar vertical surfaces 263 of each pair of bearing elements 62, to provide a clearance space between each ofthe varies and one of the surfaces 263 (as at 363 in FIG. 5c) through which some of the air from within chamber 42 may flow radially outwardly to a location outwardly beyond the vane. This air always flows radially outwardly at the pressure side of the vane, while the latter is maintained by the pressure in scaling engagement with the bearing surfaces 263 at its opposite side (as at 463 in FIG. 5c).

The entire housing 36 is mounted rotatably to the central tubular main pipe section portion 27 ofthe spinner, since pipe section 27 is to turn with the rest of the drill string while the housing remains stationary. For this purpose, there are provided two bearings 69 and 7l] about pipe section 27, and at the upper and lower ends of the housing. Each of these bearings may have inner and outer races with rollers 7l received therebetween, and disposed at

inclinations enabling bearings

69 and 70 to function as thrust bearings, so that in addition to mounting section 27 for rotation within the housing, they also retain the housing against both upward and downward movement relative to pipe section 27, and in fact serve to support the weight of the housing and its contained rotor from pipe section 27. The inner race of bearing 70 may engage against and be supported by an upwardly facing annular shoulder 72 formed on pipe section 27, while the inner race of bearing 69 is retained against upward movement by a snap ring 73 received within a groove in pipe section 27, and acting against bearing 69 through a washer 74.

Roller bearing 69 may be protected against contamination by a shield ring 75 disposed about pipe section 27 and secured thereto by setscrews 76, with this shield ring coacting with another ring 77 of the configuration illustrated in FIG. 4, secured to upper wall 44 of the housing by bolts 78, and con taining an annular deformable seal element 79 engaging a depending skirt on ring 75. The lower roller bearing 70 may be protected by connection of a shield ring 80 to the housing through screws 8l, with ring 80 containing seal elements 82 engageable with an annular surface 83 on pipe section 27.

The rotor 37 is mounted rotatably within chamber 42 by means of two ball bearings 84 and 8S (FIG. 4), whose outer races engage and are confined by

housing sections

43 and 44 respectively. The rotor itself has surfaces 86 which define the inner races of these ball bearings, with the ball contacting surfaces all being disposed at such an angle as to give the bearings a capacity to function as thrust bearings, in addition to merely mounting the rotor for turning movement. The rotation ofthe rotor is of course about main axis l2 of the apparatus.

The radially outer portion 237 of the rotor occupies the en tire vertical distance from bottom wall surface 53 of chamber 42 to top wall surface 52 of the chamber, and has a radially outer surface 87 which is circularly continuous about axis l2,

lli lli and which has the noncircular horizontal crosssectional configuration illustrated in FIG. S. This cross section continues for the entire vertical extent of chamber 42, to define a series ofcvenly cireularly spaced radially outwardly projecting lobes 88 on the rotor. and circularly intermediate portions 89 of surface 87 which, in advancing circularly from one of the lobes to thc next lobe, first progressively decrease in radius, and then progressively increasc in radius to thc next lobe. The lobes 88 are of a diameter corresponding substantially to the diameter of internal surface 54 of thc housingl to engage or substantially engage that surface continuously, and rnovc therealong, so that there are formed bctwcen succcssivc lobes, a series of air compartments 90. forming portions ol' chamber 42 which are isolated from one another. These compartments in effect vary progressively in size as the rotor turns, since vancs 48 also form sides of the compartments. As the rotor turns, the vanes of course move inwardly and outwardly, to always contact the outer surface 87 ofthe roller in sealed relation.

The radially inner portion of rotor 37 contains two annular fluid inlet and

fluid outlet passages

91 and 92, which have the vertical crosssectional shape illustrated in the left-hand portion of FIG. 4 except at the locations of certain later-to-be described openings by which these passages communicate with the exterior of the rotor. More specifically, the upper passage 91 opens upwardly, while the lower passage 92 opens downwardly. Annular seal elements 93 and 94 may be con tained within annular grooves in the housing to annularly erlgage the upper and lower surfaces of the rotor radially between

passages

91 and 92 and the outer compartments 90, to thus form a seal therebetween. Also, the

bearings

84 and 85 may be sealed by annular seal rings 95 and 96 (FIG. 4) to prevent escape of any of the air from

passages

91 and 92 into or through the bearings.

As seen in FIGS. and 5a, the upper fluid inlet and outlet passage 91 in the rotor communicates with compartments 90 through a series of openings 97 extending radially through the outer wall of the rotor at first sides of the lobes 88. Similarly, lower passage 92 communicates with compartments 90 through a series of openings 98 (see broken lines in FIG. 5 and see showing of FIG. 5b), at the opposite sides of lobes 88.

The first air inlet hose 38 communicates with the upper interior portion of the housing through a fitting 99 (FIG. 4), which opens into a cylindrical radially extending passage 100 in upper wall 44 of the housing, the opposite end of which passage communicates downwardly at 101 with the discussed upper passage 91 in the rotor.

Passage 100 in the upper portion of the housing also communicates with the atmosphere through a vent outlet 103, past a shield cap 104, with vent outlet 103 opening into the side of the cylindrical passage 100. A slide valve element 105 is slidably mounted within passage 100 for movement between the positions of FIGS. 4 and 4a. ln the position of FIG. 4a, the tubular sidewall 106 of the slide valve element extends across and closes vent outlet opening 103, to prevent the loss of any air from passage 100 to the atmosphere.

Element 105, in addition to serving as a slide valve element, also functions as a portion of a shiftable two valve assembly, and for this purpose contains a second valve clement 107, adapted to seal annularly against a valve scat surface 108 formed at the end of the tubular sidewall |06 ofthe slide valve element. The second valve element 107 has a stem 109 which is slidably guided to mount element 107 for only axial movement, and about which there is received a coil spring yieldingly urging element 107 to its closed position of FIG. 4. Stern 109 projects leftwardly beyond the end of slide valve element S, for engagement with a transverse surface or shoulder Ill in the housing, in a manner automatically shifting the second valve element 107 to its opened position of FIG. 4a in response to Ieftward movement of element 105 under the influence ofcompressed air admitted through fitting 99. Spring 110 is ofa strength or force enabling such compres sion of the spring, for opening of valve element 107, in response to the application of air pressure to the slide valve element 105.

The second air inlet line 39 communicates through a fitting 99a with a passage 100u corresponding to upper passage 100, and containing a second slide valve element l05a corresponding to upper valve and containing a spring-pressed valve corresponding to valve 107. This lower valve assembly is constructed and functions in thc same manner as the upper valve assembly to control the flow of air between inlet line 39, a vent outlet opening 1031A, and a passage 10lu leading into passage 92 in the rotor.

The outer housing 36 of the spinner and its motor is retained against rotation about axis l2 by connection to thc upper bail I9 ol' swivel 18 through a flexible vertically extending cable 112. 'I`he lower end of this cable may be connected to the housing hy forming one of the outer cover plates 46 of the housing to have an integral radially outwardly projecting partial spherical socket portion 113 (FIGS. 3 and 4), within which there is received a mating part |14 having a spherically curved ball portion IIS forming a universal connection with socket 113. The lower end of the cable may have an eye portion 116 forming an opening through which a connector pin 117 extends, with that connector also extending through openings in a pair of upwardly projecting ears 118 on a part 119, which has a partial spherical portion 120 engaging the upper surface of socket 113, and a downwardly projecting shank 121 to which a nut 122 is connected. A spring 123 bears downwardly against an element 124 retained by the nut, and upwardly against part 114, to yieldingly retain the parts in their FIG. 4 relative positions, while allowing limited resilient upward movement of the lower end ofthe cable relative to the housing in response to excessive forces. The upper end of the cable is connected to the bail by means` ofa connector bracket 12S, detachably secured in any suitable manner to bail 19, as by a clamp structure represented at 126 and extending about a portion of the bail, with bracket projecting outwardly far enough for connection to the cable at a location 127 positioned so that the cable may extend directly vertically past the main body of the swivel. As will be apparent, the cable 112 does not support the weight of housing 36 or the rest of the spinner structure, but rather merely retains the housing against rotation about axis 12, while at the same time allowing some limited rotary motion ofthe housing about that axis in response to excessive torsional forces, to thus introduce a certain amount of resiliency into the structure for holding the housing against rotation. The actual support of the weight of the housing and other parts ofthe spinner is effected through the central pipe section 27 and the various bearings which mount the spinner on that section, as has been previously indicated.

When the spinner is in use, rotor 37 is connected in driving relation to pipe section 27 by means of a clutch mechanism represented generally at 128 in FIG. 4. This mechanism includes two diametrically opposite clutch levers or elements 129, which are movably carried by a ring or sleeve 130 disposed about and rigidly connected to pipe section 27. Internally, this ring 130 is a close fit on the outer surface of pipe section 27, and keyed thereto for rotation with the pipe section by a key represented at 131 in FIG. 5. The levers are mounted pivotally to ring 130 within two vertically elongated slots 132 in the ring, and by a pair of horizontal pivot pins 133 extending through the keys and into the material of the ring. Beneath the level of pivot pin 133, each lever 129 has a downwardly projecting arm portion 134, which is engaged by a pressure actuated piston or plunger element 135 mounted for movement directly radially of axis 12, and along a radial axis 136, relative to pipe section 27. This piston 135 may be slidably mounted within a cylinder sleeve 137 which is a pressed fit within a cylindrical opening 138 extending through the sidewall of pipe section 27. To seal piston 13S with respect to cylinder 137. the radially inner end of the piston may carry an externally cylindrical seal element 139 of rubber or other resilient material, which is a tight slightly compressed fit within the sleeve, and which desirably projects slightly inwardly beyond the wall or passage 28 in the FIG. 4 position of the clutch. Seal element 139 may be secured to piston 135 by molding it about a head or projection |40 formed on the piston. As will be apparent, when pressure is applied to the radially inner end of the seal portion |39 of the piston, by drilling lluid or mud within passage 28, the piston is actuated by that pressure radially outwardly from the F|( 4 position to the FIG. 7 position, to thereby swing lever |29 to its FIG. 7 position.

Upwardly above the level of pivot pin |33, each ofthe clutch levers |28 has an upwardly projecting arm portion |41, which may be offset slightly radially inwardly and be received partially within a vertically extending groove or recess |42 in the outer surface of pipe section 27, and which is yieldingly urged radially outwardly by a coil spring |43 to normally retain the lever in its FIG. 4 position. The upper end of arm |41 forms a radially outwardly projecting clutch lug |44, which is engageable in rotary driving relation with one of two diametrically opposite clutch lugs |45 projecting radially inwardly from the otherwise straight cylindrical inner surface |46 of rotor 37. As seen best in FIG. 5, the driving surfaces or shoulder surfaces 147 through which rotary forces are transmitted between levers |29 and rotor lugs |45 lie within planes which extend substantially radially and axially with respect to axis l2. In the FIG. 7 position ofeach ofthe clutch levers |29,

these levers are moved out of driving engagement with rotor lugs |145, so that pipe section 27 may turn freely without cor responding rotation of the rotor. A seal may be provided an nularly between the upper end of ring |30 and the upper portion of the housing, at a location beneath bearing 7|, by a seal element |48 (FIG. 4).

To now describe the operation of the apparatus of FIGS. through 8, assume that the spinner 26 is connected into the drilling apparatus at the location illustrated in FIGS. and 2, beneath swivel 18, `and that the rig is initially being utilized in an actual drilling operation, with the kelly section I3 of the pipe string being driven rotatively by rotary table ll, to thus drive the rest of the string and the drill bit for deepening the well. During such rotation of the string by the rotary table, drilling fluid or mud is supplied to the swivel through line 22 of FIG. 2, and flows downwardly under pressure through the stem 2| of the swivel, and through pipe section 27 of spinner 26, to then enter and flow downwardly through the kelly and into the lower portion of the stringY The pressure of this drilling fluid acts against the seal portion |39 of piston |35 in FIG. 4, to force that piston radially outwardly from its FIG. 4 position to its FIG. 7 position, and thus pivot the clutch lever |29 to its FIG. 7 position in which it does not transmit rotary motion between pipe section 27 and the rotor 37 of the spinner, Thus, pipe section 27 of the spinner is free to tum with the stem of the swivel and with the kelly and the remainder of the well string, without turning motion of the rotor or any other portion ofthe spinner. Such disconnection of the spinner or rotor from the turning parts prevents damage to the rotor by unnecessary turning, and also prevents any pos` sibility of the string being retained against rotation by binding of the rotor 37 within the spinner housing, such as might occur for example if particles of dirt or other foreign materials were in some way to lock the rotor or its bearings against rotation. This binding is not a major factor, but could be so disastrous to all of the equipment in the vicinity, and even to persons working in the area, as to render it desirable to lake every precaution against the possibility.

When it is desired to utilize the spinner for driving the kelly and pipe string, this will always occur after mud pump 25 has been deenergized, to stop the flow of circulating fluid through the string, and thereby reduce the pressure within passage 28 of pipe section 27 (FIG. 4). As soon as the mud pressure is reduced, springs |43 will actuate the two clutching levers 129 from its FIG. 4 position to its FIG. 4a position, to thereby close off communication through outlet |03 to the atmosphere, and with the final portion of this motion serving to open valve |07 so that the compressed air may enter passage 9| of the rotor, and from that passage discharge through openings 97 in the rotor into the variable sized compartments formed between the rotor and the housing. The compressed air within these compartments drives the rotor in a clockwise direction, as viewed in FIG. 5, since the compartments into which the air is admitted will increase in size progressively during such right hand rotation, The varies 48 engage the rotor in a valving relation, so that until a particular one of the openings 97 reaches one of the vanes, that opening admits air to a compartment at a first side of the vane, but after passing the vane the air is ad mittcd to the opposite side ofthe vane.

While the rotor is turning in a clockwise direction, the openings 98 act as outlet openings, through which the air is forced into passage 92 ofthe rotor, for discharge through outlet |03a of FIG, 4 to atmosphere. If it is desired to reverse the rotation of the rotor, this may be effected by actuating selector valve 4l to a position in which the air to hose 38 is shut off, and compressed air is admitted instead to hose 39. This air will actuate the lower valve 105er leftwardly to a position corresponding to that shown for the upper valve in FIG` 4a, while the upper valve returns rightwardly to its FIG. 4 position under the influence of air discharging from passage 9| to the atmosphere through outlet |03. That is, the reduced diameter portion |40 of slide valve |05 acts within reduced portion 15| of the passage |00 as a piston, which is forced rightwardly by the discharging air, with this piston effect being enhanced in thc final portion of the travel by confinement of the larger diameter portion of slide valve element |05 within the larger diameter portion of passage |00. During the reverse or coun terclockwisc rotation, the air which enters bottom annular passage 92 ofthe rotor flows outwardly into the compartments between the rotor and housing through openings 98, while the discharging air leaves those compartments through openings 97 and passage 91 of the rotor to actuate the upper valve element 105 to open position as previously discussed, and thus discharge to atmosphere.

When drilling is again to be resumed, this will only be done after pump 24 of FIG. 2 has again been energized to produce a flow of drilling fluid and to produce a pressure within passage 28, to thus return the clutch levers |29 to their FIG. 7 inactive or released positions, so that the drill string may then be turned without rotation of rotor 37. Desirably, the clutch elements and their springs |43 are so designed as to be actuable from their FIG. 4 positions to their FIG. 7 positions by a pressure of between about 200 and 500 pounds per square inch within passage 28. The seal element |39 prevents access of any ofthe drilling fluid to the clutching parts.

During rotation of rotor 37, vanes 48 are continuously held radially inwardly against outer surface 87 of the rotor by the combined action of springs 64 and air pressure exerted radially inwardly against the varies. To bring out the manner in which the pressure of the air exerts a radially inward force against the vanes, reference is made to FIG. 5c, in which it may be assumed that compressed air at relatively high pressure is contained within the compartment a to the right of the vane, while air is being discharged from the compartment 90b to the left of the vane, and is therefore at a reduced pres sure in compartment 90h. Because of the greater pressure in compartment 90a, vane 48 of FIG. Sc is urged leftwardly by the air pressure and into tightsealing engagement with the two left-hand seal strips 62, as indicated at 463, while a gap is left between the two righthand seal elements and the vane, as indicated at 363. Thus, the highpressure air from compartto their active FIG. 4 positions` in which they become effecA 70 ment 90a can flow radially outwardly through the gaps at 363 tive to transmit rotation from rotor 37 to pipe section 27. lf it is then desired to turn the pipe section 27 and kelly 13 in a clockwise direction, selector valve 4| of FIG. l is actuated to a position to admit compressed air through hose 38 to the spinner. This compressed air moves slide valve element and into the space 563, tc exert a radially inward force against the vane. This force is partially counteracted by the exertion of a radially outward force against the inner extremity of the vane (toward the bottom of FIG. 5c), but because the vane assembly contacts outer surface 87 of the rotor at 248, the outward force against the vane can be exerted against only onehall' ol its inner extremity, that is the portion to the right of contact line 248 but not the portion to the left of that contact line. Thus, there is a net differential pressure tending to urge the vane radially inwardly, and coacting with spring 64 in assuring that the vane will continuously contact the rotor. When conditions reverse and the pressure in compartment 90h of FIG. r exceeds that in compartment 90a, the vane shifts against the vane, It is also noted that each vane may contain a passagc 200 (FIGS4 4 and 5c) through which air may flow through the interior of the vane past the radially outer pair of bearing elements 62, to reduce the resistance to flow of air outwardly past those elements, but with the passage 200 being so located as to never move far enough radially inwardly to bypass the two radially inner bearing elements 62, so that a seal will always be formed with one of these inner elementsV The passage 200 may consist of a transverse opening ex tending entirely through the thickness ofthe vane, to commu nicate with both sides of the vane, and leading into a radially extending passage 202 extending outwardly to the radially outer extremity of the vane.

FIGS. 9, l0, and II represent fragmentarily a variational form of the invention, which may be considered as identical with the arrangement of FIGS` l through 8 except as to the construction of the clutching mechanism for operatively connecting the rotor of the vane type motor to the central pipe section of the spinner device. Fig, 9 shows this changed mechanism in a view very similar to the FIG, 7 showing of the first arrangement. In FIG, 9, the central pipe section of the spinner is designated 27' (corresponding to section 27 of FIGS. 4 and 7), and contains a passage 28' (corresponding to passage 28 of the first form of the invention) through which drilling fluid flows downwardly under pressure during a drilling operation. The rotor of the vane type motor is shown fragmentarily at 37', with the outer housing being designated 36', and more particularly with the housing having a lower wall section 43' and an upper wall section 44' corresponding to

sections

43 and 44 of FIG. 4. The bearings 69', 70', 84', and 8S' serve the same function as in the lirst form ofthe invention.

Instead of the two clutching levers |29, the apparatus of FIGS. 9 to ll includes a clutching ring 160 which is annular about pipe section 27 and about axis l2' of the apparatus This ring is constructed to function as a vertically movable piston, and for that purpose has a lower enlarged diameter annular portion 161 having an internal cylindrical surface slidably engaging a corresponding external cylindrical surface on pipe 27' at |62. Above its portion |61, ring 160 has a reduced diameter portion having a cylindrical internal surface slidably engaging a reduced diameter external cylindrical surface on pipe sections 27' at |63, to form an annular pressure fluid chamber |64 between the ring and pipe section 27' to which the pressure of the pump ofthe drilling fluid within passage 28' is communicated through a passage or opening |65 in the sidewall of pipe 27'. The ring is retained against rotation relative to pipe 27', while permitting axial movement of the ring. by one or more keys or splines |66, which may be secured in fixed position within grooves or recesses in pipe 27', and be slidably received within opposed axially elongated and axially extending grooves |67 formed in the inner surface of the upper portion of ring |60, The ring is yieldingly urged downwardly by a number of evenly circularly spaced coil springs |68, which may be partially received within opposed recesses in an upper retaining ring |69 and the upper surface of movable ring |60. Retaining ring |69 may be located against upward movement by engagement against the inner race of roller bearing 69'.

jccting evenly circularly spaced lugs |71 carried by and formed in rotor 37'. These teeth are movable out oftheir driving interfitting engagement by upward movement of ring from the FIG, 9 position to the FIG. I0 position.

When superatmosphcric pressure is applied to drilling fluid or mud within the interior of passage 28', that pressure is communicated through passage to the underside of the annu lar piston or ring |60, to actuate that piston upwardly to its FIG. l0 position, in which it cannot transmit rotation between pipe 27' and rotor 37', to thus enable free rotation ofthe entire drill string and pipe section 27' without corresponding rotation of the rotor. When the drilling fluid pressure is reduced, preparatory to an operation in which the spinner may be used, the ring |60 is moved downwardly to its FIG. 9 position by springs |68, to engage teeth and l7l in a manner enabling rotor 37 to turn pipe Section 27' and the connected kelly or other pipe section therebencath, to make or break a joint in the string. The operation ofthe remainder of the apparatus is thc same in FIGS. 9 through as in the other form ofthe invention lclaim:

l. The combination comprising a fluid motor adapted to be driven in two opposite directions and having a first passage which serves as a fluid inlet when the motor is turning in a first direction and as an outlet when the motor turns in the opposite direction, and a second passage which serves as a fluid outlet when the motor turns in said first direction and as an inlet when the motor turn in said opposite direction, and two valve units interposed between a source of pressure fluid and said passages respectively and each operable automatically when pressure fluid is supplied thereto to close off communication between the associated one of said passages and a vent outlet to atmosphere.

2. The combination as recited in claim l, in which each of said valve units includes a hollow slide valve element actuable slidably within a valve body structure by said pressure fluid, said structure having said outlet to atmosphere in a wall thereof positioned to be closed by said sliding pressure fluid induced actuation of said element, each of said valve units also including a second valve movably carried by said slide valve element and spring urged to a closed position in which it closes off the flow of pressure fluid to one of said passages through the interior of said slide valve element, said second valve being actuable automatically to open position upon said actuation ofthe slide valve element.

3, The combination as recited in claim 2, in which said second valve has a stern engageable with a shoulder in said valve body structure in a relation opening said second valve upon said actuation ofthe slide valve element.

4y The combination as recited in claim l, in which said motor includes a body containing a chamber, a rotor mounted in said chamber to rotate in said two opposite directions relative to the body, said rotor having at least one lobe projecting toward a wall of said chamber and having portions at the lead ing and trailing sides of the lobe which are spaced farther from said wall to vary the spacing between said rotor and said wall as the rotor turns, at least one vane movably carried by said body and projecting from said wall into said chamber and into engagement with said rotor and forming with said body and rotor at least one compartment which varies in size as the rotor turns, said first fluid passage being formed in the rotor and communicating with said compartment through a first opening ata first side ofsaid lobe and being operable when the rotor is turning in said first direction to admit pressure f'luid into said compartment for driving the rotor, and when the rotor is turning in the second direction to discharge fluid through said opening and passage to atmosphere, said second fluid passage being formed in the rotor and communicating with said compartment through a second opening at a second side of said lobe and being operable when the rotor is turning in said compartment to atmosphere, and when the rotor is turning in said second direction to admit pressure fluid into the compartment for driving the rotor in that direction.

5. The combination as recited in claim l, in which said motor includes a body containing a chamberI a rotor mounted in said chamber to rotate in said two opposite directions relative to the body, said rotor having at least one lobe projecting toward a wall of said chamber and having portions at the leading and trailing sides ofthe lobe which are spaced farther from said wall to vary the spacing between said rotor and said wall as the rotor turns, at least one vane movably carried by said body and projecting from said wall into said chamber and into engagement with said rotor and forming with said body and rotor at least one compartment which varies in size as the rotor turns, said first fluid passage being formed in the rotor and communicating with said compartment through a first opening at a t'irst side of said lobe and being operable when the rotor is turning in said first direction to admit pressure fluid into said compartment for driving the rotor, and when the rotor is turning in the second direction to discharge Huid through said opening and passage to atmosphere, said second Fluid passage being formed in the rotor and communicating with said compartment through a second opening at a second side of said lobe and being operable when the rotor is turning in said lirst direction to discharge pressure Huid from said compartment to atmosphere, and when the rotor is turning in said second direction to admit pressure Huid into the compartment for driving the rotor in that direction, there being two passages in said body communicating in sealed relation with said two rotor passages respectivelyI and control valve means for supplying pressure Huid to said two body passages selectively, said two valve units being located in said two body passages respectively.

6. The combination as recited in claim 5, in which each of said valve units includes a hollow slide valve element actuable slidably within said body passage by said pressure fluid and operable upon such actuation to close a venting outlet in a wall ofthe passage, a second valve movably carried by said slide valve clement and spring urged to a closed position in which it closes off the flow ol` pressure fluid to one of said rotor passages through the interior of said slide valve element, and means forming a shoulder for actuating said second valve element to operi position upon movement of the slide valve element to its position for closing said venting outlet so that said pressure fluid may flow to the rotor.

7. The combination as recited in claim S, in which said rotor has a plurality of said lobes, there being a plurality of said varies and compartments, said first passage being generally annular and communicating with said compartment through a plurality of said l'irst openings at first sides ofthe lobes respec tively, said second passage being generally annular and communicating with said compartments through a plurality of said second openings at second sides ofthe lobes respectively.

Claims

1. The combination comprising a fluid motor adapted to be driven in two opposite directions and having a first passage which serves as a fluid inlet when the motor is turning in a first direction and as an outlet when the motor turns in the opposite direction, and a second passage which serves as a fluid outlet when the motor turns in said first direction and as an inlet when the motor turn in said opposite direction, and two valve units interposed between a source of pressure fluid and said passages respectively and each operable automatically when pressure fluid is supplied thereto to close off communication between the associated one of said passages and a vent outlet to atmosphere.

2. The combination as recited in claim 1, in which each of said valve units includes a hollow slide valve element actuable slidably within a valve body structure by said pressure fluid, said structure having said outlet to atmosphere in a wall thereof positioned to be closed by said sliding pressure fluid induced actuation of said element, each of said valve units also including a second valve movably carried by said slide valve element and spring urged to a closed position in which it closes off the flow of pressure fluid to one of said passages through the interior of said slide valve element, said second valve being actuable automatically to open position upon said actuation of the slide valve element.

3. The combination as recited in claim 2, in which said second valve has a stem engageable with a shoulder in said valve body structure in a relation opening said second valve upon said actuation of the slide valve element.

4. The combination as recited in claim 1, in which said motor includes a body containing a chamber, a rotor mounted in said chamber to rotate in said two opposite directions relative to the body, said rotor having at least one lobe projecting toward a wall of said chamber and having portions at the leading and trailing sides of the lobe which are spaced farther from said wall to vary the spacing between said rotor and said wall as the rotor turns, at least one vane movably carried by said body and projecting from said wall into said chamber and into engagement with said rotor and forming with said body and rotor at least one compartment which varies in size as the rotor turns, said first fluid passage being formed in the rotor and communicating with said compartment through a first opening at a first side of said lobe and being operable when the rotor is turning in said fIrst direction to admit pressure fluid into said compartment for driving the rotor, and when the rotor is turning in the second direction to discharge fluid through said opening and passage to atmosphere, said second fluid passage being formed in the rotor and communicating with said compartment through a second opening at a second side of said lobe and being operable when the rotor is turning in said compartment to atmosphere, and when the rotor is turning in said second direction to admit pressure fluid into the compartment for driving the rotor in that direction.

5. The combination as recited in claim 1, in which said motor includes a body containing a chamber, a rotor mounted in said chamber to rotate in said two opposite directions relative to the body, said rotor having at least one lobe projecting toward a wall of said chamber and having portions at the leading and trailing sides of the lobe which are spaced farther from said wall to vary the spacing between said rotor and said wall as the rotor turns, at least one vane movably carried by said body and projecting from said wall into said chamber and into engagement with said rotor and forming with said body and rotor at least one compartment which varies in size as the rotor turns, said first fluid passage being formed in the rotor and communicating with said compartment through a first opening at a first side of said lobe and being operable when the rotor is turning in said first direction to admit pressure fluid into said compartment for driving the rotor, and when the rotor is turning in the second direction to discharge fluid through said opening and passage to atmosphere, said second fluid passage being formed in the rotor and communicating with said compartment through a second opening at a second side of said lobe and being operable when the rotor is turning in said first direction to discharge pressure fluid from said compartment to atmosphere, and when the rotor is turning in said second direction to admit pressure fluid into the compartment for driving the rotor in that direction, there being two passages in said body communicating in sealed relation with said two rotor passages respectively, and control valve means for supplying pressure fluid to said two body passages selectively, said two valve units being located in said two body passages respectively.

6. The combination as recited in claim 5, in which each of said valve units includes a hollow slide valve element actuable slidably within said body passage by said pressure fluid and operable upon such actuation to close a venting outlet in a wall of the passage, a second valve movably carried by said slide valve element and spring urged to a closed position in which it closes off the flow of pressure fluid to one of said rotor passages through the interior of said slide valve element, and means forming a shoulder for actuating said second valve element to open position upon movement of the slide valve element to its position for closing said venting outlet so that said pressure fluid may flow to the rotor.

7. The combination as recited in claim 5, in which said rotor has a plurality of said lobes, there being a plurality of said vanes and compartments, said first passage being generally annular and communicating with said compartment through a plurality of said first openings at first sides of the lobes respectively, said second passage being generally annular and communicating with said compartments through a plurality of said second openings at second sides of the lobes respectively.