US3149685A - Shaft bearing fluid seal for downhole drilling engines - Google Patents

Description

sept. 22, 1964 3,149,685

SHAFT BEARING FLUID SEAL FOR DOWNHOLE DRILLING ENGINES Filed April 30, 1959 J. A. MITCHELL ETAL 2 Sheets-Sheet 1 A TTORNEYS J. A. MITCHELL ETAL 2 Sheets-Sheet 2 FIG. 5.

JSEPH A. MITCHELL MADDEN 7T WOR/(S THOMAS E. TUCKER, JR.

INVENTOR' ATTORNEYS SHAFT BEARING FLUID SEAL FOR DOWNHOLE DRILLING ENGINES Sept. 22, 1964 Filed April 30, 1959 United States Patent O 3,149,685 SHAFT BEARHNG FLUHD EAL FOR DQWNHOLE DRELMNG EGNES Joseph A. Mittelteil and Madden T. Works, Dallas, and Thomas E. Tucker, r., Midland, Tex., assignors to Dresser Industries, Inc., Dalias, Tex., a corporation of Delaware Filed Apr. 30, 1959, Ser. No. 810,111 7 Claims. (Cl. 17E-107) The present invention relates to a turbodrill or fluid driven turbine Ithat is carried on the end of a drill string and, actuated by the downowing drilling tluid, drives a rotary drill bit utilized in the drill of oil wells and the like.

Although the turbodrill has been known for a number of years, as evidenced by Cross Patent No. 142,992 issued in 1873, and Westinghouse Patent No. 307,606 issued in 1884, it is only in very recent years that the basic turbodrill invention has advanced the turbodrill toward a state of commercial usage. There were various technical reasons for the delay, such as the early development of direct rotary drilling which, following its adoption around 1900, became the accepted procedure. Rotary drilling remains the standard procedure in this country, -and from the standpoint of feet drilled per hour of operating time, it has not as yet been commercially superseded.

However, the early concepts of turbodrill operation and subsequent modifications have led the inventively minded in this lield to give a great deal of consideration Ito the realization of the great economies which this form of drilling could afford. These are evident, because in rotary drilling there may be as much as 90% energy loss due 4to the friction of the rotary pipe in the bore hole. Moreover, the effect of the heavy loading on the bit, which now runs as much as 40,000 to 100,000 pounds, not only requires very heavy drill collar sections, but under many circumstances results in angular deviations in drilling that exceed the permisisble limits for well bore verticality. With a reduction of load on the bit, there is an attendant reduction in rate of penetration and frequently supplemental equipment such as whipstocks must be used to correct these deviations.

The use of a turbodrill has the distinct advantage over rotary drilling in that the driving torque is close to the bit. It utilizes the drilling iiuid which is necessary for removing the cuttings from the well and it can be made of `adequate power to permit rapid drilling. The direct drive multiple stage type turbodrill does have a somewhat higher rotational speed as comparedto normal rotary operation, but with improved bits, the turbodrill can be expected to drill considerably faster and cheaper than is possible with rotary drilling.

A turbodrill is, however, a down-hole engine which operates in a fluid-laden well bore, and the highly abrasive fluid stands in the way of any normal lubrication of the wear parts. The limited diameter of the well bore, which is usually less than twelve inches, also limits the internal design beyond that possible with turbines used above ground.

One of the serious problems that has developed in the operation of such downhole drilling engines is a tendency of the high velocity, downwardly moving drilling iluid to leak out through the lower radial bearing of downhole drilling engine such as the turbodrill and, due to this velocity effect, to force the bit cutting back down to the rotating rock bit, thus causing wear and erosion on the bearing race of the rotating bit elements and requiring the bit to recut these formation particles which reduces the bits efficiency. Hence, one of the principal objects of this invention is to overcome this grave problem'of eitectively 3,49,5855 Patented Sept. 22., 1964 Fice protecting the rock bit against deterioration by eliminating the downward fluid ilow from the bearing.

A further and speciiic object of this invention is to provide for cooling and lubricating the turbodrill shaft bearing structure by partial bypass of drilling fluid and its return into the turbodrill driven shaft above the lower bearing packing seal. The nature of these problems and the means of their solution will be more fully understood from the following detailed description and a consideration ofthe accompanying drawings, in which:

FIG. l is a side elevational View of the lower portion of a turbodrill having parts sectioned longitudinally to show the principal parts of a drill, its bearings, and a drill bit used therewith;

FIG. 2 is an enlarged side elevation of .the lower part of the turbodrill housing partially sectioned to show a preferred form of seal and its retaining means;

FIG. 3 is a partially sectioned side elevation similar to that of FIG. 2 but embodying modiied shaft sealing means;

FIG. 3 is a partially sectioned side elevation similar to that of FIG. 2 but embodying modified shaft sealing means;

FIG. 4 is a reduced scale cross-section taken on line 4--4 of FIG. 3;

FIG. 5 shows in partially sectioned side elevation another modiiication of shaft sealing assembly; and

FIG. 6 illustrates in partially sectioned side elevation an additional shaft sealing assembly.

Reference will now be made to the drawings and to FIG. 1 in particular, which shows aturbodrill unit 18 provided with abearing assembly 10 and aconventional drill bit 12. Thelower shaft 28 of the assembly has atubular bore 13, and is surrounded on the lower end thereof by an annular bearing and sealing assembly 14. Particular attention will be directed herein to the novel fea-V tures and improvements in a turbodrill for the operation of a rotary drill bit used in downhole drilling of oil wells as described more fully in joint patent application, Serial No. 764,213, filed September 30, 1958, in the names of Otto Hammer and Joseph A. Mitchell, entitled Turbodrill.

In common with the disclosure of the above-identified prior application, there are set forth herein several shaft sealing `and packing devices for preventing high pressure leakage iiow of abrasive drilling fluid from destructively eroding the drill shaft or the housing, or interfering materially with the upward return flow of drilling fluid.

With reference to FIG. 1 of the drawing, the turbodrill and bearing assembly include one ormore turbine units 18, each provided with ashaft 20 havingrotor blades 22 which are alternately spaced with stator blades 224 mounted in the turbodrill housing. The combination of the rotor and stator blades provides a multiple stage turbine unit which is actuated by the drilling duid, and for typical operations has approximately one hundred pairs of blades or stages that develop from about one hundred fifty to three hundred horsepower. This, of course, will depend upon the drilling uid circulation rate and is merely intended to reiiect the approximate horsepower capacity."

A thrust bearing housing portion 29 extends donwardly of the turbodrill to a lower radial bearinghousing section 144, with which it is connected.

Mounted below theturbine units 18 there is provided a separate bearing sub-assembly housing generally indicated at 10. This includes a shaft 2S which has rotating thrust bearingdisks 42 which are alternately spaced with stationary' rubberized bearingmembers 44. The construction is such that there is both support `for and resistance to vertical movement of theshaft 28, as well as free passage for the drilling iiuidin the passages 4S, whereby amasser El the drilling fluid after it drives the turbine and passes down over the bearings passes through thehollow portion 13 of theshaft 28, and then to and through thedrill bit 12.

In the operation of the turbodrill, drilling fluid under high pressure ilows downwardly through the turbodrill housing wherein it acts against theturbine rotor blades 22 and reacts against thestator blades 24 to ehect a substantially continuous driving force on the driving shaft 24B of the turbodrill.

The hydraulic fluid thus applied produces a substantially continuous driving force on theshaft 20, which acting through the coupling 34 causes rotation of thelower shaft 28 and operation of thedrill bit 12.

Before reaching the bottom end of the turbodrill, the drilling fluid passes through the thrust bearings and thence into a portedlantern ring 38 having a largeuid ow passage 39 extending between the lowermost end of the thrust bearing assembly and thetubular bore 13 of theshaft 28.

In order to support the turbine shaft by thelower shaft 28 with the necessary spacing between the rotor andstator blades 22 and 24, theupper shaft 2@ is coupled to the lower shaft 2S through a coupling generally indicated by numeral 34 in FG. l. It includes two interengaging toothed clutch members, each of which has a shank portion appropriately threaded into an adjacent threaded bore of the respective shafts, such shank portions ending in a collar or shoulder section. These clutch members are in turn surrounded by a sealing collar orspacing ring 36 which is of extremely accurate length so as to precisely space the shoulder sections of the clutch members one from the other. The coupling unit referred to above comprises the subject matter of patent application Serial No. 768,474, filed Gotober 29, 1958 in the names of Madden T. Works, Joseph A. Mitchell and lohn Russell Mooney now Patent No. 2,990,895.

As more clearly shown in FIG. 2, the portedlantern ring 38 affords a large fluid flow passage between the lowermost end of the thrust bearing assembly and thetubular bore 13 of theshaft 28.

From the lower end of the shaft 23 the drilling fluid enters the bit sub 4@ and is discharged to the borehole after passing through thedrill bit 12. A radial bearing sub-assembly 14 encircles the lower end of theshaft 28 immediately above the upper extremity of the bit sub 4t).

The sub-assembly 14 comprises a lower radial bearinghousing 144 provided with a cartridge and sleevetype bearing element 46 held in place by a threadedretainer ring 53. A metallic key member d engages thesleeve 142 which thus rotates with the shaft 23. Thebearing element 46 which is the same general assembly employed in the embodiments illustrated in FIGURES 3, 4 and 6, is made up of arubber sleeve 52 reinforced by ametal sleeve 51. A resilient lip seal S4, which may be of rubber or the like, interlocks at its inner periphery with the adjacent end of the lowerbearing retainer ring 53 and is surrounded by asupport ring 60. The sealing of the lower end of this bearing assembly is completed by a seal member 55 which may be an C ring engaging theshaft 28. IThesupport ring 60 is held securely in place by a plurality ofsetscrews 58.

From the preceding description of the construction and functions of the bearing that has been set forth in detail, it will be understood that the principal part of the high pressure uid passes downward and discharges into thebore 13 ofshaft 28 through theport 39. Some of the fluid, however, is used to cool and lubricate the bearing, and this portion passes between the cartridge type bearing 46 and thebearing sleeve 142. The fluid reaching a point below the bearing will discharge through the downwardlyinclined port 62 and also enter into the shaft 2S for discharge through the drill bit.

Thelip seal 54 interengaging with the adjacent lower outturned vend of the threadedretainer'ring 53, and the iupper inner periphery of the support ring eil together with thering seal 56 acting on the shaft 2S will effectively prevent leakage from the bearing and packing assembly 14. The mounting setscrew means 5S provide for ready servicing when necessary.

The relatively minor modification of this invention as represented by the embodiments of FlGS. 3, 5 and 6 will be described in View of the detailed description previously made ofthe principal embodiment of FIGS. 1 and 2.

The most significant difference in the embodiment of FIG. 3 is the substitution of aT type seal 70 for the lip type one of FIG. 2. The leg of the T-ring seal 70 is positioned inwardly beneath a sleeve bearing assembly '72, extends inwardly and is supported by enclosing back-up rings 74 on the top and bottom, while its annular head portion bears outwardly against the bearinghousing 76. A threadedretainer ring 80 holds thesleeve bearing assembly 72 and theT ring elements 70 and 74 in operative relation in the housing.

ln the reduced size cross-section 4--4 of FIG. 3, as shown in FlG. 4, it will be noted that theinner rubber face 82 of bearing '72 is formed with spacedlongitudinal grooves 84 to permit fluid to discharge into the lateral port S6 opening to the shaft bore 13. The portions of inner-rubber face S2 betweengrooves 84 are in contact withsleeve 142, the fluid in said grooves serving to lubricate this bearing arrangement. It will be noted that in this embodiment and that illustrated in FGURE 6, theseal 70 lies above the lower end of thesleeve 142 and further that the lateral port Se is positioned slightly above the seal. Therefore, there is a possibility of a very small leakage occurring at the lower end of the sleeve 14T.. However, any such leakage would be of insignificant proportion. The important matter is the preventing of lealtage through the relatively large area of the fluted passage formed by the spaced longitudinal grooves S4 in theinner face 82 ofsleeve bearing assembly 72. bviously, if the leakage passing the lower end ofsleeve 142 was ever considered serious, the arrangement illustra-ted in FIGURES l, 2, and 5 could be employed wherein thelateral portion 62 is positioned below the lower end ofsleeve 142.

Referring now to the embodiment of FG. 5, it will be observed that an annular face seal S7 of L-hape in crosssection has its shorter leg portion interposed between the lower end of the bearing housing 76a which carries rubber sleeve bearing 77 on its inner face and theshaft 28 below the downwardlyinclined port 62, and its longer leg portion Vextending between the end face of housing '76a and a retainer ring 89a secured in place onshaft 28 by a setscrew 5&1.

Drilling Fiuld passing 4through these shaft bearings will likewise be removed through a port e2 to the bore 1.3 of shaft The only principal differences between the modification of HG. 6 as compared with the T-type seal construction 4of FlG. 3 a e the substitution of a plurality of chevron or V-type seal rings SS spaced by interengaging support rings 9?, and the positioning of the seal construction above the lower retainer ring 53a as clearly shown.

The novel packed off lower Abearing assemblies for turbodrills as described herein ao'rd numerous advantages in the operation and maintenance of turbodrills, such as the provision of effective cartridge type bearing assembly units that are replaceable with a minimum of time and labor.

A still further improvement contributing substantially to the bit cutting elliciency is obtained from the utilization of an auxiliary port below the bearing assembly and above a shaft seal arrangement to redirect the drilling fluid utilized for lubrication and cooling of the bearing means into the drill bore and thereby maintaining a high fluid pressure differential across the bit..

Having thus described our invention, what we claim as novel and desireto secure by Letters Patent of the United States is:

1. A bearing sub-assembly for a drilling fluid driven downhole drilling motor assembly having a hollow driven shaft rotated by said motor, tubular means connected to the motor and surrounding the upper portion of the driven shaft thereby forming an annular passage between said tubular means and the driven shaft adapted to receive drilling fluid discharged from said motor, and a bearing sub-assembly for and surrounding the lower portion of the driven shaft, said bearing sub-assembly comprising a cylindrical housing adapted to encircle the lower portion of the driven shaft, said housing being adapted to be secured to the lower end of the tubular means, a bearing sleeve carried Within `the housing and adapted to engage the encircled driven shaft, said sleeve having a plurality of spaced longitudinally extending grooves in the face adapted to engage the driven shaft so that drilling fluid may be passed down through the grooves to lubricate and cool the sleeve and the driven shaft riding thereagainst, a port in the driven shaft adjacent the lower end of the bearing sub-assembly adapted to discharge drilling iluid passed between the driven shaft and the bearing sub-assembly, and seal means adapted to prevent leakage of drilling fluid between the lower end portion of the housing and the encircled driven shaft.

2. The invention as described in claim 1 in which the seal means is rubber-like and has a lip seal formation.

3. The invention as described in claim l in which the seal means includes a packing ring having a T formation 6 in cross-section and the end of the leg of the T is in sealing engagement with the driven shaft.

4. The invention as described in claim 1 in which the seal means includes a face seal of L formation having one leg of the L in sealing engagement with the driven shaft.

5. The invention as described in claim 1 wherein the seal means comprises a plurality of chevron type seal rings spaced by interengaging support rings.

6. The invention as described in claim 1 and wherein the bearing sleeve is rubber-like and is molded into the housing.

7. The invention as described in claim l and wherein the bearing sleeve comprises an inner rubber-like sleeve and an outer metallic reinforcing sleeve.

References Cited in the le of this patent UNITED STATES PATENTS 2,016,067 Bannister Y Oct. 1, 1935 2,044,349 Diehl June 16, 1936 2,646,962 Wagner July 28, 1953 2,908,534 Rietsch Oct. 13, 1959 2,990,895 Works et al July 4, 1961 FOREIGN PATENTS 538,429 Italy Jan. 25, 1956 1,025,359 Germany Mar. 6, 1958 1,058,452 Germany' June 4, 1959

Claims (1)

1. A BEARING SUB-ASSEMBLY FOR A DRILLING FLUID DRIVEN DOWNHOLE DRILLING MOTOR ASSEMBLY HAVING A HOLLOW DRIVEN SHAFT ROTATED BY SAID MOTOR, TUBULAR MEANS CONNECTED TO THE MOTOR AND SURROUNDING THE UPPER PORTION OF THE DRIVEN SHAFT THEREBY FORMING AN ANNULAR PASSAGE BETWEEN SAID TUBULAR MEANS AND THE DRIVEN SHAFT ADAPTED TO RECEIVE DRILLING FLUID DISCHARGED FROM SAID MOTOR, AND A BEARING SUB-ASSEMBLY FOR AND SURROUNDING THE LOWER PORTION OF THE DRIVEN SHAFT, SAID BEARING SUB-ASSEMBLY COMPRISING A CYLINDRICAL HOUSING ADAPTED TO ENCIRCLE THE LOWER PORTION OF THE DRIVEN SHAFT, SAID HOUSING BEING ADAPTED TO BE SECURED TO THE LOWER END OF THE TUBULAR MEANS, A BEARING SLEEVE CARRIED WITHIN THE HOUSING AND ADAPTED TO ENGAGE THE ENCIRCLED DRIVEN SHAFT, SAID SLEEVE HAVING A PLURALITY OF SPACED LONGITUDINALLY EXTENDING GROOVES IN THE FACE ADAPTED TO ENGAGE THE DRIVEN SHAFT SO THAT DRILLING FLUID MAY BE PASSED DOWN THROUGH THE GROOVES TO LUBRICATE AND COOL THE SLEEVE AND THE DRIVEN SHAFT RIDING THEREAGAINST, A PORT

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