US2085986A - Deep well turbine pump - Google Patents

Description

July 1937- J. M. LEVIER 2,085,986

DEEP WELL wRBINE PUMP Filed April 11, 19:54 3 Sheet-Sheet 1 Fgggd.

J. M. LEVIER DEEP WELL TURBINE PUMP July 6, 1937.

3 Sheets-Sheet 2 Filed April 11, 1954 Jaw flzzeuzer Julyfi, 1937. J. M; LEVIER 2,035,986

- DEEP WELL TURBINE PUMP Filed April 11, 1934 s sheets-sheet s Patented July 6, 1937 UNITED STATES PATENT" OFFICE DEEP WELL TURBINE PUMP John M. Levier, Anaheim, Calif.

Application April 11, 1934, Serial No. 720,010 7 Claims. 01. 103-102) This invention relates to deep well turbine pumps and particularly to such pumps and the casings thereof which are adapted to be used in crooked holes.

It is a matter of considerable difficulty, particularly in the case of a deep well, to drill a straight hole. In general, the subterranean water level in the United States is going down and the difficulty arising from crooked holes of substantial depth is increasing.

The principal object of the present invention is to provide an improved deep well turbine pump.

A further object of the. invention is to provide a deep Well turbine pump in which the outer casl5 ing, the drive shaft, and the drive shaft housing are suitably articulated to adapt them for use in holes having a considerable deviation from straightness, the elements referred to cooperating to maintain an efiicient and non-leaking assembly.

A further object of the invention is to provide an improved lubrication system for deep well turbine pumps.

Other objects, advantages, and capabilities will appear from the following description of a preferred embodiment thereof, taken in conjunction with the accompanying drawings, in which Figure 1 is a sectional view through the motor and associated parts at the top of the well, the preferred lubrication system being shown diagrammatically in this view;

Fig. 2 is a sectional view which may be regarded as a continuation of Fig.1, showing typical joints of the casings and shaft and illustrating the manner in which they take care of deflection;

Fig. 3 is a sectional view showing the upper end of the turbine pump and associated parts, and may be regarded as an extension of Fig. 2 on a somewhat larger scale;

Fig. 4 is a sectional view showing the lower part of the turbine pump, and may be regarded as an extension of Fig. 3;

Fig. 5 is a sectional view of a well showing the whole pump assembly in operative relation thereto;

Fig. 6 is a sectional detail view, taken on the line 6-6 of Fig. 3, showing the complementary driving elements 4| and'52 in operative relation,

and

Fig. 7 is a sectional view, taken on the line 1-1 of Fig. 6, the elements being separated for the purpose of clearness.

Referring to the drawings, the motor which drives the pump is indicated by the reference numeral I0. This motor is mounted on a base II which includes the outlet l2 for the water pumped from the well. The well itself consists of anirregular hole, indicated at I3. Preferably at the top of the well is provided a block of concrete I4 having an opening in alignment with the hole I3.

The outer housing or casing comprises a plurality of lengths of pipe of suitable diameter, designated I5. These lengths of pipe are normally manufactured in ten foot lengths. It will be un- 10 derstood, however, that in order to take care of sharp angles-at a particular location, I may use shorter lengths of pipes l5, and it will be understood that corresponding sections of the drive shaft and the drive shaft housing, hereinafter to 5 be described, will be of approximately the same length, it being preferred that the articulation of the three elements, the outer housing, the drive shaft and the drive shaft housing, shall be. located at substantially the same heights. The uppermost pipe section I5 of the main housing is threaded into the base I I so that it communicates with the water outlet I2. pipe-section I5 has secured thereto, preferably by screwing it onto its threaded end, a ring I6, the outer surface of which is spherical and adapted to cooperate with the corresponding surface of a ring ll which is secured to the length of the pipe by the mounting of the ring I6 thereon. The rings I6 and I1 constitute ball and socket joints providing for a limited articulation in all, directions. The ring I1 is bolted to a flanged ring I8, a suitable gasket I9 being interposed therebetween. This ring I8 is threadedly mounted on the next lower pipe section I5 which, in turn, carries at its lower end another ring I 6.' The number of such universal joints and the number of pipe sections I5 employed, will depend upon the depth to which the housing must extend to obtain water. I 40 Each ring I! islprovided on its inner spherical surface with an annular groove which receives packing material 20. This packing material is of somewhat greater volume than the groove in which it is located so that when tension is applied 45 to the casing as a whole the packing material 20 will be compressed tightly against the adjacent ring I6 and leakage from the outer housing will thereby be effectively prevented.

The lowermost housing section I5 is connected by a similar universal joint with a relatively short section of pipe 2! of the same diameter. At its lower end the pipe H is rigidly secured to the turbine pump 22 whichwill now be described. The pipe 2| carries at its lower end the flanged 5 At its lower end the a r collar 23 which is bolted to the upper flange of the pump 22. The pump 22 comprises rotors 24 suitably located within rotor chambers and having an outlet 25 at the upper end whereby water is forced into the casing formed by the pipe sections l5. Below the rotors 24 the pump 22 is provided with a water receiving chamber 25, the wall of which is provided with lateral openings 28 whereby the water enters. The spindle 21 of the turbine pump carries the rotors 24 and extends through the chamber 25 into a bearing chamber 28 therebelow. A gland 29 is provided in the wall between the chambers 25 and 28 so as to prevent leakage from one chamber to the other. The chamber 28 may suitably be bolted to the lower end of the chamber 25 and it includes a thrust bearing 30 upon which the lower end of the shaft 21 is mounted. At its lower end the shaft 21 has mounted thereon a shouldered collar 3| which rests on the thrust bearing 30.

Mounted on the lower end of the housing 28 is a downwardly projecting chamber 32 which is utilized for a supply of oil for the bearing 30, which oil is supplied by a pipe 33 which will hereinafter be more fully described in connection with the oiling system. A pipe 34 also enters the chamber 32 and is provided with an internal extension 35 which terminates near the bottom of the chamber 32 so that any water or sludge which may leak into or which may form in the chamber 28 can be withdrawn to the surface.

The upper portion of the pump shaft 21 extends upwardly through a packing gland 36 which is contained within tubular elements 31 and 38. The former is threadedly mounted on the upper end of the pump 22 and the tubular member 38, which is of somewhat larger diameter than the tubular member 31, is threadedly mounted on the tubular member 31. The packing material of the gland 35 is contained within the tubular member 38 and is compressed by means of a spring 39, also located within the tubular member 38. The tubular member 38 has threaded thereinto a bearing sleeve 40 which provides an abutment for the spring 39. The bearing sleeve 40 is an element which is provided in all the joints of the housing and it will be described in detail in connection therewith. The upper end of the shaft 21 has threaded thereon a universal'driving element 4|, regarding which the same remarks apply.

The construction of the drive shaft and the drive shaft housing, with particular reference to a point of articulation,- will now be described. The drive shaft housing comprises a plurality of sections 42, the upper ends of which are threadedly connected to a sleeve 40, which sleeve has the same external diameter as the housing section 42. The upper end of the sleeve 40 is internally stepped so as to receive a bearing bushing 43. The drive shaft comprises a series of sections 44 which are substantially the same length as the pipe sections 42 and I5. At their upper ends they are threaded to receive universal driving elements 4| The lower edge of the driving element 4| rests upon a flange at the upper end of the bushing 43 so that the weight of the drive shaft is communicated thereby to the drive shaft housing. The next superior drive shaft housing section 42 rests upon the upper end of the sleeve 40. Where there is no angular deviation the lower end of the last named section 42 abuts upon the upper end of the sleeve 40. When, however, there is an angular deviation, there is a space between the lower end of the housing section 42 and the upper end of the sleeve 48 except at one point where they touch. An outer sleeve 45 is arranged so as to extend over the sleeve 48 and over the ends of both sections 42 adjacent thereto, this sleeve being of somewhat greater diameter than the pipe sections 42 or sleeves 40, so as to provide for the deviation referred to.

Each end of the sleeve 45 is flared so as to provide an annular pocket for the reception of packing material 46. This packing material is compressed by flanges of packing rings 41 which are located around the pipe sections 42. The packing rings 41 at each end are compressed together by means of rods 48 which extend through the bores in the sleeve 45. The sleeve 45 is formed as an integral part of a spider 49, the outer diameter of which is substantially the same as the internal diameter of the ring |8 so that the spider may move freely within the ring l8 to a limited extent.

The driving element 4| is recessed on its upper face, as indicated at 50. This recess is provided with internal teeth 5| so that it may operatively be engaged by the complementary toothed element52 which is in the form of a small gear out upon the lower end-of a short shaft 53. The teeth 52 are provided with a certain amount of camber in the longitudinal direction so that they may cooperate with teeth 5| of the driving elements 4| within the degree of deflection which it is intended to. provide. The short shafts 53 are rigidly mounted, for example by means of conplings 54, upon the lower threaded ends of the shaft sections 44. Short shafts 53 increase the effective lengths of the shaft sections 44 so as to correspond with the increase of length provided in the drive shaft casing by the provision between the pipe sections 42 of the sleeve 48 and in the main or outer casing by the elements which connect adjacent pipe sections l5. It will readily be understood that if the shaft sections 44 were made slightly longer the driving elements 52 could be directly mounted thereon. I prefer to provide small openings 5|a in the driving elements 4| to permit lubricant and sediment to escape from the recesses 58.

The shaft 55 of the motor I0 projects downwardly into the drive shaft housing and at its lower end is operatively connected to the adjacent drive shaft section in the same manner as the drive shaft sections are operatively connected. The uppermost pipe section 42 of the drive shaft housing extends freely through an opening 56 in the upper wall of the water outlet l2. Leakage of water is prevented by means of packing 51 located therearound. A plate 58 is threaded onto the upper projecting end of the-uppermost pipe section 42 and a gland 59 is mounted thereon so as to prevent escape of oil from the drive shaft housing. Stud bolts 60 mounted in the head casting project upwardly through openings in the plate 58. By tightening nuts 6| on the stud bolts pressure may be applied upon the plate 58, which pressure is communicated all along the elements constituting the drive shaft housing, the pressure eventually becoming exerted upon the stationary portion of the pump 22. As indicated above, the elements constituting the drive shaft housing have a certain freedom of longitudinal movement with respect to the elements constituting the main housing Consequently, the pressure applied to the pump 22 will result in tension being applied upon the elements constituting the main or outer housing. The result of this tension is to apply pressure which forces therings ll downwardly with respect to the rings Hi. In this way the packing rings 20 are strongly compressed at the points of articulation and the resuit is that a water-tight main housing is provided, irrespective of the depth to which the housing may go. This sealing effect is also accentuated by the weight. of the drive shaft housing and also by the weight of the drive shaft elements which, as has been pointed out above, are carried by the drive shaft housing. The sealing effect is also accentuated by the weight of'the water within the casing when the pump is being operated. V

The lubricating system will now be described. For the purpose of lubricating the drive shaft elements throughout their length, oil is supplied by a pipe 62 into the uppermost pipe section 42 of the drive shaft housing. This oil passes downwardly through the drive shaft housing lubricating all the driving elements and bearings therein. For the purpose of facilitating the downward passage of the oil, it is preferred to provide a plurality of ducts 63 in each of the sleeves 40. The oil is eventually arrested bythe packing 36 immediately above the pump 22. The oil is adapted .to pass from the tubular member 38 through a flexible metal tube 64 which passes upwardly be tween the drive shaft housing and the main housing, passing through the openings in the spiders 49. The flexible metal tube 64 terminates at the top of the well and is connected to a nipple 65 mounted in the casting l. The nipple 65 is connected to an exterior tube 66.

The flexible tubes 33 and 34, which connect into the oil reservoir 32 as previously described, extend upwardly on the outer side of the pump 22, being protected from injury by a cover plate 67. These pipes terminate adjacent the upper end of the pipe section 2| and communicate through suitable connections thereon with flexible pipes 68 and 69. These flexible pipes extend upwardly throughout the length of the main casing between the main casing and the drive shaft casing, in the same manner as the pipe 64. The pipe 68 is connected to a nipple 1B and the pipe 69 is connected to a nipple ll. These nipples extend to the outer side of the water outlet in the same manner as the nipple 65 previously described, and are connected respectively to flexible pipes 12 and 13.

The pipe 62 receives oil from a tank 14, which oil preferably passes through an oil filter 15 and a sight feed gauge 16. The supply of oil to the pipe 62 is controlled by means of a valve 11. This oil which passes downwardly through the drive shaft housing, as described above, emerges by pipe 66 and may be drawn off at a regulated rate by means of a valve 18. The pipe 66 may, however, communicate with another oil tank 19, and a valve 80 enables this supply to be regulated at will. The oil tank 19 is connected to the pipe 72 and a valve 8| is provided in this pipe to control the supply of oil. The oil thus supplied descends downwardly between the housings, being carried through pipe 68, from which it passes to pipe 33 which empties into chamber 32. Oil, together with any water, sludge or dirt, passes upwardly through pipes 35, 34, 69 and 13, the rate of the outlet being controlled by means of a valve 82. In order to apply automatically an appropriate degree of pressure to the oil system which will prevent entrance of the water into the drive shaft housing or into the thrust bearing compartment 28, by means of leakagethrough the glands to meet individual circumstances.

and joints, I prefer to provide a water pipe 83 which communicates with the water outlet of 'the pump and with a water tank 84. The upper end of the water tank is placed into communication with the upper end of the oil tank 14 by meansof a pipe 85 containing a valve 86. It will readily be understood that when the pump is working at high pressure, the pressure of the water is applied to the tanks 14 and 19 and that the whole oiling system is maintained under a substantial pressure. This pressure, of course, will be greater at progressively lower points'in the well on account of the head of oil above these points.

In installing the improved pump, it will be understood that the well is drilled and that a survey is made to determine upon points where considerable angular deviation will be located. If necessary, special short lengths may be employed In general, however, standard lengths of pipes and shafts are used whenever possible. The whole device is assembled from the bottom up, that is, the

pump and its connections are first arranged and adjusted. The pump is lowered into the well and additional sections are built onas are required. Last-bathe topmost sections are secured to the casting I I and finally the motor is mounted thereon. It is to be noted that the pump shaft 21 is adjusted at the bottom by means of the step collar 3| so as to bring the rotors 24 into exact position. This is done before the pump is in-,

stalled in the well, by means of the nuts on either side of the step collar 3i.

During the assembly anchor chains 81 are secured to the rings IT and to the pipe sections [5 above them, for the purpose of limiting the amount of rotation which may take place between adjacent pipe sections I5 and between the lowermost pipe section l5 and the pump unit.

Although the invention has been disclosed in connection with the specific details of a preferred embodiment thereof, it must be understood that such details are not intended to be limitative of the invention except in so far as set forth in the accompanying claims.

Having thus described my invention, what I claim as new and desire to secure by Letters Patent of the United States is:

1. In a deep well turbine pump assembly, in combination, an outer casing, a drive shaft and drive shaft housing therein, said outer casing comprising pipe sections and ball and socket connections between them providing free deflection at said connections between adjacent sections, means adjacent said ball and socket connections providing articulation in the drive shaft and drive shaft housing, and means for applying compressive force upon said drive shaft housing whereby said outer casing is subjected to tension and the ball and socket connections are held in liquidtight relation.

2. In a deepwell turbine pump. assembly, in combination, an outer casing formed of pipe sections, a housing within said casing rigidly connected thereto at top and bottom, ball and socket I outer casing and said packing is compressed to establish water-tight joints.

3. In a deep well turbine pump assembly, an outer casing, a drive shaft and drive shaft housing all formed of sections of substantially the same length, ball and socket elements connecting the outer casing sections providing a certain amount of deflection at said connecting elements between adjacent sections, spacer elements adjacent said ball and socket elements and freely slidable relative thereto, said spacer elements receiving adjacent ends of drive shaft housing sections freely to permit a certain amount of deflection between adjacent sections at said spacer elements, and packing means associated with said spacer elements for maintaining watertight relation between the interior and exterior of the housing.

4. In a deep well turbine pump assembly, an outer casing, a drive shaft and drive shaft housing all formed of sections, ball and socket elements connecting the outer casing sections providing a certain amount of deflection between adjacent sections, spacer elements adjacent said ball and socket elements and freely slidable relative thereto, said spacer elements receiving adjacent ends of drive shaft housing sections, at least one of said ends having a free fit with respect to said spacer element so as to permit a certain amount of deflection therebetween, packing means associated with said spacer elements for maintaining water-tight relation between the interior and exterior of the housing, sleeves secured to said housing sections, and driving connections secured to said shaft sections, said connections resting on said sleeves whereby the weight of the driving shaft is transferred to the drive shaft housing along its length.

5. A deep well turbine pump assembly, comprising a deep Well turbine pump, a drive shaft therefor extending from the surface, a drive shaft housing, a main outer casing, said shaft, housing and easing being formed of sections of substantially the same length and having ball and socket members forming the connection between adjacent casing sections to provide a certain degree of deflection between adjacent casing sections at said connections, bearings carried by said housing at the adjacent ends of the housing and casing sections for said shaft sections, and means adjacent the ball and socket means providing articulation in the drive shaft and drive shaft housing.

6. In a deep well turbine pump assembly, an outer casing, a drive shaft and drive shaft housing all formed of sections of substantially the same length and having adjacent connections to provide a certain amount of deflection between adjacent sections at said connections, the connections for the outer casing being ball and socket joints, sleeves associated with said ball and socket joints overlapping adjacent drive shaft housing sections, packing means between the sleeves and drive shaft housing sections, and internal and external gear elements operatively establishing the connection between adjacent drive shaft sections.

7. In a deep well turbine pump assembly, an outer casing, a drive shaft and drive shaft housing all formed of sections of substantially the same length and having adjacent connections to provide a certain amount of deflection between-

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