US2733663A

US2733663A - Deep well pumping apparatus

Info

Publication number: US2733663A
Authority: US
Publication date: 1956-02-07
Anticipated expiration: 1973-02-07

Description

Feb. 7, 1956 5. J. E. MARSHALL DEEP WELL PUMPING APPARATUS 3 Sheets-Sheet 1 Filed Sept. 20, 1954 5. J. E. Marsha INVENTOR ATTORNEY 7, 1955 I 5. J. E. MARSHALL 2,733,663

- DEEP WELL PUMPING APPARATUS 3 Sheets-Sheet 2 Filed Sept. 20, 1954 m v mm gm S J E. Marsha INVENTOR @z j z Feb. 7, 1956 3, J. E, MARSHALL 2,733,663

DEEP WELL PUMPING APPARATUS ATTORNEY United States Patent DEEP WELL PUMPING APPARATUS Samuel]. E. Marshall, Dallas, Tex. Application September 20, 1954, Serial No. 457,121

12 Claims. ((31. 103-118) This invention relates to pumps especially adapted to deep wellpumping and it has particular reference to a fluid and gas operated mechanism for the continuous recovery of fluids from wells.

The principal object of the invention is to provide a gas or hydraulically operated pump adapted to be lowered into. a well through its casing by any conventional running tool suited to the purpose and which is also equipped to retrieve the pump. The said pump has been designed withsa view to reducing to the very minimum the number of moving parts and to insure that the moving parts, essentially one or more hydraulic motors and one or more pumps, are protected against undue wear by equalizing the fluid pressures to which these elements would normally be exposed.

Another object of the invention is to provide a deep well pumpcomposed of an elongate manifold casing adapted to be suspended on the tubing string in a well and a pump unit assembly which is lowered by a wire line into-the manifold casing subsequent to the establishment of the latter in the well, the said manifold casing being equipped with a landing nipple which is capable of extension to accommodate a pumpunit assembly having a greaternumberof pumps and motors, thus to increase the capacity of the'pump as a whole, it being estimated that the capacity of each individual pumping unit of the apparatus is'substantially' 150 barrels per day;

Another object of the invention is to provide a highly flenihle pumping apparatus whose individual hydraulic motors are operated by fluid pumped. through macaroni tubing fromthe surface to enter the pumps through a power fluid manifold in the casing, thus to actuate a rotor carrying; both the; pumps and motors at a speed suflicient to create pump pressures in. excess or the hydrostatic well pressure to insure free and continuous how of well fluid from the'wel'l. The well" fluid enters the pumping apparatus through a suction manifold of, its casing. and; com: mingles with the power fluid in a discharge manifold. in its course to the surface, a portion of which fluid is. continuously recirculated through. the motors.

With the foregoing and other objects in view, the inuentionhas; particular reference. to certain salient featuresthe course ofpower and'well: fluidv as the latter is pumped from, a well.

Figure 5 is a transverse sectional view'taken through one of the fluid motors, on line 5---5 of. Figure7.

Figure 6 is a transverse sectional. view taken. through one of the pump units on line 66 of Figure 8.

Figure 7 is a view similar to Figure 4, taken on line 7-7 of Figure 3 and reveals the recirculation of power fluid through the apparatus.

Figure 8 is a longitudinal sectional view taken on line 88 of Figure 3-, and

Figure 9 is a. fragmentary sectional view showing an enlargement of one of the" fluid discharge ports in the shell or body of the pump assembly and the opposing sealing elements.

Continuing with a more detailed description of the drawing, reference is primarily made to Figures 1 and 3 wherein 10 generally indicates the casing of a well into which is suspended the pumping apparatus broadly idcnti fied by reference numeral 11' by'means of a string of well tubing 12, the upper end of the apparatus being threaded to receive a collar 13 by which it is connected to the tubing 12.

Specifically, the apparatus 1-1 consists of a tubular casing 14 which will be hereinafter referred to as a landing nipple, the said landing nipple having'welded or otherwise secured thereto a power fluid manifold 15, a pump suction manifold 16 and a discharge manifold 17'. The upper fluid manifold 15 is in communication at its upper end with a pipe connection 18 which is, in turn, interiorly threaded to receive the lower end of a string of macaroni tubing 19 through which power fluid from the. surface is pumped into the apparatus. p

The landing nipple 14 has a pair of' high

pressure fluid inlets

20 and 21, both of which are embraced by the power fluid manifold 15, the" upper inlet 2% serving the upper fluid motor 22 while the lower inlet 21 serves the lower fluid motor 23. Further reference to these motors will be made presently.

The pump suction manifold 16 coverswell fluid outlet and

inlet ports

24 and 25, respectively, as shown in. Figure 4 and through which well fluid is influenced upwardly the upper and

lower pumps

26 and 27.

The discharge manifold 17 is considerably longer than either the power fluid manifold 15 or the pump suction manifold 16and covers the discharge port 28 of the lower motor 23; the'discharge port 29 of the lower pump 27; the discharge port 30 of the upper pump 26and the discharge port 31 of. the upper motor 22'. The upper end of the manifold-17 communicates with the upper end of the landing nipple 14 from whence the commingled. power and well fluids are forced upwardly by the combined pres-- sures of the

pumps

26 and 27 to the surface through the tubing 12'. 4 The pump assembly is composed of a tubular shell or body 32 (Figure 2) which. is interiorly threaded-at its upper end to receive the exteriorly threaded lower end of a carrier or stem. 33, providing a connection for a suitable. running tool on. a. wire line, not shown, for lowering' the pump assembly into and withdrawing the same from the landing. nipple 14 while the latter is installed in a well An annular, internally threaded ring 34 locks the stem in position in the top oil the shell- 32.

At longitudinally spaced intervals throughout the length of the shell 32 there is provided an annular boss 35 (Figure 9). Each. annular boss has an annular groove 36" therein and within each groove 36 there is arranged an Ol-ring 37 hearing against a non-extrusion ring 38. By observing Figures 2, 4 and. 7, it will be. seenthat the'packing assembly composed of the O-rings and non-extrusion rings is disposed one on each side of, the fluid-inlet and outlet openings 'in the shelLSZ-defining annular fluid chambers or spaces aboutthershel-l when the latter is con-. fined within the landing nipple 14, such as indicated by reference numerals 32a in Figure and 32b in Figure 6, opposite the upper motor 22 and the upper pump 26, respectively. The longitudinally spaced packing assemblies are adapted to resist full pressure of the power fluid circulated through the

motors

22 and 23 as well as closing out all pressures at the inlet end of the pump which would tend to interfere with the inflow of fluid from the well.

The shell 32 is provided adjacent its upper end with a port 39 which registers with the high pressure power fluid inlet port of the landing nipple 14. Immediately below the port 39 is a discharge port 40 which registers with the discharge port 31 of the landing nipple and through which fluid discharges from the upper fluid motor 22 into a discharge manifold 17. Next below the discharge port 40 of the shell 32 is another discharge port 41 which registers with the discharge port 30 of the landing nipple 14 and which accommodates the upper pump 26. Below the discharge port 41 is a suction port 42 which registers with the port in the landing nipple to serve both

fluid pumps

26 and 27. A discharge port 43 in the shell 32 registers with the discharge port 29 for the pmp 27 and still another lower port 44 in the shell 32 registers with the fluid motor discharge port 28 which serves the lower motor 23. A high pressure inlet port 45 in the shell 32 registers with the power fluid inlet port 21 of the landing nipple, as may be seen in Figure 7. All of the described ports are in communication with the annular chambers defined by the O-rings 37 and the walls of the shell 32 and landing nipple 14 and as stated, each of the several ports above mentioned is flanked by O-rings 37 and non-extrusion rings 38 in grooves 36 in the walls of the shell 32, the O-rings being in sealing engagement with the inner wall surfaces of the landing nipple 14. The bottom O-ring 37 performs an additional vital function in the sense that it separates the hydrostatic well pressure and the power fluid pressure which latter is greater than the hydrostatic pressure and counters the force thereby imposed, tending to thrust the pump assembly upwardly in the landing nipple 14.

The lower end of the shell 32 is interiorly threaded to receive the upper threaded end of a base plug 46 for a rotor 47. The base plug 46 and consequently the rotor 47 is sustained by a sleeve or stop 48 against which the base bears and immediately above the lower end of the base an annular groove 49 is formed to receive an O- ring seal 50, which closes off hydrostatic pressures originating in the well and insures free upward flow of well fluid through the strainer 51 whose upper end is threaded into the lower end of an axial bore 52 in the base 46 whose upper end is in communication with a plurality of radial passages 53 in the base 46, all of which communicate with the suction port 24 of the landing nipple 14 so that fluid influenced upwardly from the well by the

pumps

26 and 27 may flow through the suction manifold 16.

The rotor 47 is fabricated from a cylindrical bar or mandrel which is substantially coextensive with the space in the shell 32 between the stem 33 and the rotor base 46. It is provided, however, that a disc-like bearing 54 be interposed between the upper end of the rotor 47 and the stem 33 and a similar bearing is interposed between the lower end of the rotor and the base 46. There is suflicient space between these disc-like bearings and adjacent parts to be occupied by fluid under pressure providing a film of oil at the ends of the rotor, thus minimizing friction. The upper end of the rotor 47 is embraced by a sleeve 55 which has a longitudinal fluid by-pass 56, shown in dotted lines in Figures 4 and 7, which communicates with a diametrical channel 54a in the underside of the upper bearing 54 and permitts high pressure fluid from

entrance ports

20 and 39 to enter the small clearance between the bearing 54 and its adjacent parts for the purpose above stated. In like manner, a rotor sleeve 57 embraces the lower end of the rotor"47 and has a bypass 58 which effects communication between the

high pressure ports

21 and 45 and the diametrical channel 54a 4 in the lower bearing 54 to introduce a film of oil between the bearing 54a and the lower end of the rotor 47 for the same reasons as explained above.

Against the upper end of the rotor 47 there is provided a group of diametrical, circumferentia-lly spaced slots 59 (Figure 5) which intersect at the longitudinal axis of the rotor. In each of the slots 59 is disposed a vane 60 for radial sliding displacement. The outward movement of these vanes is limited by the walls of the ovate chamber 61 of a rotor cylinder 62. Diametrically opposed, flattened surfaces 63 in the exterior wall surfaces of the rotor cylinder 62 provide vertical fluid chambers 64 into which power fluid is discharged by the vanes 60 through ports 65 in the walls of the rotor cylinder after having entered through ports 66 from the

ports

20 and 39 of the landing nipple 14 and shell 32, respectively, to actuate the motor 22.

Disposed immediately below and supporting the rotor cylinder 62 is a rotor sleeve 67. This sleeve likewise has diametrically opposed, flattened sides as indicated at 68 in Figure 8, thus to define vertical fluid passages for conveying fluid discharged by the motor 22 to the

discharge ports

31 and 40 in the landing nipple 14 and shell 32, respectively, such fluid being conveyed upwardly through the manifold 17 to the tubing 12 along with fluids discharged from the lower motor 23 as well as that discharged from both the

pumps

26 and 27.

It will be observed in dotted lines in Figure 5 that the rotor 47 is actually hexagonal in transverse section through the

motors

22 and 23, thus providing flats 69 between the vanes of the motors. These flats are to provide relief for the fluid between the outer ends of the vanes 60 and the walls of the chamber as they traverse the fluid exhaust ports 65.

Surrounding the rotor 47 below the rotor sleeve 67 is a pump cylinder 70 (Figure 6). At this point, the rotor 47 is provided with a group of diametrical slots 71 which intersect the longitudinal axis of the rotor and in these slots are slidably disposed blades 72, operating in the ovate chamber 73 of the pump cylinder 70. Diametrically opposed flattened sides 74 of this cylinder provide vertical fluid passages 75 by which communication is eflected between the two

pumps

26 and 27, there being a third rotor sleeve 76 below the pump cylinder 70, as may be seen in Figures 4, 7 and 8 and which also has flattened sides to continue the passages 75 to the lower pump 27.

The rotor 47 is also hexagonal in transverse section through each of the

pumps

26 and 27, as in the case of the

motors

22 and 23, in order to define flats 76a (Figure 6) to relieve fluid which would otherwise be trapped between the vanes 72 and the walls of the chamber 73 as the vanes traverse the discharge ports 77a of the chamber 73.

The lower motor 23 is identical in construction and operation to the motor 22 just described. Moreover, the lower pump 27 is of the same construction and operates in the same manner as the pump 26 which has been described above, hence it is considered that the detailed description of the upper motor and pump will suffice for the lower motor and pump 23 and 27, respectively.

It is considered an important characteristic of the invention that the

motors

22 and 23 are each aided in their starting action by power fluid introduced behind the vanes 60 by way of axial passages 77 in the rotor 47 which extend axially in the rotor 47 from the diametrical passages 54a in the end bearing plates 54 to the space behind the vanes 60 of the

motors

22 and 23. Fluid thus entering behind the vanes 60 tends to impose an outward radial thrust thereon for the initial starting action of the motors. The fluid is bled from the motors through axial passages 77b, from which a part of the fluid escapes through a lateral passage 78 in the rotor 47, which effects communication between the axial passage 77b and an annular groove 77c (Figure 8) in the external surface of the rotor and from which groove fluid emerges into the fluid discharge passage 68 through the orifice 77d. The remaining fluid passing downwardly through the axial passage 77 greases" continues through an axial passage 77a (Figure ,8') into h s e h the v nes 72 Q he pr r mp'z o thus thrust the vanes radially outward; From the pump 26 fluid is bled through an axial passage 77 from which part of the fluid moves through a lateral passage 77g in the 'rotor 47 intoan annular groove 77h in the wall ofthe rotor byway of an orifice 77;, to thus lubricate between the rotor 47 and the rotor sleeve 76. The remaining fluid continues downwardly through an axial passage 77 into the space behind the vanes of the lower pump 27 to extend the vanes thereof as in the case of the upper pump 26 and the motor 22.

Fluid' under pressure from the power fluid inlet of the lower motor 23 passes through the lower by-pass 58' into the diametrical channel 54a of the lower rotor bearing 54,

thence thrqugh the axial fluid passage 79 and into the space behind'its vanes 60 and is" bled therefrom through axial fluid passage 72 1 from which a part of the fluid moves through'a-l'ateral passage 78 into the annular space 78b in the rotor 47 and is released therefrom for discharge through an orifice 781: (Figure 8') in the rotor. sleeve'cmbra'cing the rotor 47 between; the lower pump and

motor

27 and 23", respectively. Communication is'eflected' between the axial passage 72a and the lower pump 27 through an axial fluid passage 78d.

From the foregoing it will be seen that balanced fluid pressures are maintained on the vanes of both of the

motors

22 and 23 as well as on the vanes ofboth pumps 26 and 27 while at the same time lubricating the space between the rotor sleeves and rotor.

In operation, the manifold casing II is run into the well casing. 10 on the string of tubing 1 2 with the macaroni tubing. 19 Strung with the tubing 12". After the manifold casing 11 has been submerged in the fluid of the well, thepump assembly- 32 is run into the manifold casing by. means of a wire lineto whichfi's attached a running tool' adaptedfor releasable engagement. with the stem or pump carrier33, and the landing nipple 14 is set down on the stop collar 48. A pup joint 80 (Figure 1) is suspended from the lower end of the manifold casing 11 before it is run into the well and below the pup joint is the conventional standing valve, not shown.

Power fluid is pumped from the surface downwardly through the macaroni tubing 19 and this fluid enters the inlet ports to the

motors

22 and 23 by way of the manifold and the registering

ports

20 and 39 of the landing nipple 14 and shell 32, respectively, and the registering

ports

21 and 45 of these elements to serve respectively the upper motor 22 and the lower motor 23. Also, the fluid passes into the motor cylinders 62 by way of its inlet ports 66 to cause the vanes 60 to rotate. At the same time, fluid enters at each end of the rotor 47 by means of the by-passes 56 in the motor cylinders and channels 54a of the bearings 54 to equalize the pressures on the ends of the rotor, causing the latter to float during ,its high speed rotation.

Power fluid also enters the space within the rotor 47 rearwardly of the blades or vanes 60 at the same time rotary thrust is applied to revolve the vanes so that the latter are at all times urged operatively outward against the walls of the chamber 61.

Rotation of the rotor 47 by the vanes 60 of both

motors

22 and 23 causes the

pumps

26 and 27 to create a partial vacuum in the suction manifold 16, to fill which fluid from the well rises through the strainer 51, through the suction manifold 16 and into the inlet ports of both pumps as indicated by the arrows in Figure 8. Fluid elevated by pump suction is discharged into the manifold 17, along with the power fluid discharged by the two

motors

22 and 23. The commingled fluids are forced to the surface by the combined pressures developed by the pumps through the tubing 12 and a part of the fluid is recirculated under pressure through the pumping apparatus after having been suitably cleansed to remove foreign matter therefrom.

It is clearly evident from the drawing and the fore going; description that in wells producing considerable saltwater along with the-oil, it is desirable to increase the capacity of the pump. This is easily accomplished by extending the landing nipple 14 to accommodate two or more of the assemblies shown and described.

Manifestly, the construction as shown and described is capable of some modification, and such modification as may be construed to fall within the scope and meaningof' the appended claims is also considered to be within the spirit and intent of. the invention.

' What is claimed is:

1. In a hydraulic deep well pump, a manifold casing adapted for suspension on a string of tubing in a well and comprisinga landing nipple having a power fluid inlet manifold, a well suction manifold and a discharge manifold, each having'ports in communication with said landing nipple, a tubular shell slidably mounted in said landing nipple and having ports in communication with) the ports of said' landing nipple, annular, longitudinally spaced packing means carried by said shell in sealing engagement with the walls of said landing nippleon opposite sidesof said ports, an elongate rotor rotatable in said shell, longitudinally spaced fluid actuated vane motors carried by said rotor, longitudinally spaced fluid pumpscarried by'said rotor, means for introducing power fluid from the surface to said motors through said inlet manifold to actuate the same and to' propel said rotor and pumps to influence upward travel of well" fluid into and through the ports of said landing nipple, said pumps and into said discharge manifold to commingle with power fluid discharged by said motors in its upwardcourse through said tubing string, means for introducing power fluid into said shell at each end of said rotorat equal pressures to suspend the same in said shelland means for injecting power fluid into said' motorstoextend the vanes thereof. a

' 2.. In a hydraulic deep well pump, an elongate, tubular landing nipple having a power fluid inlet port, a well fluid inlet port and a plurality of fluid motor and pump discharge ports, a manifold embracing said power fluid inlet port, a suction manifold for said well fluid port and a discharge manifold for said discharge ports, a tubular shell slidable into said landing nipple having ports in register with the ports of said landing nipple, packing means carried by said shell in sealing engagement with said landing nipple on opposite sides of each of said ports, a rotor in said shell, a plurality of fluid motors spaced longitudinally in said rotor, each having communication with the manifolds of said power fluid inlet and said discharge ports, said motors each comprising a series of radially movable vanes, a plurality of fluid pumps in said rotor, each comprising radially movable vanes, means for introducing power fluid into the manifold of said power fluid inlet port to actuate said motors to propel said motor and pumps to suck well fluid into said suction manifold through said well fluid inlet port, its manifold and said pumps into said discharge manifold for admixture with the discharge fluid of said motors.

3. The structure of claim 2, and means for the fluid counterbalancing of said rotor by the introduction of power fluid into said shell at each end of said rotor at equal pressures.

4. The structure of claim 2, and means for introducing power fluid under pressure behind the vanes of said fluid motors to effect outward radial displacement thereof as a starting action for said motors.

5. The structure of claim 4, in which the fluid introduced behind the vanes of said motors is released into an annular passage about the rotor for lubricating the walls thereof.

6. A deep well hydraulic pump comprising an elongate, tubular landing nipple having a well fluid inlet port adjacent its lower end and a power fluid inlet port spaced above said well fluid inlet port, a series of fluid discha-rge ports, a tubular shell slidable into said landing nipple, annular packing means spaced longitudinally on said shell in sealing engagement with the walls of said landing nipple on opposite sides of each of said ports, an elongate rotor rotatable in said shell, a fluid motor spaced from each end of said rotor, each of said motors comprising vanes movable in radial slots in said rotor, a pair of fluid pumps spaced apart between said motors, each comprising vanes slidable in radial slots in said rotor, means eifecting communication between each of said motors and the power fluid inlet ports and said discharge ports, means eifecting communication between said well fluid inlet port and said pumps and between said pumps and said discharge ports for the upward passage of fluid from a well, means for introducing power fluid into said power fluid inlet port to actuate said motors to revolve said rotor and to operate said pumps.

7. The structure of claim 6, said rotor having axial fluid passages at each end for the ingress of power fluid into said motors behind their vanes to efiect outward radial thrust thereon as a starting action of said motors; said fluid being discharged into annular grooves in said rotor between its walls and said sleeve to lubricate said rotor.

8. The structure of claim 6, and means for by-passing apart ofsaid power fluid into said shell at each end of said rotor in equal pressures to suspend the same for free rotation in said shell.

9. A deep well hydraulic pump comprising an elongate landing nipple having a well strainer on its lower end, an elongate tubular shell slidably disposed in said landing nipple, said shell and said landing nipple having registering power fluid inlet ports, well suction ports communicating with said well strainer, and fluid discharge ports, packing means on said shell in sealing engagement with said landing nipple on opposite sides of each of said ports, an elongate rotor rotatable in said shell, a plurality of fluid vane motors spaced longitudinally in said rotor and having communication with said power fluid inlet ports and said discharge ports, a plurality of.

fluid pumps spaced longitudinally in said rotor and having communication with said well suction ports and said discharge ports and means for introducing power fluid under pressure into said power fluid inlet ports to actuate said rotor and pumps to influence well fluid upwardly through said suction ports, said pumps and into said discharge ports for admixture with fluid discharged by said motors.

10. The structure of claim 9, and means to floatingly suspend said rotor by power fluid introduced under equal pressures into said shell at each end of said rotor.

11. The structure of claim 9, said rotor having axial fluid passages above and below each of said fluid motors for maintaining internal fluid pressure on the vanes of said motors to impose a starting thrust on said vanes, the fluid being discharged through one of said passages exteriorly of said rotor to lubricate the same between said rotor and shell.

12. The structure of claim 9, and a rotor sleeve embracing said rotor between said fluid motors and said pumps, each formed to define longitudinal and circumferential fluid passages between said shell and said rotor to eifect communication between said motors and their respective intake and discharge ports and between each of said pumps and their respective intake and discharge ports and with each other.

References Cited in the file of this patent UNITED STATES PATENTS 1,403,699 Loewenthal et al. Jan. 17, 1922 1,818,455 Bigelow Aug. 11, 1931 1,896,108 Simmons Feb. 7, 1933 1,980,985 Deming Nov. 20, 1934 1,980,986 Deming Nov. 20, 1934 2,022,781 Pigott Dec. 3, 1935 2,202,439 Topanelian, Jr May 28, 1940