GB2152587A - Helical down-hole machine - Google Patents

Abstract

In a helical down-hole machine (a motor or pump) having helical rotor sections 5, 6 and helical stator sections 3, 4 forming cavities of variable volume for the axial passage of fluid therethrough, identical rotor sections 5, 6 or identical stator sections 3, 4 are rigidly interconnected with at least one of the connections comprising a detachable frictional joint. Such joint is formed by a projection 9, 11 provided at the end of one such section 4, 6 and a corresponding recess 10, 12 provided at the end of the adjacent section 3, 5, the cooperating projection and recess being forcibly secured against relative angular and axial displacements during rotation. The projection and recess may be shaped as a truncated cone. <IMAGE>

Description

SPECIFICATION Helical down-hole machine This invention relates to drilling technology, and more specifically to helical down-hole machines.

The down-hole machine embodying the present invention may be used with advantage to drive rock-breaking tools in oil and gas drilling.

The machine may operate as a motor, when drilling oil or gas wells, cleaning pipes and bottom-hole milling, i.e. when it is necessary to employ it as a drive motor to the output shaft of which a bit is attached, and as a pump, particularly for oil recovery, lifting water or pumping other fluids.

The essence of the invention resides in that in helical down-hole machine wherein a plurality of sections defined each by arranged with a preselected eccentricity a helical rotor and a helical stator to form cavities of variable volume for the passage of fluid therethrough are disposed in series axially, indentical elements of these sections being rigidly interconnected, according to the invention, the rigid connection of at least one of these identical elements is detachable through the use of a friction coupling fashioned as a projection-and-recess assembly, the projection having the form of a body of revolution provided at the end of one of the elements of the section, the recess being provided at the end of the adjacent element of the section and having a shape conforming to the shape of the projection, the assembly being secured against angular and axial displacements by a forcibly induced external force.

Preferably, the projection and the recess are provided at the ends of adjacent rotors.

In this case the external force will be induced during operation of the machine by virtue of forces produced under the action of a pressure drop acting also on the rotors.

The above arrangement is recommended for machines of small diameter.

When there is no limitations with respect to the diameter of helical down-hole machines, it is advisable to provide the projection and the recess at the ends of adjacent stators. Therewith, in order to prevent the stators from relative angular and axial displacements, they are enclosed by a housing having at the ends thereof thrust elements engageable with the free ends of the stators, at least one of the thrust elements being capable of axial movement thanks to which an external force is provided to prevent axial and angular displacements of the stators being connected.

Preferably, the projection and the recess of identical mating elements are cylindrical in shape.

Such an arrangement is advantageous because it is the most simple in manufacture.

More advantageous is the arrangement of the projection and the recess on identical mating elements, stators or rotors, in the form of truncated cones, which improves the reliability of connection.

Still more advantageous is to make the projection and the recess in the form of a cylinder terminating in a truncated cone.

Such a mating arrangement assures reliable connection of elements and considerably improves the capacity to transmit torque from one section to the adjacent one.

The arrangement of the mating surfaces of the recess-and-projection assembly is the best when they have the form of a cylinder expanding to a truncated cone with the difference between the diamters of the larger and smaller bases of the truncated cone being not less than four eccentricities.

This modification, apart from assuring reliable connection, facilitates joining the elements together by that the projection with a small cone base easily enters the recess.

The helical down-hole machine according to the invention provides for joining together mating elements automatically.

In view of the foregoing, the detachable connections make it possible to shorten the time required to assemble a required number of sections. They further facilitate dismantling of the sections and replacement of faulty elements without resorting to the use of special auxiliary means, or increasing the number of operations required.

The invention will now be described in greater detail with reference to various specific embodiment thereof taken in conjunction with the accompanying drawings, in which: Figure 1 is a sectional longitudinal view of a helical down-hole machine according to the invention; Figure 1a'is a continuation of Fig. 1; Figure la" is a continuation of Fig. la'; Figure 2 is an enlarged cross-section taken along the line ll-ll in Fig. 1:: Figure 3 is a longitudinal sectional view of a modified form of the helical down-hole machine according to the invention wherein projection and recess having the form of a truncated cone are arranged at the ends of adjacent stators; Figure 3a' is a continuation of Fig. 3; Figure 4 shows a longitudinal sectional view of a modification wherein projection and recess at the ends of rotors have the form of a cylinder terminating in a truncated cone; Figure 4a' is a continuation of Fig. 4: Figure 5 illustrates a longitudinal section of connection between the rotors fashioned as a projection-and-recess assembly in the form of a cylinder expanding to a truncated cone, the difference between the diameters of the large and small bases of the cone being not less than four values of the eccentricity; and Figures 6 to 10 show the sequence of assembling identical elements to be rigidly connected by means of projection-and-recess assembly having the form of a cylinder terminating in truncated cone.

The helical down-hole machine is comprised of arranged axially in series two sections 1 (Fig. 1) and a spindle assembly 2. Each section 1 is defined by installed with a preselected eccentricity ''e' stator 3 (4) and rotor 5 (6). The stators 3, 4 and the rotors 5, 6 are rigidly connected therebetween. Each of the stators 3 and 4 has a metal housing 7 with a shaped elastic lining 8 bonded to the inner walls thereof. The outer surface of the metal rotors 5 and 6 also has shaped thread or grooves, the number of such grooves on the rotors being one less than those on the shaped elastic lining 8 of the stator.

The rigid interconnection of the stators 3 and 4 is detachable for which purpose the adjacent ends of the stators 3 and 4 are provided with a recess-and-projection linkage; more particularly, the stator 4 has a projection 9 in the form of a body of revolution, whereas the stator 3 has a recess 10 of a corresponding shape.

The rigid interconnection between the rotors 5 and 6 is executed in a substantially similar manner, viz. by providing a projection 11 in the form of a cylinder at the rotor 6 and a recess 1 2 of a shape to receive the projection 11 at the end of the rotor 5.

The rotors 5 and 6 are forcibly held together in the course of rotation by virtue of an axial load arising due to a pressure drop. In order to prevent the stators 3 and 4 from angular and axial displacements, they are enclosed by a casing 1 3 and are held against angular and axial displacements by an axial force produced by axially movable thrust elements 1 4 arranged on adapters 1 5 and 1 6.

The adapters 1 5 and 1 6 are threadingly connected to the casing 13, which makes it possible to move them axially to thereby produce a required clamping effect on the thrust elements 14.

The adapter 1 6 is connected by the lower portion thereof to an adapter 1 7 of the spindle assembly 2. Arranged inside the adapter 1 6 is a double-hinged coupling 1 8 intended to connect the lower rotor 6 with sleeve 1 9 of the output shaft 20 of the spindle assembly 2.

The sleeve 1 9 holds on the shaft 20 sleeves 21 of radial bearings 22 and a thrust bearing 23. The radial bearings 22 Der se and the thrust bearing 23 are secured along their outer surfaces in a casing 24 between the adapter 1 7 and a nipple 25. In its lower portion the shaft 20 terminates in an adapter 26 serving to be connected to a bit (not shown).

With reference to Fig. 2 there is shown a cross-sectional view of the section 1. The stator 3 is in meshing engagement with the rotor 5. The planetary motion of the rotor 5 inside the elastic lining 8 of the stator 3 may be described as rolling without slippage of the initial circle of the rotor 5 of a radius b = ez in the initial circle of the stator 3 of a radius a = e(z + 1), where e is the eccentricity equalling half the radial height of the helical grooves of the rotor 5 or the stator 3; and z is the number of helical grooves cut on the rotor 5.The initial circle of the rotor 5 has its center in the point 0,, while the initial circle of the stator 3 has its center in the point 2 In the heretofore described helical downhole machine similar elements of the sections 1, i.e. stators 3, 4 and rotors 5, 6 are connected by means of detachable frictional coupling in the form of recess 10 (12) on one of these elements and projection 9 (11) on the adjacent element, both being shaped as cylinders.

Referring now to Fig. 3, there is shown a connection between stators 27 and 28 wherein projection 29 and recess 30 have the form of truncated cones. thus enabling to improve the reliabiiity of the detachable frictional coupling. The stator 27 and 28 are prevented from angular and axial displacements in the manner described above. Rotors 31 of these sections 1 are interconnected by means of assembly 32 (such as a spline coupling) which provides for their rigid connection and prevents their relative angular displacement.

Identical elements, particularly rotors 33 (Fig. 4) and 34, are connected by a detachable friction coupling; more precisely, by means of a projection 35 arranged on the rotor 33 and having the form of a cylinder 35a terminating in a truncated cone 35b, and a corresponding recess 36 made in the rotor 34. Stators 37 are interconnected in this modified form of connection by means of all adapter 38. Otherwise, the helical down-hole machine is analogous to the modification thereof described heretofore.

With reference to Fig. 5, in order to assure a more reliable connection of rotors 39 and 40 having projections 41 and recesses 42 in the form of cylinders expanding to truncated cones, it is preferable that the diameter d of the smaller base of the truncated cone be less than the diameter D of the larger base thereof by a value being not less than four eccentricities "e", i.e. D - d4e.

Figs. 6 to 10 represent a sequence of operations for positioning rotors and stators during assembly, the rigid connection therebetween being effected by means of detachable recess-and-projection assemblies.

Prior to explaining the operation of the helical down-hole machine, the manner in which similar elements thereof are put together by means of the rigid detachable friction connection of the recess-and-projection type is to be elaborated.

The initial step of assembly includes connecting in series the rotors 43 (Fig. 6) and 44 to form a string by means of any of the heretofore described rigid detachable connections. In this particular case the rotors 43, 44 aligned along a common axis 0, O, are joined together by a conical. spline coupling 45, whereupon stators 46 (Fig. 7) and 47 are mounted on the thus joined rotors.

After the stator 46 assumes working position, the stator 47 is rotated to threadingly engage with the rotor 44 and moved until it comes into contact with the stator 46. Therewith, as best seen in Fig. 8, the stators are put into contact by their end surfaces, the end of the stator 46 having a recess 48, the other stator 47 having a projection 49. The projection 49 and recess 48 are shaped as cylinders terminating in tapered cone portions.

Referring now to Fig. 8, let us consider a quite probable situation when the mating surfaces of the rigid connection between the stators are not in registration, that is when the axes O2 02 and 03 03 of the stators 46, 47 are spaced apart from the common axis 0, O, of the string of rotors 43, 44. In such a case one of the stators, particularly the stator 47, while rotating about the axis O O, of the rotor 44 engaged therewith will tend to assume a positon where its axis is aligned with the axis O2 2 of the adjacent stator 46, in other words, both stators 46 and 47 have a common axis O2 3 (Fig. 9), while the mating surfaces of the stators are not completely in contact.

The stator 47 must be so rotated to threadingly engage with the rotor 44 as to provide an axial force capable of moving the stator 47 toward the stator 46 fixedly mounted on the rotor 43 until the two stators are in complete mating engagement as seen in Fig. 10.

The helical down-hole machine embodying the present invention operates as follows.

When a drilling fluid is supplied to the helical down-hole machine operating as a motor, the rotors 5 and 6 are caused to execute a planetary motion inside the elastic linings of the stators 3 and 4; this planetary motion, as has been explained with reference to Fig. 2, may be described kinematically as rolling without slippage of the initial circle of the rotor 5 of the radius b = ez in the initial circle of the stator 3 of the radius a = e (z + 1).The cross-sectional center 0, of the rotor 5 executes translatory rotation relative to the crosssectional center 02 of the stator 3 to move over the circle of the radius "e" counterclockwise with the speed of rotation w,, whereas the rotor 3 per se turns about its own axis clockwise with a speed or rotation 2 (absolute rotation), with a), = Z Torques acting on the rotor 5 in translatory motion (M,) and in absolute motion (M2) relative to the stator 3 correlate in a reverse proportionality to the speed of rotation of these motions, i.e.

1 M1 = -M2.

z Because the mating surfaces of the frictional connection between the rotors 5, 6 and the recess 1 2 and projection 11 are coaxial with the helical surfaces of the rotors 5 and 6, a torque, i.e. the torque M1, is transmitted from the upper rotor 5 to the lower rotor 6 in the course of their translatory motion.

Transmission of this torque produces a radial force M1 P= 2e acting from the female cylindrical surface of the recess 1 2 of the upper rotor 5 on the male cylindrical surface of the projection 11 of the lower rotor 6.

At minimum tolerances between the mating surfaces of the frictional connection these surfaces fail to displace angularly whereby the torque is transmitted without friction losses between the mating surfaces.

The total torque M1 of all the rotors is imparted through their translational motion to the lower rotor 6. By means of the doublehinged coupling 1 8 this torque is taken off the lower rotor 6 to be transformed into the absolute torque M2 at the output shaft 20 of the spindle assembly 2. Axial load is transmitted from the upper rotor 5 to the lower rotor 6 through end surfaces of the projection 11 and recess 1 2. The cylindrical surfaces of the projection 11 and those of the recess 1 2 also take up radial loads imparted by hydraulic skewing moments acting on the rotors 5 and 6 in a plane passing across the axes of the stator 3 (4) and rotor 5 (6).These loads tend to reduce the eccentricity at the lower end of the upper rotor 5, whereas at the upper end of the rotor 6 these loads act to increase the eccentricity due to their opposite direction. Interaction between the projection 11 and recess 1 2 eliminates harmful skewing effect, which facilitates stabilization of the rotor motion. The stators 3 and 4 interconnected by the projection 9 and the recess 10 and secured in the casing 1 3 between the two thrust elements 1 4 on the adapters 1 5 and 1 6 take up a reactive torque moment imparted through the adapter 1 5 to the drill string.

A more reliable take up and transmission of torque from the lower stator 28 (Fig. 3) to the upper stator 27 are effected in a modification where the projection 29 and the recess 30 of the friction coupling are fashioned as truncated cones. Still more advantageous is a friction coupling where the projection 35 and the recess 36 have the form of a cylinder 35a terminating in a truncated cone 35b. Such an arrangement facilitates fitting of the rotors 33 and 34 and makes the connection more monolithic. The axial load in this case is transmitteri through the tapered surfaces of the projection 35 and recess 36, while torque is transmitted through the cylindrical and tapered surfaces.

In order to simplify disassembly of the machine, the value of taper angle of the mating surfaces is preferably in excess of the angle of friction of the materials of the projection and recess.

The helical down-hole machine according to the invention features automatic aligning of the rotors in working position and simplified disassembly.

In addition, the machine provides for improved operating conditions of the stators and rotors because, on the one hand, radial forces resulting from intermediate shafts are obviated, while, on the other hand, the construction of the friction couplings, particularly those of the rotors, makes it possible to mutually compensate oppositely directed radial forces arising from hydrauiic skewing moments acting on the rotors. The foregoing improves the reliability of the machine and makes it more durable.

Claims (9)

1. A helical down-hole machine wherein sections defined by arranged with a preselected eccentricity helical rotors and stators defining cavities of variable volume for the passage of fluid therethrough are disposed in series axially, identical elements of these sections being rigidly interconnected therebetween; the rigid connection of at least one of these identical elements being detachable by frictional jointing a projection in the form of a body of revolution provided at the end of one of the elements and a recess of a corresponding shape provided at the end of the adjacent element forcibly secured against mutual angular and axial displacements.

2. A helical down-hole machine according to claim 1 wherein projection and recess are provided at the ends of adjacent rotors and forcibly secured against mutual displacement during rotation by virtue of a pressure drop.

3. A helical down-hole machine according to claim 1 wherein projection and recess are provided at the ends of adjacent stators, the patter being secured against mutual angular and axia dispac3 ;i1t by p.aci*19 there inside a common housing having at the ends thereof thrust elements engageable with the free ends of the stators, at least one of these thrust elements being capable of axial movement.

4. A helical down-hole machine according to claim 1 wherein projection and recess are cylindrical in shape.

5. A helical down-hole machine according to claim 1 wherein projection and recess are shaped as a truncated cone.

6. A helical down-hole machine according to claim 1 wherein projection and recess are each shaped as a cylinder expanding into a truncated cone.

7. A helical down-hole machine according to claim 5 or claim 6 wherein the difference between the larger and smaller bases of the truncated cone amounts to at least not less than four values of the eccentricity.

8. A helical down-hole machine substantially as heretofore described with reference to the accompanying drawings.

9. A helical down-hole machine wherein sections, each of which is defined by a stator and a rotor with a preselected eccentricity arranged within said stator, having corresponding profile helical surfaces and defining cavities of variable volume for the passage of fluid, are disposed in series axially, identical elements of these sections being rigidly interconnected therebetween and disposed on one, each element on its own, axis correspondingly; the rigid connection of at least one of these identical elements being detachable by means of frictional jointing a projection in the form of a body of revolution provided at the end of one of the elements, and a recess of a corresponding shape provided at the end of the adjacent element-and forcibly secured against mutual angular and axial displacements, in particular, without additional technical means, and ensuring in the process of mounting in each section automatical setting in a working position of the rotors and stators, the helical profile surfaces of the adjacent identical elements being in an indifferent position to each other.