CA2174017A1 - Rotor-to-rotor coupling - Google Patents
Rotor-to-rotor couplingInfo
- Publication number
- CA2174017A1 CA2174017A1 CA002174017A CA2174017A CA2174017A1 CA 2174017 A1 CA2174017 A1 CA 2174017A1 CA 002174017 A CA002174017 A CA 002174017A CA 2174017 A CA2174017 A CA 2174017A CA 2174017 A1 CA2174017 A1 CA 2174017A1
- Authority
- CA
- Canada
- Prior art keywords
- rotor
- coupling
- stator
- grooves
- connecting rod
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
- 230000008878 coupling Effects 0.000 title claims abstract description 56
- 238000010168 coupling process Methods 0.000 title claims abstract description 56
- 238000005859 coupling reaction Methods 0.000 title claims abstract description 56
- 230000013011 mating Effects 0.000 claims abstract 3
- 238000006073 displacement reaction Methods 0.000 claims description 14
- 238000007789 sealing Methods 0.000 claims description 4
- 238000000034 method Methods 0.000 abstract description 10
- 238000005553 drilling Methods 0.000 description 20
- 239000012530 fluid Substances 0.000 description 18
- 230000009977 dual effect Effects 0.000 description 11
- 238000000926 separation method Methods 0.000 description 5
- 230000000712 assembly Effects 0.000 description 3
- 238000000429 assembly Methods 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000001360 synchronised effect Effects 0.000 description 3
- VYZAMTAEIAYCRO-UHFFFAOYSA-N Chromium Chemical compound [Cr] VYZAMTAEIAYCRO-UHFFFAOYSA-N 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 150000001875 compounds Chemical class 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 239000004593 Epoxy Substances 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- RDYMFSUJUZBWLH-UHFFFAOYSA-N endosulfan Chemical compound C12COS(=O)OCC2C2(Cl)C(Cl)=C(Cl)C1(Cl)C2(Cl)Cl RDYMFSUJUZBWLH-UHFFFAOYSA-N 0.000 description 1
- 239000011152 fibreglass Substances 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 238000010587 phase diagram Methods 0.000 description 1
- 230000001681 protective effect Effects 0.000 description 1
- 150000003839 salts Chemical class 0.000 description 1
- 238000004513 sizing Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
- F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
- F16D1/0876—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with axial keys and no other radial clamping
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH DRILLING; MINING
- E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B4/00—Drives for drilling, used in the borehole
- E21B4/02—Fluid rotary type drives
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T403/00—Joints and connections
- Y10T403/70—Interfitted members
- Y10T403/7018—Interfitted members including separably interposed key
- Y10T403/7021—Axially extending
Abstract
A rotor to rotor coupling providing a connecting rod having longitudinal grooves mating to longitudinal grooves in a rotor end. The mated grooves forming chambers for which pins are received therein. A rotor cap secures the captured pins within the chambers and further strengthens the coupling. An optional thrust bearing assembly is disclosed along with a preferred method of synchronizing the rotors and timing the stators.
Description
-APPLICATION FOR PATENT
lN v~NlOR: hllc~ ~'LL J. HOUMAND and JAMES E. KRAUS
TITLE: ROTOR-TO-ROTOR COUPLING
SPECIFICATION
Backqround of the Invention 1. Field of the Invention The invention relates to a downhole drilling coupling and more particularly to a rotor-to-rotor coupling for synchronizing two positive displacement motors.
lN v~NlOR: hllc~ ~'LL J. HOUMAND and JAMES E. KRAUS
TITLE: ROTOR-TO-ROTOR COUPLING
SPECIFICATION
Backqround of the Invention 1. Field of the Invention The invention relates to a downhole drilling coupling and more particularly to a rotor-to-rotor coupling for synchronizing two positive displacement motors.
2. Background of the Invention In the oil and gas industry, downhole drilling motors have been used for many years, especially in directional drilling. Typically, the drilling motor is contained in a housing, and supplies a rotational force by way of a drive shaft for turning a drill bit. The motor housing is connected to the lower end of a conventional drill string comprised of sections of drill pipe and drill collars. The drill string extends to the surface, where it is connected to a kelly, mounted in the rotary table of a drilling rig.
As the drilling begins, drilling fluid is pumped down through the drill string to the bottom of the bore hole and back up to remove the cuttings resulting from the drilling operation. Since the drilling fluid is constantly flowing through the drill string, a positive displacement motor is commonly used.
Positive displacement motors, or Moineau motors, have fixed volumetric displacement and, thus, their speed is directly proportional to the flow rate. These types 13~2~- 3324~3 EXPRESS MAIL ~B693235422US
of motors are well known in the art. The positive displacement motor (PDM) comprises a helical rotor within a helical cavity of a stator. The stator is bonded to the housing of the motor and is composed of rubber or rubber-like helical lobes, or threads for coacting with the helical rotor. The number of stator lobes is one more than the number of rotor lobes, thus creating a number of chambers along the length of the stator. As the drilling fluid is pumped down the drill string, under pressure, and through the cavity of the stator, the fluid imparts a torque to the rotor, causing the rotor to turn and pass the fluid from chamber to chamber. As the helical rotor rotates, it also orbits eccentrically about the axis of the stator in a reverse direction relative to its axial rotation. The rotor torque is then transferred to the drive shaft of the drill bit by a universal joint.
The torque developed by the PDM is also well understood to be proportional to the rotor pitch (or distance the fluid advances in one rotation of the rotor) and the number of rotor and stator lobes. While in theory, one long motor section provides a large amount of torque, in practice, single long sections have not been used with much success. Manufacturing, transportation and handling practicalities limit the length. Further, if any part of the motor malfunctions, the entire motor must be removed and replaced. This is particularly true of the stator. As the stator must have an effective hydraulic seal around the rotor, it is a vulnerable portion of the motor because it is subjected to continuous rubbing and deformation by the rotor.
Additionally, the stator and rotor are subjected to abrasive and corrosive drilling fluids and salts. Thus, replacement of worn stators is routine. To further reduce the abrasive effects of the downhole environment, 13~2~4- 3324~3 the rotors are chrome plated. When the chrome is damaged along any part of the rotor body it becomes susceptible to failure from corrosion and the entire rotor body must be rechromed which is costly.
Multilobed motors provide more torque but at a lower rotational speed. Thus, it is desirable to produce the large amounts of torque possible with the long motor and multilobed motors, while avoiding the manufacturing, handling, transportation and costly maintPnAnce problems associated with long motor sections.
One way of simulating a long motor is to connect together several shorter motors in series, as described in Tschirky, U.S. Pat. No. 3,999,901. However, as each rotor is designed to eccentrically orbit within its own stator, difficulty in connecting the multiple motors together has resulted in limited success for this arrangement. Tschirky discloses a method for connecting the rotors in which the rotors are simply welded together. Welding the rotors together effectively eliminates the benefits of having separate motors.
Another method described in Tschirky utilizes a pair of universal joints. The universal joints transfer torque between the rotors while permitting the rotors to eccentrically orbit within their respective stators, but out of phase with one another. While a universal joint may provide a working connection, it suffers from certain problems. The harsh environment of operating in the drilling fluid causes the universal joints to corrode and wear quickly. Additionally, the out of phase rotor operation causes a slight longitudinal movement that results in power transfer inefficiencies, instability and above normal wear on the stator.
Thus, it would be desirable to have a sturdy rotor-to-rotor coupling that allows two positive displacement 13~2~4- 3324~3 EXPRESS ~LAIL TB693235422US
motors to be releasably connected in series for increased torque but without the wear joints or moving bearing assemblies common in universal joints. It is also desirable to provide a sturdy rotor-to-rotor coupling to minimize the wear on the stators, and improve overall stability of the downhole motor arrangement.
Summarv of the Invention A rotor coupling according to the present invention includes a connecting rod for being telescopically received into a cavity of a rotor end. The rotor cavity provides a plurality of elongated longitll~; nA 1 grooves in its cavity side wall and the connecting rod provides a plurality of elongated longitudinal grooves on its outer surface. When the connecting rod is received into the cavity, the grooves align to form a plurality of elongated chambers.
A plurality of elongated drive pins are disposed in the chambers for engaging the connecting rod and the rotor. A tubular rotor cap, placed over the connecting rod, provides threads on its outer surface to mate with threads on the cavity side wall for maintaining the drive pins in the chambers and thereby securing the connecting rod to the rotor. The drive pins and the rotor cap provide a stable coupling in which, in operation, omnidirectional movement of the connecting rod with respect to the rotor is effectively eliminated. Because omnidirectional movement is effectively eliminated, rotors coupled at each end of the connecting rod are substantially coaxial.
In the assembly of the dual rotor assembly, the rotors are preferably synchronized with respect to each other. In the assembly of the dual motor assembly, the stators are preferably timed to their respective rotors.
l3~2~4- 3324~3 EXPP~ESS ~AIL TB693235422US
For this purpose, a synchronizing pin with a correspon~innly sized chamber and a method of timing the stators is conveniently provided.
Brief Description of the Drawinqs A better understAn~ing of the present invention can be ob~Aine~ when the following detailed description of a preferred embodiment is considered in conjunction with the following drawings, in which:
Figure 1 illustrates a longitll~inAl cross-section of the coupling according to the preferred embodiment of the invention;
Figure 2 illustrates a cross-section taken at line A-A' of Figure 1;
Figure 3 illustrates an enlarged view of the lower motor coupling of Figure l;
Figure 4a illustrates the phase relationships of the stator lobes along the length of the stators;
Figure 4b illustrates the phase relationships of the rotor lobes along the rotors, and projected along the connecting rod;
Figure 4c illustrates a longitudinal cross-section of the synchronized dual motor arrangement;
Figure 4d illustrates a cross-section taken at line B-B' of Figure 4c;
Figure 4e illustrates a cross-section taken at line C-C' of Figure 4c;
Figures 5a and 5b illustrates the method of aligning the stators according to the preferred embodiment of the invention; and Figure 6 illustrates a longitudinal cross-section of the coupling according to an alternative embodiment.
Detailed Descri~tion of Preferred Embodiment 13~2~4-...3324~3 EXPRESS MA~L TB693235422US
Reference will now be made in detail to a preferred embodiment of the invention, an example of which is illustrated in the accompanying drawings.
With reference to Figure 1, an upper positive displacement motor 2 is shown coupled to a lower positive displacement motor 4 by way of coupling assembly 5. As shown, the upper motor 2 includes an outer housing 6, a stator 8 having a helical inner wall 22 and a helical rotor 10 having a helical outer wall 24 for hydraulically coacting with the stator 8. The lower motor 4 similarly includes an outer housing 12, a helical stator 14 having a helical inner wall 26, and a helical rotor 16 having a helical outer wall 28 for hydraulically coacting with the stator 14. In practice, the upper portion (not shown) of the upper motor 2 would be operatively connected to an uphole drill string with the lower portion (not shown) of the lower motor 4 being operatively connected to the drive shaft of a drill bit. The motors 2 and 4 are disposed end-to-end and connected in series by the coupling assembly 5 at the housings 6 and 12 by way of adapter 18, and at the rotors 10 and 16 by way of connecting rod 20, which operates to transfer axial and rotational forces between the motors 2 and 4. As will be more fully explained below, the connecting rod 20 and the adapter 18 also synchronize the motors 2 and 4 to allow for a very efficient dual power motor arrangement.
The housings 6 and 12 have threaded box ends 30 and 32 for engaging threaded pin ends 34 and 36 of the adapter 18. The housings 6 and 12 screw onto the adapter 18 and bear against shoulders 38 and 40 of the adapter 18. Optionally, an annular shim 200 (Figure 3) may be installed over a pin end and adjacent a shoulder of the adapter for timing the stators. A preferred method of timing the stators is described below.
13562~4- 3324813 The adapter 18 has a hollow cylindrical bore 42, ext~n~ing entirely through the adapter 18 for passing the drilling fluid from one motor to another and for housing the connecting rod 20. The exterior surface of the adapter 18 may conveniently include annular notch 44 and externally threaded annular rib 46 for mounting a guide sleeve (not shown) for the drill string. To protect the notch 44 and rib 46 when the guide sleeve is not used, a protective sleeve (not shown) may be placed over the threaded rib 46.
Before continuing with further description of the coupling assembly 5, it may be helpful to briefly describe the rotational forces involved when a positive displacement motor is operating in a drill string.
Because the upper rotor operates in an identical fashion, only the lower rotor is shown and described in detail.
As best shown in Figures 1 and 2, the stator 14 is secured to the housing 12 and has a plurality of helical lobes 100, or threads forming an helical inner wall 26 about an axis 108. As is conventional with positive displacement motors, the rotor 16 has at least one helical lobe 102, but always one less than the number of stator lobes. Therefore, the stator pitch length is defined as the rotor pitch length multiplied by the number of stator lobes and divided by the number of rotor lobes (see Figure 4c). For purposes of illustration, the drawing shows four stator lobes and three rotor lobes.
However, as will be more fully appreciated in light of the ~iscllcsion below, the invention can be used to couple together single lobe positive displacement motors or multilobe motors of any number of lobes, as long as the stator lobes number one more than the rotor lobes.
Since the number of stator lobes is one more than the number of rotor lobes, a series of helical chambers l3~2~4- 3324~3 104 (Fig. 2) are created along the length of the motor 4 between the stator 14 and the rotor 16. In the operation of the motor, as drilling fluid is pumped down the drill string, under pressure, and through the helical inner wall 26 of the stator 14, the fluid passes into the chambers 104 and imparts a torque on the rotor 16, causing the rotor 16 to turn and pass the fluid from chamber to chamber. Since when two motors are connected in series, the drilling fluid must pass through both motors, the rotational velocity of the coupled rotors will be substantially identical. As each helical rotor rotates about its axis 106, it also orbits eccentrically about the axis 108 of its associated stator 14 in a reverse direction relative to its axial rotation.
Because of the eccentricity of the orbital axis of the rotors, coupling the rotors by welding them end-to-end creates a stress point and hence weakness at the weld. A conventional universal joint can be used, but with a significant loss of power due to wobble through the joint and improper timing. In addition, the abrasive and corrosive drilling fluid quickly wears away the moving joint interfaces of the universal joint.
With reference to Figure 3, the preferred embodiment of a rotor-to-rotor coupling in accordance with the invention will now be described in detail. Again, since the upper rotor connection is substantially the same as the lower rotor connection, only the lower rotor connection will be described in detail.
With reference to Figures 2 and 3, upper end 224 of the lower rotor 16 provides a cavity 202, centered about the lower rotor axis 106 and having a terminal end 204 and a side wall 206. In accordance with the present invention, a plurality of annularly spaced, internal elongated longit~l~inAI grooves 208 are provided along the 13~2~4- 3324~3 rotor side wall 26 and parallel to its axis 106.
Althollgh not nec~s~ry to the practice of the invention, in the preferred embodiment, at least one of the rotor grooves 208, e.g. 208a, is conveniently centered on a radius which intersects the top or crown of one of the rotor lobes, e.g. rotor lobe crest 102a. As will be appreciated in light of the further description below, the rotor cavity terminal end 204 may conveniently be provided with a cutout portion 232 (Fig. 3) for receiv-ng thrust pin 210 for cooperating with thrust ball 212 to provide a bearing assembly for taking up thrust forces between the rotor and the connecting rod 20.
As best shown in Figure 3, the connecting rod 20 includes a plurality of annularly spaced, external, elongated longitudinal grooves 218 running parallel to the connecting rod 20 axis which, as illustrated, is coaxial with the lower rotor axis 106 axis of the connecting rod 20. At each terminal end of the connecting rod 20, the rod grooves 218 are preferably placed at identical angular placements relative to the connecting rod axis so that proximal and distal terminal end grooves are coaxial. The connecting rod 20 is sized to be telescopically received into the cavity 202.
Although not essential for the practice of the invention, as shown, a thrust pin 210 and a thrust ball 212 may be provided for transferring axial forces from the rotor 16 to the coupling rod 20. For this purpose, the terminal end of connecting rod 20 includes a ball socket 214 and the thrust pin 210 includes a corresponding seat 216. With this arrangement, the thrust ball 212 or thrust pin 210 can be replaced during routine maintenance. The thrust pin 210 includes an o-ring 236 to prevent abrasive drilling fluids from entering the terminal end 202 from a rotor bore 238. The 13~2~4- 3324~3 EXPRESS MI~IL TB693235422US
rotor bore 238 is present in certain rotors to allow drilling fluids to pass. In the operation of the rotor with the thrust ball assembly, lubricants are placed in the terminal end 202 and o-rings 234 and 236 provide effective sealing from the drilling fluids. As can be appreciated, the connecting rod could be sized to bear directly on the end 204 of the rotor cavity 202 to minimize parts, if wear on the connecting rod is not of substantial concern.
The connecting rod grooves 218 and the internal rotor grooves 208 are preferably sized and mated so that, when the rotor-to-rotor coupling is assembled, adjoining groove pairs form a plurality of elongated pin chambers 220. Although in the illustrated embodiment the elongated pin chambers 220 are cylindrical for ease of machining, as will be appreciated, the chambers 220 can be any elongated shape. A number of elongated pins 222, equal to the number of chambers 220, are provided for placement within the chambers 220 for coupling the connecting rod 20 to the rotor 16 and for transferring rotational forces between the rotors. The elongated pins 222 are preferably sized to closely fit into the chambers 220 to substantially prevent omnidirectional movement between the coupling rod 20 and the rotor 16.
To complete the lower coupling assembly, a rotor cap 226 is provided having annular threads 228 on an exterior surface of the cap for engaging corresponding threads 230 on the rotor side wall 206. The rotor cap 226 functions to secure the rotor to the connecting rod 20 by contAining the pins 222 within their chambers 220 and to further limit omnidirectional movement of the connecting rod 20 relative to the rotor 16. An O-ring 234 on an inner surface of the rotor cap is provided such that in l3~2~4- 3324~3 conjunction with the threaded fitting, the cavity 202 is sealed from the drilling fluid.
Therefore, by providing a coupling with elongated drive pins, in the operation of the rotor to rotor coupling, the rotors are coaxially positioned for synchronous eccentrical orbit of their respective stators, which results in a very sturdy coupling without the wear points of the prior art couplings. As will be ~icc~lcce~ below, the coAYiAl rotor alignment also permits performance benefits by synchronizing the rotors and timing the stators.
An alternative embodiment includes the plurality of elongated chambers 220 in a longitudinally staggered formation, as shown in Figure 6. Rotor grooves 208 are longitudinally staggered from rotor grooves 208b, and connecting rod grooves 218 are longitudinally staggered from connecting rod grooves 218b to form a plurality of elongated chambers 220b which are longitudinally staggered from the plurality of longitudinal chambers 220. A plurality of pins 222 are received into both the staggered chambers 220b and the unstaggered chambers 220.
Thus, when the rotor cap 226 is threaded into the rotor, only the elongated pins 222 in the unstaggered chambers 220 will be in close proximity, about 1/16~, to the rotor cap 226. In a variation of this alternative embodiment, a plurality of pins 222b having a shorter length are provided for placing into the plurality of chambers 220 for producing a similar effect as the staggered formation.
As can be appreciated, misalignment of a stator relative to its rotor creates additional, unnecessary wear on the rubber stator. Although not necessary to achieve the positive torque transfer and durability advantages of the invention, enhanced efficiency can be 13~2~4- 3324~3 achieved by synchronizing the rotors 10 and 16 being coupled. Keeping in mind the earlier explanation of the operation of a positive displacement motor, it will be appreciated that the upper and lower motors will be in synch when the rotors are in synch with one another and the stators are properly timed to their respective rotors. As used herein, the term "in synch" refers to the condition in which coupled rotors are both coaxially and phase aligned. Coaxial alignment occurs when the rotors are coupled together according to the coupling assembly 5 described above. Phase alignment occurs when, for a given rotor separation, the helical lobes of respective rotors are rotationally positioned such that a continuous phase relationship exists between the separated rotors, as illustrated in Figure 4b.
For this purpose, as shown in Figure 3, one of the pins 222, labeled 222', is conveniently sized and located to be a synchronizing pin. The synchronizing pin 222l and its corresponding chamber labeled 220l in Figure 3, are sized differently from the other pins 222 and chambers 220 for synchronizing the rotors during assembly. As can be appreciated, positioning of the rotors for "in phase" alignment is dependant upon rotor separation and relative rotational positioning. Although not required, in the preferred embodiment, the rotor separation distance is conveniently set to equal an integer multiple of the rotor pitch lengths (Pr) divided by the number of rotor lobes. Therefore, to provide an uin phase~ alignment, the rotors only need to have identical rotational positioning. This is conveniently provided by the synchronizing pin 222~. The axis of the synchronizing pin 222' (Figure 2) preferably intersects a radius between the rotor axis 106 and the top or crest of a lobe, e.g. lobe crest 102a. Thus, with the 13~2~4- 3324~3 EXPRESS ~SAIL TB693235422US
synchronizing pin feature and properly dimensioned components, synchronization of the upper and lower rotors is assured. As can be appreciated, pin and chamber ch~p~c, placement, spacing and number can be varied ~epe~ing on the available size and wall thickness of the rotor cavity and manufacturing preferences. Rotor to rotor phase alignment can be accomplished by machining upper rotor pin grooves in the same position relative to a particular lobe crest of the upper rotor as the lower rotor pin ylooves are positioned relative to a particular lobe crest of the lower rotor. The additional use of the synchronizing pin 222~ and corresponding pin chambers 220' assure that for a given separation, the rotor to rotor coupling will always be assembled in phase, as illustrated in Figure 4b. In a variation of the synchronizing pin, a single rotor groove 208, connecting rod ~oove 218 and pin 222 are omitted, thereby providing an alignment mechanism similar to the synchronizing pin which is especially useful on smaller diameter rotors and connecting rods.
Turning now to the timing of the stators, the phase diagrams of Figures 4a - 4e illustrate the preferred alignment of the stators 8, 14 to their respective rotors and 16. In the preferred rotor-to-rotor synchronization, the connecting rod 20 is conveniently dimensioned to separate the rotors 10 and 16 by a distance equal to an integer number of rotor pitch lengths (Pr) divided by the number of rotor lobes and the rotors are positioned "in phase~ with respect to each other. As such, proper stator-to-rotor timing may also be achieved when the stators 8 and 14, or housings 6 and 12, are separated by a distance consistent with to the rotor separation distance and the stator lobes are also uin phase~, as illustrated in Figures 4d and 4e.
13~2~4- 3324~3 Figures 4c and 4d illustrates a lobe X coacting with a longit~ nAl portion 400 of the helical inner wall 26 at a point B-B'. Proper stator alignment occurs, such as at the cross-section B-B', when, along the longitudinal portion 400, the rotor lobes are in phase with the stator lobes. Stator alignment is illustrated graphically in Figures 4a and 4b. Comparing Figures 4a and 4b, at point B, the rotor lobe X is shown to be intersecting the stator lobe U. Thus, at points along the longitudinal portion 400, the intersection of rotor and stator lobes in this manner result in a proper stator alignment with respect to the rotor.
As can be appreciated in the dual motor assembly, stator to rotor timing is dependant upon the distance between the stators and the stator rotational position about each respective rotor. As discussed above, altholl~h the dual rotor assembly is coaxially aligned by the rotor to rotor coupling, phase alignment of a dual rotor assembly is dependant upon the distance between the rotors and the relative rotational position of the rotors. Although the timing method herein described will apply to both "in phase or "out of phase dual rotor assemblies, it is preferable to use only "in phase~ dual rotor assemblies, as will become apparent.
A preferred method of timing the stators is illustrated in the flow diagram of Figures 5a and 5b. A
stator adapter housing 18 is provided for securing the upper and lower stators housings, 6 and 12. As shown in Figure 5a, before coupling the housings, a distance between the shoulders 38 and 40, of the stator adapter housing 18 is measured. This is preferably a predetermined length, such as 15". Knowing this distance, the stator housings can be placed into a 13~2~4- 3324~3 calibration rack with the stators rotatably separated by the measured distance.
Next a stator core is inserted through the upper and lower stators. The stator core can be made by using one of the stators to be coupled as a mold and any convenient molding compound, such as fiberglass/epoxy compound.
Once the core is made, it can be used repeatedly for similarly sized and configured stators to be coupled. It is noted that the stator core has the same number- of lobes as the stator. By using a mold of the stators, the stators will conveniently be "in phase~ with respect to each other. It is further noted that although other methods of timing the stators can be employed, by utilizing the stator core, the dual rotor assembly is also conveniently required to be "in phase~. If an "out of phase~ rotor assembly is desired, then the stator core is simply cut in two and rotationally positioned backed together at the desired "out of phaser angle.
While inserting the stator core, it may be nec~-cs~ry to rotate one of the stator housings to slide the core through both stators. Once the stator core is inserted, top dead center of each stator is located and a mark is scribed on the exterior surface of each stator housing, adjacent its end. Thus, at this point, it is apparent that this is the desired rotational position of the stators for proper timing of the stators to the "in phase~ rotors.
Next, a series of marks are calculated for placing about the circumference of one of the stator housings.
The angular displacement of the marks is determined by dividing 360 degrees by the number of stator lobes.
Thus, with reference to the top dead center mark, a series of marks are distributed about the circumference of the stator housing. The total number of marks will 13~2~4- 3324~3 `- 2 1 7401 7 equal the number of stator lobes. For example, a six lobe stator will have six marks separated by 60 degrees each.
After the series of marks are placed on one of the stator housings, the stator adapter housing 18 is threaded and fully torqued onto the other stator housing.
Next, the top dead center mark from the coupled stator housing is conveniently transferred onto the stator adapter housing to provide a better reading when the remaining stator is threaded. Next, with respect to the open end of the stator adapter housing, a second mark is placed 15 degrees counterclockwise from the top dead center mark. The off center mark represents the amount of rotation back to top dead center expected to fully tighten the stator to the stator adapter from a hand tightened position.
The remaining stator is then threaded clockwise and hand tightened onto the open end of the stator adapter housing. With respect to the hand tightened end of the stator adapter housing and from the off center mark, the closest mark clockwise from the off center mark is located. The stator is then rotated counterclockwise back to the off center mark and the gap is measured to determine a shim 200 (Figure 3) width. Alternatively, the stator is fully torqued and the angle from the stator adapter housing top dead center to the first clockwise stator mark is measured to determine the shim width.
Knowing the thread pitch, usually 0.25", the angle is readily translated into a shim 200 distance.
Finally, the stator is removed, the shim 200 is placed over the stator adapter housing pin end, and the stator is then threaded and fully torqued. Thus, by appropriately sizing a shim, the stators are timed for receiving the dual rotor assembly.
I3~2~4- 3324~3 The foregoing disclosure and description of the invention are illustrative and explanatory thereof, and various changes in the size, shape, materials, as well as in the details of the illustrated embodiments and cGI.~L,~ction and method of operation may be made without departing from the spirit of the invention.
13~2~4-...3324~3 EXPRESS ~IL TB693235422US
As the drilling begins, drilling fluid is pumped down through the drill string to the bottom of the bore hole and back up to remove the cuttings resulting from the drilling operation. Since the drilling fluid is constantly flowing through the drill string, a positive displacement motor is commonly used.
Positive displacement motors, or Moineau motors, have fixed volumetric displacement and, thus, their speed is directly proportional to the flow rate. These types 13~2~- 3324~3 EXPRESS MAIL ~B693235422US
of motors are well known in the art. The positive displacement motor (PDM) comprises a helical rotor within a helical cavity of a stator. The stator is bonded to the housing of the motor and is composed of rubber or rubber-like helical lobes, or threads for coacting with the helical rotor. The number of stator lobes is one more than the number of rotor lobes, thus creating a number of chambers along the length of the stator. As the drilling fluid is pumped down the drill string, under pressure, and through the cavity of the stator, the fluid imparts a torque to the rotor, causing the rotor to turn and pass the fluid from chamber to chamber. As the helical rotor rotates, it also orbits eccentrically about the axis of the stator in a reverse direction relative to its axial rotation. The rotor torque is then transferred to the drive shaft of the drill bit by a universal joint.
The torque developed by the PDM is also well understood to be proportional to the rotor pitch (or distance the fluid advances in one rotation of the rotor) and the number of rotor and stator lobes. While in theory, one long motor section provides a large amount of torque, in practice, single long sections have not been used with much success. Manufacturing, transportation and handling practicalities limit the length. Further, if any part of the motor malfunctions, the entire motor must be removed and replaced. This is particularly true of the stator. As the stator must have an effective hydraulic seal around the rotor, it is a vulnerable portion of the motor because it is subjected to continuous rubbing and deformation by the rotor.
Additionally, the stator and rotor are subjected to abrasive and corrosive drilling fluids and salts. Thus, replacement of worn stators is routine. To further reduce the abrasive effects of the downhole environment, 13~2~4- 3324~3 the rotors are chrome plated. When the chrome is damaged along any part of the rotor body it becomes susceptible to failure from corrosion and the entire rotor body must be rechromed which is costly.
Multilobed motors provide more torque but at a lower rotational speed. Thus, it is desirable to produce the large amounts of torque possible with the long motor and multilobed motors, while avoiding the manufacturing, handling, transportation and costly maintPnAnce problems associated with long motor sections.
One way of simulating a long motor is to connect together several shorter motors in series, as described in Tschirky, U.S. Pat. No. 3,999,901. However, as each rotor is designed to eccentrically orbit within its own stator, difficulty in connecting the multiple motors together has resulted in limited success for this arrangement. Tschirky discloses a method for connecting the rotors in which the rotors are simply welded together. Welding the rotors together effectively eliminates the benefits of having separate motors.
Another method described in Tschirky utilizes a pair of universal joints. The universal joints transfer torque between the rotors while permitting the rotors to eccentrically orbit within their respective stators, but out of phase with one another. While a universal joint may provide a working connection, it suffers from certain problems. The harsh environment of operating in the drilling fluid causes the universal joints to corrode and wear quickly. Additionally, the out of phase rotor operation causes a slight longitudinal movement that results in power transfer inefficiencies, instability and above normal wear on the stator.
Thus, it would be desirable to have a sturdy rotor-to-rotor coupling that allows two positive displacement 13~2~4- 3324~3 EXPRESS ~LAIL TB693235422US
motors to be releasably connected in series for increased torque but without the wear joints or moving bearing assemblies common in universal joints. It is also desirable to provide a sturdy rotor-to-rotor coupling to minimize the wear on the stators, and improve overall stability of the downhole motor arrangement.
Summarv of the Invention A rotor coupling according to the present invention includes a connecting rod for being telescopically received into a cavity of a rotor end. The rotor cavity provides a plurality of elongated longitll~; nA 1 grooves in its cavity side wall and the connecting rod provides a plurality of elongated longitudinal grooves on its outer surface. When the connecting rod is received into the cavity, the grooves align to form a plurality of elongated chambers.
A plurality of elongated drive pins are disposed in the chambers for engaging the connecting rod and the rotor. A tubular rotor cap, placed over the connecting rod, provides threads on its outer surface to mate with threads on the cavity side wall for maintaining the drive pins in the chambers and thereby securing the connecting rod to the rotor. The drive pins and the rotor cap provide a stable coupling in which, in operation, omnidirectional movement of the connecting rod with respect to the rotor is effectively eliminated. Because omnidirectional movement is effectively eliminated, rotors coupled at each end of the connecting rod are substantially coaxial.
In the assembly of the dual rotor assembly, the rotors are preferably synchronized with respect to each other. In the assembly of the dual motor assembly, the stators are preferably timed to their respective rotors.
l3~2~4- 3324~3 EXPP~ESS ~AIL TB693235422US
For this purpose, a synchronizing pin with a correspon~innly sized chamber and a method of timing the stators is conveniently provided.
Brief Description of the Drawinqs A better understAn~ing of the present invention can be ob~Aine~ when the following detailed description of a preferred embodiment is considered in conjunction with the following drawings, in which:
Figure 1 illustrates a longitll~inAl cross-section of the coupling according to the preferred embodiment of the invention;
Figure 2 illustrates a cross-section taken at line A-A' of Figure 1;
Figure 3 illustrates an enlarged view of the lower motor coupling of Figure l;
Figure 4a illustrates the phase relationships of the stator lobes along the length of the stators;
Figure 4b illustrates the phase relationships of the rotor lobes along the rotors, and projected along the connecting rod;
Figure 4c illustrates a longitudinal cross-section of the synchronized dual motor arrangement;
Figure 4d illustrates a cross-section taken at line B-B' of Figure 4c;
Figure 4e illustrates a cross-section taken at line C-C' of Figure 4c;
Figures 5a and 5b illustrates the method of aligning the stators according to the preferred embodiment of the invention; and Figure 6 illustrates a longitudinal cross-section of the coupling according to an alternative embodiment.
Detailed Descri~tion of Preferred Embodiment 13~2~4-...3324~3 EXPRESS MA~L TB693235422US
Reference will now be made in detail to a preferred embodiment of the invention, an example of which is illustrated in the accompanying drawings.
With reference to Figure 1, an upper positive displacement motor 2 is shown coupled to a lower positive displacement motor 4 by way of coupling assembly 5. As shown, the upper motor 2 includes an outer housing 6, a stator 8 having a helical inner wall 22 and a helical rotor 10 having a helical outer wall 24 for hydraulically coacting with the stator 8. The lower motor 4 similarly includes an outer housing 12, a helical stator 14 having a helical inner wall 26, and a helical rotor 16 having a helical outer wall 28 for hydraulically coacting with the stator 14. In practice, the upper portion (not shown) of the upper motor 2 would be operatively connected to an uphole drill string with the lower portion (not shown) of the lower motor 4 being operatively connected to the drive shaft of a drill bit. The motors 2 and 4 are disposed end-to-end and connected in series by the coupling assembly 5 at the housings 6 and 12 by way of adapter 18, and at the rotors 10 and 16 by way of connecting rod 20, which operates to transfer axial and rotational forces between the motors 2 and 4. As will be more fully explained below, the connecting rod 20 and the adapter 18 also synchronize the motors 2 and 4 to allow for a very efficient dual power motor arrangement.
The housings 6 and 12 have threaded box ends 30 and 32 for engaging threaded pin ends 34 and 36 of the adapter 18. The housings 6 and 12 screw onto the adapter 18 and bear against shoulders 38 and 40 of the adapter 18. Optionally, an annular shim 200 (Figure 3) may be installed over a pin end and adjacent a shoulder of the adapter for timing the stators. A preferred method of timing the stators is described below.
13562~4- 3324813 The adapter 18 has a hollow cylindrical bore 42, ext~n~ing entirely through the adapter 18 for passing the drilling fluid from one motor to another and for housing the connecting rod 20. The exterior surface of the adapter 18 may conveniently include annular notch 44 and externally threaded annular rib 46 for mounting a guide sleeve (not shown) for the drill string. To protect the notch 44 and rib 46 when the guide sleeve is not used, a protective sleeve (not shown) may be placed over the threaded rib 46.
Before continuing with further description of the coupling assembly 5, it may be helpful to briefly describe the rotational forces involved when a positive displacement motor is operating in a drill string.
Because the upper rotor operates in an identical fashion, only the lower rotor is shown and described in detail.
As best shown in Figures 1 and 2, the stator 14 is secured to the housing 12 and has a plurality of helical lobes 100, or threads forming an helical inner wall 26 about an axis 108. As is conventional with positive displacement motors, the rotor 16 has at least one helical lobe 102, but always one less than the number of stator lobes. Therefore, the stator pitch length is defined as the rotor pitch length multiplied by the number of stator lobes and divided by the number of rotor lobes (see Figure 4c). For purposes of illustration, the drawing shows four stator lobes and three rotor lobes.
However, as will be more fully appreciated in light of the ~iscllcsion below, the invention can be used to couple together single lobe positive displacement motors or multilobe motors of any number of lobes, as long as the stator lobes number one more than the rotor lobes.
Since the number of stator lobes is one more than the number of rotor lobes, a series of helical chambers l3~2~4- 3324~3 104 (Fig. 2) are created along the length of the motor 4 between the stator 14 and the rotor 16. In the operation of the motor, as drilling fluid is pumped down the drill string, under pressure, and through the helical inner wall 26 of the stator 14, the fluid passes into the chambers 104 and imparts a torque on the rotor 16, causing the rotor 16 to turn and pass the fluid from chamber to chamber. Since when two motors are connected in series, the drilling fluid must pass through both motors, the rotational velocity of the coupled rotors will be substantially identical. As each helical rotor rotates about its axis 106, it also orbits eccentrically about the axis 108 of its associated stator 14 in a reverse direction relative to its axial rotation.
Because of the eccentricity of the orbital axis of the rotors, coupling the rotors by welding them end-to-end creates a stress point and hence weakness at the weld. A conventional universal joint can be used, but with a significant loss of power due to wobble through the joint and improper timing. In addition, the abrasive and corrosive drilling fluid quickly wears away the moving joint interfaces of the universal joint.
With reference to Figure 3, the preferred embodiment of a rotor-to-rotor coupling in accordance with the invention will now be described in detail. Again, since the upper rotor connection is substantially the same as the lower rotor connection, only the lower rotor connection will be described in detail.
With reference to Figures 2 and 3, upper end 224 of the lower rotor 16 provides a cavity 202, centered about the lower rotor axis 106 and having a terminal end 204 and a side wall 206. In accordance with the present invention, a plurality of annularly spaced, internal elongated longit~l~inAI grooves 208 are provided along the 13~2~4- 3324~3 rotor side wall 26 and parallel to its axis 106.
Althollgh not nec~s~ry to the practice of the invention, in the preferred embodiment, at least one of the rotor grooves 208, e.g. 208a, is conveniently centered on a radius which intersects the top or crown of one of the rotor lobes, e.g. rotor lobe crest 102a. As will be appreciated in light of the further description below, the rotor cavity terminal end 204 may conveniently be provided with a cutout portion 232 (Fig. 3) for receiv-ng thrust pin 210 for cooperating with thrust ball 212 to provide a bearing assembly for taking up thrust forces between the rotor and the connecting rod 20.
As best shown in Figure 3, the connecting rod 20 includes a plurality of annularly spaced, external, elongated longitudinal grooves 218 running parallel to the connecting rod 20 axis which, as illustrated, is coaxial with the lower rotor axis 106 axis of the connecting rod 20. At each terminal end of the connecting rod 20, the rod grooves 218 are preferably placed at identical angular placements relative to the connecting rod axis so that proximal and distal terminal end grooves are coaxial. The connecting rod 20 is sized to be telescopically received into the cavity 202.
Although not essential for the practice of the invention, as shown, a thrust pin 210 and a thrust ball 212 may be provided for transferring axial forces from the rotor 16 to the coupling rod 20. For this purpose, the terminal end of connecting rod 20 includes a ball socket 214 and the thrust pin 210 includes a corresponding seat 216. With this arrangement, the thrust ball 212 or thrust pin 210 can be replaced during routine maintenance. The thrust pin 210 includes an o-ring 236 to prevent abrasive drilling fluids from entering the terminal end 202 from a rotor bore 238. The 13~2~4- 3324~3 EXPRESS MI~IL TB693235422US
rotor bore 238 is present in certain rotors to allow drilling fluids to pass. In the operation of the rotor with the thrust ball assembly, lubricants are placed in the terminal end 202 and o-rings 234 and 236 provide effective sealing from the drilling fluids. As can be appreciated, the connecting rod could be sized to bear directly on the end 204 of the rotor cavity 202 to minimize parts, if wear on the connecting rod is not of substantial concern.
The connecting rod grooves 218 and the internal rotor grooves 208 are preferably sized and mated so that, when the rotor-to-rotor coupling is assembled, adjoining groove pairs form a plurality of elongated pin chambers 220. Although in the illustrated embodiment the elongated pin chambers 220 are cylindrical for ease of machining, as will be appreciated, the chambers 220 can be any elongated shape. A number of elongated pins 222, equal to the number of chambers 220, are provided for placement within the chambers 220 for coupling the connecting rod 20 to the rotor 16 and for transferring rotational forces between the rotors. The elongated pins 222 are preferably sized to closely fit into the chambers 220 to substantially prevent omnidirectional movement between the coupling rod 20 and the rotor 16.
To complete the lower coupling assembly, a rotor cap 226 is provided having annular threads 228 on an exterior surface of the cap for engaging corresponding threads 230 on the rotor side wall 206. The rotor cap 226 functions to secure the rotor to the connecting rod 20 by contAining the pins 222 within their chambers 220 and to further limit omnidirectional movement of the connecting rod 20 relative to the rotor 16. An O-ring 234 on an inner surface of the rotor cap is provided such that in l3~2~4- 3324~3 conjunction with the threaded fitting, the cavity 202 is sealed from the drilling fluid.
Therefore, by providing a coupling with elongated drive pins, in the operation of the rotor to rotor coupling, the rotors are coaxially positioned for synchronous eccentrical orbit of their respective stators, which results in a very sturdy coupling without the wear points of the prior art couplings. As will be ~icc~lcce~ below, the coAYiAl rotor alignment also permits performance benefits by synchronizing the rotors and timing the stators.
An alternative embodiment includes the plurality of elongated chambers 220 in a longitudinally staggered formation, as shown in Figure 6. Rotor grooves 208 are longitudinally staggered from rotor grooves 208b, and connecting rod grooves 218 are longitudinally staggered from connecting rod grooves 218b to form a plurality of elongated chambers 220b which are longitudinally staggered from the plurality of longitudinal chambers 220. A plurality of pins 222 are received into both the staggered chambers 220b and the unstaggered chambers 220.
Thus, when the rotor cap 226 is threaded into the rotor, only the elongated pins 222 in the unstaggered chambers 220 will be in close proximity, about 1/16~, to the rotor cap 226. In a variation of this alternative embodiment, a plurality of pins 222b having a shorter length are provided for placing into the plurality of chambers 220 for producing a similar effect as the staggered formation.
As can be appreciated, misalignment of a stator relative to its rotor creates additional, unnecessary wear on the rubber stator. Although not necessary to achieve the positive torque transfer and durability advantages of the invention, enhanced efficiency can be 13~2~4- 3324~3 achieved by synchronizing the rotors 10 and 16 being coupled. Keeping in mind the earlier explanation of the operation of a positive displacement motor, it will be appreciated that the upper and lower motors will be in synch when the rotors are in synch with one another and the stators are properly timed to their respective rotors. As used herein, the term "in synch" refers to the condition in which coupled rotors are both coaxially and phase aligned. Coaxial alignment occurs when the rotors are coupled together according to the coupling assembly 5 described above. Phase alignment occurs when, for a given rotor separation, the helical lobes of respective rotors are rotationally positioned such that a continuous phase relationship exists between the separated rotors, as illustrated in Figure 4b.
For this purpose, as shown in Figure 3, one of the pins 222, labeled 222', is conveniently sized and located to be a synchronizing pin. The synchronizing pin 222l and its corresponding chamber labeled 220l in Figure 3, are sized differently from the other pins 222 and chambers 220 for synchronizing the rotors during assembly. As can be appreciated, positioning of the rotors for "in phase" alignment is dependant upon rotor separation and relative rotational positioning. Although not required, in the preferred embodiment, the rotor separation distance is conveniently set to equal an integer multiple of the rotor pitch lengths (Pr) divided by the number of rotor lobes. Therefore, to provide an uin phase~ alignment, the rotors only need to have identical rotational positioning. This is conveniently provided by the synchronizing pin 222~. The axis of the synchronizing pin 222' (Figure 2) preferably intersects a radius between the rotor axis 106 and the top or crest of a lobe, e.g. lobe crest 102a. Thus, with the 13~2~4- 3324~3 EXPRESS ~SAIL TB693235422US
synchronizing pin feature and properly dimensioned components, synchronization of the upper and lower rotors is assured. As can be appreciated, pin and chamber ch~p~c, placement, spacing and number can be varied ~epe~ing on the available size and wall thickness of the rotor cavity and manufacturing preferences. Rotor to rotor phase alignment can be accomplished by machining upper rotor pin grooves in the same position relative to a particular lobe crest of the upper rotor as the lower rotor pin ylooves are positioned relative to a particular lobe crest of the lower rotor. The additional use of the synchronizing pin 222~ and corresponding pin chambers 220' assure that for a given separation, the rotor to rotor coupling will always be assembled in phase, as illustrated in Figure 4b. In a variation of the synchronizing pin, a single rotor groove 208, connecting rod ~oove 218 and pin 222 are omitted, thereby providing an alignment mechanism similar to the synchronizing pin which is especially useful on smaller diameter rotors and connecting rods.
Turning now to the timing of the stators, the phase diagrams of Figures 4a - 4e illustrate the preferred alignment of the stators 8, 14 to their respective rotors and 16. In the preferred rotor-to-rotor synchronization, the connecting rod 20 is conveniently dimensioned to separate the rotors 10 and 16 by a distance equal to an integer number of rotor pitch lengths (Pr) divided by the number of rotor lobes and the rotors are positioned "in phase~ with respect to each other. As such, proper stator-to-rotor timing may also be achieved when the stators 8 and 14, or housings 6 and 12, are separated by a distance consistent with to the rotor separation distance and the stator lobes are also uin phase~, as illustrated in Figures 4d and 4e.
13~2~4- 3324~3 Figures 4c and 4d illustrates a lobe X coacting with a longit~ nAl portion 400 of the helical inner wall 26 at a point B-B'. Proper stator alignment occurs, such as at the cross-section B-B', when, along the longitudinal portion 400, the rotor lobes are in phase with the stator lobes. Stator alignment is illustrated graphically in Figures 4a and 4b. Comparing Figures 4a and 4b, at point B, the rotor lobe X is shown to be intersecting the stator lobe U. Thus, at points along the longitudinal portion 400, the intersection of rotor and stator lobes in this manner result in a proper stator alignment with respect to the rotor.
As can be appreciated in the dual motor assembly, stator to rotor timing is dependant upon the distance between the stators and the stator rotational position about each respective rotor. As discussed above, altholl~h the dual rotor assembly is coaxially aligned by the rotor to rotor coupling, phase alignment of a dual rotor assembly is dependant upon the distance between the rotors and the relative rotational position of the rotors. Although the timing method herein described will apply to both "in phase or "out of phase dual rotor assemblies, it is preferable to use only "in phase~ dual rotor assemblies, as will become apparent.
A preferred method of timing the stators is illustrated in the flow diagram of Figures 5a and 5b. A
stator adapter housing 18 is provided for securing the upper and lower stators housings, 6 and 12. As shown in Figure 5a, before coupling the housings, a distance between the shoulders 38 and 40, of the stator adapter housing 18 is measured. This is preferably a predetermined length, such as 15". Knowing this distance, the stator housings can be placed into a 13~2~4- 3324~3 calibration rack with the stators rotatably separated by the measured distance.
Next a stator core is inserted through the upper and lower stators. The stator core can be made by using one of the stators to be coupled as a mold and any convenient molding compound, such as fiberglass/epoxy compound.
Once the core is made, it can be used repeatedly for similarly sized and configured stators to be coupled. It is noted that the stator core has the same number- of lobes as the stator. By using a mold of the stators, the stators will conveniently be "in phase~ with respect to each other. It is further noted that although other methods of timing the stators can be employed, by utilizing the stator core, the dual rotor assembly is also conveniently required to be "in phase~. If an "out of phase~ rotor assembly is desired, then the stator core is simply cut in two and rotationally positioned backed together at the desired "out of phaser angle.
While inserting the stator core, it may be nec~-cs~ry to rotate one of the stator housings to slide the core through both stators. Once the stator core is inserted, top dead center of each stator is located and a mark is scribed on the exterior surface of each stator housing, adjacent its end. Thus, at this point, it is apparent that this is the desired rotational position of the stators for proper timing of the stators to the "in phase~ rotors.
Next, a series of marks are calculated for placing about the circumference of one of the stator housings.
The angular displacement of the marks is determined by dividing 360 degrees by the number of stator lobes.
Thus, with reference to the top dead center mark, a series of marks are distributed about the circumference of the stator housing. The total number of marks will 13~2~4- 3324~3 `- 2 1 7401 7 equal the number of stator lobes. For example, a six lobe stator will have six marks separated by 60 degrees each.
After the series of marks are placed on one of the stator housings, the stator adapter housing 18 is threaded and fully torqued onto the other stator housing.
Next, the top dead center mark from the coupled stator housing is conveniently transferred onto the stator adapter housing to provide a better reading when the remaining stator is threaded. Next, with respect to the open end of the stator adapter housing, a second mark is placed 15 degrees counterclockwise from the top dead center mark. The off center mark represents the amount of rotation back to top dead center expected to fully tighten the stator to the stator adapter from a hand tightened position.
The remaining stator is then threaded clockwise and hand tightened onto the open end of the stator adapter housing. With respect to the hand tightened end of the stator adapter housing and from the off center mark, the closest mark clockwise from the off center mark is located. The stator is then rotated counterclockwise back to the off center mark and the gap is measured to determine a shim 200 (Figure 3) width. Alternatively, the stator is fully torqued and the angle from the stator adapter housing top dead center to the first clockwise stator mark is measured to determine the shim width.
Knowing the thread pitch, usually 0.25", the angle is readily translated into a shim 200 distance.
Finally, the stator is removed, the shim 200 is placed over the stator adapter housing pin end, and the stator is then threaded and fully torqued. Thus, by appropriately sizing a shim, the stators are timed for receiving the dual rotor assembly.
I3~2~4- 3324~3 The foregoing disclosure and description of the invention are illustrative and explanatory thereof, and various changes in the size, shape, materials, as well as in the details of the illustrated embodiments and cGI.~L,~ction and method of operation may be made without departing from the spirit of the invention.
13~2~4-...3324~3 EXPRESS ~IL TB693235422US
Claims (20)
1. A rotor to rotor coupling comprising:
a rotor end having at least two, spaced apart, internal longitudinal grooves in a cavity adjacent the rotor end;
a connecting rod having at least two correspondingly spaced longitudinal, external grooves adjacent one end of the rod, wherein the rod end containing the external grooves is sized to be telescopically received within the rotor end containing the internal grooves such that the external and internal grooves form at least two spaced chambers;
at least two pins sized to fit within the spaced chambers; and means for releasably securing the rotor end to the rod end with the pins captured within the spaced chambers.
a rotor end having at least two, spaced apart, internal longitudinal grooves in a cavity adjacent the rotor end;
a connecting rod having at least two correspondingly spaced longitudinal, external grooves adjacent one end of the rod, wherein the rod end containing the external grooves is sized to be telescopically received within the rotor end containing the internal grooves such that the external and internal grooves form at least two spaced chambers;
at least two pins sized to fit within the spaced chambers; and means for releasably securing the rotor end to the rod end with the pins captured within the spaced chambers.
2. The rotor to rotor coupling of claim 1, wherein the releasably securing means is sized to fit about the connecting rod and includes a threaded connector having at one end external threads for mating with internal threads within the rotor end cavity to contain the captured pins within the chambers.
3. The rotor to rotor coupling of claim 1, further comprising a thrust bearing assembly between the rotor end and the connecting rod end.
4. The rotor to rotor coupling of claim 3, wherein the thrust bearing assembly includes a thrust pin secured within the rotor end cavity and having a ball socket and wherein the connecting rod end incudes a ball socket corresponding to the thrust pin ball socket and a ball sized to fit within the thrust pin and connecting rod ball sockets.
5. The rotor to rotor coupling of claim 1, wherein alternate ones of the external rod grooves are longitudinally staggered and alternate ones of the internal rotor grooves are longitudinally staggered such that alternate ones of the spaced chambers are longitudinally staggered.
6. The rotor to rotor coupling of claim 1, wherein alternate ones of the pins are shorter than the others.
7. A coupling for connecting a pair of positive displacement motors in series wherein each motor includes a rotor and a stator, the coupling comprising:
a rotor to rotor coupling including a rotor end having at least two, spaced apart, internal longitudinal grooves in a cavity adjacent the rotor end, a connecting rod having at least two correspondingly spaced longitudinal, external grooves adjacent one end of the rod, wherein the rod end containing the external grooves is sized to be telescopically received within the rotor end containing the internal grooves such that the external and internal grooves form at least two spaced chambers, at least two pins sized to fit within the spaced chambers, and means for releasably securing the rotor end to the rod end with the pins captured within the spaced chambers; and a stator to stator coupling including a cylindrical housing having a bore therethrough and including releasable securing means at each of its terminal ends for releaseably securing the housing to the lower end of the stator of one of the motors and to the upper end of the stator of the other motor.
a rotor to rotor coupling including a rotor end having at least two, spaced apart, internal longitudinal grooves in a cavity adjacent the rotor end, a connecting rod having at least two correspondingly spaced longitudinal, external grooves adjacent one end of the rod, wherein the rod end containing the external grooves is sized to be telescopically received within the rotor end containing the internal grooves such that the external and internal grooves form at least two spaced chambers, at least two pins sized to fit within the spaced chambers, and means for releasably securing the rotor end to the rod end with the pins captured within the spaced chambers; and a stator to stator coupling including a cylindrical housing having a bore therethrough and including releasable securing means at each of its terminal ends for releaseably securing the housing to the lower end of the stator of one of the motors and to the upper end of the stator of the other motor.
8. The coupling of claim 7, wherein the rotor to rotor releasably securing means is sized to fit about the connecting rod and includes a threaded connector having at one end external threads for mating with internal threads within the rotor end cavity to contain the captured pins within the chambers.
9. The coupling of claim 7, wherein when said rotor to rotor coupling is assembled, said pair of rotors are coaxially aligned.
10. The coupling of claim 9, wherein when said rotor to rotor coupling is assembled, said pair of rotors are aligned in phase with respect to each other.
11. The coupling of claim 7, wherein when said stator to stator coupling is assembled, said stators are timed to said rotors.
12. The coupling of claim 11, wherein when said stators are timed, said pairs of stators are aligned in phase with respect to each other.
13. The couping of claim 7, wherein said cylindrical housing further includes a shim placed adjacent to one of the terminal ends, the shim having a width for causing said stators to be timed to said rotors.
14. The coupling of claim 13, wherein when said stators are timed, said pairs of stators are aligned in phase with respect to each other.
15. The coupling of claim 7, wherein one of said spaced chambers is sized different to form a synchronizing chamber and wherein one of said pins is sized to fit within the differently sized synchronizing chamber.
16. The coupling of claim 7, further comprising a thrust bearing assembly between the rotor end and the connecting rod end.
17. The coupling of claim 16, wherein the thrust bearing assembly includes a thrust pin secured within the rotor end cavity and having a ball socket and wherein the connecting rod end incudes a ball socket corresponding to the thrust pin ball socket and a ball sized to fit within the thrust pin and connecting rod ball sockets.
18. The coupling of claim 17, wherein the thrust pin includes a sealing ring and said releasably securing means includes a sealing ring for sealing the thrust bearing assembly.
19. The coupling of claim 7, wherein alternate ones of the external rod grooves are longitudinally staggered and alternate ones of the internal rotor grooves are longitudinally staggered such that alternate ones of the spaced chambers are longitudinally staggered.
20. The coupling of claim 7, wherein alternate ones of said pins are shorter than the others.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US08/433,544 US5588818A (en) | 1995-04-20 | 1995-04-20 | Rotor-to-rotor coupling |
| US433,544 | 1995-04-20 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2174017A1 true CA2174017A1 (en) | 1996-10-21 |
Family
ID=23720527
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002174017A Abandoned CA2174017A1 (en) | 1995-04-20 | 1996-04-12 | Rotor-to-rotor coupling |
Country Status (2)
| Country | Link |
|---|---|
| US (1) | US5588818A (en) |
| CA (1) | CA2174017A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| WO2015196282A1 (en) * | 2014-06-25 | 2015-12-30 | Evolution Engineering Inc. | Fluid pressure pulse generator for a downhole telemetry tool |
| US9840909B2 (en) | 2014-06-25 | 2017-12-12 | Evolution Engineering Inc. | Flow bypass sleeve for a fluid pressure pulse generator of a downhole telemetry tool |
| US9840910B2 (en) | 2014-06-25 | 2017-12-12 | Evolution Engineering Inc. | Fluid pressure pulse generator for a downhole telemetry tool |
| US9874092B2 (en) | 2014-06-25 | 2018-01-23 | Evolution Engineering Inc. | Fluid pressure pulse generator for a downhole telemetry tool |
| US10180059B2 (en) | 2016-12-20 | 2019-01-15 | Evolution Engineering Inc. | Telemetry tool with a fluid pressure pulse generator |
| US10415377B2 (en) | 2017-07-14 | 2019-09-17 | Evolution Engineering Inc. | Fluid pressure pulse generator and flow bypass sleeve for a telemetry tool |
Also Published As
| Publication number | Publication date |
|---|---|
| US5588818A (en) | 1996-12-31 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| FZDE | Discontinued |