Vibrational tool with rotating engagement surfaces and method

A vibrational tool and method is disclosed, which may be utilized to assist in lowering a drill string into a wellbore. In one embodiment, a reciprocating member and a symmetrical rotating member are mounted within a vibrational tool housing. The reciprocating member is urged in one embodiment by a spring assembly toward the rotating member whereby engagement surfaces on the reciprocating member and rotating member encounter each other. As the rotating member rotates, variable surfaces on the engagement surface cause the reciprocating member to reciprocate as the variable surfaces follow or cam with respect to each other during rotation. The resistance to rotation by engagement surfaces and spring assembly, and mass of the rotating member, result in vibrational forces, when drilling fluid flows through the vibration tool housing.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates generally to vibrator tool assemblies and, in one possible particular embodiment, to a vibrator tool with rotating engagement surfaces or camming surfaces which repeatably engage each other to produce vibrations for advancing bottom hole assemblies in oil and gas operations.

2. Description of the Prior Related Art

Oil and gas operators have continually found new methods of incorporating coiled tubing into various rig applications. Coiled tubing often has advantages over a conventional rig and drillstring, in that coiled tubing units can be less expensive and quicker to set up than conventional drilling rigs.

One major problem to both conventional and coiled tubing rigs is the ability to push tubing further into a wellbore under certain drilling conditions. Generally, drillers rely on the weight of the drillstring to counteract the frictional forces generated between the wellbore and drillstring. Once a certain depth is reached, or certain formations are drilled into, or at certain angles of the wellbore, the weight of the drill string is not sufficient to overcome the friction of the drill string to move the drill string downwardly as drilling continues. This tends to be especially true in coiled tubing operations, because coiled tubing cannot be rotated at the surface to overcome or reduce the friction the drill string with respect to the wellbore. Another significant factor is that coiled tubing tends to be more flexible and lighter compared to traditional drill pipe. As a result, coiled tubing may experience increased drag problems in the wellbore as compared with traditional drill pipe and is more prone to become lodged in the wellbore. This effect can become exacerbated in deviated wells and those with horizontal sections, where movement of pipe by the injector rig at the surface does not result in additional movement of the coiled tubing string into the wellbore. Furthermore, coiled tubing is more likely to stick in the wellbore based on the coiled design and spooled storage, which can create a spiral effect that may increase the number of sticking points inside the wellbore.

Various tools and methods have been utilized to deal with this problem, including vibrating tools, jars, tractors, centralizers, and pulsators. Thus, many designs have been utilized. While such tools have been utilized successfully, the forces created thereby are not necessarily efficient in utilizing the energy created thereby. Accordingly, the present invention will be appreciated by those of skill in the art.

SUMMARY OF THE INVENTION

One possible object of the present invention is to provide an improved vibrational tool for use in a bottom hole assembly.

Another possible embodiment of the present invention is provide engagement surfaces which rotate with respect to each other with a camming action to thereby produce vibrations.

Another possible object of the present invention is to provide a tool to overcome drag between coiled tubing and the inside of a wellbore.

Another possible object of the present invention is to provide a tool that produces vibrations that are directed substantially in line downwardly and/or upwardly axially in line with the drilling string

Another possible object of the present invention is provide a stabilizing gyroscopic effect due to rotation of a symmetrical mass around the axis of the tool.

These objects, as well as other objects, advantages, and features of the present invention will become clear from the description and figures to be discussed hereinafter. It is understood that the objects listed above are not all inclusive and are intended to aid in understanding the present invention, not to limit the scope of the present invention.

Accordingly, the present invention may comprise a vibration tool for use with a tubular string in a well bore through which drilling fluid is pumped which may comprise a housing attachable to the tubular string and a rotatable symmetrical mass mounted within the housing for relative rotation with respect to the housing.

A first pair of variable shaped engagement surfaces may comprise a first variable shaped engagement surface and a second variable shaped engagement surface. At least one of the first variable shaped engagement surface or the second variable shaped engagement surface are mounted to the rotatable mass with a remaining one being supported within housing.

A spring mounted within the housing urges the first variable shaped engagement surface and the second variable shaped engagement surface together, whereby the relative rotation of the mass with results in relative reciprocal motion of between the first variable shaped engagement surface and the second variable shaped engagement surface as the first variable shaped engagement surface and the second variable shaped engagement surface rotate with respect to each other and a fluid flow path through the housing which engages the mass to urge the rotation of the mass.

In one embodiment, the vibrational tool may further comprise a reciprocating member mounted for reciprocating movement at least generally axially with respect to the housing, wherein the spring is mounted to the reciprocating member. The first pair of variable shaped engagement surfaces may be mounted between the reciprocating member and the rotatable mass.

In one embodiment, a plurality of mounts within the housing to rotatably mount the mass for the relative rotation with respect to the housing at least substantially along an axis of the housing, wherein rotation of the mass results in reciprocating movement of the reciprocating member.

The first variable shaped engagement surface and the second variable shaped engagement surface may comprise indentations. The first variable shaped engagement surface and the second variable shaped engagement surface comprise a plurality of curved surfaces and relatively smooth camming surfaces or effectively spring-loaded surfaces which follow each other with a camming action. The curved surfaces comprise a number of undulations which number affects a rate of vibration of the vibration tool, e.g., more undulations for the same RPM of the mass results in a high vibration frequency.

The first variable shaped engagement surface and the second variable shaped engagement surface can be made to be readily replaceable, mounted with fasteners or the like, with different numbers of undulations to thereby change the rate of vibration of the vibration tool.

In one possible embodiment, at least one of the first variable shaped engagement surface and the second variable shaped engagement surface comprise roller bearings. In one embodiment, the roller bearing may comprise at least substantially cylindrical roller bearings.

In one embodiment, at least two of the plurality of mounts for the housing for rotationally mounting the mass are positioned on axially opposite sides of the mass with respect to an axis of the housing and prevent axial movement of the mass with respect to the housing.

The vibrational tool may further comprise a second housing or multiple housings mountable with respect to the first housing. The multiple housings, such as the second housing may comprise a second reciprocating member, a second mass, and a second pair of variable shaped engagement surfaces.

The second pair of variable shaped engagement surfaces can be configured to produce vibrations at a different frequency than the first pair of variable shaped engagement surfaces, whereby the vibrational tool vibrates at a multiple of frequencies. If other housings are utilized, then other frequencies can be produced.

In another embodiment, a method provides a vibration tool for use with a tubular string in a well bore through which drilling fluid is pumped. The method may comprise steps such as providing a housing attachable to the tubular string, mounting a reciprocating member within the housing for reciprocating movement with respect to the housing, rotatably mounting a mass within the housing for relative rotation with respect to the housing around an axis of the housing, and mounting a spring, such as any type of urging mechanism to urge the reciprocating member into engagement with the mass so that the mass is positioned for spring-loaded engagement with the reciprocating member.

Other steps may comprise providing a first pair of variable shaped engagement surfaces wherein a first variable shaped engagement surface is mounted reciprocating member and a second variable shaped engagement surface is mounted to the mass that is urged into engagement the first variable shaped engagement surface by the spring, whereby the relative rotation of the mass with respect to the spring loaded member results in reciprocal motion of the reciprocating member as the first variable shaped engagement surface and the second variable shaped engagement surface rotate with respect to each other.

The method may comprise mounting the reciprocating member in a manner that prevents rotational movement of the reciprocating member.

The method may comprise providing at least one of the first variable shaped engagement surface and the second variable shaped engagement surfaces with a plurality of indentations wherein a number of the plurality of indentations is related to a frequency of vibration of the vibrational tool.

The method may comprise changing the frequency of operation by replacing the engagement surfaces with different numbers of indentations to thereby change the frequency of vibration of the vibration tool.

In another embodiment, a vibration tool for use with a tubular string in a well bore through which drilling fluid is pumped may comprise elements such as, but not restricted to, a housing attachable to the tubular string, a reciprocating member within the housing for reciprocating movement with respect to the housing, a rotatable mass within the housing mounted for rotation in response to flow of the drilling fluid, a spring such as any type of urging mechanism mounted to urge reciprocating member into engagement with the rotatable mass, and a pair of engagement surfaces that may comprise a first engagement surface mounted on the reciprocating member and a second engagement surface mounted on the rotatable mass. The pair of engagement surfaces is urged into engagement with the spring. The pair of engagement surfaces comprise a plurality of varying surfaces, whereby when the rotatable mass rotates then the reciprocating member reciprocates in response to interaction between the pair of engagement surfaces.

DETAILED DESCRIPTION OF THE INVENTION

Referring now to the drawings, and more particularly toFIG. 1, there is shown coiled tubing unit10with coiled tubing20extending into earth30. In this example, turbine40is rotating bit50. Turbine40spins in response to drilling fluid pumped by pump60which pumps drilling fluid80down the tubing and drilling fluid70outside the tubing through the annulus back to pump60.

It will be noted that the drawings are intended to be conceptual embodiments of the invention, which may be shown greatly simplified or exaggerated to emphasize the various concepts of the invention. The drawings are not intended to be manufacturing level drawings. Moreover, to the extent terms such as “upper,” “lower,” “top,” “bottom,” and the like are utilized herein they refer to the drawings. The tool100may be oriented differently during operation or transport than shown.

One or more vibrator sections100in accord with the present invention may be utilized to assist downward movement of the coiled tubing20or other tubular strings. Vibrators100may be positioned above or below turbine40and, if desired, can be rotated with bit50. In one embodiment shown inFIG. 4and discussed hereinafter, one or more vibrator sections may be built into the bit housing50itself, if desired, and used either with or without other vibrator sections.

Vibrators100can be especially desirable in high angle or horizontal wells where the weight of the string may not be adequate in itself or not at all to cause the tubing to move downwardly for drilling. Vibrator sections100utilize drilling fluid flow80to vibrate, activate, move, oscillate, or otherwise work the string in order to move the drill string further down the hole to, for example, drill deeper. In one possible embodiment of the present invention, pulsating resistance to drilling fluid flow creates vibrations that tend to push the string into the wellbore.

FIGS. 2A and 2Bshow one possible embodiment of internal components of vibrator100. Vibrator100may comprise sliding member102, sometimes referred to herein as reciprocating member102, which reciprocates upwardly and downwardly (as per drawing orientation) as indicated by arrow130. Reciprocating member102may be cylindrical but other shapes, e.g., triangular, square, hexagonal, and other shapes, could also be possible at least for portions of reciprocating member102.

In this embodiment, reciprocating member reciprocates in response to camming action, discussed hereinafter, and rotation of mass104, which rotates in response to flow of entering drilling fluid as indicated by flow arrow106into tubular vibrator housing108and exiting as indicated by flow arrow107.

It will be understood that the drawings are intended to show concepts and that many variations are possible, only some of which are discussed hereinafter. For example, in one possible embodiment, reciprocating member may not be utilized and/or may be oriented differently with respect to mass104. The caroming action could move other components and might be utilized to cause reciprocation of rotating mass104, which could be spring loaded in some way.

InFIG. 2A, engagement surface120on upper portion122of rotating mass104meshes or cams or follows with engagement surface114of reciprocating member102. InFIG. 2Areciprocating member102is spring loaded and reciprocates with respect to rotating mass104due to camming or following action as mass104rotates while reciprocating member102is prevented from rotation. In other words, as the protrusions and recessions, or caroming surfaces of surface120and114, rotate with respect to each other, reciprocating member102is pushed away from and then urged back towards mass104by spring150. However, as noted above, the present invention is not limited to this embodiment.

Accordingly, in one embodiment of vibrator100, a mechanical connection connects rotation of mass104and changes the rotating motion of rotating mass104to reciprocating motion of reciprocating member102. Many different types of mechanical connections could be utilized to interconnect rotating mass104to reciprocating member102including geared connections, fluid connections, insertions, strap or chain connections, hydraulic connections, and the like. Mechanical connections of various types could be utilized between rotating mass104and reciprocating member102to create vibrations, different types of jarring effects, and the like. However, in the embodiment ofFIG. 2A,FIGS. 2B, and3, vibrator100utilizes sturdy camming, or following action and drilling fluid flow to create the vibrations thereof.

In this embodiment, frame110supports reciprocating member102therein for sliding or reciprocating motion of reciprocating member102. Frame110may be secured to vibrator housing108by various means such as but not limited to mounts113. As shown inFIG. 2A, guide members111, slots, or the like in the sides of frame110may be utilized to allow sliding axially directed motion of reciprocating member102but prevent rotation of reciprocating member102. Because in this embodiment reciprocating member102cannot rotate, reciprocating member is constrained to reciprocate in response to rotation of mass104. Reciprocating member102may comprise various shapes. In one embodiment, reciprocating member102comprises a tubular sliding section upward section, which reciprocates generally along the axis of tubular vibrator housing108. Reciprocating member102and/or frame110may also have a middle portion, upper portion or other portions one or more of which can be circular, elliptical, triangular, square, rectangular, star shaped or the like. If desired, reciprocating member102or portions thereof may be solid and weighted or may be of relatively light weight. In any case, reciprocating member102and frame110are sufficiently sturdy to undergo significant vibration over long periods of time. If desired, weights may be added or removed from reciprocating member102.

In one embodiment, reciprocating member or mass102may also engage stops, anvils, or the like117, which may be utilized on either or both ends of the sliding travel during each stroke, which may repeatedly make contact in jarring fashion if desired. Reciprocating member102could be designed to engage upper surfaces or lower surfaces or both in frame110with a jarring action as described in one embodiment here.

Accordingly, in one embodiment shown inFIG. 2A,FIG. 2B, andFIG. 3, camming engagement surfaces114and120are utilized to provide reciprocating motion of member102. Reciprocating member102may be of different sizes and lengths as desired. The stroke of reciprocating member102is determined by the length of the protrusions and recessions of engagement surfaces, such as recessions118and protrusions116, which may vary in one embodiment, but are not limited to, between one-quarter inch and one inch.

While spring150is shown on the top side of reciprocating member102in the orientation ofFIG. 2, the spring could be on the bottom side to create a jarring against the upper surface of frame110whereby reciprocating member102could be, for example only, tightened, spring-loaded, and released for acceleration again a jarring surface such as the top of frame110by an engagement mechanism with rotating mass104. Thus, the embodiment shown in the figures with spring150above reciprocating member102is only one possible embodiment of construction and operation. In another embodiment, spring150could be utilized to spring load rotating mass104to provide axially directed vibrational forces produced by mass104instead of reciprocating member102, which may also include jarring action at one end or the other of travel.

Accordingly, in one possible non-limiting example, reciprocating member102has an engagement end or surface114at a bottom end, which may be more clearly shown inFIG. 2B. Engagement end or surface114may operate as a type of cam. At the opposite end of reciprocating member102, reciprocating member102may comprise spring loaded end115. Spring-loaded end115may be energized with spring150, which urges engagement surface114of reciprocating member102against engagement surface120on mass104. The engagement surfaces114and120on each end, when rotated with respect to each other, cause a cam following motion, which in this embodiment, constrains spring-loaded reciprocating member102to reciprocate because reciprocating member102does not rotate and rotating mass104is axially fixed in position and does not reciprocate.

Spring150may comprise a spring assembly, which may be of many constructions. Spring150may comprise a spring or spring assembly which is intended to refer any type of mechanism to urge the engagement surfaces together including coiled resilient metal springs, compressed gas, multiple coiled springs, leaf springs, compression springs, extension springs, torsion springs, tapered springs, multi-spring combinations, magazine springs, elastomeric members, foam springs, combinations thereof, or any desired types of springs and is intended generally to cover resilient members that are operative as described in this embodiment. Conceivably the flow of drilling fluid might be utilized as an urging mechanism if the components are reconfigured. If the system were reversed in position with respect to fluid flow, then fluid flow could be directed to provide the spring or urging mechanism that urges the camming surfaces together.

In this embodiment, the tension required to compress spring150and the mass of reciprocating member102relates to the intensity of vibrations produced during operation. However, various factors such as spring tension, mass of reciprocating member102, mass of rotating mass104, stops or anvils117at the end of the stroke of reciprocating member102, the length of the protrusions/recessions of the engagement surfaces, different types of turbine or rotor fins, blades, grooves or the like will affect the vibration frequency and intensity and pattern of the vibrations produced by vibration tool110.

In the embodiment ofFIG. 2AandFIG. 2B, engagement surface114has variations such as protrusions116and/or recessions118. In one embodiment, the surfaces such as protrusions116may be much smoother than shown, and in one embodiment the engagement surfaces may preferably be smooth or undulating, and spaced at any desired intervals, of any desired number, as is related to frequency characteristics and motions of vibrations produced thereby.

Accordingly, in one embodiment, engagement ends or surfaces114and120may comprise camming surfaces whereby the protrusions116and/or recessions118may preferably be smooth and quite rounded to produce a cam following type of action. However, if desired, the protrusions may slope upwardly and come to a distinct sharp edge whereby only one or two significant vibrations or jars occur per rotation of mass104. Thus, the engagement surfaces may not be completely smooth.

A relatively larger number of protrusions may be utilized to produce higher frequency vibrations. Irregular vibrations may be produced by spacing the cams at irregular or non-symmetrical spacing. Accordingly, the arrangement of protrusions and recessions may allow the vibrations to occur at a continuous frequency or at irregular frequencies, e.g., several quick beats and/or pauses and one beat, or the like, depending on the spacing of the cams. For example, with only one camming element, then only one beat might be produced per revolution of mass104. In another example, multiple and/or irregular beats may be produced per revolution of mass104. Accordingly, the number of protrusions/recessions and the spacing therebetween may be selected to create a desired frequency of vibration and motion. In one embodiment, the camming surfaces, such as protrusions116and/or recessions118and/or camming surfaces120may be interchangeable to change the vibration frequencies.

In one embodiment, corresponding camming surfaces120are provided on engagement end122of mass104, which is the upper end as shown inFIG. 2. Camming engagement surfaces120may be of various types, shapes, and the like.

In one embodiment, roller bearings may be, but are not required to be utilized as camming surfaces120.FIG. 3, which is cross-section3-3ofFIG. 2A, looks down on roller bearing assembly126, which may comprise roller bearings124, as part of bearing race128, which is fastened with respect to mass104, and is fixed in position. Roller bearings124may be free to rotate individually but the roller bearing assembly126is fixed in position with respect to mass104, so as to rotate with mass104.

The camming surfaces may be reversed in position. In other words, the roller bearings could be affixed to reciprocating member102and/or roller bearings or other bearings could be used on both reciprocating member102and rotating mass104. Other types of frictionless bearings such as roller bearings, cylindrical bearings, ball bearings, thrust bearings, tapered bearings, combinations of the above, and the like may be utilized. Due to the opening and closing action, the camming surfaces are highly lubricated with each vibration, oscillation, or the like. Lubrication fluid may comprise the drilling fluid directed onto the camming surfaces and/or the camming surfaces may be mounted within a lubrication chamber.

Accordingly, in this embodiment, in response to rotation of mass104, member102reciprocates as indicated at arrow130. In this embodiment, spring150is positioned at a top end (as shown in the orientation ofFIGS. 2A and 2B) of reciprocating member102to urge engagement of engagement surface114against engagement surface120of mass104.

In one possible embodiment, mass104may rotate at least substantially symmetrically around the axis of vibrator housing108. Mass104arrow145indicates rotation of mass104but is not intended to necessarily show the direction of rotation, which may be in either direction, depending on the rotary drive features such as blades, grooves, or the like in rotating mass104. Mass104may be mounted by various mounting such as rotary mountings132and shaft134on opposite axial ends of rotating mass104. Rotary mountings132and134may in one embodiment be secured to housing108by support members136and138(shown at top and bottom ofFIG. 2B). In one non-limiting embodiment, rotary mountings132and134are designed to prevent axial movement. Rotary mountings132and134, and/or different types or numbers of mountings, may be utilized. Accordingly, in one possible preferred embodiment rotating mass104rotates in the axis of housing108but does not move axially. However, in another embodiment, rotating mass104may move axially for jarring action. Camming surfaces could be provided along the sides of rotating mass104and/or ends thereof to facilitate axial and rotational movement of a spring-loaded mass. In yet another embodiment, the drilling fluid may act as the spring force because the drilling fluid acts to urge a member in the direction of fluid flow.

Rotating mass104may comprise various shapes and can be generally rounded with a relatively flattened top, as shown inFIG. 2AandFIG. 2B. However, rotating mass104could be conical and have a triangular cross-section with relatively straight or slightly curving sides. In one embodiment, rotating mass104increases in diameter in the direction of fluid flow or the top (as shown inFIG. 2Aor2B) in order to more fully and efficiently pull power out of the drilling fluid flow. In this embodiment, mass104increases in diameter in the direction of drilling fluid flow until reaching the top or another position at which time the drilling fluid is directed as desired, such as into the camming surfaces for lubrication purposes. Thus, in one presently preferred embodiment, from end170where fluid enters to drive rotating mass104, at least a portion of rotating mass104increases in diameter.

In one embodiment, rotating mass104, which rotates around an axis of housing104, which is also in line with the axis of the tubing connected thereto, may be utilized to produce a gyroscopic effect to stabilize the position of the tubing within the wellbore. Mass104may comprise a diameter in the range of but not limited to from 60 to 90 percent of the diameter of the tubing or housing108, and a length in the range of but not limited to from 40 to 80 percent of the length of housing108. Accordingly, the size of rotating mass104can be significant with respect to vibration tool100. If mass104is substantially solid metal, and depending of the rotational speed of mass104, the gyroscopic lateral stabilizing effect produced around the axis of housing108can be significant.

Mass104may be built in longitudinal sections so as to be more easily constructed. The grooves or fins of mass104utilized to rotate mass104in response to fluid flow may then be more easily formed, machined, cast or the like. Fasteners can then be used to put the sections of mass104back symmetrically with the mass of mass104being symmetric about the axis of vibrator housing108.

In one embodiment, the amount of mass of mass104is much greater, in the range of 50 to 100 times or more than the mass of reciprocating member102. In this embodiment, mass104may be largely solid and may therefore comprise in the range of but not limited to 30 to 80 percent of the total mass of vibrator section100. In one possible embedment, reciprocating member102may comprise less than 10 percent of the total mass of vibrator section100and therefore may be considered a relatively lightweight component. In yet another embodiment, reciprocating member102may be made much heavier and used for jarring purposes, such as jarring against anvil surfaces117in which case reciprocating member102may comprise 30 to 80 percent of the total mass of vibrator section100.

FIG. 2BandFIG. 5illustrate some non-limiting examples of fluid flow grooves or vanes to provide that mass104is effectively a turbine or rotor. One feature of a presently preferred embodiment, where mass104is prevented from axial movement, is that the diameter of all flow paths does not change due to paddles or the like that may be inserted in the fluid flow path. In other words, in this embodiment, vibration tool100is not driven by paddles or the like that may momentarily block fluid flow when they are engaged by the flow stream. This feature is useful in that a more consistent flow of fluid through vibration tool100does not impede operation of the turbine to rotate the drill bit and/or MWD systems that transmit signals to the surface. However, the invention is not limited to this embodiment. For example, if mass104were axially moveable and reciprocal, a possibility discussed hereinbefore, then the flow path volume might increase and decrease corresponding to axial movement of mass104.

FIG. 5shows a flattened view of conceptual fluid flow lines with bottom170of mass104shown and the fluid flow lines, grooves, or fins effectively stripped off of mass104and flattened to a two dimensional view.FIG. 2Bshows one possible view with flow lines on the sides of mass104. InFIG. 5, fluid flow may enter four openings, grooves, flow lines, fins or the like, such as opening172. The width and depth of opening172may be varied. As well, the flow line, fins, or the like could be formed internally to mass104instead of being formed on the external surface as indicated.

Opening172then feeds flow lines, grooves, fins, or the like which may split from each other as indicated by162,164,166, and168shown conceptually inFIG. 2BandFIG. 5. Thus, in one embodiment, multiple branches are provided.

In one embodiment, in order to keep the fluid pressure in each branch relatively constant so as to maximize the energy derived from the drilling fluid flow, the depths of each subsequent branch may be made shallower so that the total flow pressure through each of the branches until exit of the fluid from each branch is relatively constant. This may be accomplished in different ways. For example, at the split of a branch, e.g., the branch from162to164, the subsequent depth of the groove162and initial depth of grove164may be halved, with respect to the initial depth of groove162as indicated at172. At the branch from groove164to166, the subsequent depth of groove164may be halved and the initial portion of groove166may be halved again. The multiple branches and increasing diameter of rotating mass104provides that a large amount of the available power in the drilling fluid flow is utilized for rotating mass104and producing the pulsating or vibrational power. In another embodiment, additional more elongated fluid flow grooves or fins could be utilized that are longer but do not branch and have a relatively constant depth.

As well fluid flow may also (or may not) be provided through grooves in housing108as indicated in dashed lines by grooves174and176shown inFIG. 2BandFIG. 5. In the embodiment shown in the figures, while rotating mass104has at least a portion thereof with an increasing diameter in the direction of fluid flow, housing108has a corresponding increasing internal diameter to accommodate rotating mass104.

FIG. 4shows another embodiment of invention wherein in one embodiment a vibration section100is built into housing51of the drill bit50(shown for example inFIG. 1). Normally, drill bit housing51is a very sturdy structure into which bits such as roller cones, PDC cutters, jets, diamond cutters, and the like are built into the housing. Drill bit housings are well known. Vibration section100may be as described hereinbefore but could be built using various ways to create vibrations, jarring, or the like. By having the vibration section into drill bit housing51, the rates of drilling can often be improved significantly. The rotation of mass104could be utilized to stabilize the position of the drill bit due to the gyroscopic effect discussed hereinbefore, and prevent or reduce bit whirl should gage inserts try to grab the sides of the wellbore. Moreover, should vibration section100cease functioning, as long as the drilling fluid flow continues, then the bit can continue operation so bit reliability is not affected by mounting vibration section100therein. Drill bit housing may include sensors180built therein as well, which can be sent by systems such as MWD systems or other transmission systems as desired or the data may be stored in a memory for retrieval without the need for a transmission system. Sensors180for the bit may comprise vibration sensors to monitor operation of vibration section100and/or other sensors such as fluid flow, weight on bit, and the like.

In yet another embodiment, mass104may be utilized as a gyro without necessarily utilizing vibrational members. The use of rotating mass104as a gyro can be utilized to drill a smoother and/or straighter hole. Moreover, in combination with a flexible housing182, the gyroscopic effect of mass104may be used reactively to aid in steering the drill string. Even a small mass104at high speeds can produce large gyroscopic forces, which react strongly to being pushed one way or the other by use of flexible housing182, which may be of various constructions. Flexible housing182may be constructed in different ways to flex in different directions thereby interacting with the gyroscopic effect to enhance and/or control the direction of drilling. Flexible housing182may comprise a different sub attached to the bit or may be built into the shank of the drill bit housing itself. The angle shown for flexible sub182is exaggerated for effect and will typically comprise much smaller angles as known for directional drilling purposes. Rotating mass104can be lengthened and/or used in a different sub for gyroscopic purposes with or without flexible sub182.

Accordingly, in operation, drilling fluid flow enters vibrator housing100as indicated by fluid flow arrow106and exits from the opposite end thereof as indicated by flow arrow107. The drilling fluid flowing through vanes or fins formed on rotating mass104, which can be of many variations, cause rotation thereof. The rotation of mass104causes camming surfaces or engagement surfaces114and120or other mechanical interconnections to interact and produce reciprocating movement of reciprocating member102. In this embodiment, spring150presses the engagement surfaces together to create varying resistance to rotation of rotating mass104, which results in vibrations.