BEARING ASSEMBLY WITH FLOW RESTRICTOR FOR A DUAL ROD DIRECTIONAL DRILLING APPARATUS AND METHOD OF USE

Abstract

A rock housing for horizontal directional drilling machine includes a cylindrical housing body with walls defining a longitudinal cavity. A bearing assembly is provided as a part of the housing and is located above a bit box region of the housing. The bearing assembly is lubricated by drilling mud which flows through the drill string of the drilling machine. A portion of the drilling mud is diverted and passes through a gap formed between the bearing races of the bearing assembly, the gap being sized so as to create the necessary back pressure to divert the needed flow of drilling mud to the assembly. In some cases, an additional flow restrictor can be provided in the gap between the bearing races when needed, as when the driller is using a very low viscosity drilling fluid.

Claims

1. A bearing assembly for a rock housing used in a horizontal directional drilling apparatus, the apparatus comprising: a horizontal boring machine having a frame, a rotary machine supported on the frame, a drill string and a directional boring head, where the drill string has a first end, which is operatively connected to the rotary machine to drive the rotation of the drill string, and a second end, which is attachable to the directional boring head, the drill string itself being comprised of a plurality of lengths of dual-rod pipe which include passageways for conducting drilling mud to the boring head to cool the head and remove cuttings produced during drilling operations; wherein the rock housing is located in the drill string at a lower extend thereof, the rock housing having an upper connecting end for connection in the drill string and an opposite, lower end, the lower end including a lower housing and a bearing mandrel bit box for connection to the boring head, the lower housing containing the bearing assembly and also containing an internal flow path for the passage of drilling mud; wherein the bearing assembly is lubricated by special passageways formed within the bearing assembly which divert a portion of the flow of drilling mud passing through the drill string and through the rock housing to the boring head, the internal passageways serving as a metering device for the flow of drilling mud through the bearing assembly; wherein the bearing assembly includes a plurality of inner bearing races and a plurality of companion outer bearing races, the inner and outer races having a plurality of bearing elements located therebetween, and wherein a first inner race and its companion first outer race are intentionally machined so that a gap of a predetermined width exists between the races when the races are assembled with the bearing elements located therebetween; wherein the bearing assembly is made up of five or more companion inner and outer races separated by a plurality of ball bearings, and wherein the gap which exists between the first inner race and its companion first outer race is smaller in size than the gap which exists between each remaining inner and outer pairs of races in the bearing pack in the downhole direction toward the boring head; wherein the size of the gap between the bearing races can be adjusted to provide a desired amount of back pressure in the fluid passageway which controls the amount of drilling mud that is allowed to pass through the bearing assembly, the remaining flow being encouraged to flow toward the boring head; and wherein an additional flow restrictor is provided, integral to the bearing assembly, within the flow passageway defined by the gap between the bearing races, where very low viscosity drilling fluids are being used.

2. The bearing assembly of claim 1, wherein the additional flow restrictor is a circumferential band which is located within a groove cut in a selected face of one of the inner and outer races.

3. The bearing assembly of claim 2, wherein the band is a flat, circumferential member having a generally square or rectangular cross section, the band having a section removed therefrom to thereby form an opening which allows drilling fluid to pass through.

4. The bearing assembly of claim 2, wherein the band is round in cross section.

5. The bearing assembly of claim 2, wherein the first bearing race is made up of inner race having an outer circumferential region and a mating outer race having an inner circumferential region, and wherein the groove is cut in the outer circumferential region of the first inner race of the bearing assembly.

6. The bearing assembly of claim 2, wherein the band is formed of a metal, synthetic or composite material having the requisite strength, corrosion resistance and abrasion resistance for the drilling environment at hand.

7. The bearing assembly of claim 2, wherein the band is formed of an Ultra-High-Molecular Weight thermoplastic material.

8. The bearing assembly of claim 2, wherein the band is formed of Ultra-High-Molecular-Weight polyethylene.

9. The bearing assembly of claim 2, wherein the band is formed of a metal such as stainless steel.

10. The bearing assembly of claim 1, wherein the bearing elements are a plurality of ball bearings.

11. The bearing assembly of claim 1, wherein the bearing assembly is characterized by the absence of any type of sealed cavity containing oil or grease lubricant, but instead relies solely on the flow of drilling mud through the bearing assembly.

12. A method of lubricating a bearing assembly for a rock housing used in a horizontal directional drilling apparatus, the method comprising the steps of: providing a bearing assembly for a horizontal boring machine having a frame, a rotary machine supported on the frame, a drill string and a directional boring head, where the drill string has a first end, which is operatively connected to the rotary machine to drive the rotation of the drill string, and a second end, which is attachable to the directional boring head, the drill string itself being comprised of a plurality of lengths of dual-rod pipe which include passageways for conducting drilling mud to the boring head to cool the head and remove cuttings produced during drilling operations; wherein a rock housing is located in the drill string at a lower extend thereof, the rock housing having an upper connecting end for connection in the drill string and an opposite, lower end, the lower end including a lower housing and a bearing mandrel bit box for connection to the boring head, the lower housing containing the bearing assembly and also being provided with an internal flow path for the passage of drilling mud; wherein the bearing assembly is provided with a plurality of inner bearing races and a plurality of companion outer bearing races, the inner and outer races having a plurality of bearing elements located therebetween, and wherein a first inner race and its companion first outer race are intentionally machined so that a predetermined gap exists between the races when the races are assembled with the bearing elements located therebetween, the gap between the first pair of inner and outer races in the bearing pack being less than the gap which exists between any of the remaining inner and outer pairs of races in the bearing pack, the gap forming special lubricant passageways within the bearing assembly which divert a portion of the flow of drilling mud passing through the drill string and through the rock housing to the boring head, the internal passageways serving as a metering device for the flow of drilling mud through the bearing assembly; and wherein an additional flow restrictor is provided, integral to the bearing assembly, within the flow passageway defined by the gap between the bearing races, where very low viscosity drilling fluids are being used.

13. The method of claim 12, wherein the additional flow restrictor is a circumferential band which is located within a groove cut in a selected face of one of the inner and outer races.

14. The method of claim 13, wherein the band is a flat, circumferential member having a generally square or rectangular cross section, the band having a section removed therefrom to thereby form an opening which allows drilling fluid to pass through.

15. The method of claim 12, wherein the first bearing race is made up of inner race having an outer circumferential region and a mating outer race having an inner circumferential region, and wherein the groove is cut in the outer circumferential region of the first inner race of the bearing assembly.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0024] FIG. 1 is a perspective view of the rock housing of the invention showing the outer components thereof.

[0025] FIG. 2 is a partly exploded view of the rock housing of FIG. 1.

[0026] FIG. 3 is an isolated view of the bearing assembly used in the rock housing of FIG. 1, shown in exploded fashion.

[0027] FIG. 4 is simplified sectional side view of the rock housing of the invention showing the ball bearings in their respective bearing races.

[0028] FIG. 5 is a close-up, side cross sectional view of the bearing assembly of the invention, taken from the region illustrated as 5 in FIG. 4, showing the direction of flow of the mud lubricant.

[0029] FIG. 6 is an isolated cross sectional view of the bearing region of the rock housing showing the relative gap regions between the inner and outer bearing races which form the flow path for the mud lubricant.

[0030] FIG. 7 is a simplified, schematic illustration of a horizontal directional drilling machine of the type which would utilize the improved bearing assembly of the invention.

[0031] FIG. 8 is an isolated cross sectional view, similar to FIG. 6, but showing the groove cut in the first bearing race which contains the circumferential band used to provide further flow restriction in cases where very low viscosity drilling fluids are being used.

[0032] FIG. 9 is a perspective end view of the bearing assembly of FIG. 8, partially disassembled, showing the groove cut in the first bearing race and the circumferential band located in the groove.

[0033] FIG. 10 is a top perspective view of the circumferential band used in the version of the invention illustrated in FIG. 9.

DETAILED DESCRIPTION OF THE INVENTION

[0034] The preferred version of the invention presented in the following written description and the various features and advantageous details thereof are explained more fully with reference to the non-limiting examples included and as detailed in the description which follows. Descriptions of well-known components and processes and manufacturing techniques are omitted so as to not unnecessarily obscure the principal features of the invention as described herein. The examples used in the description which follows are intended merely to facilitate an understanding of ways in which the invention may be practiced and to further enable those skilled in the art to practice the invention. Accordingly, the examples should not be construed as limiting the scope of the claimed invention.

[0035] Directional drilling systems of the type referred to above are sometimes referred to as trenchless drilling, systems and are commonly used, e.g., to install utilities around immovable objects, such as roadways, rivers and/or lakes, etc. They may often be seen being used to tunnel under sidewalks and city streets to install such things as fiber optic cables, or other electrical utility lines.

[0036] The boring machine used in conventional horizontal boring techniques is thus commonly used to push and/or rotate a drill string, the drill string carrying a directable drill bit to achieve an underground path or direction through which a conduit or utility device can be installed. A sonde follows the drill bit as it is directed around, over or under obstructions. The sonde transmits electronic positioning signals to a worker vertically above the sonde, for example, by way of a hand-held complementary receiving device.

[0037] The particular class of drilling machines which utilize the rock housing of the invention include a horizontal boring machine comprising a frame, a rotary machine supported on the frame, a drill string and a directional boring head. The drill string has a first end, which is operatively connectable to the rotary machine to drive the rotation of the drill string, and a second end, which is attachable to the directional boring head. The drill string itself is comprised of a system of pipe joints connecting lengths of drill pipe. These type systems are sold commercially by Vermeer and Ditch Witch, as well as others in the HDD industry and will be readily familiar to those skilled in the relevant arts.

[0038] Turning first to FIG. 7, there is shown a simplified representation of a horizontal directional drilling (HDD) machine 11, the machine being shown driving a drill string 13 into the ground. The distal end of the drill string includes a drill tool assembly, illustrated in simplified fashion as 15. A coupling fits between an end of the drill string 13 and the drill tool assembly 15. Particularly for rock drilling applications, dual-member drill string systems are preferred, sometimes referred to as dual-rod systems. Dual-member drill strings are comprised of a plurality of pipe joints, each of which comprises an inner member supported inside an outer pipe or member. The inner member of the drill pipe constantly drives rotation of the boring head to excavate the formation, while the outer member of the drill pipe is selectively rotated to align the steering mechanism to change the direction of the borehole while the rotating bit continues to drill. Typical systems of this type are shown in U.S. Pat. No. 5,490,569, issued Feb. 13, 1996, entitled Directional Boring Head With Deflection Shoe, and in RE38,418, reissued Feb. 10, 2004, entitled Dual Member Pipe Joint for a Dual Member Drill String, by way of example.

[0039] In one type of dual-rod drilling system known in the industry, the ends of both the inner member and outer members of a dual member drill string are threaded. Thus, making up and breaking out pipe joints in a dual member drill string system is more time consuming requiring two pipe connections instead of one for each joint. In another type of dual-rod drilling system, the time required to make and break pipe joint connections is reduced by providing, for example, a slip fit connection at each end of the inner member and a threaded connection at each end of the outer pipe member. This single-action connection is achieved by forming the ends of the inner members in a particular shape which permits, for example, axial sliding connection of a like joint to form a connector-free, torque-transmitting connection.

[0040] U.S. Pat. No. 10,167,680, issued Jan. 1, 2019, to Adkins, shows a threaded connection for connecting a removable downhole tool assembly to a drill string. The threaded connection has a downhole end portion configured to interface with the removable downhole tool assembly and an up-hole end portion opposed to the downhole end portion. The up-hole end portion is configured to interface with the drill string as part of a torque-less coupling using a special adapter body.

[0041] This rather detailed discussion of dual-rod directional drilling (HDD) machines of the type used for trenchless drilling, and commonly used, e.g., to install utilities around immovable objects, such as roadways, rivers and/or lakes, etc., is intended to specifically distinguish oil and gas well drilling operations, some of which use mud-motors in directional drilling activities. Obviously, the stresses and forces involved in drilling, for example, an oil well, differ considerably from those involved in the type of HDD activities envisioned with the use of the present invention. There are other important structural differences, as well.

[0042] Turning now to FIG. 1, there is shown a rock housing of the invention, designated generally as 17. The rock housing 17 will be located in the drill string at a lower extent thereof. The rock housing 17 has an upper connecting end 19 for connection in the drill string and an opposite, lower end 21. The lower end includes a lower housing 23 and a bearing mandrel bit box 25 for connection to the boring head (drill bit). The lower housing 23 contains the bearing assembly (shown in exploded fashion as 27 in FIG. 3). The lower housing 23 is also provided with an internal flow path 29 for the passage of drilling fluid (mud). The drilling mud provides lubrication for the drill bit and also serves as the medium for removing cuttings from the borehole as drilling proceeds. The particular rock housing shown in FIG. 1 has a removable locking lid 31 which provides access to the steering sonde (not shown).

[0043] FIG. 2 shows the lower housing with the bearing assembly 27 of the invention being shown in exploded fashion. As will be explained more fully in the description which follows, the bearing assembly 27 is lubricated by special passageways formed within the bearing assembly which divert a portion of the flow of drilling mud passing through the drill string and through the rock housing to the boring head. The internal passageways serve as a metering device for the flow of drilling mud through the bearing assembly 27.

[0044] As can be seen in FIG. 2, the rock housing 17 contains the bearing mandrel 33 which carries a front bearing spacer 35. The lower housing 23 has an outer threaded extent 37 which has left hand threads, the interior of which receives the bearing set (39 in FIG. 2). The bearing set 39 is followed by a rear bearing spacer 41 and spanner nuts 43. The bearing retainer cap 45 encloses the bearing set 39 from the end opposite the lower housing 23. FIG. 3 shows the lower housing 23, bearing set 27 and bearing retainer cap 45 in isolated, exploded fashion.

[0045] With reference now to FIG. 6, the bearing assembly, in the assembled state, is shown in cross section. The bearing assembly includes a plurality of inner bearing races 47, 49, 51, 53, 55, and a plurality of outer bearing races 57, 59, 61, 63 and 65. In the example shown, there are five inner and five outer races for a total of ten races in the bearing pack. As can be seen in FIG. 6, the inner and outer bearing races have a plurality of bearing elements (such as element 67) located therebetween. In the case of the exemplary bearing pack shown in FIG. 6, there are a total of sixty four individual ball bearings 67 making up the bearing elements.

[0046] It will also be appreciated from FIG. 6 that the first inner race 47 and its companion first outer race 57 are intentionally machined so that a gap (g.sub.1) exists between the races when the races are assembled with the bearing elements located therebetween. Thus, as shown in FIG. 6, there is a very small gap (illustrated as g.sub.1) between the inner and outer bearing races, which gap increases in size in the subsequent inner and outer bearing race pairs, as viewed from the retainer cap 45 in the direction of the lower housing 23 and the drill bit. The size of the gaps between the bearing races can be adjusted to provide a desired amount of back pressure which controls the amount of drilling mud that is allowed to pass through the bearing assembly, the remaining flow being encouraged to flow toward the boring head.

[0047] In the example shown, the gap between the bearing races is less than about 0.015 inches between the first pair of inner and outer races. The gap on the other end of the bearing pack and also the gap between the inner and outer races between all of the remaining rows of bearings is typically about 0.100 inches, or more. This type of exemplary spacing allows drilling mud to flow through the bearings, to lubricate and cool the bearings. Typically, on mud lube bearings of the type used in oil and gas mud motors, this 0.100 inch or greater gap exists between all of the inner and outer races and the metering of mud is controlled in an entirely different manner.

[0048] The bearing assembly of the invention is thus characterized by the absence of any type of sealed cavity containing oil or grease lubricant, but instead relies solely on the flow of drilling mud through the bearing assembly to provide lubrication.

[0049] FIGS. 4 and 5 will be used to explain the flow of drilling mud through the bearing assembly 27. FIG. 4 shows the rock housing in cross section. FIG. 5 shows the bearing pack in enlarged fashion for ease of understanding. With reference to FIG. 5, the entering drilling mud would be flowing through the regions 67, 69 from the drilling machine. The majority of the fluid would continue from region 67 through the downward port 69 to the horizontal region 71 where it would continue on to ultimately lubricate the drill bit located below the lower housing 23.

[0050] However, it will also be appreciated from FIG. 5 that a portion of the drilling mud flows through the smaller passageways 73, 75, where it then enters the small gap g.sub.1 between the first inner and outer bearing races, 47 and 57, respectively. As previously described, the gap g.sub.1 increases in size from the first set of bearing races 47, 57 in the direction of the last set of races, in this case bearing races 55, 65.

[0051] In operation, for a typical example, inch discharge nozzles are used on the tricone or PDC drilling bit for purposes of this discussion. This is typically enough resistance to create fluid back pressure that will feed the mud lube bearings. Before the initial bore, with a bit installed, the inner rod is rotated at approximately 10 rpm. The flow of drilling mud is increased until a small amount of drilling fluid can be seen exiting the rock housing at the point 77 in FIG. 1, which is in front of the lower housing 23 and behind the bit box 25 on the bearing mandrel. Once a small stream has been established, the operator should note the fluid rate (gpm and pressure). This should be the minimum amount of flow used during drilling. If mud flows through the bit and the operator is unable to establish a small stream of fluid through the bearing pack, it may be necessary to increase the mud flow or to reduce the orifice size in the drill bit. Preferably 90-95% of the drilling mud should exit through the drill bit with 5-10% exiting through the bearing pack. This type of flow rate has been found to be satisfactory for providing adequate lubrication to the bearing assembly.

[0052] As briefly mentioned, there are some situations, as where the driller is using a very low viscosity drilling fluid (basically straight water), where the low viscosity fluid passes through the bearings very quickly. In these situations, there is a need to further control this low viscosity fluid flow through the bearings. One preferred design feature/option for controlling the fluid flow in these situations is illustrated in FIGS. 8-10 of the drawings. The bearing assembly 127 is again made up of an upper housing 145 and a lower housing 123 which are threadedly connected by the left-hand threads 124 on the lower housing 123 and mating threads on the upper housing 145. The lower housing 123 generally contains the bearing assembly, as has been described and illustrated with respect to FIG. 3.

[0053] With further reference to FIG. 8, the bearing assembly is again shown in the assembled state and in cross section. The bearing assembly includes a plurality of inner bearing races 147, 149, 151, 153, 155, and a plurality of outer bearing races 157, 159, 161, 163 and 165. In the particular example shown, there are five inner and five outer races for a total of ten races in the bearing pack, although more or less races might be used, depending upon the drilling situation. As has been described with respect to FIG. 6, the inner and outer bearing races have a plurality of bearing elements (such as element 167) located therebetween. In the case of the exemplary bearing pack shown in FIG. 8, there are a total of sixty four individual ball bearings 67 making up the bearing elements.

[0054] As has been described with respect to FIG. 6, the first inner race 147 and its companion first outer race 157 are intentionally machined so that a gap again exists between the races, shown as g.sub.1 in FIG. 6, after assembly. The gap between the races increases in size between the inner and outer bearing races, with the gap increasing in size in the subsequent inner and outer bearing race pairs, as viewed from the retainer cap 45 in the direction of the lower housing 23 and the drill bit. As described with respect to FIG. 6, the size of the gaps g.sub.1 and g.sub.2 between the bearing races can, in most cases, be adjusted to provide a desired amount of back pressure which controls the amount of drilling mud that is allowed to pass through the bearing assembly, the remaining flow being encouraged to flow toward the boring head.

[0055] The gaps are not illustrated in FIG. 8 in order to perhaps more easily illustrate the new optional feature of the bearing assembly of the invention which is intended to address the low viscosity drilling fluid problem previously mentioned. In the bearing assembly illustrated in FIG. 8, a further flow restrictor is provided between the inner and outer bearing races. A particularly preferred restrictor is a circumferential band 154 located in a groove 152 cut in a selected face of one of the inner and outer races. As such, the flow restrictor is thus integral to the bearing itself rather than being located above or below the bearing assembly in the drill string. With reference to FIG. 8, the first bearing race is made up of inner race 147 having an outer circumferential region 148 and a mating outer race 157 having an inner circumferential region 150. In the version of the invention shown in FIG. 8, the groove 152 is cut in the outer circumferential region (exterior face) of the first inner race 147 of the bearing pack. FIG. 9 shows the band 154 in exploded fashion.

[0056] FIG. 10 shows a top view of the band 154 in isolated fashion. As is evident from FIGS. 8-10, the preferred band 154 is flat having a cross section which is generally rectangular (see FIGS. 8 and 9), although the band could assume other forms, for example, a round cross section. It will be noted that the band 154 has a section cut out of the band to provide an opening Op at one circumferential location. The opening, Op, allows some of the drilling fluid to pass through and the size of the opening can be expanded to allow more fluid to pass, if desired. For example, for one typical example, for a band having a 2.44 inch internal diameter, a 2.64 inch external diameter and a 0.200 inch width, the opening in the band might be approximately inch in size.

[0057] The band can be made of any number of metal, synthetic or composite materials, depending upon the particular drilling environment envisioned. While a number of metals such as stainless steel might be used, synthetic materials often provide better corrosion resistance in a drilling environment and may be less costly. For example, the band 154 might be formed of one of the Ultra-High-Molecular Weight thermoplastic materials (UHMW), such as Ultra-high-molecular-weight polyethylene (UHMWPE), a subset of the thermoplastic polyethylene. Also known as high-modulus polyethylene (HMPE), it has extremely long chains which serve to transfer loads more effectively to the polymer backbone by strengthening intermolecular interactions. This results in a very tough material, with a very high impact strength. UHMWPE is odorless, tasteless, and nontoxic. It embodies all the characteristics of high-density polyethylene (HDPE) with the added traits of being resistant to concentrated acids and alkalis, as well as numerous organic solvents. It is highly resistant to corrosive chemicals except oxidizing acids; has extremely low moisture absorption and a very low coefficient of friction; is self-lubricating; and is highly resistant to abrasion. All of these characteristics make it a good candidate material for use as the band 154 in the present application.

[0058] An invention has been provided with several advantages. The bearing assembly for an HDD apparatus of the invention uses the drilling mud passing through the system for lubrication, rather than using a separate sealed cavity containing oil or grease lubricant. The bearing system uses a specially sized gap in the area of the bearing races to divert a portion of the flow of drilling mud to the bearing assembly to lubricate the assembly. This design does not require a separate sleeve and piston or additional components as were used in some prior art oil and gas well drilling mud motors. As such, it only requires machining of the bearing components already present and does not add an additional component or add to the overall expense of the system. It also eliminates the possibility that such additional components might add to the maintenance requirements of the drilling system.

[0059] The system is economical to manufacture and results in overall cost savings as compared to sealed grease type lubricating systems.

[0060] While the invention has been shown in only one of its forms, it will be appreciated that it is not thus limited, but is susceptible to various changes and modifications without departing from the spirit thereof.