Quick reverse mechanism for pneumatic boring tool

Abstract

A reversible impact-operated pneumatic boring tool for reversing the direction of operation of the tool is disclosed. The tool includes two fluid supply lines, a striker and a non-mechanically biased directional control sleeve. The primary fluid supply line provides pressurized fluid for striker reciprocation within the tool body to drive the tool through the soil. The secondary fluid supply line provides pressurized fluid to determine direction of operation of the tool. Pressurized fluid is supplied to a sealed chamber behind the directional control sleeve to drive the sleeve forward and operate the tool in a forward mode. The control sleeve is held forward solely by maintaining sufficient positive pressure of the fluid in the sealed chamber. Whereas, the depressurization of the chamber solely, will cause the sleeve to be moved to a rearward position thereby causing the tool to operate in the reverse mode.

Description

FIELD OF THE INVENTION

The present invention relates to boring tools for underground boring, and more particularly, it relates to pneumatic impact operated boring tools for use with horizontal boring machines during horizontal boring operations for placement of utility lines and the like.

BACKGROUND OF THE INVENTION

Pneumatic impact-operated boring tools are well-known in the art. U.S. Pat. No. 3,756,328 issued to Sudnishnikov et al. discloses one such device. Typically, pneumatic impact-operated boring tools are used for burrowing holes in soil, particularly horizontal or near horizontal passages for installation of utility lines when trenching is undesirable. An example of such usage would be for the installation of services underneath an existing structure, such as a driveway or highway, where installation of the line by traditional open cut methods would be impractical. In this situation, the pneumatic impact-operated boring tool is launched from a pit on one side of the structure and is advanced to a receiving pit on the opposite side of the structures.

As the name implies, such boring tools function by impact. The tools possess a striking member (striker) slidable within a cylindrical housing. The striker delivers impacts on a surface at the front end of the housing. This impacting motion within the tool itself causes the soil around the tool to compact away from the nose of the housing, thus forming a hole. The tools are typically driven by a compressed air source. As the compressed air flows through the tool, the striker will be driven in a reciprocal motion generating a series of rapid impacts against the front of the tool housing, causing it to be driven through the ground.

Utility service lines to be installed may either be inserted into the hole formed by the piercing tool, or may be pulled into the hole behind the tool as it operates. Alternatively, pneumatic piercing tools have also been used to install rigid service lines such as steel lines by driving the steel line into place.

It is occasionally desirable to retract the piercing tools from the borehole being formed. For example, if the piercing tool encounters an obstruction in the soil such as a rock or stone or deviates from the desired path or is damaged in any way, quick withdrawal of the tool from the borehole may be necessary. Most tools are designed to facilitate this retraction by having a mode wherein the striker impacts the rear of the tool causing a retrograde progression of the tool within the borehole.

Thus, reversible impact-operated boring tools are also well-known in the art. U.S. Pat. No. 4,683,960 issued to Kostylev et al. discloses such a device. The prior art discloses various means for accomplishing the reverse motion. In the older designs, the shift from the forward operation mode of the tool to the reverse/withdraw mode is accomplished in any one of the following ways. Some require interrupting the pressurized fluid supply. Others require manipulation of the hose supplying the pressurized fluid to the tool, either by rotating the hose or by pulling it back. Still others require both the interruption of the pressurized fluid supply and the manipulation of the hose.

However, there are several disadvantages associated with these processes. For example, when the pressurized fluid supply is interrupted and the tool is therefore momentarily shut off, the tool may not restart when the pressurized fluid supply is recommenced. In tools requiring hose manipulation, when the hose is flexible, it is often difficult to relate the degree of rotational motion of the hose at the surface to the degree of rotational motion at the tool itself, which may be some distance away. In addition, cave-ins of the hole wall can bind the hose, making it difficult to rotate the hose, or preventing it altogether. Consequently, it is often difficult to reverse the operation of the tool, or to be certain of the direction of operation.

In the more recent designs, the mechanism of shifting the pneumatic tool from forward to reverse is somewhat simplified. U.S. Pat. No. 5,172,771 ('771 patent) and U.S. Pat. No. 5,327,636 ('636 patent), both issued to Wilson and both incorporated fully herein by reference, disclose such a device. In Wilson's '771 patent, a second air hose was added to act as a control mechanism for switching the tool from forward to reverse. Pressurizing the control hose caused a valve mechanism in the tool to move to a forward position, creating the forward movement of the pneumatic tool. Releasing the pressurized air from the control hose caused the valve mechanism to move to a rearward position, resulting in a reverse/withdrawal movement of the tool. However, the valving mechanism in the tool of the '771 patent is complex, and difficult to assemble, requiring assembly of several parts such as a pre-load spring, snap ring, etc. for valve containment. Additionally, the valving mechanism of the '771 patent is rigid in terms of deflection perpendicular to the longitudinal axis of the tool body. This inherent rigidity of the valving member makes the tool more prone to stalling if the tool body is deflected along its longitudinal axis by contact with an underground obstacle.

Due to the complexity presented by the current means for the reversing operation of impact-operated boring tools, and the increased labor and time associated with servicing the various component parts, an alternate simpler mechanism for switching a pneumatic piercing tool from forward to reverse operation is needed.

SUMMARY OF THE INVENTION

In one aspect, the invention relates to an impact-operated, ground-penetrating tool powered by a primary supply of pressurized fluid, and controlled between a forward operating mode and a reverse operating mode by a second supply of pressurized fluid. The tool comprises a housing, a striker, a manifold, a primary inlet tube, a valve chamber, and a control sleeve. The housing has a front end, a rear end, and body. The body of the housing defines an interior operating chamber with an inner surface, an exhaust conduit to provide fluid communication between the operating chamber and the outside of the tool, a forward striker surface, and a rearward striker surface.

The striker is reciprocally supported within the operating chamber of the housing between the forward and rearward striker surfaces. The striker has a forward end, a rear portion terminating in a rear end, and a striker body defining an interior striker chamber. The rearward portion of the striker sealingly engages the inner surface of the operating chamber to divide the operating chamber into a forward operating chamber and a rearward operating chamber. The rearward operating chamber is continuous with the exhaust conduit. Whereas, the striker body has at least one striker port to provide fluid communication between the forward operating chamber of the housing and the interior striker chamber.

The manifold is located near the rear end of the housing and comprises a primary conduit connectable to the primary fluid supply and a secondary conduit connectable to the secondary fluid supply. A primary fluid inlet tube extends from primary conduit of the manifold. Additionally, the valve chamber is in fluid communication with the secondary conduit in the manifold.

The control sleeve has a rear portion, a front portion, and an interior sleeve chamber defining a passage between the rear portion and the front portion. The front portion of the control sleeve is slidably and sealingly supported inside the rear portion of the striker. Whereas, the rear portion of the control sleeve is slidably and sealingly supported on the primary fluid inlet tube at least partially inside the valve chamber. The control sleeve provides continuous fluid communication between the primary fluid inlet tube and the striker chamber, so that in response to supply of primary fluid the striker reciprocates between a forward position and a rearward position. In the forward position, the striker port is open between the interior striker chamber and the forward operating chamber. Whereas, in the rearward position, the striker port is open between the forward operating chamber and the rearward operating chamber and the exhaust conduit.

Finally, the rear portion of the control sleeve includes a nodular lobe inside the valve chamber that is movable between a forward position in response to pressurization of the valve chamber and a reverse position in response to depressurization of the valve chamber. This causes the forward portion of the control sleeve to move between a forward position in which the striker hits the forward striker surface as it reciprocates and a rearward position in which the striker hits the rearward striker surface as it reciprocates.

In another aspect, the invention relates to an impact-operated, ground-penetrating tool powered by a primary supply of pressurized fluid, and controlled between a forward operating mode and a reverse operating mode by a second supply of pressurized fluid. The tool comprises a housing, a striker, a means for operably connecting the primary fluid supply, a valve chamber, a means for operably connecting the secondary fluid supply and a control sleeve. The housing has a front end, a rear end, and body. The body defines an interior operating chamber with an inner surface, an exhaust conduit providing communication between the operating chamber and the outside of the tool, a forward striker surface and a rearward striker surface.

A striker is reciprocally supported within the operating chamber of the housing between the forward and rearward striker surfaces. The striker has a forward end, a rear portion terminating in a rear end, and a striker body defining an interior striker chamber. The rearward portion of the striker sealingly engages the inner surface of the operating chamber to divide the operating chamber into a forward operating chamber and a rearward operating chamber. The rearward operating chamber is continuous with the exhaust conduit and the striker body has at least one striker port to provide fluid communication between the forward operating chamber and the interior striker chamber.

The means for operably connecting the primary fluid supply connects the primary fluid supply to the interior striker chamber. Additionally, the means for operably connecting the secondary fluid supply connects the secondary fluid supply to the valve chamber at the rear end of the housing.

The control sleeve has a rear portion and a front portion. The front portion of the control sleeve is slidably and sealingly supported inside the rear portion of the striker. Whereas, the rear portion of the control sleeve is slidably and sealingly received at least partially inside the valve chamber. The control sleeve provides continuous fluid communication between the means for operably connecting the primary fluid supply and the interior striker chamber. As a result, in response to supply of primary fluid the striker reciprocates between a forward position and a rearward position. In the forward position, the striker port is open between the interior striker chamber and the forward operating chamber. Whereas, in the rearward position, the striker port is open between the forward operating chamber and the rearward operating chamber and the exhaust conduit.

Finally, the rear portion of the control sleeve includes a nodular lobe inside the valve chamber that is movable between a forward position in response to pressurization of the valve chamber and a reverse position in response to depressurization of the valve chamber. This causes the forward portion of the control sleeve to move between a forward position in which the striker hits the forward striker surface as it reciprocates, and a rearward position in which the striker hits the rearward striker surface as it reciprocates.

In yet another aspect, the invention is an impact-operated, ground-penetrating tool powered by a primary supply of pressurized fluid, and controlled between forward operating mode and a reverse operating mode by a second supply of pressurized fluid. The tool comprises a housing, a striker, a primary connecting assembly, a valve chamber, a secondary connecting assembly and a control sleeve. The housing having a front end, a rear end, and body defining an interior operating chamber with an inner surface, an exhaust conduit providing communication between the operating chamber and the outside of the tool, a forward striker surface, and a rearward striker surface.

A striker is reciprocally supported within the operating chamber of the housing between the forward and rearward striker surfaces. The striker has a forward end, a rear portion terminating in a rear end, and a striker body defining an interior striker chamber. The rearward portion of the striker sealingly engages the inner surface of the operating chamber to divide the operating chamber into a forward operating chamber and a rearward operating chamber. The rearward operating chamber is continuous with the exhaust conduit and the striker body has at least one striker port to provide fluid communication between the forward operating chamber and the interior striker chamber.

The primary connecting assembly operably connects the primary fluid supply to the interior striker chamber. Whereas, the secondary connecting assembly operably connects the secondary fluid supply to the valve chamber located at the rear end of the housing.

The control sleeve has a rear portion and a front portion. The front portion of the control sleeve is slidably and sealingly supported inside the rear portion of the striker. Whereas, the rear portion is slidably and sealingly received at least partially inside the valve chamber. The sleeve provides continuous fluid communication between primary connecting assembly and the interior striker chamber. As a result, in response to supply of primary fluid the striker reciprocates between a forward position and a rearward position. In the forward position, the striker port is open between the interior striker chamber and the forward operating chamber. Whereas, in the rearward position, the striker port is open between the forward operating chamber and the rearward operating chamber and the exhaust conduit.

Finally, the rear portion of the control sleeve includes a nodular lobe inside the valve chamber that is movable between a forward position in response to pressurization of the valve chamber and a reverse position in response to depressurization of the valve chamber. This causes the forward portion of the control sleeve to move between a forward position in which the striker hits the forward striker surface as it reciprocates, and a rearward position in which the striker hits the rearward striker surface as it reciprocates.

In another aspect, the invention is a reversible impact ground penetrating boring tool comprising a housing, a striker, a primary fluid supply assembly, a control sleeve, and a secondary fluid supply assembly. The housing has a rear end, and an interior chamber defining a forward striker surface and a rearward striker surface.

The striker has an external wall surrounding an interior striker chamber. The striker is slidably and sealingly receivable within the interior chamber of the housing and is adapted to reciprocally move between the forward striker surface and the rearward striker surface. The external wall of the striker and the interior chamber of the housing define an operating chamber. The primary fluid supply assembly is operably connectable to the striker and is adapted to provide pressurized primary fluid to the interior striker chamber. As a result, the striker will be driven in a reciprocal motion within the interior chamber of the housing when the pressurized primary fluid is supplied.

The control sleeve has a front end, a rear end and an interior sleeve chamber defining a passage from the front end to the rear end. The front end of the control sleeve is slidably and sealingly receivable within the interior striker chamber. Whereas, the rear end of the control sleeve is slidably and sealingly receivable within a valve fluid chamber at the rear end of the tool housing. The valve fluid chamber has a first end and a second end. The rear end of the control sleeve is adapted to move toward the first end of the valve fluid chamber during tool advancement. Whereas, the rear end of the control sleeve is adapted to move toward the second end of the valve fluid chamber during tool withdrawal. Additionally, the striker will impact the forward striker surface when the control sleeve is at the first end of the valve fluid chamber and the rearward striker surface when the control sleeve is at the second end of the valve fluid chamber.

The secondary fluid supply assembly is operably connectable to the valve fluid chamber. The valve fluid chamber is pressurized by the secondary fluid supply assembly. The valve fluid chamber must be pressurized to move and hold the sleeve at the first end during tool advancement and the valve fluid chamber must be depressurized to permit the control sleeve to move toward and remain at the second end during tool withdrawal.

BRIEF DESCRIPTION OF THE DRAWINGS

For a more complete understanding of the present invention, and the advantages thereof, reference is now made to the following description, taken in conjunction with the accompanying drawings, in which:

FIG. 1 is a diagrammatic representation of the reversible impact-operated boring tool assembly with a longitudinal sectional view of the tool constructed in accordance with the present invention.

FIG. 2 is an exploded view of the tool of FIG. 1 showing the component parts of the reversible impact-operated boring tool.

FIG. 3 is a longitudinal sectional view of the reversible impact-operated boring tool constructed in accordance with the present invention illustrating the boring tool in the forward mode with the striker at the forward striker surface.

FIG. 4 is a longitudinal sectional view of the reversible impact-operated boring tool constructed in accordance with the present invention illustrating the boring tool in the forward mode with the striker away from the forward striker surface.

FIG. 5 is a longitudinal sectional view of the reversible impact-operated boring tool constructed in accordance with the present invention illustrating the boring tool in the reverse mode with the striker at the rearward striker surface.

FIG. 6 is a longitudinal sectional view of the reversible impact-operated boring tool constructed in accordance with the present invention illustrating the boring tool in the reverse mode with the striker away from the rearward striker surface.

FIG. 7 is a longitudinal sectional view of the reversible impact-operated boring tool constructed in accordance with the present invention illustrating an end of the tool body adapted to receive replaceable nose pieces.

FIG. 8 is a cross-sectional view of the tail piece assembly of FIG. 5 in accordance with the present invention illustrating exhaust conduits.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

Typically, the reversible impact-operated boring tool includes a hollow outer body that consists of a torpedo-shaped front end and a coaxial tailpiece. A fluid driven piston-like striker reciprocates lengthwise in the hollow body between the front end and the coaxial tailpiece. If the striker impacts the front end of the hollow body, the tool will be driven forward. Conversely, if the striker impacts the tailpiece, the reverse motion results. However, the determining factor on whether the striker will impact the front or the rear of the tool as it cycles back and forth is the position of a fluid actuated control sleeve. When the control sleeve is in the rearward position, the striker will impact the tail piece for reverse motion of the tool. When the control sleeve is in a forward position, the striker will impact the front of the tool for forward motion.

Turning now to the drawings in general and FIGS. 1 and 2 in particular, there is shown therein a pneumatic reverse impact-operated boring tool assembly 1 in accordance with the present invention. The boring tool, designated by the reference numeral 10 , generally comprises an outer housing 12 , striker 14 , control sleeve 16 , a tail piece assembly 17 , and two fluid supply assemblies 18 and 20 respectively.

With reference to FIGS. 1-3 , the housing 12 preferably comprises a missile shaped front end 32 , a rear end 34 , and a hollow interior defining an interior operating chamber 38 . The housing 12 , is generally made of a durable metal such as steel, ductile iron, or titanium, with an outside diameter generally ranging between 2-8 inches, and an overall length generally between 2.5-5 feet. However, the housing 12 , may be made with any other durable material in varying lengths and diameter. Preferably, the housing 12 is a two-piece assembly joined by friction welding. Utilizing a friction welded housing 12 results in a less expensive outer body as compared to machining the body out of a single piece of steel. Additionally, the friction weld forms a full cross section weld with strength comparable to the original material. It should be noted, however, that the housing 12 may be made of a single, machined piece of steel or any other durable metal without departing from the spirit of the invention.

In the preferred embodiment, the missile shaped front end 32 of the housing 12 comprises a nose piece 33 that will act as the first point of contact for the tool against the surrounding soil. With reference to FIG. 7 , the front end 32 of the housing 12 may be adapted to receive different types of nose pieces 33 a to accommodate boring through different types of soils. For example, a tapered head nose piece may be attached when boring in wet, spongy or loose soil conditions where no obstructions are anticipated. Alternatively, a stepped head nose piece for boring through roots and small rocks, or a splined stepped head for hard, dry, compacted soils where obstacles may be encountered may be used. Preferably, the front end 32 of the housing 12 , has a recessed thread 40 for receiving an adapter stud 42 . The adapter stud 42 receives the replaceable nose pieces discussed above. Alternatively, an electronic transmitter housing as discussed in U.S. Pat. No. 4,907,658 by Stangl et al. the contents of which are incorporated fully herein by reference, may be used on the front end 32 of the tool housing 12 .

With reference again to FIGS. 1-3 , the interior operating chamber 38 of the tool housing 12 defines a closed front end 43 corresponding with the front end 32 of the outer housing 12 , an open rear end 44 corresponding with the rear end 34 of the outer housing and a body 45 in between defining an inner surface. An exhaust conduit 47 (described later) is provided at the rear end 44 of the interior operating chamber 38 between the inner surface of the housing 12 and the tail piece assembly 17 for fluid communication between the operating chamber 38 and the outside of the tool 10 . Additionally, the open rear end 44 of the interior operating chamber 38 , preferably receives a front end 48 of the tail piece assembly 17 , forming a rearward striker surface 49 for the piston or striker 14 . Whereas, the closed front end 43 of the interior operating chamber 38 , preferably defines a forward striker surface 50 for the piston or striker 14 .

In the preferred embodiment, the striker 14 is slidably and sealingly receivable within the interior operating chamber 38 and is driven by an external compressed fluid supply system 51 . The compressed fluid from the fluid supply system 51 causes the striker 14 to reciprocally move within the interior operating chamber 38 in a manner yet to be described.

Preferably, the striker 14 has a cylindrical body with a tapering closed forward end 56 , a rear portion 57 terminating in an open rear end 58 and an external wall 59 surrounding an interior striker chamber 60 . As defined below, the control sleeve 16 is receivable through the open rear end 58 of the striker 14 . As used herein, the interior striker chamber 60 is defined as the area inside the striker 14 and forward of the control sleeve 16 . The tapering forward end 56 of the striker 14 preferably has a flattened nose 62 for impact with the forward striker surface 50 during reciprocal motion. It should be noted however, that the striker 14 may have any other alternate shape or structure that permits it to be slidingly and sealingly receivable within the interior operating chamber 38 as above.

The rear end 58 of the striker 14 sealingly engages the inner surface of the interior operating chamber 38 to divide the operating chamber into a forward operating chamber 64 and a rearward operating chamber 65 . The rear portion 57 of the striker 14 comprises at least one radial port, disposed to permit fluid communication between the operating chambers 64 and 65 , the interior striker chamber 60 and the exhaust conduit 47 . In the preferred embodiment, a plurality of radial ports 66 are positioned along the outer circumference of the rear portion 57 of the striker 14 . The number of radial ports may be increased or decreased so long as fluid communication is permitted between the interior striker chamber 60 , the forward operating chamber 64 , the rearward operating chamber 65 , and the exhaust conduit 47 .

Additionally, in the preferred embodiment, the rear portion 57 of the striker 14 further comprises an annular groove 68 . Preferably, the groove 68 is located behind the radial ports 66 . A wear ring 70 is situated within the groove 68 and has a slightly larger diameter than the outer diameter of the striker 14 . As a result, instead of the outer surface of the striker 14 making contact with the inner surface of the interior chamber 38 of the tool housing 12 , the wear ring 70 , makes contact with the inner surface of the interior chamber to form the forward and rearward operating chambers 64 and 65 , respectively, as discussed above. The wear ring 70 serves a dual purpose. Firstly, the wear ring 70 acts as a seal to help prevent pressurized fluid from leaking from the forward operating chamber 64 to the rearward operating chamber 65 . Secondly, the wear ring 70 serves as a wear surface to prevent the striker 14 from wearing out prematurely and can be easily replaced when the tool 10 is disassembled. Typically, the wear ring 70 is made of a plastic material or other material softer than the interior surface of the tool housing 12 such as, phenolic, UHMW polyethylene, or PET. The wear characteristics of nylon materials are consistent with the needs of this application, but nylon materials are generally unsuitable for this application because of the water absorption characteristics of those materials. It is understood however, that the wear ring 70 may be made of other materials, such as a nitrile o-ring, or may be deleted from the design altogether without affecting the spirit of this invention.

With continued reference to FIGS. 2 and 3 , to control motion of the striker 14 , a directional control member such as the control sleeve 16 is provided. In the preferred embodiment, the control sleeve 16 is slidably receivable with the interior striker chamber 60 of the striker 14 and requires no external mechanical device to bias it in either the forward or rearward position.

Preferably, the control sleeve 16 comprises a cylindrical body with an interior sleeve chamber 80 . The cylindrical body defines a front portion 84 , a central portion 86 , and a rear portion 88 . More preferably, the central portion 86 has a smaller diameter than either the front portion 84 or the rear portion 88 . Additionally, the rear portion 88 defines a nodular lobe that has a larger diameter than the front portion 84 to create a larger cross sectional area for reasons that will become obvious later.

In the preferred embodiment, the front portion 84 , of the sleeve 16 , comprises a circumferential groove 90 that contains a wear ring 92 as illustrated in FIG. 2 . The wear ring 92 has a diameter slightly larger than the outer diameter of the front portion 84 of the control sleeve 16 . As a result, instead of the outer surface of the front portion 84 of the control sleeve 16 making contact with the interior of the striker 14 , the wear ring 92 makes contact with the interior of the striker. In this location, the wear ring 92 also serves a dual purpose of first acting as a seal to prevent fluid leaking from between the interior of the striker 14 and the exterior of the control sleeve 16 , and additionally, serving as a wear surface to prevent the outer surface of the sleeve 16 from wearing out prematurely. The wear ring 92 can be easily replaced when the tool 10 is disassembled. The wear ring 92 preferably is made of a plastic material or other material that is softer than the interior surface of the striker 14 . The wear ring 92 may be made of other materials, such as a nitrile O-ring, or may be deleted from the design altogether without affecting the spirit of the invention.

Preferably, the control sleeve 16 is composed of a flexible material such as PET thermoplastic. However, other materials such as aluminum or steel may be used in the alternative. The control sleeve 16 is movable within the hollow interior of the striker 14 and a valve fluid chamber (defined later) of the tailpiece assembly 17 between a forward control sleeve position 98 and a rearward control sleeve position 100 . When the member 16 is in the forward position 98 , the tool 10 will operate in the forward mode. When the control sleeve 16 is in the rearward position 100 , the tool 10 will operate in the reverse mode.

With continued reference to FIGS. 2 and 3 , the tailpiece assembly 17 , preferably comprises a manifold nut 104 with two internally threaded ports 106 and an external thread 108 , a body coupling 110 with a generally cylindrical front portion 112 , a protective tail nut 114 , and a primary fluid inlet tube 116 . The outer surface of the tail nut 114 forms the rear portion of the outer housing 12 , and protects the connections of the fluid supply assemblies 18 and 20 respectively.

In the preferred embodiment, the manifold nut 104 is located substantially within the interior of the protective nut 114 near the rear end 44 of the interior chamber 38 and has a first end 118 and a second end 120 both of which are internally threaded. The internal thread of the first end 118 of the manifold nut 104 is threaded to the primary fluid inlet tube 116 and an external thread of the first end of the nut 104 is threaded to an internal thread of a rear end 122 of the body coupling 110 . The internal thread of the second end 120 , of the nut 104 , is threaded to the compressed fluid supply 51 for both the striker 14 and the sleeve 16 . That is, the manifold nut 104 , forms a primary fluid conduit 128 for the fluid supply for movement of the striker 14 and a secondary fluid conduit 130 for the fluid supply for movement of the sleeve 16 . It is the forward most end of the body coupling 110 of the tail piece assembly 17 that forms the rear ward striker surface 49 .

With reference to FIG. 2 the outer circumference of the body coupling 110 comprises external threads 132 . Slots milled along the longitudinal axis of the body coupling 110 permit the passage of fluid. This arrangement serves a dual purpose. Firstly, the external threads 132 provide an attachment mechanism whereby the protective tail nut 114 is threaded onto the rear part of the body coupling 110 and the front part of the is threaded into the rear end 34 of the external housing 12 body. Secondly, the milled slots through the threads 132 form the exhaust conduit 47 that allows for the passage of air from the rear operating chamber 65 to the exterior of the tool. This arrangement is further shown in the cross-section illustration of FIG. 8 .

With reference now to FIGS. 4 and 5 , the body coupling 110 bottoms out on a shoulder inside the tool body 12 before all the external thread is used up. The internal thread on the protective tail nut 114 is threaded onto the remaining exposed thread of the body coupling 110 . Once the front shoulder of the protective tail nut 114 contacts the rear shoulder of the outer housing 12 of the tool 10 , as the protective tail nut 114 is tightened further, the threaded connections between the outer housing 12 and the body coupling 110 and between the body coupling 110 and the protective tail nut 114 become preloaded to lock all three components together.

With reference now to FIG. 3 , the first end 118 of the manifold nut 104 and a front end 140 of the body coupling 110 form a valve fluid chamber 142 . The valve fluid chamber 142 , may be pressurized or depressurized through a supply of compressed fluid as will be discussed herein. It is the pressure in this valve fluid chamber 142 , or the lack thereof, that determines the position of the control sleeve and, thus, whether the tool 10 will operate in a forward mode or a reverse mode.

Shown in FIGS. 3-6 , the rear portion 88 of the control sleeve 16 includes a nodular lobe 146 inside the valve fluid chamber 142 . The control sleeve 16 is movable between a forward position 140 wherein the front end of the nodular rear portion 88 of the sleeve contacts the front end 140 of the body coupling 110 , and a rearward position 150 wherein the rear end of the nodular rear portion 88 contacts the first end 118 of the manifold nut 104 . The movement towards the forward position 148 is in response to pressurization of the valve fluid chamber 142 and movement towards the rearward position 150 is in response to depressurization of the valve fluid chamber 142 . One skilled in the art will appreciate that the control sleeve 16 is moved towards the forward position 148 and held in that position solely by positive pressure in the valve fluid chamber 142 . When the valve fluid chamber 142 is depressurized, the force of the primary pressurized fluid acting on the front surface 84 of the control sleeve 16 will cause the control sleeve to move to the rearward position. As a result of the reciprocating motion, the front portion 84 of the control sleeve 16 will also move between a forward position in which the striker 14 hits the forward striker surface 50 , and a rearward position in which the striker hits the rearward impact surface 49 .

With reference to FIGS. 1-3 , prior to the attachment of the manifold nut 104 to the rear end 122 of the body coupling 110 , the control sleeve 16 is inserted into the front cylindrical portion 112 of the body coupling 110 from the rear of the body coupling. The control sleeve 16 is then slidingly movable toward the front end 140 . The front end 140 comprises an abutting shoulder around the outer rim such as a stop 154 that prevents the larger diameter nodular rear portion 88 of the control sleeve 16 from exiting from the front end 140 of the body coupling 110 . The stop 154 may be made as an integral part of the body coupling 110 . However, any other mechanism such as a snap ring, radially placed pin, or threaded ring may be used either integrally as part of the inner tube of the body coupling or the interior chamber 38 of the housing 12 , that would act as the limiting boundary for the forward progression of the control sleeve 16 .

One skilled in the art will appreciate a loose sliding fit exists between the exterior of the nodular rear portion 88 of the control sleeve 16 and the interior of the inner tube 112 of the body coupling 110 . This fit is typically the equivalent of an ASME RC 9 loose running fit, or looser. The sealing between these pieces is typically accomplished using an O-ring 164 . The loose fit between the exterior of the nodular rear portion 88 of the sleeve 16 and the inner tube 112 of the body coupling 110 gives a small amount of angular deflection capability of the sleeve within the body coupling, somewhat like a ball and socket joint. The angular deflection capability coupled with the flexible material in the control sleeve 16 itself gives the tool the ability to accommodate slight tool body deflections without stalling.

The determining factor on whether the striker 14 will impact the front or the rear of the tool 10 as it cycles back and forth is the position of the control sleeve 16 . That is, when the control sleeve 16 is in the rearward position 150 as shown in FIG. 5 , the striker 14 will impact the front end 140 of the body coupling 110 and the progression of the tool in the hole will be in the reverse direction. When the control sleeve 16 is in the forward position 148 as shown in FIG. 3 , the striker 14 will impact on the forward impact surface 50 at the front of the tool 10 and drive it forward in the hole.

Referring again to FIG. 1 , the compressed fluid supply to the striker 14 and the control sleeve 16 is from a common source such as the compressed fluid supply system 51 . However, the fluid supply is provided to the interior striker chamber 60 and the valve fluid chamber 142 by way of separate fluid supply assemblies, such as the primary fluid supply assembly 18 and the secondary fluid supply assembly 20 respectively.

The primary fluid supply assembly 18 comprises a supply tube 170 that is connectable to the primary fluid inlet tube 116 through the primary fluid conduit 128 of the manifold nut 104 . The primary fluid inlet tube 116 extends from the primary conduit 128 a distance into the hollow interior passage of the control sleeve 16 . The nodular rear portion 88 of the control sleeve 16 is slideably and sealingly supported on the primary fluid inlet tube 116 at least partially inside the sleeve 142 to form a through channel for the passage of fluid from the supply tube 170 to the interior of the striker 14 . Additionally, there is no annular passage between the control sleeve 16 and the primary fluid inlet tube 116 . Instead, both these members are close fitting and any remaining gap between them is sealed with an O-ring 171 to form a pressurized chamber within the interior of the body coupling 110 . As a result, in response to the supply of operating fluid, the interior striker chamber 60 will become pressurized and cause the striker 14 to reciprocate between the forward position 52 in which the radial ports 66 are open between the interior striker chamber 60 and the forward operating chamber 64 , and the rearward position 54 in which the ports 66 are open between the front operating chamber and the rear operating chamber 65 , thereby allowing the pressurized fluid in the forward operating chamber 64 to escape out the back of the tool through the exhaust conduit 47 .

In the preferred embodiment, as illustrated in FIG. 1 , the secondary fluid supply assembly 20 comprises a secondary fluid supply tube 172 that is connectable to the valve fluid chamber 142 through the secondary fluid conduit 130 of the manifold nut 104 . That is, the manifold nut 104 provides the passage or channel for the fluid through the nut from the secondary fluid supply tube 172 to the valve fluid chamber 142 . Preferably, the secondary fluid supply tube 172 is smaller in diameter than the supply tube 170 . Additionally, the tubes 170 and 172 are preferably non-concentric with each other.

Preferably, both fluid supply tubes 170 and 172 are connected to separate hoses supplying compressed fluid at the same pressure. More preferably, the supply tube 170 and the secondary supply tube 172 are connected to a primary fluid supply hose 174 and secondary fluid supply hose 176 respectively, through quick connect fittings 178 and 180 respectively. The quick connect fittings 178 and 180 simplify the connection of these lines to their respective fluid supply hoses coming from the compressor. However, it is understood that more traditional twist type connectors, or any other type of connectors, may be substituted on the hoses without departing from the spirit of the invention.

With continued reference to FIG. 1 , the secondary fluid supply assembly 20 comprises a control valve 190 mounted at a convenient position for control, preferably at an operator's station, for supplying pressurized fluid to or exhausting pressurized fluid from the valve fluid chamber 142 . The control valve 190 contains ports (not shown) such that when the control valve is shut off, the pressurized fluid is exhausted from the valve fluid chamber 142 . When the control valve 190 is opened, pressurized fluid passes into the valve fluid chamber 142 . In the preferred embodiment, the pressurized fluid used to move the sleeve 16 and the striker 14 is air. However, it is understood that alternate fluids such as water, hydraulic oil, or compressed carbon dioxide could be used without departing from the spirit of the invention.

Turning now to FIGS. 3-6 , the operation of the detailed sequence of events at each mode of operation of the tool will be described for the preferred embodiment. As illustrated in FIG. 3 , to begin the boring operation, the tool 10 is operated in the forward mode. For this, the control valve 190 is opened to permit the valve fluid chamber 142 to become pressurized. As the valve chamber 142 is pressurized, the pressurized fluid acting on the rear portion 88 of the control sleeve 16 will cause the control sleeve to move forward into the forward sleeve position 98 . Positive pressure in the valve fluid chamber 142 will hold the non-mechanically biased control sleeve 16 in the forward position 98 for so long as sufficient positive pressure is maintained.

Simultaneously, the drive fluid for the tool 10 is routed through the manifold nut 104 into the primary fluid inlet tube 116 . The drive fluid passes through the primary fluid inlet tube 116 and through the interior of the control sleeve 16 into the interior striker chamber 60 . The pressure of the fluid inside the striker 14 will cause the striker to move forward within the interior operating chamber 38 of the tool housing 12 . As the striker 14 , progresses forward in the interior chamber 38 of the tool housing 12 , eventually the port holes 66 in the rear end wall of the striker 14 will pass by the front portion 84 of the sleeve as seen in FIG. 3 .

At this time, the compressed fluid in the cavity inside the striker 14 , that is, in the interior striker chamber 60 will be free to flow into the annular space between the outside of the striker and the inside of the tool body, that is, into the forward operating chamber 64 . Once the forward operating chamber 64 fills with fluid, pressure develops in this region which begins to slow the forward progress of the striker 14 . When the tool 10 is running in the forward mode, the striker 14 will proceed forward until the forward end 56 of the striker impacts on the forward striker surface 50 of the interior chamber 38 of the tool housing 12 .

At this point, since the striker 14 will tend to rebound off of the forward striker surface 50 and since the cross-sectional area on the outside of the striker 14 is greater than on the inside of the striker, the striker will begin to move towards the rear of the tool 10 . This rearward progress of the striker 14 will continue largely unabated until the port holes 66 in the striker 14 pass by the rear edge of the front cylindrical portion 84 of the control sleeve 16 . Once the port holes 66 in the striker reach this point, the pressurized fluid in the cavity between the outside of the striker 14 and inside of the tool housing 12 , that is in the front operating chamber 64 , will flow through the striker ports 66 into the rear operating chamber 65 and will be vented out of the tool 10 through exhaust passages 47 .

When the pressurized fluid in front of the striker 14 , that is, in the forward operating chamber 64 is vented to atmosphere, then the pressure of the air in the interior striker chamber 60 will cause the striker 14 to begin to slow its rearward movement. As a result, the striker 14 will stop its rearward progression and begin to move forward again without impacting the front end of the body coupling 110 , that is, the rearward striker surface 49 , as illustrated in FIG. 4 .

To begin operation in the reverse mode, the control valve 190 is shut off. This simultaneously terminates the supply of pressurized fluid to the valve fluid chamber 142 and enables the exhaust of pressurized fluid present in the valve fluid chamber 142 to the atmosphere through the port 176 in the control valve 190 . As the fluid is exhausted from the valve fluid chamber 142 , the pressure exerted on the control sleeve 16 by the pressurized fluid in the interior striker chamber 60 will cause the control sleeve 16 to slide rearward, thereby moving the control sleeve 16 to the rearward position 150 .

The primary fluid supply assembly 18 continually supplies pressurized fluid to the interior striker chamber 60 . With the control sleeve 16 now in the position depicted in FIG. 5 , the forward travel of the striker 14 is shortened, and the rearward travel is lengthened. During forward movement of the striker 14 , as illustrated in FIG. 6 , the ports 66 in the striker 14 connect the interior striker chamber 60 with the forward operating chamber 64 sooner than when the tool is operating in the forward mode. The striker 14 thus begins traveling rearward before impacting on the forward striker surface 50 .

Thus, when the tool 10 is operating in the reverse mode, fluid pressure in the cavity between the front of the tool 10 and the striker 14 , that is, the forward operating chamber 64 , will bring the striker 14 to a stop before it impacts the forward striker surface 50 . At this point, since the cross-sectional area on the outside of the rear end 58 of the striker 14 is greater than that on the inside of the striker 14 , that is, in the interior striker chamber 60 , the striker will begin to move toward the rear of the tool 10 . This rearward progression of the striker 14 , will continue largely unabated until the port holes 66 in the striker 14 pass by the rear edge of the front cylindrical portion 84 of the control sleeve 16 . Once the port holes 66 in the striker 14 reach this point, the pressurized fluid in the cavity between the outside of the striker 14 and the inside of the tool housing 12 , that is, in the rear operating chamber will be vented to atmospheric pressure. From this point on, the fluid is free to flow out of the rear operating chamber 65 through the exhaust conduit 47 , that is the milled slots on the outer circumference of the body coupling 110 . When the pressurized fluid in the front of the striker 14 , that is, in the forward operating chamber 64 , is vented to the atmosphere, then the pressure of the fluid inside of the striker 14 , that is, in the interior striker chamber 60 , will cause the striker to begin to slow its rearward movement. However, the striker 14 will continue its rearward motion until it impacts the front end of the body coupling 110 , that is the rearward striker surface 49 . This impact is what causes the tool housing 12 to be driven backwards within the formed hole.

During the rearward movement of the striker 14 , it may be noted that the ports 66 in the striker 14 connect the forward operating chamber 64 with the atmosphere through the exhaust passages 47 much later (i.e., the striker must be closer to the tailpiece than when this occurs in the forward mode). As shown in FIG. 5 , the ports 66 in the striker 14 do not connect the forward operating chamber 64 with the axial exhaust passages 47 until the rear end 58 of the striker 14 approaches the rearward striker surface 49 of the interior chamber 38 . Impact against the rear of the tool 10 is thereby achieved. As with the forward operation, the striker 14 will continue to reciprocate against the rearwardly facing impact surface 49 as long as the primary fluid supply assembly 20 continues to supply pressurized fluid to the interior striker chamber 60 .

To switch back to the forward mode, the control valve 190 is once again opened. As pressurized fluid begins to pass into the valve fluid chamber 142 , the pressure exerted on the nodular rear portion 88 of the control sleeve 16 and will cause the control sleeve 16 to slide forward to the position shown in FIG. 3 , abutting the stop 154 of the body coupling 110 . The stop 154 prevents the control sleeve 16 from sliding any further forward. With the control sleeve 16 in the position shown in FIG. 3 , the striker 14 once again impacts against the forward striker surface 50 of the interior chamber 38 during forward axial movement.

It will be understood that the above description is of a preferred exemplary embodiment of the invention and is meant to be illustrative, not limitative. Modifications may be made in the structural features of the invention without departing from the scope of the invention as expressed in the appended claims.

Claims

1. An impact-operated, ground-penetrating tool powered by a primary supply of pressurized fluid, and controlled between a forward operating mode and a reverse operating mode by a second supply of pressurized fluid, the tool comprising:a housing having a front end, a rear end, and body defining an interior operating chamber with an inner surface, an exhaust conduit providing communication between the operating chamber and the outside of the tool, a forward striker surface, and a rearward striker surface; a striker reciprocally supported within the operating chamber of the housing between the forward and rearward striker surfaces, the striker having a forward end, a rear portion terminating in a rear end, and a striker body defining an interior striker chamber, wherein the rearward portion sealingly engages the inner surface of the operating chamber to divide the operating chamber into a forward operating chamber and a rearward operating chamber, the rearward operating chamber continuous with the exhaust conduit, wherein the striker body has at least one striker port to provide fluid communication between the forward operating chamber and the interior striker chamber; a manifold near the rear end of the housing and comprising a primary conduit connectable to the primary fluid supply and a secondary conduit connectable to the secondary fluid supply; a primary fluid inlet tube extending from the primary conduit of the manifold; a valve chamber in fluid communication with the secondary conduit in the manifold; a control sleeve having a rear portion, a front portion, and an interior sleeve chamber defining a passage between the rear portion and the front portion, wherein the front portion is slidably and sealingly supported inside the rear portion of the striker, wherein the rear portion is slidably and sealingly supported on the primary fluid inlet tube at least partially inside the valve chamber, whereby the sleeve provides continuous fluid communication between the primary fluid inlet tube and the striker chamber, so that in response to a supply of primary fluid the striker reciprocates between a forward position in which the striker port is open between the interior striker chamber and the forward operating chamber and a rearward position in which the striker port is open between the forward operating chamber and the rearward operating chamber and exhaust conduit; a primary fluid inlet tube extending from primary conduit of the manifold a distance into the interior sleeve chamber of the control sleeve; and wherein the rear portion of the sleeve includes a nodular lobe inside the valve chamber movable between a forward position in response to pressurization of the valve chamber and a reverse position in response to depressurization of the valve chamber, so that the forward portion of the sleeve moves between a forward position in which the striker hits the forward striker surface as it reciprocates and a rearward position in which the striker hits the rearward striker surface as it reciprocates.

2. The tool of claim 1 wherein the largest cross sectional area of the rear portion of the control sleeve taken perpendicular to the longitudinal axis of the control sleeve must be greater than the largest cross sectional area of the front portion of the control sleeve taken perpendicular to the longitudinal axis of the control sleeve.

3. The tool of claim 1 wherein the body of the housing comprises at least two separate components joined by friction welding.

4. An impact-operated, ground-penetrating tool powered by a primary supply of pressurized fluid, and controlled between a forward operating mode and a reverse operating mode by a second supply of pressurized fluid, the tool comprising:a housing having a front end, a rear end, and body defining an interior operating chamber with an inner surface, an exhaust conduit providing communication between the operating chamber and the outside of the tool, a forward striker surface and a rearward striker surface; a striker reciprocally supported within the operating chamber of the housing between the forward and rearward striker surfaces, the striker having a forward end, a rear portion terminating in a rear end, and a striker body defining an interior striker chamber, wherein the rearward portion sealingly engages the inner surface of the operating chamber to divide the operating chamber into a forward operating chamber and a rearward operating chamber, the rearward operating chamber continuous with the exhaust conduit, wherein the striker body has at least one striker port to provide fluid communication between the forward operating chamber and the interior striker chamber; a means for operably connecting the primary fluid supply to the interior striker chamber; a valve chamber at the rear end of the housing; a means for operably connecting the secondary fluid supply to the valve chamber; a control sleeve having a rear portion and a front portion, wherein the front portion is slidably and sealingly supported inside the rear portion of the striker, wherein the rear portion is slidably and sealingly received at least partially inside the valve chamber, whereby the control sleeve provides continuous fluid communication between means for operably connecting the primary fluid supply and the interior striker chamber, so that in response to supply of primary fluid the striker reciprocates between a forward position in which the port is open between the striker chamber and the forward operating chamber and a rearward position in which the striker port is open between the forward operating chamber and the rearward operating chamber and exhaust conduit; and wherein the rear portion of the control sleeve includes a nodular lobe inside the valve chamber movable between a forward position in response to pressurization of the valve chamber and a reverse position in response to depressurization of the valve chamber, so that the forward portion of the control sleeve moves between a forward position in which the striker hits the forward striker surface as it reciprocates and a rearward position in which the striker hits the rearward striker surface as it reciprocates.

5. The tool of claim 4 wherein the largest cross sectional area of the rear portion of the control sleeve taken perpendicular to the longitudinal axis of the control sleeve must be greater than the largest cross sectional area of the front portion of the control sleeve taken perpendicular to the longitudinal axis of the control sleeve.

6. The tool of claim 4 wherein the body of the housing comprises at least two separate components joined by friction welding.

7. An impact-operated, ground-penetrating tool powered by a primary supply of pressurized fluid, and controlled between a forward operating mode and a reverse operating mode operation by a second supply of pressurized fluid comprising:a housing having a front end, a rear end, and body defining an interior operating chamber with an inner surface, an exhaust conduit providing communication between the operating chamber and the outside of the tool, a forward striker surface and a rearward striker surface; a striker reciprocally supported within the operating chamber of the housing between the forward and rearward striker surfaces, the striker having a forward end, a rear portion terminating in a rear end, and a striker body defining an interior striker chamber, wherein the rearward portion sealingly engages the inner surface of the operating chamber to divide the operating chamber into a forward operating chamber and a rearward operating chamber, the rearward operating chamber continuous with the exhaust conduit, wherein the striker body has at least one striker port to provide fluid communication between the forward operating chamber and the interior striker chamber; a primary connecting assembly to operably connect the primary fluid supply to the interior striker chamber; a valve chamber at the rear end of the housing; a secondary connecting assembly to operably connect the secondary fluid supply to the valve chamber; a control sleeve having a rear portion and a front portion, wherein the front portion is slidably and sealingly supported inside the rear portion of the striker, wherein the rear portion is slidably and sealingly received at least partially inside the valve chamber, whereby the control sleeve provides continuous fluid communication between primary connecting assembly and the interior striker chamber, so that in response to supply of primary fluid the striker reciprocates between a forward position in which the striker port is open between the striker chamber and the forward operating chamber and a rearward position in which the striker port is open between the front operating chamber and the rearward operating chamber and exhaust conduit; and wherein the rear portion of the sleeve includes a nodular lobe inside the valve chamber movable between a forward position in response to pressurization of the valve chamber and a reverse position in response to depressurization of the valve chamber, so that the forward portion of the control sleeve moves between a forward position in which the striker hits the forward striker surface as it reciprocates and a rearward position in which the striker hits the rearward striker surface as it reciprocates.

8. A pneumatic reversible impact operated ground penetrating boring tool comprising:a housing having a rear end, and an interior chamber defining a forward striker surface and a rearward striker surface; a striker having an external wall surrounding an interior striker chamber; wherein the striker is slidably and sealingly receivable within the interior chamber of the housing and is adapted to reciprocally move between the forward striker surface and the rearward striker surface; and wherein the external wall of the striker and the interior chamber of the housing define an operating chamber; a primary fluid supply assembly operably connectable to the striker and adapted to provide pressurized primary fluid to the interior striker chamber to drive the striker in a reciprocal motion within the interior chamber of the housing when the pressurized fluid is supplied; a control sleeve having a front end, a rear end, and an interior sleeve chamber defining a passage from the front end to the rear end; wherein the front end of the control sleeve is slidably and sealingly receivable within the interior striker chamber; wherein the rear end of the sleeve is slidably and sealingly receivable within a valve fluid chamber at the rear end of the housing, the valve fluid chamber having a first end and a second end; wherein the rear end of the control sleeve is adapted to move toward the first end of the valve fluid chamber during tool advancement; and wherein the rear end of the control sleeve is adapted to move toward the second end of the valve fluid chamber during tool withdrawal; and wherein the striker impacts the forward striker surface when the control sleeve is at the first end of the valve fluid chamber; and wherein the striker impacts the rearward striker surface when the control sleeve is at the second end of the valve fluid chamber; and a secondary fluid supply assembly operably connectable to the valve fluid chamber; wherein the valve fluid chamber is pressurized by the secondary fluid supply assembly; wherein the valve fluid chamber must be pressurized to move and hold the control sleeve at the first end during tool advancement; and wherein the valve fluid chamber must be depressurized to permit the control sleeve to move toward and remain at the second end during tool withdrawal.

9. The tool of claim 8 wherein the largest cross sectional area of the rear portion of the control sleeve taken perpendicular to the longitudinal axis of the control sleeve must be greater than the largest cross sectional area of the front portion of the control sleeve taken perpendicular to the longitudinal axis of the control sleeve.

10. The tool of claim 8 wherein the body of the housing comprises at least two separate components joined by friction welding.