Impact assisted rotary drill bit and method of operating the same

专利摘要:
42 SUMMARY A method of drilling through a formation comprises providing a drill and a drill string, and operatively connecting an earth drill to the drill through the drill string. An air floc is created through the drill string at an air pressure of less than about one hundred pounds per square inch (100 psi) and an superimposed force is applied to the earth drill, the superimposed force being less than about four foot-pounds per square inch (5 ft-lb / in2).
公开号:SE1050868A1
申请号:SE1050868
申请日:2009-08-06
公开日:2010-08-24
发明作者:Allan W Rainey；James W Langford
申请人:Atlas Copco Secoroc Llc；
IPC主号:

专利说明:

1 SLOW ASSISTANT ROTARY GROUND DRILL AND METHOD OF MANUVERING THE SAME REFERENCE TO RELATED APPLICATIONS This application takes precedence over U.S. Provisional Application No. 61/086740, filed August 6, 2008 by the same inventor, the contents of which are incorporated herein by reference.
BACKGROUND OF THE INVENTION Field of the Invention This invention relates to drilling rigs.
Description of the Related Art An earth auger is commonly used for drilling through a formation to form a drill bit. Such drilling rigs can be formed by many different shells, such as drilling for oil, minerals and geothermal steam. There are several different types of earth drills used to form a drill bit. One type is a triangular rotary earth auger, and in a typical installation it comprises three earth auger carcasses rotatably mounted on separate tabs. The flaps are joined together by welding to form a drill body. The earth drilling rigs rotate in response to the contact with the formation when the earth drilling body rotates in the drill tail. Several examples of rotary earth drills are shown in U.S. Pat. patent no. 3,550,972, 3,847,235, 4,136,748, 4,427,307, 4,688,651, 4,741,471 and 6,513,607. Some attempts have been made to form boreholes at a faster rate, which is discussed in more detail in U.S. Pat. patent no. 3,250,337, 3,307,641, 3,807,512, 4,502,552, 5,730,230, 6,371,223 and 6,986,394, as well as in U.S. Pat. Patent Application No. 20050045380. Some of these references show the use of a percussion hammer to apply a superimposed force to the earth auger. However, it is undesirable to increase the drilling speed when the hammer is used, and to reduce the amount of damage to the earth drill in response to the superimposed force. BRIEF SUMMARY OF THE INVENTION The present invention relates to a percussion-assisted rotary earth auger, and to a method of maneuvering the same. The novel features of the invention are set forth in detail in the appended claims. The invention will be understood from the following description when read in conjunction with the accompanying drawings. These and other features, aspects, and advantages of the present invention will be better understood by reference to the following drawings and description.
BRIEF DESCRIPTION OF THE DRAWINGS FIGURE 1 is a side view of a drilling rig connected to a drill string. FIGURE 2a is a perspective view of a rotary drilling system coupled to the drill string of Figure 1, the rotary drilling system including a rotary earth drill coupled to a hammer assembly. FIGURE 2b is a sectional side view of the rotary drilling system of Figure 2a connected to the drill string. FIGURE 3a is a perspective view of a rotating tool joint enclosed with the hammer assembly of Figures 2a and 2b. FIGURE 3b is a perspective view of a hammer housing enclosed with the hammer assembly of Figures 2a and 2b. FIGURE 3c is a perspective view of a flow control tube enclosed with the hammer assembly of Figures 2a and 2b. FIGURE 3d is a perspective view of a piston enclosed with the hammer assembly of Figures 2a and 2b. FIGURE 3e is a perspective view of a drive chuck enclosed with the hammer assembly of Figures 2a and 2b. FIGURE 3f is a perspective view of an adapter member enclosed with the hammer assembly of Figures 2a and 2b. FIGURES 4a and 4b are side views in close-up of the hammer assembly according to Figures 2a and 2b showing the piston in the first and second layers, respectively. FIGURES 5a and 5b are side views of the rotary drilling system of Figures 2a and 2b with the rotary drill in the retracted and extended position, respectively. FIGURE 6 is a side view of a back piece of the hammer assembly of Figures 2a and 2b. FIGURE 7a is a perspective view of the adapter part and the rotary earth drill according to Figures 2a and 2b in a disassembled condition. FIGURES 7b and 7c are cross-sectional views of the adapter part and the rotary earth drill according to Figures 2a and 2b in the connected state. FIGURE 7d is a side view of trapezoidal rotary earth drill passages of the rotary earth drill of Figures 2a and 2b. FIGURE 7e is a side view of trapezoidal tool bandages of the adapter member of Figures 2a and 2b. FIGURES 8a and 8b are flow diagrams of the methods of drilling a slide. FIGURES 8c and 8d are flow diagrams of the methods of manufacturing a rotary drilling system. FIGURES 9a, 9b and 9c are flow charts of the methods of drilling through a formation.
DETAILED DESCRIPTION OF THE INVENTION Figure 1 is a side view of a drill 160 connected to a drill string 106. In this embodiment, the drill 160 includes a platform 161 which carried a drive motor 162 and driver cab 163. A tower chassis 164a of a tower 164 is connected to the platform 161 by a tower coupling 168, and the tower coupling 168 allows the tower 164 to be repeatedly moved between the raised and lowered layers. In the erected layer, shown in Figure 1, a tower crown 164b of the tower 164 is furthest from the Than platform 161. In the erected layer, the front 165 of the tower 164 is water towards the driver's cab 163 and the rear 166 of the tower 164 is water towards the drive notor 162. the lowered layer, the rear 166 of the tower 164 is moved toward the platform 161 and the drive motor 162. The tower 164 generally supported a feed cable system (not shown) fixed to a rotary head 167, the feed cable system allowing movement of the rotary head 167 between raised and lowered bearing the tower 164. The feed cable system moves the rotary head 167 to a raised and lowered position by its movement towards the tower crown 164b and the tower base 164a, respectively. The rotary head 167 is moved slightly raised and lowered to lift and lower the drill string 106 through a drill bit, respectively. The rotary head 167 is further used to rotate the drill string 106, the drill string 106 extending through the tower 164. The drill string 106 generally includes one or more dowels connected at one end. The drill bit of the drill string 106 is capable of being attached to an earth drill, such as a three-pin rotating earth drill. Figure 2a is a perspective view of a rotary drill system 100 connected to the drill string 106, and Figure 2b is a sectional side view of the rotary drill system 100 connected below the drill string 106. In Figure 2a, the rotary drill system 100 extends longitudinally through a borehole. 105. A center line 147 extends longitudinally along the center of the rotary drilling system 100, and a radial line 169 extends radially and perpendicular to the center line 147. The drill tail 105 has a circular cross-sectional shape in response to the rotary drilling system 100 having a circular cross-sectional shape. The drill tail 105 has a cross-sectional dimension D1, which corresponds to a diameter when the drill tail 105 has a circular cross-sectional shape. The rotary drilling system 100 further has a cross-sectional dimension D2, which corresponds to a diameter when the rotary drilling system 100 has a circular cross-sectional shape. The value of dimension D1 corresponds to the value of dimension D2. For example, dimension D1 increases and decreases in response to increasing and decreasing dimension D2, respectively. It should be noted that the cross-sectional shapes of the drill tail 105 and the rotary drill system 100 are determined by creating a cut line through the drill tail 105 and the rotary drill system 100, respectively, in a direction along the radial line 169. In this embodiment, the rotary drill system 100 includes a rotary drill 102 interconnected. with a hammer assembly 103. The rotary drill 102 is repeatably movable between interconnected and disassembled condition with the hammer assembly 103, as will be discussed in more detail below with Figure 7a. The rotary drill102 can be of many different types. In this embodiment, the rotary drill 102 is formed as a three-cone rotary drill. A three-cone rotary earth auger comprises three flaps connected together to form an earth auger body, the habitual tab carrying a rotatably mounted scarecrow. Rotating earth drills 102 include at least one or more tabs, and a corresponding carcass rotatably mounted to the habit tab. It should be noted that two scars are shown in Figures 2a and 2b for illustrative purposes. In this embodiment, the hammer assembly 103 includes a rotating tool joint 107 with a central opening 104 (Figure 3a) extended therethrough. One end of the drill string 106 is connected to the drill 160 (Figure 1) and the other end of the drill string 106 is connected to the rotary drill system 100 through the tool joint 107. In particular, one end of the drill string 106 is connected to rotary head 167 and the other end of 20 the drill string 106 is connected to the rotary drilling system 100 by tool joints 107. More information regarding drilling machines is provided in US patent no. 4,320,808, 6,276,453, 6,315,063 and 6,571,867, the contents of all of which are incorporated herein by reference. The connection between the drill string 106 and rotating tool joints 107 is often referred to as a threaded box connection. The drill string 106 is connected to the rotary drill system 100 so that the drill string 106 is in fluid communication with the rotary drill 102 through the hammer assembly 103. The drill string 106 supplies liquid to the hammer assembly 103 through a drill string opening 108 and the central opening 104 of the tool connection leads the drill to the drill. the hammer assembly 103 through rotary head 167 and drill string 106. The rotary drill 102 discharges a portion of the fluid so that the drill bit is lifted upwardly through the drill tail 105. The drill 160 provides the fluid with a desired pressure 6 to clean the rotary drill 102, as well as to evacuate the drill string. will be discussed in more detail below, the drill 160 supplies the fluid with the desired pressure to drive the hammer assembly 103. The fluid can be of many different types, such as a fluid and / or gas. The liquid can be of many different kinds, such as oil, water, borer clay, and combinations thereof. The gas can be of many different types, such as air and other gases. In some situations, the liquid includes a liquid and gas, such as air and water. It should be noted that the drilling machine 160 (Figure 1) typically comprises a compressor (not shown) which supplies a gas, such as air, to the liquid. The fluid anyands to drive the rotary auger 102, and to drive the hammer assembly 103. The fluid, for example, to lubricate and cool the rotary auger 102 and, as discussed in more detail below, to drive the hammer assembly 103. It should also be noted that the drill string 106 is usually is rotated by the rotary head 167, and the rotating drill bit 100 rotates in response to the rotation of the drill string 106. The drill string 106 can be rotated at many different speeds. For example, in one situation, the rotary head 167 rotates the drill string 106 at a speed less than about one hundred and fifty vary per minute (150 RPM). In a particular situation, the rotary head 167 rotates the drill string 106 at a speed between about fifty vary per minute (50 RPM) to about one hundred and fifty vary per minute (150 RPM). In some situations, the rotary head 167 rotates the drill string 106 yid at a speed between about forty vary per minute (40 RPM) to about one hundred vary per minute (100 RPM). In another situation, the rotary head 167 rotates the drill string 106 at a speed between about one hundred vary per minute (100 RPM) to about one hundred and fifty vary per minute (150 RPM). In general, the penetration speed of the rotary drilling system 100 increases and decreases as the rotational speed of the drill string 106 increases and decreases, respectively. The penetration speed of the rotary drilling system 100 is consequently adjustable in response to adjusting the rotational speed of the drill string 106. In most embodiments, the earth drill 102 operates with a drilling pressure applied thereto. In general, the penetration speed of the rotary drilling system 100 increases and decreases as the drilling pressure increases and decreases, respectively. The penetration speed of the rotary drilling system 100 is consequently adjustable in response to adjusting the drilling pressure. The drilling pressure is usually applied to the earth drill 102 through the drill string 106 and hammer assembly 103. The drilling pressure can be applied to the earth drill 102 through the drill string 106 and hammer assembly 103 in many different ways. For example, the drilling machine 160 may apply the drilling pressure to the earth drill 102 through the drill string 106 and hammer assembly 103. In particular, the rotary head 167 may apply the drilling pressure to the earth drill 102 through the drill string 106 and hammer assembly 103. The value of the drilling pressure depends on many factors. resist drilling pressure without fail. The earth drill 102 is more prone to failure if the applied drill pressure is too great. The drilling pressure can have the load values in many different intervals. For example, in a situation the drill pressure is less than ten thousand pounds per square inch (10,000 psi) of the drill neck diameter. In a particular situation, the drill pressure is in the range of about one thousand pounds per square inch (1000 psi) of the drill neck diameter to about ten thousand pounds per square inch (10,000 psi) of the drill neck diameter. In one situation, the drill pressure is in the range of about two thousand pounds per square inch (2000 psi) of the drill neck diameter to about eight thousand pounds per square inch (8000 psi) of the drill neck diameter. In another situation, the drill pressure is in the range of about four thousand pounds per square inch (4000 psi) of the drill neck diameter to about six thousand pounds per square inch (6000 psi) of the drill neck diameter. It should be noted that the drill neck diameter of the drill pressure corresponds to the dimension D1 of the drill tail 105, which corresponds to the dimension D2 of the rotary drill system 100, as discussed in more detail above. The drill pressure can also be determined by using other units of the number of pounds per square inch of the drill neck diameter. For example, in some situations the drilling pressure is less than about one hundred and thirty thousand pounds (130,000 lbs). In a particular situation, the drilling pressure is in the range of about thirty thousand 8 pounds (30,000 lbs) to about one hundred and thirty thousand pounds (130,000 lbs). In one situation, the drilling pressure is in the range of about ten thousand pounds (10,000 lbs) to about sixty thousand pounds (60,000 lbs). In another situation, the drilling pressure is in the range of about sixty thousand pounds (60,000 lbs) to about one hundred and twenty thousand pounds (120,000 lbs). In one situation, the drilling pressure is in the range of about ten thousand pounds (10,000 lbs) to about forty thousand pounds (40,000 lbs). In another situation, the drilling pressure is in a range of about eighty thousand pounds (80,000 lbs) to about one hundred and eighty thousand pounds (110000 lbs). During operation, hammer assembly 103 applies a superimposed force to the rotary earth drill 102. However, it should be noted that the superimposed force can be applied to the rotary earth drill 102 in many other ways. For example, in one embodiment, the superimposed force is applied to the earth drill 102 by a spring-driven mechanical tool. In another embodiment, the superimposed force is applied to the earth drill 102 by a spring-driven mechanical tool instead of an air-driven hammer. In some embodiments, the superimposed force is applied to the earth drill 102 by an electromechanically driven tool. In some embodiments, the superimposed force is applied to the earth drill 102 through an electromechanically driven tool instead of an air driven hammer. In the embodiment of Figures 2a and 2b, the hammer assembly 103 applies the superimposed force to the rotary earth drill 102 in response to actuation. As mentioned above, hammer assembly 103 is driven in response to a flood of the fluid thereby, the fluid being supplied by the drill 160 through the drill string 106. The drill 160 provides the fluid with a controlled and adjustable pressure. As discussed in more detail below, the upright fluid pressure is maintained so that the hammer assembly 103 is operated at a desired frequency and amplitude. In this way, the hammer assembly 103 supplies a desired superimposed force to the rotary earth drill 102. During operation, the hammer assembly 103 is driven when the shear cone (s) of the rotary earth drill 102 are in contact with a formation.
The hammer assembly 103 applies the superimposed force to the rotary earth drill 102 and consequently the rotary earth drill 102 advances into the formation as the shear cone (s) crush it. The speed at which the formation is crushed is affected by the magnitude and frequency of the force produced by the hammer assembly 103 in response to actuation. In this way, the hammer assembly 103 drives the rotary drill 102 into the formation and the drill tail 105 is formed. It should be noted that the magnitude of the superimposed force usually corresponds to the absolute value of the amplitude of the superimposed force. As mentioned above, the hammer assembly 103 includes rotating tool joints 107 with a central opening 104 extending therethrough, the rotary tool joint 107 being shown in a perspective view in Figure 3a. The central opening 104 allows fluid to flow through the rotating tool joint 107. The drill string 106 is connected to the hammer assembly 103 through the rotary tool joint 107. In this way, the drill string 106 is connected to the rotary drilling system 100. In this embodiment, the hammer assembly body 103 includes a hammer hole body 103. 110, which is shown in a perspective view in Figure 3b. The marble oil body 110 has a cylindrical shape with a circular cross-sectional shape. The hammer hole body 110 has opposite openings, and a central channel 112, which extends between the opposite openings.
The hammer oil body 110 defines a piston cylinder 113 (Figure 3b) which is part of the central channel 112. It should be noted that the rotating tool joint 107 is connected to the hammer oil body 110 so that the central channel 112 is in fluid communication with the central opening 104. The drill string 106 is further in fluid communication with the earth drill 102 and the hammer assembly 103 through the central channel 112. The rotating tool joint 107 can be connected to the hammer housing body 110 in many different ways. In this embodiment, the rotating tool joint 107 is connected to the hammer housing body 110 with a back piece 114 (Figure 2b). The back piece 114 is in continuous engagement with the male casing body 110 and has a central opening defined and shaped to receive the rotating tool joint 107. A throttle plate 116 is located between the back piece 114 and the rotating tool joint 107. The throttle plate 116 together with a non-return valve 115 (Figure 6 ) restricts the backflow of drill cuttings and cuttings inside the hammer assembly 103. The throttle plate 116 and the check valve 115 also restrict the air flow through the hammer assembly 103, which will be discussed in more detail below. The throttle plate 116 and the check valve 115 are located against the rear end of the hammer assembly 103 to allow adjustment without having to remove the rotary drill bit 100 from the drill tail 105. This allows in place adjustment of the discharge pressure in the male assembly 103 to adjust its power take-off. In this embodiment, the hammer assembly 103 includes a flow control tube 118, shown in a perspective view in Figure 3c. In this embodiment, the flow control tube 118 extends through the central opening 104 of the rotating tool joint 107, as well as through the central channel 112. The control tube 118 includes a flow control tube body 120 with head and sleeve portions 121 and 123. The sleeve portion 123 extends away from the central channel 112. the drill string 106. The control tube 118 includes opposing drive control ports 122a and 122b and opposing return control ports 122c and 122d, which extend through the sleeve portion 123. In this embodiment, the hammer assembly 103 includes a piston 124, shown in a perspective view in Figure 3d. In this embodiment, the piston 124 is positioned opposite the piston cylinder 113 of the hammer sleeve body 110. The piston 124 includes a piston body 126 having a central opening 125 through which the sleeve portion 123 extends. The central opening 125 extends between a drive surface 128 and the return surface 130 of the piston body 126. The drive surface 128 faces the rotating tool joint 107 and the return surface 130 moves away from the rotating tool joint 107. The piston body 126 is located within the cylinder 113 and the cylinder 113 has a return chamber 140, adjacent to the return surface 130, and a drive chamber 141, adjacent to the drive surface 128, which will be discussed in more detail with Figures 4a and 4b. In this embodiment, the piston body 126 includes opposing drive piston ports 132a and 132b and adjacent return piston ports 132c and 132d. The drive piston ports 132a and 132b and the return piston ports 132c and 132d extend between the central opening 125 and the outer periphery of the piston body 126. The drive piston ports 132a and 132b and the return piston ports 132c and 132d can extend through the piston body 126 in many different ways. In this embodiment, the drive piston ports 132a and 132b are angled toward the drive surface 128. The drive piston ports 132a and 132b are angled toward the drive surface 128 so that the drive piston ports 132a and 132b are not parallel to the radial line 169. The drive piston ports 132a and 132b are angled toward the drive surface 128 so are not parallel to the centerline 147. Further, the return piston ports 132c and 132d are angled toward the return surface 130. The return piston ports 132c and 132d are angled toward the drive surface 130 so that the return piston ports 132c and 132d are not parallel to the radial line 169.
The return piston ports 132c and 132d are angled to the drive surface 130 so that the return piston ports 132c and 132d are not parallel to the centerline 147. As will be discussed in more detail below, the piston body 126 is repeatably movable along sleeve portion 123, between a first layer and the drive piston ports 132 in fluid communication with the central channel 112 through drive control ports 122a and 122b, respectively, and a second layer wherein the return piston ports 132c and 132d are in fluid communication with the central channel 112 through return control ports 122c and 122d, respectively. It should be noted that, in the first layer, the return piston ports 132c and 132d are not in fluid communication with the central channel 112 through the return control ports 122c and 122d. In addition, in the second layer, the drive piston ports 132a and 132b are not in fluid communication with the central channel 112 through drive control ports 122a and 122b. Hence, in the first layer, material than the central channel 112 is restricted than to flow through the return piston ports 132c and 132d in the piston body 126. Furthermore, in the second layer, material from the central channel 112 is restricted from flowing through the drive piston ports 132a and 132b in the piston body 126. The flow of material through these ports of the hammer assembly 103 is discussed in more detail with Figures 4a and 4b, the first and second layers of the piston 124 corresponding to the disengaged and engaging layers, respectively. In this embodiment, the male assembly 103 includes a drive chuck 134, which is shown in a perspective view in Figure 3e. The drive chuck 134 is connected to the casing body 110. The drive chuck 134 can be coupled to the hammer casing body 110 in many different ways. In this embodiment, the drive chuck 134 is coupled to the hammer housing body 110 by operatively coupling them together. In this embodiment, the hammer assembly 103 includes an adapter member 136, shown in a perspective view in Figure 3f. The adapter part 136 is connected to the hammer housing body 110, which can be done in many different ways. In this embodiment, the adapter part 136 is slidably connected to the drive chuck 134, which as mentioned above is connected to the hammer housing body 110. In this way, the adapter part 136 can slide relative to the drive chuck 134. The adapter part 136 comprises a rotating drill bit 138 and a tool joint 139 at one end. At the opposite end, the adapter portion 136 includes a abutment surface 131 which winds toward the return surface 130. It should be noted that the drive surface 128 extends away from the abutment surface 131. As mentioned above, the rotary drill system 100 includes the rotary drill 102 connected to the hammer assembly 102. can be connected to the hammer assembly 103 in many different ways. In this embodiment, the rotary auger 102 is connected to the hammer assembly 103 by connecting it to the adapter portion 136. In this embodiment, the rotary auger 102 is interconnected to the adapter portion 136 by extending it through the rotating auger port 138 and connecting it to the tool conveyor conveyor 13. between an interconnected and ice-coupled state with the adapter portion 136, as will be discussed in more detail with Figure 7a. It should be noted that the rotary earth drill 102 can slide relative to the drive chuck 134 because it is coupled to the adapter part 136, which is slidably coupled to the drive chuck 134. Hence, the rotary earth drill 102 slides relative to the drive chuck 134 in response to the adapter part 136 sliding relative to the drive chuck 134. In this way, the adapter part 136 and the rotary earth drill 102 can slide relative to the drive chuck 134 and the hammer housing body 110. As will be discussed in more detail with Figures 4a and 4b, the adapter part 136 slides in response to the movement of the piston 124, which applies a superimposed force F to it ( Figure 4b). As will be discussed in more detail with Figures 5a and 5b, the rotary drill 102 moves between the extended and retracted layers in response to sliding of the adapter member 136. In this manner, the rotary drill 102 moves between the extended and retracted layers in response to the movement of the piston 124 between the first and second team. Figures 4a and 4b are side views in close-up of the hammer assembly 103, which show the piston 124 in the first and second layers, respectively. Furthermore, Figures 5a and 5b are side views of the drilling system 100 with the rotary earth drill 102 in the retracted and extended layers, respectively. Figure 6 is a side view of a back piece 10 of the hammer assembly 103 showing how the washers flow out through the rotary drilling system 100. In this embodiment, the hammer assembly 103 includes drive outflow ports 142a and 142b in fluid communication with the drive chamber 141. Further, the hammer port 103 includes return outlet assembly 15. and 142d in fluid communication with the return chamber 140. The drive outflow ports 142a and 142b allow material to flow from the drive chamber 141 to a region outside the hammer assembly 103. Further, the return outflow ports 142c and 142d allow material to flow from the return chamber 20 to the region of the return chamber 140. material The return chamber 140 and the drive chamber 141 will be discussed in more detail with Figure 6. In this embodiment, the piston 124 is repeatably movable between the first and second layers. In the first layer the piston 124 is disengaged from the adapter part 136 and in the second layer the piston 124 engages the adapter part 136. In the disengaged layer the piston body 126 is positioned so that the drive piston ports 132a and 132b are in fluid communication with the central channel 112 through drive port 122a respectively 122b. In the disengaged layer, the piston body 126 is positioned so that the return piston ports 132c and 132d are not in fluid communication with the central channel 112 through return control ports 122c and 122d. In the disengaged layer, the piston body 126 defines the flow of material through the return control ports 122c and 122d. Furthermore, the piston body 126 in the disengaged layer is positioned so that the return chamber 140 is in fluid communication with return outflow ports 142c and 142d and the drive chamber 141 is not in fluid communication with drive outflow ports 142a and 142b. In the engaging stroke, the piston body 126 is positioned so that the drive piston ports 132a and 132b are not in fluid communication with the central channel 112 through the drive control ports 122a and 122b. In the engaging layer, the piston body 126 is positioned so that the return piston ports 132c and 132d are in fluid communication with the central channel 112 through return control ports 122c and 122d, respectively. In the engaging layer, the piston body 126 defines the flow of material through drive control ports 122a and 122b. Furthermore, the piston body 126 in the engaging layer is positioned so that the return chamber 140 is not in fluid communication with return outflow ports 142c and 142d and the drive chamber 141 is in fluid communication with drive outflow ports 142a and 142b. In one situation, the piston 124 is in the disengaged layer, as shown in Figure 4a, so that the return chamber 140 is in fluid communication with the return outflow ports 142c and 142d. In this way, the liquid in the return chamber 140 is able to flood the return chamber 140 to the region outside the hammer assembly 103. Furthermore, the drive chamber 141 is in fluid communication with the central channel 112 through the drive piston ports 132a and 132b and through the drive control ports 122a and 122b, respectively. In this way, the liquid flowing through the central channel 112, which is provided through the drill string opening 108, is able to flow into the drive chamber 141. When the liquid flows into the drive chamber 141, its pressure is increased, which applies a superimposed force to the drive surface 128 of the piston body 126 and moves the piston body 126 along the sleeve portion 123 away from the main part 121. The piston body 126, in response to the superimposed force F applied to the drive surface 128, to the adapter part 136, the return surface 130 engaging the abutment surface 131. The adapter part 136 slides relative to the drive chuck 134 in response to the return surface 130 engaging the abutment surface 131. As mentioned above, the rotary auger 102 is interconnected with the adapter portion 136. Thereby, the rotary auger 102 also slides in response to the return surface 1 engaging the abutment surface 131, the rotating auger sliding then it is moved from a retracted layer (Figure 5a) to an extended layer (Figure 5b). In the retracted bearing, the adapter part 136 engages the drive chuck 134, as shown by an indicator arrow 148 in Figure 5a. Furthermore, the piston 124 is free of the abutment surface 131 of the adapter part 136, as shown by an indicator arrow 150 in Figure 5a. In the extended position, the adapter portion 136 is free Than the drive chuck 134 at a distance ti as shown by an indicator arrow 152 in Figure 5b. Furthermore, the piston 124 engages the abutment surface 131 of the adapter part 136, as shown by an indicator arrow 154 in Figure 5b. In another situation, the piston 124 in the engaging stroke, shown in Figure 4b, is said to have the drive chamber 141 in fluid communication with return outflow ports 142a and 142b. In this way, the liquid in the drive chamber 141 is able to flow Than drive chamber 141 to the region outside the hammer assembly 103. Furthermore, the return chamber 140 is in liquid communication with the central channel 112 through the drive piston ports 122c and 122d and through drive control ports 132c and 132d, respectively. In this way, the liquid flowing through the central channel 112, which is provided through the drill string opening 108, is able to flow into the return chamber 140. As the liquid flows into the return chamber 140, its pressure increases, which applies a force to the return surface 130 of the piston body. 126 and moves the piston body 126 along the sleeve portion 123 towards the main part 121. The piston body 126 moves, in response to the superimposed force F applied to the return surface 130, away from the adapter part 136, whereby the return surface 130 is disengaged than the impact surface 131. the adapter part 136 slides 134 in response to the return surface 130 being disengaged from the abutment surface 131. As mentioned above, the rotary auger 102 is interconnected with the adapter portion 136. Thereby the rotary auger 102 also slides in response to the return surface 1 being disengaged from the abutment surface 131, the rotating auger sliding off (Figure 5b) to the retracted layer (Figure 5a). In the retracted position, the adapter part 136 engages the drive chuck 134, as discussed in more detail above. In another embodiment, the piston body 126 is moved away from the adapter portion 136 as a result of a rebound, the rebound comprising the portion of the impact energy that is not passed through the adapter portion 136 and the earth drill 102 toward the formation. In this embodiment 16, the adapter member 136 is moved relative to the drive chuck 134 in response to the impact of the piston body 126 toward the surface 131 of the adapter member 136. Thereby, the superimposed force F is transferred to the adapter member 136 and the motion of the piston body 126 responds to a reaction force applied to it through the adapter member. 136. Thereby, the piston 124 is moved between engaged and disengaged bearings by adjusting the fluid pressure in the return sensor 140 and the drive sensor 141. The fluid pressure in the return chamber 140 and the drive chamber 141 is adjusted so that oscillating forces are applied to the return surface 130 and the drive surface 128, and the piston 124 is moved. and away from the abutment surface 131. The rotary drill 102 typically operates at a spruce value at the inlet pressure of about 40 pounds per square inch (psi). However, most drills provide a feed pressure of between about 50 psi to 100 psi. Only about 10 psi to 60 psi will be armed to drive the hammer assembly 103 if the hammer assembly 103 and the rotary earth drill 102 are connected together in series. In accordance with the invention, the hammer assembly 103 is capable of maneuvering at full system pressure so that the piston 124 can apply more impact force to the adapter portion 136 and the rotary drill 102. The fluid pressure at which the hammer assembly 103 acts is thereby driven to equalize the fluid pressure at which the rotary earth 102 operates. As mentioned above, the drill string 106 supplies water shoes to the hammer assembly 103 through the drill string opening 108, and the water shoes may be of many different types, such as air or other gases, or a combination of gases and water shoes, such as oil and / or water. In one embodiment, the fluid comprises air and the air is passed through the drill string 106 at a rate less than about 5000 cubic feet per minute (cfm). In one embodiment, for example, the air is conducted at a rate in a range of about 1000 cfm to about 4000 cfm. In another embodiment, the fluid includes air and the air passed through the drill string 106 is maintained at an air pressure of less than about one hundred pounds per square inch (100 psi). For example, in one embodiment, the pressure of the air flowing through the drill string 106 is at a pressure in a range of about 40 psi to about 100 psi. In another embodiment, the pressure of 17 is the air flowing through the drill string 106 at a pressure in a range of about 40 psi to about 80 psi. In accordance with the invention, the pressure of the air used to drive the hammer assembly 103 is driven to equalize the pressure of the air used to drive the rotary drill 102.
The penetration rate of the earth drill 102 increases and decreases in general as the air pressure increases and decreases, respectively. The superimposed force F is typically applied to the earth drill 102 with an amplitude and frequency. When the superimposed force F is applied to the earth drill 102 at a frequency other than its amplitude as a function of time. In this way, the superimposed force F is a time-varying superimposed force. The frequency of the superimposed force F is typically periodic, although it may be non-periodic in some situations. The frequency of the superimposed force F corresponds to the number of times the piston 124 strikes the adapter part 136. As mentioned above, the magnitude of the superimposed force F typically corresponds to the full value of the amplitude of the superimposed force F. The superimposed force F may have the magnitude value in many different intervals. However, the superimposed force F is typically less than about four foot-pounds per square inch (5 ft-lb / in 2). In one embodiment, the superimposed force F is in a range of about 1 ft-lb / in 2 to about 4 ft-lb / in 2. In one embodiment, the superimposed force F is in a range of about 1 ft-lb / in 2 to about 5 ft-lb / in 2. In another embodiment, the superimposed force F is in a range of about 1.2 ft-lb / in2 to about 3.6 ft-lb / in2. The penetration rate of the earth drill 102 is increased and decreases in general as the superimposed force is increased and decreased, respectively. However, it is typically not unreasonable to apply a superimposed force to the earth drill 102 with a value that will damage the earth drill 102. It should be noted that the area over which the superimposed force F is applied can be many different areas. For example, in one embodiment, the area above which the superimposed force F is applied by the bottom line to the abutment surface 131 of the adapter part 136 corresponds to (Figure 3f). The frequency of the superimposed force F can have many different values.
For example, in one embodiment, the superimposed force F to 18 is applied to the earth drill 102 at a rate less than about 1500 times per minute. In a particular embodiment, the superimposed force F is applied to the earth drill 102 at a speed in a range of about 1100 times per minute to about 1400 times per minute. The frequency and amplitude of the superimposed force F can be adjusted. The frequency and amplitude of the superimposed force F can be adjusted for several different reasons, such as to adjust the penetration rate of the earth drill 102 into the formation. In one embodiment, the amplitude and / or frequency of the superimposed force F is adjusted in response to an indication of a penetration velocity of the drill 102 through the formation. The indication of the penetration rate of the earth drill 102 through the formation can be accomplished in many different ways. For example, the rate of penetration of the drill 102 through the formation is typically monitored with equipment included with the drill. The penetration rate of the earth drill 102 through the formation is adjusted by adjusting at least one of an amplitude and frequency of the superimposed force F. For example, in one embodiment, the penetration rate of the earth drill 102 through the formation is adjusted by adjusting the amplitude of the superimposed force F. In another example, the penetration rate of the earth drill 102 through the formation is adjusted by adjusting the frequency of the superimposed force F. In another example, the penetration rate of the earth drill 102 through the formation is adjusted by adjusting the frequency and amplitude of the superimposed force F. In one embodiment the amplitude of the superimposed force F is adjusted in response to the indication of the penetration velocity of the earth drill 102 through the formation. In another embodiment, the frequency of the superimposed force F is adjusted in response to the indication of the penetration rate of the earth drill 102 through the formation. In one embodiment, both the frequency and the amplitude of the superimposed force F are adjusted in response to the indication of the penetration rate of the drill 102 through the formation. In this way, the superimposed force F is adjusted in response to an indication of an intrusion velocity of the earth drill 102 through the formation. In general, the superimposed force F is adjusted to drive the penetration speed of the earth auger 102 through the formation ion to a desired penetration rate. The frequency and / or amplitude of the superimposed force is typically increased to increase the penetration rate of the drill bit 102 through the formation. Furthermore, the frequency and / or amplitude of the superimposed force is typically reduced to reduce the penetration rate of the earth drill 102 through the ancient nation. Furthermore, the superimposed force F is typically adjusted to reduce the likelihood of the drill 102 being subjected to any damage. The frequency and amplitude of the superimposed force F can be adjusted in many different ways. In one embodiment, the frequency and amplitude of the superimposed force F are adjusted in response to adjusting the liquid flow through the drill string 106. The frequency and amplitude of the superimposed force F are typically increased and decreased in response to increasing and decreasing liquid flow through the drill string 106. For example, in a embodiment, the frequency and amplitude of the superimposed force F are increased and decreased in response to increasing and decreasing pressures of the air flowing through the drill string 106. It should be noted that in some embodiments the frequency and amplitude of the superimposed force F are automatically adjusted by the equipment of the drill by adjusting the liquid flow. In other embodiments, the liquid flow is adjusted manually to adjust the frequency and amplitude of the superimposed force F. The material flowing out of the drive chamber 141 and the return chamber 140 can be directed to the outer region of the hammer assembly 103 in many different ways, one of which is shown in Figure 6. In this embodiment, the outflow flows through drive outflow ports 142a and 142b and return outflow ports 142c and 142d and into an outflow ring 117. It should be noted that the outflow ring 117 extends radially about the outer periphery of the hammer casing body 110. The outflow flow outflow ring to the outflow ring 117 119 of the hammer assembly, which protrudes through the rear piece 114. When the pressure of the liquid within the outflow ring 117 and the outflow port 119 of the hammer assembly reaches a predetermined pressure level, the non-return valve 115 opens to relieve it.
When the pressure of the liquid within the outflow ring 117 and the outflow port 119 of the hammer assembly is below the predetermined pressure level, the non-return valve 115 remains closed so that it is not relieved. The predetermined pressure level can be adjusted in many different ways, such as by replacing the non-return valve 1 with another non-return valve which has a different pressure level. The non-return valve 1 can be easily replaced because it is placed against the rear end of the male assembly 103. As discussed above, the superimposed force F of the piston 124 is applied to the rotary drill 102 through the adapter part 136. The magnitude of the superimposed force F can be controlled in many different ways. . Then the amount of the superimposed force is controlled by selecting the adapter part 136 to have a desired mass. As the mass of the adapter part 136 increases, the superimposed force transmitted from the piston 124 to the rotary earth drill 102 decreases in response to the return surface 130 engaging the abutment surface 131. In addition, as the mass of the adapter part 136 decreases, more of the superimposed force is transmitted from the piston 124. to the rotary earth drill 102 in response to the return surface 130 engaging the abutment surface 131. In another manner, the amount of the superimposed force is controlled by selecting the piston 124 to have a desired mass. Since the mass of the piston 124 is increased, the more of the superimposed force to the rotary earth drill 102. In addition, when the mass of the piston 124 is reduced, the less of the superimposed force to the rotary earth drill 102 is reduced. The superimposed force applied through the piston 124 can be controlled by check the size of cylinder 113. As the size of cylinder 113 increases, the superimposed force increases as the piston 124 moves a longer distance before engaging the adapter portion 136. As the size of cylinder 113 decreases, the superimposed force decreases as the piston 124 moves over a shorter distance. before engaging the adapter member 136. The superimposed force F applied through the piston 124 can be controlled by controlling the size of the drive chamber 141. As the size of the drive chamber 141 increases, the superimposed force F increases as the liquid pressure in the drive chamber 141 increases more gradually. which increases the length of the movement of the piston 124. A long The length of the motion allows the liquid pressure of the drive chamber 141 to accelerate accelerating the piston 124, which increases the superimposed force F. As the magnitude of the drive chamber 141 decreases, the superimposed force F decreases because the upward motion of the piston 124 is retarded by a faster increasing fluid pressure of the drive chamber 141, which shortens the length of the piston movement and the superimposed force F. The superimposed force F applied through the piston 124 can also be controlled by controlling the size of the return chamber 140. As the size of the return chamber 140 increases, the superimposed force F increases. as the fluid pressure of the return chamber 140 increases more gradually on the forward stroke of the piston 124, allowing large acceleration of the piston 124. As the size of the return chamber 140 decreases, the superimposed force F decreases as the faster increasing fluid pressure of the return chamber 140 decreases the piston 124, which reduces the superimposed the force F. [0082] Den the superimposed force applied through the piston 124 can be controlled by controlling the size of drive gates 122a and 122b. As the size of the drive control ports 122a and 122b increases, the piston 124 applies a greater superimposed force to the adapter portion 136 because more liquid can flow at a higher speed than the central channel 112 to the drive chamber 141. As the size of the drive control ports 122a and 122b decreases, the piston 124 applies a less Superimposed force to the adapter part 136 because less liquid can flow at a slow speed Than the central channel 112 to the drive chamber 141. The frequency of the superimposed force F applied through the piston 124 to the rotary drill 102 through the adapter part 136 can be controlled in many different ways. true. The frequency of the superimposed force F is increased as the superimposed force F is applied through the piston 124 to the rotary earth drill 102 more often, and the frequency of the superimposed force F decreases as the superimposed force F is applied through the piston 124 to the rotary earth drill 102 less often. The frequency that the superimposed force F applies to the adapter part 136 can be controlled by controlling the size of the return control ports 122c and 122d. As the size of the return control ports 122c and 122d increases, the frequency increases because liquid Man the central channel 112 can be led into the return chamber 140 at a higher speed. As the size of the return control ports 122c and 122d decreases, the frequency decreases because liquid from the central channel 112 can be led into the return chamber 140 at a slow speed. The frequency that the superimposed force F applies to the adapter part 136 can be controlled by controlling the size of the return ejection ports 142c and 142d. As the size of the return outflow ports 142c and 142d increases, the frequency increases because liquid from the return chamber 140 can be discharged from the return chamber 140 at a higher speed. As the size of the return outflow ports 142c and 142d decreases, the frequency decreases because liquid from the return chamber 140 can be discharged from the return chamber 140 at a slow speed. The hammer assembly 103 provides many advantages. An advantage provided by the hammer assembly 103 is that the piston 124 applies low energy and high frequency force to the rotary earth drill 102. This is useful for reducing the amount of stress experienced by the rotary earth drill 102. Another advantage provided by the hammer assembly 103 is that there are parallel supplies and outflow flow paths which enables improved air and force control without having to increase the fluid pressure provided by the drill string 106. Furthermore, the amount of force provided by the hammer assembly 103 to the rotary earth drill 102 can be adjusted by adjusting the throttle plate 116 and / or the check valve 115m. The benefit provided by the hammer assembly 103 is adjusted without having to adjust the fluid pressure provided by the drill string 106. Another advantage is that the outflow from the hammer assembly 103 is led out of the hammer assembly 103 toward its rear end and is directed upwardly through the drill tail 105. the opening from the hammer assembly 103 in separating drill cuttings from the drill tail 105. Figure 7a is a perspective view of the adapter part 136 and the rotary earth drill 102 in an ice-coupled condition. The adapter part 136 and the rotary earth drill 102 are in an interconnected state in Figures 2a and 2b. The adapter part 136 and the rotary earth drill 102 are in the grounded state when they are grounded apart. Furthermore, the adapter part 136 and the rotary earth drill 102 are in the interconnected state when they are interconnected. The adapter portion 136 and the rotary drill 102 are repeatably movable between the interconnected and ice-coupled state. The rotary earth drill 102 can be connected to the adapter part 136 in many different ways. In this embodiment, the tool joint 139 and the rotary earth drill 102 comprise trapezoidal tool joint passages 143 and trapezoidal rotary earth bore passages 144, respectively. the ice-coupled state by operatively releasing the trapezoidal tool connection passages 143 and the trapezoidal rotating earth-bore passages 144. In this way, the adapter part 136 and the rotary earth-drill 102 are repeatably movable between interconnected and ice-coupled states. It should be noted that a central channel 151 of the rotary earth drill 102 is in fluid communication with the central channel 112 when the rotary earth drill 102 and the adapter part 136 are interconnected. In this way, liquid flows from the drill string 106 through the drill string nozzle 108 and the central channel 112 to the central channel 151 has the rotary earth drill 102 (Figures 2a and 2b). It should also be noted that an annular surface 159 extends around an opening has the central channel 151 facing the adapter part 136. Furthermore, an annular surface 158 extends around an opening of the central channel 112 facing the rotary earth drill 102. The annular surfaces 158 and 159 rotate toward each other when the rotary earth drill 102 and the adapter portion 136 are in the interconnected state. In some embodiments, the annular surfaces 158 and 159 are spaced apart, and in other embodiments, the annular surfaces 158 and 1591 are engaged with each other, as will be discussed in more detail below. The aisles of the adapter part 136 and the rotary earth drill 102 are complementary to each other, which allows the rotary earth drill 102 and the adapter part 136 to be repeatably movable between interconnected and ice-coupled state. The adapter portion 136 and the rotary earth drill 102 may include many other types of passages in addition to trapezoidal passages. For example, as shown by an indicator arrow 149a, the adapter portion 136 may comprise V-shaped passages 143a and the rotary drill 102 may comprise complementary V-shaped passages. As shown by an indicator arrow 149b, the adapter portion 136 may comprise square passages 143b and the rotary earth drill 102 may comprise complementary square passages. Further, as shown by an indicator arrow 149c, the adapter portion 136 may comprise rope passages 143c and the rotary earth drill 102 may comprise complementary rope passages. More information regarding the passage of the son may be included with the rotary earth drill 102 and the adapter portion 136 provided in U.S. Pat. patent no. 3,259,403, 3,336,992, 4,600,064, 4,760,887 and 5,092,635, as well as U.S. Pat. patent application no. 20040251051, 20070199739 and 20070102198. Figure 7b is a cross-sectional view of the adapter part 136 and the rotary earth drill 102 in interconnected condition. In this embodiment, a line of sight 192 extends through tool connecting passages 143 and rotating earth drill passages 144 when the tool joint 139 and the rotary drill 102 are in the interconnected condition, the aiming line 192 having an angle relativt relative to the centerline 147. extends at an angle 9 relative to the centerline 147. The tool joint 139 is enclosed with the adapter portion 136 so that the adapter portion 136 includes a convex surface which extends at an angle 9 relative to the centerline 147. Further, the rotary drill 102 includes a convex surface which extends at an angle 9 relative to to the center line 147. Angle 9 can have many different angular values. In some embodiments, the angle β is in a range between about one degree (1 °) to about nine degrees (9 °). In some embodiments, angle 9 is in a range between about one and a half degrees (1.5 °) to about eight degrees (8 °). In some embodiments, the angle p is in a range between about three degrees (3 °) to about five degrees (5 °). In a particular embodiment, angle 9 is about four and three quarters of a degree (4.75 °). Angle 9 is generally selected so that the rotary earth drill 102 is positioned in line with the adapter part 136 in response to movement of the rotary earth drill 102 and the adapter part 136 from the disengaged state to the engaged state.
In this way, the rotary auger 102 experiences less oscillation in response to the rotation of the male assembly 103 and the drill string 106. It should be noted that the value of angle 9 affects the amount of rotational energy transferred between the drill string 106 and the rotary auger 102 through the adapter portion 136. The amount of rotational energy transferred between the drill string 106 and the rotary earth drill 102 is increased and decreased as the value of angle 9 increases and decreases, respectively. In this embodiment, the annular surfaces 158 and 159 are separated from each other in response to the fact that the rotary earth drill 102 and the adapter part 136 are in the interconnected state. The annular surfaces 158 and 159 are separated by each other so that the superimposed force F does not flow between the adapter part 136 and the rotary earth drill 102 through the annular surfaces 158 and 159. Instead, a first part of the superimposed force F flows between the adapter part 136 and the rotary earth drill 102 through the The trapezoidal tool connection passages 143 and the trapezoidal rotary earth drill passages 144. The adapter part 136 and the rotary earth drill 102 are interconnected so that radial surfaces 153 and 154 (Figures 7a and 7b) abut each other and form a spruce surface therebetween. The surfaces 153 and 154 are radial surfaces because they extend radially relative to the centerline 147. The radial surfaces 153 and 154 abut each other so that a second portion of the superimposed force F flows between the adapter portion 136 and the rotary drill 102 through the surfaces 153 and 154. [ It should be noted that the superimposed force F flows more efficiently between the adapter part 136 and the rotary earth drill 102 through the surfaces 153 and 154 than through the trapezoidal tool connecting passages 143 and the trapezoidal rotary earth drill passages 144. The superimposed force F experiences more steam in response to the flow through the trapezoidal 26 tool joint passages 143 and the trapezoidal rotary earth bore passages 144 through the surfaces 153 and 154. The superimposed force F experiences less damping in response to the flow through the surfaces 153 and 154 than through the trapezoidal tool joint passages 143 and the trapezoidal rotary earth bore passages 144. put streams it overl the force F is more efficiently agitated through the surfaces 153 and 154 through the trapezoidal tool connecting passages 143 and the trapezoidal rotating earth drill passages 144. It should be noted, however, that the efficiency with which the superimposed force F flows through the trapezoidal tool connecting passages 143 and the trapezoidal rotating earth passages 144 increases and decreases as the angle increases and decreases. It should also be noted that the spruce surface between the adapter part 136 and the rotary earth drill 102 can have many other shapes, of which a snarl will be discussed in more detail. Figure 7c is a cross-sectional view of the adapter portion 136 and the rotary drill 102 in the interconnected state. In this embodiment, the annular surfaces 158 and 1591 are engaged with each other in response to the rotary earth drill 102 and the adapter portion 136 being in the interconnected state. The annular surfaces 158 and 159 are engaged with each other so that a third part of the superimposed force F flows between the adapter part 136 and the rotary drill 102 through the annular surfaces 158 and 159. As mentioned above, the first part of the superimposed force F flows between the adapter part 136 and the rotary auger 102 through the trapezoidal tool connecting passages 143 and the trapezoidal rotary auger passages 144. In this embodiment, the adapter portion 136 and the rotary auger 102 are interconnected so that an outer radial surface 153a wanders toward an outer radial surface 154a, and radial surface 153b winds toward an outer radial surface 154b. The surfaces 153a, 153b, 154a and 154b are radial surfaces because they protrude radially relative to the centerline 147. In addition, the surfaces 153a and 154a are outer surfaces because they are located away from the centerline 147. The surfaces 153a and 154a are located away from the centerline 27 147 because they are located further away from the center line 147 of the surfaces 153b and 154b. The surfaces 153b and 154b are inner surfaces because they are located toward the centerline 147. The surfaces 153b and 154b are located toward the centerline 147 because they are located closer to the centerline 147 than the surfaces 153a and 154a. The surfaces 153a and 153b are spaced apart to form an annular projection 156, and the surfaces 154a and 154b are spaced apart to form an annular projection 157. The annular projections 156 and 157 are located against the inner surfaces 153b and 154b, respectively. The annular projections 156 and 157 are located away from the inner surfaces 153a and 154a, respectively. The inner surfaces 153b and 154b are spaced apart, and the annular projections 156 and 157 are spaced apart to form an annular groove 155. The surfaces 153a and 154a are spaced apart when the adapter portion 136 and the rotary earth drill 102 are in the engaged state, so that the superimposed force F does not flow between the adapter part 136 and the rotary earth drill 102 through the surfaces 153a and 154a. In this way, the superimposed force F is limited than to flow between the adapter part 136 and the rotary earth drill 102 through the surfaces 153a and 154a. Furthermore, the surfaces 153b and 154b are separated from each other when the adapter part 136 and the rotary earth drill 102 are in the engaged state, so that the superimposed force F does not flow between the adapter part 136 and the rotary earth drill 102 through the surfaces 153b and 154b. In this way, the superimposed force F is limited from flowing between the adapter part 136 and the rotary earth drill 102 through the surfaces 153b and 154b. The superimposed force F flows more efficiently between the adapter part 136 and the rotary drill 102 through the surfaces 158 and 159 through the trapezoidal tool connecting passages 143 and the trapezoidal rotating earth drill passages 144. The superimposed force F experiences more steaming in response to the flow through the trapezoidal tool passages. 143 and the trapezoidal rotary earth bore passages 144 through the surfaces 158 and 159. The superimposed force F experiences less evaporation in response to the flow through the surfaces 158 and 159 than through the trapezoidal tool connecting passages 143 and the 28 trapezoidal rotary earth bore passages 144. In this way the superimposed stream flows the force F is more effective through the surfaces 158 and 159 than through the trapezoidal tool connection passages 143 and the trapezoidal rotary earth bore passages 144. Figure 7d is a side view of the trapezoidal rotary earth bore passages 144 in a region 145 of Figure 7b, and Figure 7e is a side view av the trapezoidal tool joints 143 in region 145 of Figure 7b. In region 145 of Figure 7b, the trapezoidal tool joint passages 143 and the trapezoidal rotary earth auger passages 144 are engaged with each other. As shown in Figure 7d, the rotary earth augers 144 include an earth auger 180 and an auger cam 181. In this embodiment, the auger 180 includes a longitudinal rock 185 and conical side rocks 184 and 186. The conical side rockers 184 and 186 extend outwardly. of the longitudinal cradle 185 and toward the centerline 147 (Figure 7b). The longitudinal cradle 185 is parallel to a longitudinal line of sight 192, and perpendicular to a radial line of sight 191. The longitudinal cradle 185 extends at an angle 9 relative to the centerline 147. In this embodiment, the earth drilling root 180 includes a longitudinal side rock bearing 183 and conical side grooves 183. 182. The conical side cradles 182 extend -Iran a spirit of the longitudinal cradle 185 opposite to the conical side cradle 184 and towards the center line 147 (Figure 7d). The longitudinal cradle 183 is parallel to the longitudinal aiming line 192 and the longitudinal cradle 185, and perpendicular to a radial aiming line 191. The longitudinal cradle 183 extends at an angle 9 relative to the centerline 147. The conical side cradles of the trapezoidal rotary earth bore 144s with a non-parallel angle relative to the longitudinal line of sight 192, which will be discussed in more detail below. The rotary earth drill passages 144 have a pitch L2, the pitch L2 being a length along the longitudinal line of sight 192 along which the ground drill gang root 180 and the earth drill gate cam 181 extend. 29 More information regarding the ascent of a gang can be found in the above-cited U.S. Pat. patent application no. 20040251051. As the incline L2 is increased and decreased, the number of passages per unit length of the trapezoidal rotary earth drilling passages 144 increases and decreases, respectively. Furthermore, as the rise L2 increases and decreases, the number of earth auger jugs 181 per unit length increases and decreases, respectively. The path rise L2 can have many different lengths. In some embodiments, the aisle L2 has a length in a range between about a quarter of a turn to about a turn. In some embodiments, the walkway L2 has a length in an interval between about one-half turn to about one turn. In a particular embodiment, the aisle L2 has a length of one eighth of a turn. As mentioned above, the conical side cradles of the trapezoidal rotary earth drill passages 144 extend at a non-parallel angle relative to the longitudinal line of sight 192. In this embodiment, for example, the conical side rock 182 extends at an angle relativt3 relative to the radial line of sight. 191. In addition, the conical side rock 184 extends at an angle 044 relative to the radial line of sight 161.
It should be noted that the conical side cradles of the trapezoidal rotary earth drill bits 144 extend with the same angular size relative to the longitudinal line of sight 192. The angles 03 and 04 can have many different angular values. In some embodiments, the angles e3 and 04 are in a range between about one degree (1 °) to about nine degrees (9 °). In some embodiments, the angles 03 and 04 are in a range between about one and a half degrees (1.5 °) to about eight degrees (8 °). In some embodiments, the angles 03 and 04 are in a range between about three degrees (3 °) to about four degrees (5 °). In a particular embodiment, the angles 03 and 04 are equal to each other by about four and three quarters of a degree (4.75 °). In some embodiments the angles 03 and 04 are equal to each other and, in other embodiments, the angles 03 and 04 are not equal to each other. In some embodiments, the angles 03 and 04 are equal to each other with the angle p and, in other embodiments, the angles e3 and 04 are not equal to the angle cp. It should be noted that the values for the angles 03 and 04 are not shown in scale in Figure 7d. In general, the angles e3 and 04 are chosen to reduce the probability that the rotary earth drill 102 and the adapter part 136 will be spanned together. Furthermore, the angles 03 and 04 are chosen to increase the efficiency with which the superimposed force F is transferred from the hammer assembly 103 to the rotary earth drill 102 through the adapter part 136. In general, the efficiency with which the unobstructed force F is transferred from the hammer assembly 103 to the rotary assembly 102 through the rotation earth drill 102 through the adapter part decreasing as the angles 03 and 04 decrease respectively. It should be noted that the helical angle of the trapezoidal rotary drill bits 144 may have many different angular values. More information regarding the helix angle of a thread can be found in the references above U.S. Pat. patent application no. 20040251051. In some embodiments, the helical angle has the trapezoidal rotary drill bits 144 in a range between about one degree (1 °) to about ten degrees (10 °). In some embodiments, the helical angle has the trapezoidal rotary drill bits 144 in a range between about one and a half degrees (1.5 °) to about four degrees (5 °). In a particular embodiment, the helical angle has the trapezoidal rotary earth drill holes 144 about two and a half degrees (2.5 °). As shown in Figure 7e, the trapezoidal tool connecting passages 143 include a tool connecting root 170 and a tool connecting comb 171. In this embodiment, the tool connecting root 170 comprises a longitudinal rock 175 and conical side rocks 174 and 176 facing the conical sidewalls 174 and 176. spirits of the longitudinal cradle 175 and toward the centerline 147 (Figure 7b). The longitudinal cradle 175 is parallel to the longitudinal aiming line 192, and perpendicular to a radial aiming line 191. The longitudinal cradle 175 extends at an angle p relative to the centerline 147. In this embodiment, the tool connection rootstock 170 includes a longitudinal sidewall 173 and conical ridges 173. 172. The conical side cradles 172 extend from a spirit ay the longitudinal cradle 175 opposite 31 to the conical side cradle 174 and towards the center line 147 (Figure 7b). The longitudinal cradle 173 is parallel to the longitudinal aiming line 192 and the longitudinal cradle 175, and perpendicular to the radial aiming line 191. The longitudinal cradle 173 projects at an angle relative to the centerline 147. The conical side cradles of the trapezoidal tool union bores 14 a non-parallel angle relative to the longitudinal line of sight 192, which will be discussed in more detail below. The trapezoidal tool joint passages 143 have a pitch I-1, the pitch Li being a length along the longitudinal line of sight 192 through which the tool joint gangrene 170 and the tool joint gang cam 171 extend. As the pitch L1 increases and decreases, the number of passages per unit length of the trapezoidal tool joint passages 143 increases and decreases, respectively.
Furthermore, as the pitch L1 increases and decreases, the number of tool connection aisles 171 per unit length increases and decreases, respectively. The gangway L1 can have many different lengths. In some embodiments, the aisle Li has a longitudinal distance in a range between about a quarter of an inch to about a turn. In some embodiments, the ascent L has a longitudinal value in an interval between about one-half turn to about one turn. In a particular embodiment, the riser L1 has a length of one eighth of an inch. It should be noted that the aisles L1 and L2 are generally the same to facilitate the means for repeatedly moving the adapter part 136 and the rotary earth drill 102 between the interconnected and ice-coupled state. As mentioned above, the conical side cradles of the trapezoidal tool joint passages 143 protrude at a non-parallel angle relative to the longitudinal line of sight 192. For example, in this embodiment, the conical side cradle 174 extends at an angle G1 relative to the radial Further, the conical side cradle 176 protrudes at an angle relativt2 relative to the radial line of sight 190. It should be noted that the conical side cradles of the trapezoidal 32 tool joint passages 143 protrude at the same size of the angle relative to the longitudinal aiming line 192. Further generally extends the conical side cradles of the trapezoidal tool joint passages 143 out at the same size of the angle relative to the longitudinal line of sight 192 as the conical side cradles of the trapezoidal rotary earth bore passages 144 to facilitate the shape to repeatably move the adapter portion 136 and the rotary auger 102 between the coupled and ice-coupled state. The angles G1 and 02 can have slightly different angular values. In some embodiments, the angles G1 and O2 are in a range between about one degree (1 °) to about nine degrees (9 °). In some embodiments, the angles Gi and O 2 are in a range between about one and a half degrees (1.5 °) to about eight degrees (8 °). In some embodiments, the angles G1 and 02 are in a range between about three degrees (3 °) to about four degrees (5 °). In a particular embodiment, the angles G1 and O2 are equal to about four and three quarters of a degree (4.75 °). In some embodiments, the angles G1 and O2 are equal to each other, and in other embodiments, the angles G1 and O2 are not equal to each other. In some embodiments, the angles G1 and 82 are equal to the angle p and in other embodiments, the angles G1 and 02 are not equal to the angle cp. It should be noted that the values for the angles G1 and 02 are not shown in scale in Figure 7e. In general, the angles G1 and 02 are chosen to reduce the probability that the rotary earth drill 102 and the adapter part 136 will be spanned together. Further, the angles G1 and O2 are selected to increase the efficiency at which the superimposed force F transfers the hammer assembly 103 to the rotary drill 102 through the adapter portion 136. In general, the efficiency at which the superimposed force F is transferred from the hammer assembly 103 to the rotary assembly 102 through the rotary drill 102 through the adapter portion 136 is unknown. decreasing as the angles G1 and 02 decrease respectively. It should be noted that the angles G1, 02, 03 and 04 all have a true size of the angular value to facilitate the shape to repeatably move the adapter part 136 and the rotary earth drill 102 between interconnected and ice-coupled state. It should also be noted that the helical angle of the trapezoidal tool joints 143 can have many different angular values. In some embodiments, the helical angle of the trapezoidal tool joints 143 is in a range between about one degree (1 °) to about ten degrees (10 °). In some embodiments, the helical angle of the trapezoidal tool joints 143 is in the range of about one and a half degrees (1.5 °) to about four degrees (5 °). In a particular embodiment, the helical angle of the trapezoidal tool joints 143 is about two and a half degrees (2.5 °). It should be noted that the helical angle of the trapezoidal tool connection passages 143 and the trapezoidal rotary earth drill passages 144 is generally the same to facilitate the shape of the receptacle for moving the adapter portion 136 and the rotary auger 102 between interconnected and ice-coupled states. Figure 8a is a flow chart of a method 200, in accordance with the invention, for drilling a slide. In this embodiment, the method 200 comprises a step 201 for providing a rotary drilling system, the rotary drilling system comprising a drive chuck and an adapter member slidably engaged with each other, a rotary earth drill connected to the adapter member, and a piston repeatably movable between engagement and disengaged bearing with adapter part. The adapter part slides relative to the drive chuck in response to the piston movement between disengaged and engaged bearings. The method 200 comprises a step 202 in which a liquid flows through the rotary drilling system so that the piston moves between engaged and disengaged bearings. In this way, the piston moves between the engaged and disengaged position in response to being driven by a liquid. The rotating earth auger moves between the extended and retracted layers in response to the piston being moved between the engaged and disengaged bearings. Figure 8b is a flow chart of a method 210, in accordance with the invention, for drilling a slide. In this embodiment, the method 210 includes a step 211 of providing a rotary drilling system, the rotary drilling system comprising a drive chuck and an adapter member slidably engaged with each other, a rotating earth drill coupled to the adapter member, and a piston repeatably movable between engaged and disengaged bearings. adapter part. The adapter part slides relative to the drive chuck in response to the piston being moved between the disengaged and the engaging stroke. In this embodiment, the piston includes a return piston port located away from the Than adapter portion and a drive piston port located adjacent the adapter portion.
Furthermore, the rotary drilling system may comprise a flow control rudder with a return link port and a drive link port. The return joint port is repeatably movable between a first layer in connection with the return piston port and a second layer not in connection with the return piston port. Furthermore, the drive port is repeatably movable between a first layer in connection with the drive piston port and a second layer not in connection with the drive piston port. Method 210 includes a step 212 of flowing a liquid through the ports of the piston so that it moves between engaged and disengaged bearings. In this way, the piston moves between the engaged and disengaged position in response to being driven by a liquid. The rotating auger moves between the extended and retracted bearings in response to the piston being moved between the engaged and disengaged bearings. Figure 8c is a flow chart of a method 220, in accordance with the invention, for manufacturing a rotary drilling system. In this embodiment, the method 220 includes a step 221 of providing a rotating earth drill and a step 222 of connecting a hammer assembly to the rotating earth drill. In accordance with the invention, the hammer assembly comprises a drive chuck and an adapter part slidably engaged with each other, and a piston repeatably movable between engaged and disengaged bearings with the adapter part. The adapter part slides relative to the drive chuck in response to the piston being moved between disengaged and engaged. The rotating earth drill is connected to the adapter part so that it slides in response to the adapter part sliding. A drill string is connected to the hammer assembly and a liquid floats there. The piston moves between the engaged and disengaged position in response to the flow of the liquid. In this way, the piston moves between the engaged and disengaged position in response to being driven by a liquid. Furthermore, the rotating earth auger moves between the extended and retracted bearings in response to the piston being moved between the engaged and disengaged bearings. Figure 8d is a flow chart of a method 230, in accordance with the invention, for manufacturing a rotary drilling system. In this embodiment, the method 230 includes a step 231 of providing a rotating earth drill and a step 232 of interconnecting a hammer assembly to the rotating earth drill. In this embodiment, the hammer assembly comprises a drive chuck and an adapter part slidably engaged with each other and a piston repeatably movable between engagement and disengaged bearing with the adapter part. The adapter part slides relative to the drive chuck in response to the movement of the piston between disengaged and engaged. In this embodiment, the piston includes a drive piston port located away from the adapter portion and a drive piston port located adjacent the adapter portion. Furthermore, the rotary drilling system may comprise a flow control rudder with a return link port and a drive link port. The return joint port is repeatably movable between a first layer in connection with the return piston port and a second layer not in connection with the return piston port. Furthermore, the drive port is repeatedly movable between a first layer in connection with the drive piston port and a second layer not in connection with the drive piston port. In operation, the piston moves between engaged and disengaged bearings in response to a flood of fluid through the rotary drilling system. In this way, the piston moves between the engaged and disengaged position in response to being driven by a liquid. The rotating earth drill moves between the extended and retracted bearings in response to the piston moving between the engaged and disengaged bearings. It should be noted that method 200 may comprise many other steps, several of which have been discussed in more detail with method 210. Furthermore, method 220 may comprise many other steps, several of which have been discussed in more detail with method 230. It should also be noted that steps in methods 200, 210, 220 and 230 can be performed in many different sequences. Figure 9a is a river diagram of a method 240, in accordance with the invention, for drilling through a formation. In this embodiment, the method 240 comprises a step 241 of providing an earth drill operatively connected to a drilling machine with a drill string, the drilling machine 36 applying a drilling pressure to the earth drill through the drill string. Method 240 includes a step 242 of applying a superimposed force to the drill, the superimposed force being in a range of about one foot-pound per square inch (1 ft-lb / in 2) to about four foot-pounds per square inch (4 ft -lb / in2). The drilling pressure can be in many different ranges. For example, in one embodiment, the drilling pressure is in a range of about 1000 pounds per turn of the Haldian diameter to about 10,000 pounds per square barrel of the Haldian diameter. The superimposed force can be applied to the earth auger in many different ways. For example, in some embodiments, the superimposed force is applied to the earth auger with a male marrow assembly. In these embodiments, the hammer assembly acts in response to a liquid flow through the drill string. It should be noted that method 240 may include many other steps. For example, in some embodiments, the method 240 includes a step of applying the superimposed force to the drill at a rate in a range of about 1100 times per minute to about 1400 times per minute. In some embodiments, the method may comprise a step of adjusting the superimposed force in response to adjusting a liquid flow through the drill string. Method 240 may include a step of adjusting an amplitude and / or frequency of the superimposed force in response to an indication of an intrusion velocity of the drill through the formation. Method 240 may comprise a step of providing an air flow through the drill string at a rate in a range of about 1000 cubic feet per minute (cfm) to about 4000 cubic feet per minute (cfm). Method 240 may comprise a step of providing an air floc through the drill string at a pressure in a range of about forty pounds per square inch (40 psi) to about eighty pounds per square inch (80 psi). Figure 9b is a flow chart of a method 250, in accordance with the invention, for drilling through a formation. In this embodiment, the method 250 includes a step 251 of providing a drill and drill string and a step 252 of operatively coupling an earth drill to the drill through the drill string. Method 250 includes a step 253 of providing an air flow through the drill string at an air pressure in a range of about forty pounds per square inch (40 psi) to about eighty pounds per square inch (80 psi) and a step 254 of applying a superimposed force to 37 the earth drill, the superimposed force being less than about four foot-pounds per square inch (5 ft-lb / in2). The superimposed force can be in many different ranges. For example, in one embodiment, the superimposed force is in a range of about 1 ft-lb / in2 to about 4 ft-lb / in2. It should be noted that method 250 may include many other steps. For example, in some embodiments, the method 250 includes a step of adjusting the superimposed force in response to an indication of an intrusion velocity of the drill through the feed nation. In some embodiments, the method 250 includes a step of adjusting the superimposed force to bring the drive penetration rate of the drill through the formation to a desired penetration rate. The method 250 may comprise a step of adjusting the penetration rate of the drill through the formation by adjusting at least one of an amplitude and a frequency of the superimposed force. The method 250 may comprise a step of applying a drilling pressure to the earth drill through the drill string, the drilling pressure being in a range of about 30,000 pounds to about 130,000 pounds. Figure 9c is a flow chart of a method 260, in accordance with the invention, for drilling through a formation. In this embodiment, the method 260 comprises a step 261 of providing an earth drill operatively connected to a drill with a drill string, the drill applying a drilling pressure to the earth drill and a step 262 of providing an air flow through the drill string at an air pressure less than about eighty pounds per square foot (80 psi). Method 260 includes a step 263 of applying a time-varying superimposed force to the drill, the time-varying superimposed force being less than about four foot-pounds per square inch (5 ftlb / in 2). The time-varying superimposed force can have many different values. For example, in one embodiment, the time varying superimposed force is in a range of about 1.2 ft-lb / in2 to about 3.6 ft-lb / in2. The time-varying superimposed force can be applied to the earth auger in many different ways. For example, in some embodiments, the time-varying superimposed force is applied to the ground with a hammer assembly. It should be noted that Method 260 may include many other steps. For example, in some embodiments, method 260 includes a step of adjusting an amplitude of the time-varying superimposed force in response to an indication of an intrusion velocity of the drill through the formation.
In some embodiments, the method 260 includes adjusting a frequency of the time-varying superimposed force in response to an indication of an intrusion velocity of the drill through the previous nation. While particular embodiments of the invention have been shown and described, a variety of variants and alternative embodiments may occur to those skilled in the art. Accordingly, the intended invention is limited only by the terms of the appended claims.

权利要求:
Claims (21)
[1]
A method of drilling through a formation, comprising: operatively coupling an earth drill to a rotary head through a drill string, the rotary head applying a drilling pressure to the earth drill through the drill string; and applying a superimposed force to the earth drill, the superimposed force being in a range of about one foot pound per square inch (1 ft-lb / in 2) to about four foot pounds per square inch (5 ft-lb / in 2).
[2]
The method of claim 1, further comprising applying the superimposed force to the earth auger at a rate in a range of about eleven hundred (1100) times per minute to about fourteen hundred (1400) times per minute.
[3]
The method of claim 1, further comprising adjusting the superimposed force in response to adjusting a liquid flow through the drill string.
[4]
The method of claim 3, further comprising adjusting an amplitude and / or a frequency of the superimposed force in response to an indication of an intrusion velocity of the drill through the formation.
[5]
The method of claim 1, further comprising providing an air flow through the drill string at a rate in the range of about one thousand cubic feet per minute (1000 cfm) to about four thousand cubic feet per minute (4000 cfm).
[6]
The method of claim 1, further comprising providing an air flow through the drill string at a pressure less than about one hundred pounds per square inch (100 psi).
[7]
The method of claim 1, wherein the drilling pressure is in a range of about one thousand (1000) pounds per square inch of the Haldian diameter to about ten thousand (10000) pounds per square inch of the Hald diameter.
[8]
The method of claim 1, wherein the superimposed force is applied to the earth auger with a male marrow assembly.
[9]
The method of claim 8, wherein the hammer assembly acts in response to a flow of liquid through the drill string.
[10]
A method of drilling through a formation, comprising: providing a drill and a drill string; operatively connecting an earth drill to the drilling machine through the drill string; providing an air flow through the drill string at an air pressure of less than about one hundred pounds per square inch (100 psi); and providing an air flow through the drill string at a rate in the range of about one thousand cubic feet per minute (1000 cfm) to about four thousand cubic feet per minute (4000 cfm).
[11]
The method of claim 10, wherein the superimposed force is in a range of about one pound per square inch (1 psi) to about four pounds per square inch (4 psi).
[12]
The method of claim 10, further comprising adjusting the superimposed force in response to an indication of an intrusion velocity of the drill through the formation.
[13]
The method of claim 10, further comprising adjusting the superimposed force to achieve an undesired intrusion rate.
[14]
The method of claim 10, further comprising adjusting the penetration rate of the drill through the previous nation by adjusting at least one of an amplitude and a frequency of the superimposed force.
[15]
The method of claim 10, further comprising applying a drilling pressure to the earth drill through the drill string, the drilling pressure being in a range of about thirty thousand pounds (30,000 lbs) to about one hundred and thirty thousand pounds (130,000 lbs). 41
[16]
A method of drilling through a formation, comprising: operatively coupling an earth drill to a rotary head with a drill string, the rotary head applying a drilling pressure to the earth drill; providing an air flow through the drill string at an air pressure between about forty pounds per square inch (40 psi) to about one hundred pounds per square inch (100 psi); and providing an air flow through the drill string at a rate in the range of about one thousand cubic feet per minute (1000 cfnn) to about four thousand cubic feet per minute (4000 cfm).
[17]
The method of claim 16, further comprising applying a time varying superimposed force to the drill, the time varying superimposed force being applied at a force less than about four pounds per square inch (5 psi) and a frequency less than about fifteen hundred ( 1500) times per minute.
[18]
The method of claim 17, wherein the time-varying superimposed force is applied to the earth auger with a hammer assembly.
[19]
The method of claim 17, further comprising adjusting an amplitude of the time-varying superimposed force in response to an indication of an intrusion velocity of the drill through the formation.
[20]
The method of claim 17, further comprising adjusting a frequency of the time-varying superimposed force in response to an indication of an intrusion velocity of the drill through the formation.
[21]
The method of claim 17, wherein the time-varying superimposed force is in a range of about 1.2 pounds per square inch (1.2 psi) to about 3.6 pounds per square inch (3.6 psi).

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同族专利:

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公开号 | 公开日

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EA201001323A1|2011-04-29|

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AU2009279628B2|2015-11-12|

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ZA201205688B|2016-09-28|

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BRPI0905374A2|2015-06-30|

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US8627903B2|2014-01-14|

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SE538300C2|2016-05-03|

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CN102016217A|2011-04-13|

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BRPI0905374B1|2019-01-02|

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US8353369B2|2013-01-15|

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MX2010003947A|2010-08-09|

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US20130098684A1|2013-04-25|

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WO2010017367A3|2010-09-30|

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AU2009279628A1|2010-02-11|

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CA2701507A1|2010-02-11|

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PE20100617A1|2010-08-20|

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ZA201002478B|2013-08-25|

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US20100032209A1|2010-02-11|

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CA2701507C|2017-09-19|

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CN102016217B|2015-09-09|

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CL2010000443A1|2010-12-10|

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法律状态:

优先权:

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申请号 | 申请日 | 专利标题

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US8674008P| true| 2008-08-06|2008-08-06|

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US12/536,424|US8353369B2|2008-08-06|2009-08-05|Percussion assisted rotary earth bit and method of operating the same|

---

PCT/US2009/052968|WO2010017367A2|2008-08-06|2009-08-06|Percussion assisted rotary earth bit and method of operating the same|

---