DETAILED ACTION
Notice of Pre-AIA or AIA Status
The present application, filed on or after March 16, 2013, is being examined under the first inventor to file provisions of the AIA .
Priority
Applicant’s claim for the benefit of a prior-filed application under 35 U.S.C. 119(e) or under 35 U.S.C. 120, 121, 365(c), or 386(c) is acknowledged.
Claim Rejections - 35 USC § 103
In the event the determination of the status of the application as subject to AIA 35 U.S.C. 102 and 103 (or as subject to pre-AIA 35 U.S.C. 102 and 103) is incorrect, any correction of the statutory basis (i.e., changing from AIA to pre-AIA ) for the rejection will not be considered a new ground of rejection if the prior art relied upon, and the rationale supporting the rejection, would be the same under either status.
The following is a quotation of 35 U.S.C. 103 which forms the basis for all obviousness rejections set forth in this Office action:
A patent for a claimed invention may not be obtained, notwithstanding that the claimed invention is not identically disclosed as set forth in section 102, if the differences between the claimed invention and the prior art are such that the claimed invention as a whole would have been obvious before the effective filing date of the claimed invention to a person having ordinary skill in the art to which the claimed invention pertains. Patentability shall not be negated by the manner in which the invention was made.
Claim(s) 1-8 and 11-15 is/are rejected under 35 U.S.C. 103 as being unpatentable over US 2015/0107420 A1 to (Webb et al.) in combination with US 8,109,179 B2 to (Richardson).
Regarding claim 1, (Webb et al.) provides a system for torquing or untorquing a tool joint, the system comprising:
a wrench
-“first torque device member body 10 has three clamp bodies 22, 24, 26 that are designed to move between a retracted passive position, wherein the clamp bodies 22, 24, 26 are disengaged from the first pipe 4, and an active extended position, wherein the clamp bodies 22, 24, 26 are in contact with the first pipe 4”; (para. [0072])-
with multiple actuators
-(clamp bodies 22, 24, 26 are moved by their respective clamp actuators 36, 38, 40 to their active positions engaging the first pipe 4; {para. [0082])-
configured to engage a portion of a tubular joint (connection tool joint 2 between a first pipe 4 and a second pipe 6) when the multiple actuators are extended, and a first actuator of the multiple actuators being configured to intensify a first engagement force
-in para. [0137], “The first, second and third clamp actuators 33, 38, 40, here in the form of hydraulic rams, see FIG. 2, are connected to a first flow control valve 216, a second flow control valve 218 and a third flow control valve 220 respectively. The flow control valves 216, 218, 220 are designed to operate over a range of differential pressures… Flow control valves 216, 218 are calibrated to the same flow value, and the third flow control valve 220 is calibrated to a lower flow rate than the first and second flow control valves 216, 218.”); thus, flow control valves 216, 218 (first actuator) have a higher pressure than flow control valve 220 (second actuator).-
In other words, (Webb et al.) provides “a first actuator of the multiple actuators being configured to (capable of) intensify a first engagement force.”
However, (Webb et al.) does not explicitly provide that one of the actuators is configured to intensify a first engagement force applied to the portion of the tubular joint “in response to slippage between at least one of the multiple actuators and the portion of the tubular joint.”
(Richardson) provides a power tong having a main drive, rotary jaw (22) and back-up jaw (24), wherein the rotary jaw preferably has three gripper cylinders (44a, 44b and 44c)(i.e., actuators) arranged radially around the tubular 8 and spaced nominally 120 degrees apart as shown in FIG. 7 (Col. 7, lines 9-13). (Richardson) continues:
-“Hydraulic cylinders 52a-52c (on back-up jaw section 24) are disposed radially inward in an arrangement corresponding to that of cylinders 44a-44c (on rotary jaw 22) so that the operative ends of the actuators which may be selectively actuated telescopically into the center of yoke 40 so as to clamp therein a tubular 8 and in particular a lower portion of a tubular joint while an upper portion of the tubular joint is clamped within cylinders 44a-44c and rotated in rotary jaw section 22 in direction B about axis of rotation A relative to the fixed actuating stages of main drive 10 and back-up jaw section 24.”(Col. 8, lines 43-53) “The rotary jaw hydraulic system 53 is a dual (high/low) pressure system or infinitely variable pressure system which produces high pressures (in the order of 10,000 psi) necessary for adequately gripping large and heavy-duty tubulars…” (Col. 9, lines 22-26) and, in the schematic of the preferred rotary jaw (22) hydraulic system (Fig. 10), “a directional control valve 63 directs hydraulic pressure to the gripper cylinders. The directional control valve is solenoid-actuated with the solenoids controlled by the rotary jaw control system. There are two flow paths from the directional control valve 63 to the extend side of the gripper cylinders. The first is the rapid-advance flow path which directs a large flowrate, in the order of thirty-five gallons per minute, from the pump(s) 36 and accumulator(s) 55 to the gripper cylinders at relatively low pressure, in the order of 2500 psi, for rapid extension of the gripper cylinders until they contact the tubular 8. The second is the high-pressure path in which pressure is regulated by a proportional pressure control valve 64 which is controlled by the rotary jaw control system of FIG. 11. The regulated pressure is supplied to an intensifier 65 which boosts the pressure by a factor in the order of 4:1 to supply high pressure, in the order of 10,000 psi, to the gripper cylinders. A check valve 66 prevents the high pressure fluid from flowing back into the rapid-advance low pressure flow path. The directional control valve 63 can also be solenoid actuated to direct fluid to the rod side of the gripper cylinders for retraction” (Col. 9, lines 44-67 and Col. 10 lines 1-3). “When torquing, the control system monitors the applied torque and controls the grip pressure via proportional pressure control 64 at an appropriate level to avoid slippage of the tubular 8 clamped in the three gripper cylinders. The grip pressure is adaptive according to applied torque which avoids both slippage caused by inadequate pressure and crushing of the tubular 8 caused by excessive pressure.” (Col. 10, lines 8-14)-
Thus, (Richardson) teaches intensifying a first engagement force applied to the portion of the tubular joint in response to slippage between at least one of the multiple actuators and the portion of the tubular joint.
Therefore, it would have been obvious to one having ordinary skill in the art at the time of the effective filing date of the invention to have modified the hydraulic control circuit, e.g., Fig. 23, of (Webb et al.) by providing at least one directional control valve with two flow paths from the directional control valve(s), one of which being the rapid-advance flow path with relatively low pressure, and the other path is the high-pressure path in which pressure is regulated by a proportional pressure control valve 64, as taught by (Richardson), and having the predictable result of controlling the grip pressure at an appropriate level to avoid slippage of the tubular clamped in the three gripper cylinders.
Regarding claim 2, in the combination of (Webb et al.) and (Richardson) as applied to claim 1, the multiple actuators comprise a second actuator that is configured to intensify a second engagement force applied to the portion of the tubular joint in response to slippage between either one of the first actuator or the second actuator, and the portion of the tubular joint - both (Webb et al.) and (Richardson) provide three actuators, thus it would have been obvious to apply the intensifying force to any one of the three actuators relative to the others.
Regarding claim 3, in the combination of (Webb et al.) and (Richardson) as applied to claim 2, the multiple actuators comprise a third actuator that is configured to apply a third engagement force to the portion of the tubular joint, and wherein the third engagement force is greater than either one of the first engagement force or the second engagement force - both (Webb et al.) and (Richardson) provide three actuators, thus it would have been obvious to apply the intensifying force to any one of the three actuators relative to the others.
Regarding claim 4, in the combination of (Webb et al.) and (Richardson) as applied to claim 3, (Webb et al.) provides a pressure equalizer
-“The flow valves 216, 218, 220 are supplied with hydraulic fluid through a supply line 222 that receives fluid through a pressure reducing valve 224. The clamping sequence terminates when no flow is detected through the pressure reducing valve 224. The pressure set at the reduction valve 224 and present after the flow control valves 216, 218, 220 is equivalent to the desired clamp force.”; para. [0139])-
that substantially equalizes a first pressure to a second pressure, wherein the first pressure is applied to the first actuator and the second pressure is applied to the second actuator.
Regarding claim 5, in the combination of (Webb et al.) and (Richardson) as applied to claim 4, (Richardson) provides a pressure equalizer (proportional control valve 64)(Col. 9, lines 60-62) that “substantially equally” increases the first pressure and the second pressure in response to the slippage of either one of the first actuator or the second actuator
-“When torquing, the control system monitors the applied torque and controls the grip pressure via proportional pressure control valve 64 at an appropriate level to avoid slippage of the tubular 8 clamped in the three gripper cylinders. The grip pressure is adaptive according to applied torque which avoids both slippage caused by inadequate pressure and crushing of the tubular 8 caused by excessive pressure.” (Col. 10, lines 36-42)-
Regarding claim 6, in the combination of (Webb et al.) and (Richardson) as applied to claim 4, in (Richardson) a valve (check valve 66) selectively blocks fluid from flowing away from the pressure equalizer (proportional control valve 64), such that the fluid is trapped in the pressure equalizer, the first actuator, and the second actuator, (Col. 9, lines 66-67) and the trapped fluid causes the first pressure and the second pressure to increase in response to the slippage of either one of the first actuator or the second actuator
-“It can be seen that in spite of the small input power, the hydraulic system can intermittently supply large flowrates for rapid grip cylinder advance and high pressures for high-torque operations. The system can regulate the grip pressure, adapting to the applied torque, for optimum gripping performance.
The rotary jaw control system seen in FIG. 11 activates and de-activates the gripper cylinders at the operator's discretion, regulates grip pressure and monitors system function without any power supply or control wires…” (Col. 10, lines 15-24)-
Regarding claim 7, (Webb et al.) provides a system for torquing or untorquing a tool joint, the system comprising:
a torque wrench
-“first torque device member body 10 has three clamp bodies 22, 24, 26 that are designed to move between a retracted passive position, wherein the clamp bodies 22, 24, 26 are disengaged from the first pipe 4, and an active extended position, wherein the clamp bodies 22, 24, 26 are in contact with the first pipe 4” (para. [0072])-
with multiple actuators
-“clamp bodies 22, 24, 26 are moved by their respective clamp actuators 36, 38, 40 to their active positions engaging the first pipe 4” {para. [0082])-
configured to engage a tubular joint (connection tool joint 2 between a first pipe 4 and a second pipe 6) when the multiple actuators are extended (connection tool joint 2 between a first pipe 4 and a second pipe 6), the torque wrench being configured to rotate at least a portion of the tubular joint about a center axis when engaged with the portion of the tubular joint (Abstract and para. [0002]), and at least one of the multiple actuators being configured to intensify an engagement force
-in para. [0137], “The first, second and third clamp actuators 33, 38, 40, here in the form of hydraulic rams, see FIG. 2, are connected to a first flow control valve 216, a second flow control valve 218 and a third flow control valve 220 respectively. The flow control valves 216, 218, 220 are designed to operate over a range of differential pressures… Flow control valves 216, 218 are calibrated to the same flow value, and the third flow control valve 220 is calibrated to a lower flow rate than the first and second flow control valves 216, 218.”); thus, flow control valves 216, 218 (a first actuator) have a higher pressure than flow control valve 220 (a second actuator), i.e., “a first actuator of the multiple actuators being configured to (capable of) intensify a first engagement force.”-
In other words, (Webb et al.) provides “a first actuator of the multiple actuators being configured to (capable of)
intensify a first engagement force.”
However, (Webb et al.) does not explicitly provide that one of the actuators is configured to intensify a first engagement force applied to the portion of the tubular joint “in response to slippage between at least one of the multiple actuators and the portion of the tubular joint.”
(Richardson) provides a power tong having a main drive, rotary jaw (22) and back-up jaw (24), wherein the rotary jaw preferably has three gripper cylinders (44a, 44b and 44c)(i.e., actuators) arranged radially around the tubular 8 and spaced nominally 120 degrees apart as shown in FIG. 7(Col. 7, lines 9-13).
-“Hydraulic cylinders 52a-52c (on back-up jaw section 24) are disposed radially inward in an arrangement corresponding to that of cylinders 44a-44c (on rotary jaw 22) so that the operative ends of the actuators which may be selectively actuated telescopically into the center of yoke 40 so as to clamp therein a tubular 8 and in particular a lower portion of a tubular joint while an upper portion of the tubular joint is clamped within cylinders 44a-44c and rotated in rotary jaw section 22 in direction B about axis of rotation A relative to the fixed actuating stages of main drive 10 and back-up jaw section 24.”(Col. 8, lines 43-53) “The rotary jaw hydraulic system 53 is a dual (high/low) pressure system or infinitely variable pressure system which produces high pressures (in the order of 10,000 psi) necessary for adequately gripping large and heavy-duty tubulars…” (Col. 9, lines 22-26) and, in the schematic of the preferred rotary jaw (22) hydraulic system (Fig. 10), “a directional control valve 63 directs hydraulic pressure to the gripper cylinders. The directional control valve is solenoid-actuated with the solenoids controlled by the rotary jaw control system. There are two flow paths from the directional control valve 63 to the extend side of the gripper cylinders. The first is the rapid-advance flow path which directs a large flowrate, in the order of thirty-five gallons per minute, from the pump(s) 36 and accumulator(s) 55 to the gripper cylinders at relatively low pressure, in the order of 2500 psi, for rapid extension of the gripper cylinders until they contact the tubular 8. The second is the high-pressure path in which pressure is regulated by a proportional pressure control valve 64 which is controlled by the rotary jaw control system of FIG. 11. The regulated pressure is supplied to an intensifier 65 which boosts the pressure by a factor in the order of 4:1 to supply high pressure to the gripper cylinders applied to the portion of the tubular joint in response to slippage between at least one of the multiple actuators and the portion of the tubular joint. A check valve 66 prevents the high pressure fluid from flowing back into the rapid-advance low pressure flow path. The directional control valve 63 can also be solenoid actuated to direct fluid to the rod side of the gripper cylinders for retraction” (Col. 9, lines 44-67 and Col. 10 lines 1-3). “When torquing, the control system monitors the applied torque and controls the grip pressure via proportional pressure control 64 at an appropriate level to avoid slippage of the tubular 8 clamped in the three gripper cylinders. The grip pressure is adaptive according to applied torque which avoids both slippage caused by inadequate pressure and crushing of the tubular 8 caused by excessive pressure.” (Col. 10, lines 8-14)
Thus, (Richardson) teaches intensifying a first engagement force applied to the portion of the tubular joint in response to slippage between at least one of the multiple actuators and the portion of the tubular joint.
Therefore, it would have been obvious to one having ordinary skill in the art at the time of the effective filing date of the invention to have modified the hydraulic control circuit, e.g., Fig. 23, of (Webb et al.) by providing at least one directional control valve with two flow paths from the directional control valve(s), one of which being the rapid-advance flow path with relatively low pressure, and the other path is the high-pressure path in which pressure is regulated by a proportional pressure control valve 64, as taught by (Richardson), and having the predictable result of controlling the grip pressure at an appropriate level to avoid slippage of the tubular clamped in the three gripper cylinders.
Regarding claim 8, in the in the combination of (Webb et al.) and (Richardson) as applied to claim 7, (Webb et al.), as discussed previously, provides a force equalizer (Flow control valves 216, 218 are calibrated to the same flow value)(para. [0137]) that ensures that a first actuator and a second actuator of the multiple actuators each apply a first engagement force when the first actuator and the second actuator are extended.
Regarding claim 11, in the in the combination of (Webb et al.) and (Richardson) as applied to claim 8, in (Richardson), the hydraulic circuitry is configured to supply equalized pressure to input ports of the first actuator and the second actuator and trap the equalized pressure at the input ports, and wherein the equalized pressure is increased in response to the slippage
-“It can be seen that in spite of the small input power, the hydraulic system can intermittently supply large flowrates for rapid grip cylinder advance and high pressures for high-torque operations. The system can regulate the grip pressure, adapting to the applied torque, for optimum gripping performance.
The rotary jaw control system seen in FIG. 11 activates and de-activates the gripper cylinders at the operator's discretion, regulates grip pressure and monitors system function without any power supply or control wires…” (Col. 10, lines 15-24)-,
and wherein a check valve (check valve 66) in the hydraulic circuitry prevents hydraulic fluid to flow away from the input ports, when the first actuator and the second actuator are extended (Col. 9, lines 66-67).
Regarding claims 12 and 13, in the combination of (Webb et al.) and (Richardson) as applied to claim 7, both (Webb et al.) and (Richardson) provide a first actuator, a second actuator, and a third actuator, and wherein the first actuator and the second actuator are circumferentially spaced away from the third actuator by an arc distance (See Figs. 1, 2, 6, and 11-15 in (Webb et al.); and, Figs. 7 and 8 in (Richardson)); wherein the arc distance is selected from a range of arc distances from 110 degrees up to 160 degrees (Figs. 1, 2, 6, and 11-15 in (Webb et al.); and, “spaced nominally 120 degrees apart as shown in Fig. 7”; Col. 7, lines 9-12 in (Richardson).
Regarding claims 14 and 15, in the combination of (Webb et al.) and (Richardson) as applied to claim 7, since (Webb et al.) teaches in paras. [0137], “The first, second and third clamp actuators 33, 38, 40, here in the form of hydraulic rams, see FIG. 2, are connected to a first flow control valve 216, a second flow control valve 218 and a third flow control valve 220 respectively. The flow control valves 216, 218, 220 are designed to operate over a range of differential pressures… Flow control valves 216, 218 are calibrated to the same flow value, and the third flow control valve 220 is calibrated to a lower flow rate than the first and second flow control valves 216, 218.”); and, (Richardson) teaches “…the control system monitors the applied torque and controls the grip pressure via proportional pressure control 64 at an appropriate level to avoid slippage of the tubular 8 clamped in the three gripper cylinders. The grip pressure is adaptive according to applied torque which avoids both slippage caused by inadequate pressure and crushing of the tubular 8 caused by excessive pressure.” (Col. 10, lines 8-14), it would have been obvious to perform a method for torquing or untorquing a tool joint, the method comprising: engaging a portion of a tubular joint with a plurality of actuators; applying a first engagement force to the portion of the tubular joint via a first actuator of the plurality of actuators; and intensifying the first engagement force in response to slippage between at least one of the plurality of actuators and the portion of the tubular joint; further comprising: applying a second engagement force to the portion of the tubular joint via a second actuator of the plurality of actuators; and intensifying the second engagement force in response to slippage between either one of the first actuator or the second actuator, and the portion of the tubular joint.
Allowable Subject Matter
Claims 9, 10 and 16-20 are objected to as being dependent upon a rejected base claim, but would be allowable if claims 9 and 16 are rewritten in independent form including all of the limitations of the base claim and any intervening claims.
The following is a statement of reasons for the indication of allowable subject matter: regarding claim 9, that a third actuator of the multiple actuators applies a second engagement force when the third actuator is extended, and wherein the second engagement force is higher than the first engagement force; and, regarding claim 16, the step of applying a third engagement force to the portion of the tubular joint via a third actuator of the plurality of actuators, and wherein the third engagement force is greater than either one of the first engagement force or the second engagement force, has neither been disclosed nor suggested by the prior art of record considered as a whole, alone, or in combination.
Conclusion
The prior art made of record and not relied upon is considered pertinent to applicant's disclosure as describing numerous hydraulic systems utilized in the field of drilling and processing of wells..
Any inquiry concerning this communication or earlier communications from the examiner should be directed to David B. Thomas whose telephone number is (571) 272-4497. The examiner’s e-mail address is: dave.thomas@uspto.gov. The examiner can normally be reached on Mon-Fri 11:30-7:30.
If attempts to reach the examiner by telephone are unsuccessful, the examiner’s supervisor, David Posigian can be reached on (313) 446-6546. The fax phone number for the organization where this application or proceeding is assigned is (571) 273-8300.
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/David B. Thomas/
Primary Examiner, Art Unit 3723
/DBT/