US2693084A

US2693084A - Rate of change and weight on bit automatic drilling control system

Info

Publication number: US2693084A
Application number: US379791A
Authority: US
Inventors: Algernou S Badger
Original assignee: Standard Oil Development Co
Current assignee: Standard Oil Development Co
Priority date: 1953-09-14
Filing date: 1953-09-14
Publication date: 1954-11-02
Anticipated expiration: 1971-11-02

Description

Nov. 2, 195 1 A. S. BADGER RATE OF CHANGE AND WEIGHT ON BIT AUT 2,693,084 OMATIC DRILLING CONTROL SYSTEM 2 Sheets-Sheet 1 Filed Sept. 14, 1953 r0 TAL Isle/1 r 4 IR SUPPL Y All? SUPPLY IR SUPPLY 4m suPPLr IIYDRAULIC uh:

III! 717 INVENTOR. Algernon 5. Badgefr; BY fi &

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2,693,084 Patented Nov. 2, 1954 RATE OF CHANGE AND WEIGHT ON BIT AUTO- MATIC DRILLING CONTROL SYSTEM Algernon S. Badger, Houston, Tex., assignor, by mesne assignments, to Standard Oil Development Company, Elizabeth, N. .L, a corporation of Delaware Application September 14, 1953, Serial No. 379,791

4 Claims. (Cl. 60-97) to the art for controlling the rate at which the drawworks is allowed to rotate, this in turn controlling the rate at which the drill string is lowered. Hydraulically controlled systems fordrilling oil wells are disclosed in U. S. Patents 1,831,437, Brantly, November 10, 1931, 2,133,016, Brantly, October 11, 1938, and 2,489,449, Crookston, November 29, 1949.

The present system is particularly adapted for regulating the flow of hydraulic fluid through a hydraulic valve which in turn controls the rate of rotation of the drawworks drums in accordance with variation in the fluid pressure in a weight indicator which is attached to a drilling line and indicates the tension being exerted thereon.

Other objects and advantages in the present invention will be seen from the following description taken in conjunction with the drawing in which Fig. 1 is in the form of a schematic flow sheet incorporating an embodiment of the present invention and its purpose in operation;

Fig. 2 is in the form of an elevation partly in section showing details of construction of one of the assemblies of Fig. 1; and

Fig. 3 is a view taken along line 3-3 of Fig. 2.

' Turning now specifically to the drawing a valve body A'has valve elements B and C arranged therein. Fluid motor means for actuating the valve elements are D, E, F, and G. A specific design showing valve body 'A, members B and C and fluid motor means F and G is de scribed and claimed in U. S. Patent No. 2,665,713, issued Jan. 12:, 1954, in the names of Robert R. Crookston and Arthur I. Seljos.

H is a weight on bit indicating and signalling apparatus. Suitable apparatus for this purpose is described and claimed in the copending U. S. application, Serial No.

242,301, filed in the name of Arthur I. Seljosv and Algernon S. Badger, August 17, 195 1. Diaphragm valve assemblies J and K are operatively connected to assembly H. Diaphragm assembly I is connected to fluid motor elements F and G. Diaphragm assembly K is connected through interrupter assembly L to fluid motor D and 7 through interrupter assembly M to fluid motor E.

In the drawing compressed air is furnished by a source not shown. For convenience, the compressed air lines be pistons slidingly arranged within the body A and cooperating therewith to form chambers 17 and 18, respectively. Thus, when the pressure in chamber 17 is sulficient to overcome both the pressure eXertedin chamber 18 and the tension of the spring 16, valve C will move to the rightas viewed in the drawing. However, when the pressure in chamber 18 1s sufflcient to overcome both the supplied with the compressed air are designated by the common reference3=number 10.

Hydraulic valve body A is provided with a hydraulic fluid inlet 11 and a hydraulic fluid outlet 12. The flow of fluid through the body is controlled by the two cooperating valve elements B and C. Valve element B is carried by a valve stem 13 which. in turn carries a gear or toothed. wheel 14 so that the position of element B and valve body A is altered by rotation of gear 14. Valve C is carried by piston rod 15 which is biased to a predetermined central position by spring 16 and 16'. Mounted on piston rod 15 are fluid motor elements F and G. As shown in the drawing, members F and G may -be engaged with the drilling line 31.

pressure exerted in chamber 17 and the tension in spring 16, valve C will move to the left as viewed in the drawing.

Fluid motors D and E are arranged to rotate gear 14. The construction of these motors is identical so that the separate parts making them up are designated by identical reference numbers. In each motor a housing 20 has arranged therein a piston 21 carrying a piston rod 22. Piston rod 22 projects a substantial distance below the housing and terminates in a pivoted ratchet 23. The piston and housing define a chamber 24 with a fluid inlet 25 for said chamber. A spring 26 embraces piston rod 22 and exerts a bias on the piston toward the head end of housing 20. It will be seen that fluid motor D is arranged to rotate gear 14 in the clockwise direction as viewed in the drawing while fluid motor E is arranged to rotate gear 14 in counterclockwise direction as viewed in the drawing.

The assembly H consists of a clamp 30 adapted to Clamp 30 is operatively connected by a hydraulic conduit or line 32 to controller housing 33. As heretofore explained, a suitable design for assembly H is described and claimed in copending U. S. application, Serial No. 242,301. In order to simplify the drawing the interior construction of housing 33 is not shown, but as a suitable construction housing 33 may contain diaphragms arranged so that the hydraulic fluid in line 32 is balanced against compressed air introduced from line 10 through regulator 34 and line 35 to housing 33. A valve schematically indicated by rectangle 36 is controlled by said dia phragm arrangement and in turn controls the How of compressed air from line 10 through inlet line 37 which is connected with a manifold N. A compressed air gauge 38 connected to line 37 indicates the total weight on it.

The assemblies J and K are identical in construction. In Fig. 2 and Fig. 3 details of construction of assembly I are shown, but it will be understood that assembly K has an identical construction and thus the component parts will be designated by identical reference numbers. Each assembly J and K may be considered as consisting of first and second valves with fluid motor means capable of separately actuating the valves to release compressed air to the atmosphere.

Turning now specifically to Figs. 2 and 3, in assembly I a housing 4t) has arranged therein a pair of

diaphragms

41 and 42. The center portions of the diaphragms are secured together by a rod 43. Between diaphragm 41 and the housing is a chamber 44 with access thereto provided by inlet port 45. A spring 46 is arranged within chamber 44. Similarly, at the other end of the housing between diaphragm '42 and the end of the housing is a chamber 47 with access to the chamber provided by inlet port 48. A spring 49' is arranged between the housing and diaphragm 42. It will be seen that the springs 46 and 49 are arranged in opposition and tend to maintain the

diaphragms

41 and 42 in a predetermined central position. However, when the pressure in chamber 44 is suflicient to overcome the pressure in chamber 47 plus the force of spring 49, rod 43 will move to the right as viewed in the drawing. Similarly, when the pressure in chamber 47 is suflicient to overcome the pressure in chamber 44 plus the force exerted by spring 46, diaphragm 42 will move rod 43 to the left as viewed in the drawing. Within housing is a central partition 50 at the side of which is a passage 51 having an outlet 521 and at the other side of which is a passage 53 having an outlet 54. An inlet port 55 leads into partition 50 and terminates in a valve seat 56. Another inlet port 57 enters partition 50 and terminates in a valve seat 58. A valve closure means 59 is biased against valve seat 56 by spring 60 and similarly a valve closure 61 is biased against seat 58 by spring 62. A tripping mechanism 63, which may be a washer, is carried by rod 43 so that upon movement of the rod to the right as viewed in the drawing member 58 is moved away from valve seat 56 and allows the passage of fluid from inlet 55 through seat 56 and out through port 52. A similar valve tripping mechanism 64 is also carried by rod 43 and upon movement of valve rod to the left tripping mechanism 64 moves closure element 61 away from valve seat :58 and allows the passage of fluid from inlet 57 through seat 58 and out through opening 54.

Port 55 of assembly I is connected to line 57 is connected to line 71. line 73 to a regulator 72 which may be set by hand to any desirable amount. The inlet of regulator 72 is connected to compressed air inlet line 10. A compressed air gauge 74 is connected to line 73 by connecting line 7 and port Manifold N is connected through branch line 80 to port 48 of assembly I, through branch 81 to the outlet of a piston controlled valve 0, through branch line 83 to piston controlled valve P, through branch line 85 to an orifice member 86 and through branch line 87 to chamber 44 of assembly K. The chamber 47 of assembly K is connected through line 88 and brane-h line 89 to volume 76 through line 88 and branch line 77, to orifice member 86, through line 88 and branch line 90 to the inlet of piston operated valve P and through line 88 and branch line 91 to the inlet of piston operated valve 0. In assembly K inlet port 55 is connected to compressed air line 92 and inlet port 57 is connected to compressed air line 93. valve 0 is connected by branch line 94 to line 70 and the air actuated piston of valve P is connected by branch line 95 to line 71.

Line 70 connects port 55 of assembly I with chamber 17 of housing A. Compressed air is supplied to line 70 from compressed air line through orifice member 100 and line 101 controlled by hand operated valve 102. Line 71 connects inlet port 57 of assembly I with chamber 18 of housing A. Air is supplied to line 71 from compressed air supply line 10, through orifice member 103 and line 104 controlled by hand operated valve 105.

Line 93 connects the port 57 of assembly K to an inlet side of double check valve 120. The other inlet of double check valve 120 is connected through line 115 and three-way valve 116 to compressed air supply line 10. Compressed air is introduced into line 93 from compressed air supply line 10 by way of orifice member 111 and branch line 112. The outlet side of double check Valve .128 is c nnected throu h line 121 to interrupter assembly L. The outlet line 122 of interrupter assembly L is connected through port 25 to chamber 24 to fluid motor assembly D.

Line 92 connects port 55 of assembly K with an inlet side of double check valve 123. The other inlet of double check valve 123 is connected through line 115 and three-way valve 116 to compressed air supply line 10. Compressed air is introduced into line 92 from compressed air supply line 10 by way of orifice member 113 and branch line 114.

The three-way valve 116 causes the control mechanism to be deactivated when it is set to deliver line pressure to

valves

120 and 123. respectively. When the system is operating, valve 116 is set to connect the inlet sides of

valves

120 and 123, to which it is connected, to the atmosphere.

The outlet of double check valve 123 is connected throu h line 124 to interrupter assembly M. The outlet line 125 of interrupter assembly M is c nnected to port 25 and chamber 24 of fluid motor assembly E.

The interrupter assemblies L and M are identical and for convenience corresponding parts will be designated by identical reference numbers. Q is a conventional four-way bleeder type piston operated valve and R is Port 45 is connected byv The air actuated piston of supplied to the inlet of valve a conventional three-way bleeder type piston operated valve. Compressed air is supplied to the inlet of valve Q from compressed air line 10. Valve Q has delivery ports 129 and 130. A double check valve 132 has its outlet connected through line 133 to the operating piston of valve 0. Inlet port 134 of double check valve 132 serves as the inlet for assembly L. The other inlet port of valve 132 is connected to line 135. which in turn connects to one side of orifice member 136 and through branch line 137 to a chamber 138. Orifice member 136- is connected through line 139 to the delivery port of valve R. Delivery line 131. connects delivery port 130 of valve Q to one side of orifice member 140. The other side of orifice member 140 is connected through line 141 to chamber 142 and through branch line 143 to the operating piston of valve R. Compressed air is R by compressed air line 10.

The action of interrupter L will now be described. Compressed air is supplied from compressed air line 10 and flows through orifice member 111 and branch line 112 to line 93. Normally this compressed air will flow through double check valve and line 121, through inlet port 134 of double check valve 132 and through line 133 to the actuating piston of valve Q. As long as a predetermined pressure is imposed on the actuating piston of valve Q, this actuating piston remains in its down position. When the actuating piston of valve Q is in its down position, compressed air is delivered to outlet port 129 and air is bled from port 130. However, if the pressure is bled from actuating piston of valve Q (as by actuating assembly K to bleed airfrom line 93 through double check valve 120 and line 121), this reduces the pressure imposed on the actuating piston of valve Q and allows it to assume its up position. When the actuating piston of valve Q is in its up position, air is bled from port 129 and is delivered to port 130. The bleeding of air through port 129 reduces the pressure in the fluid make an upstroke. At the same time air is being bled through port 129 of valve Q, compressed air is being delivered through port 130, line 131, orifice member 140 and the actuating piston of valve R. The arrangement of orifice member 140 and chamber 142 introduces a time delay which is predetermined by the selection of the size of orifice in member 140 and the volume of chamber- 142 and the volume of the operating piston of valve R.; After the predetermined time delay, air pressure builds up in the actuating piston of valve R to a sufficientv extent to cause this normally closed valve to open,-which..

in turn allows air from compressed air line '10 to pass through valve R, line 139 and orifice member 136 andthen by branch line 137 to 'chamber'138 and through? double check valve 132 to the actuating piston' of valve The arrangement of orifice member 136 and chamber 138 introduces a time delay which is predeterminedr by the size of orifice in member 136, the size of chamberv 138 and the size of the actuating piston of valve Q. After this predetermined time delay, the'pre'ssure;.-

builds up in the actuating piston of 'valve Q to a sixthcient extent to force the piston down, which inturn causes compressed air to be delivered to port 129 and. air to be bled from port 130. The delivery of com-" pressed air to port 129 in turn suppliescompressed airto fluid motor D and causes the plunger in fluid motor D to be forced downward thus completing one cycle'of' operation of fluid motor D. The bleeding of air froml.

port withdraws air through line 131, orifice member 140, chamber 142 and the operating piston of valve assumes its normally closed position.

inlet 134. The compressed airpressure imposed on inlet port 134 of check valve 132 then takes command. If air is still being bled from line 121 (as by actuation of assembly K), the cycle will repeat.

As viewed in the drawing, the actuation of fluid motor D causes gear 14 and valve stem 13 to rotate in a clockwise direction. The actuation of fluid motor E causes gear 14 and valve stem 13 to rotate in the counterclockwise direction. For convenience in describing the invention, it may be assumed that when gear 14 is. rotated in the clockwise direction, it causes valve element B to reduce the area of flow through the valve body A and when it is rotated in the counterclockwise directiomfit increases the area of flow through valve body A.

The operation of interrupter L and fluid motor D has been described in detail. Interrupter M and fluid motor E operate in identical manner, except that whereas fluidmotor D causes gear 14 to rotate in a counterclockwise motor D and allows this motor to line 141 to chamber 142 and through line 143 to direction and reduce the area of flow through the valve body A, fluid motor B when actuated through interrupter M, causes gear 14 to rotate in the counterclockwise direction and increase the area of flow of valve body A. Port 55 of assembly I is connected through line 70 with chamber 17 of valve body A. Port 57 of assembly I is connected through line 71 to chamber 18 of valve body A. Valve element C is carried on piston rod 15 upon which are mounted fluid, motor elements F and G. For convenience in describing the invention, it will be assumed that when valve element C moves: to the left, as viewed in the drawing, the area of flow in valve body A is reduced and that when valve element C is moved to the right, the area of flow through the valve body A is increased.

If suflicient air is bled from outlet 52 (Fig. 2) 01 assembly I to reduce the pressure in line 70 (which is connected to chamber 17) to such an extent that the pressure in chamber 18- overcomes the force of spring 16 and pressure in chamber 17, valve element C moves to the left, as seen in of flow through valve air is being bled from chamber 17 by means of line 70 and outlet 52, it is also bled by way of line '70 and;

branch line 94 from the actuating piston of valve 0, which in turn causes this valve to open and lay-pass the orifice member 86. This actuation of valve 0, causing orifice member 86 to be lay-passed, inactivates assembly K, inasmuch as it allows the pressure imposed on the diaphragms 40 and 41 to be equalized. Thus, when assembly I takes command in bleeding air from line 70, it inactivates assembly K as well as activating fluid motor element F.

As compressed air is bled from outlet port 54 of assembly K, it bleeds air from line 71 and chamber 18. When the pressure in chamber 18 becomes reduced to such an extent that the pressure in chamber 17 is able to overcome the force of spring 16' and pressure in chamber 18, the fluid motor element G moves to the right, as viewed in the drawing, causing valve member C to move to the right and increasing the area of flow through valve body A. At the same time that air is being bled from chamber 18 of valve body A by way of line 71, pressure is also being bled through branch line 95 and line 71 from the actuating piston of valve P, thereby causing this normally closed valve to open. When valve P opens, it bypasses orifice member 86. Thus, when assembly I actuates fluid motor element G by bleeding off the pressure from chamber 18 by way of line 71, it also inactivates assembly K by bleeding off pressure from the operating piston of valve P, allowing this valve to open, which in turn equalizes the pressure imposed against diaphragms 40 and 41 of assembly K.

From the foregoing description, it will be seen that the control assembly of the present application includes a valve body with first and second cooperating movable valve members. First and second fluid motor means control the position of the first valve member and third and fourth fluid motors control the position of the second valve member. A first assembly consists of first and second compressed air valves, actuated by a fifth fluid motor. These first and second compressed air valves are fluidly connected to said first and second fluid motor means and said fifth fluid motor is arranged to be actuated in response to changes in the pressure of fluid in a selected chamber (specifically a drilling line weight indicator). A second assembly consisting of third and fourth compressed air valves arranged to be actuated by a sixth fluid motor means has said third and fourth air valve fluidly connected to said third and fourth fluid motors respectively. Said sixth fluid motor is arranged to be actuated by changes in the pressure in said selected chamber. Means is provided to inactivate the sixth fluid motor of said second assembly when the fifth fluid motor of the first assembly actuates either the first or second compressed air valve.

While a specific embodiment of the present invention has been shown and described, it will be obvious to a workman skilled in the art that various changes may be made without departing from the scope of the invention.

I claim:

1. A control system comprising, in combination, a valve body, first and second cooperating movable valve members in said valve body for altering the area of flow through said valve body, a first fluid motor operatively connected to the first valve member for giving it movethe drawing, and reduces the area body A. At the same time-that 6 ment a first direction, a second fluid motor operatively connected to the first valve member forgiving a movement ina second direction opposite to the movement" produced by said first fluid motor, a third fluid motor oper atively connected to the second valve member for giving: it movement in a first direction, a fourth fluid motor operatively connected to the second valve member for giving it movement in a second direction opposite to the movement produced by the third fluid moton a first compressedair valve fluidly connected to the first fluid motor, a second compressed air valve fluidly connected to the second fluid motor, a third compressed air valve fluidly connected to the third fluid motor, afourth compressed air valve fluidly connected to the fourth fluid motor, a fifthfluid motor means arranged for separately actuating the first andsecon'd compressed air valves, a sixth fluid motor means arranged for separately actuating thethird and fourth compressed air valves, means fluidly connected with said first and second compressed air valves for in-' activating said sixth fluid motor means when one of said compressed air valves is actuated and a meansfor actuating said fifth and sixth fluid motor means in response: to' changes in the pressure of a fluid in a selected chamber.

2. A control systemfor altering the rate of flow of fluid through a valvein response to changes in pressure in a fluid filled chamber comprising, in combination, a valve bo'dy, fi rst and second cooperating movable valve members arranged in said valve body foraltering the area-of flow through said valve body, a first motor operatively connected to the first valve member for giving it movement in a first direction and a second fluid motor operatively connected to said first valve member for giving it movement in a second direction opposite to the direction of movement produced by said first fluid motor, a third fluid motor operatively connected to the second valve member for giving it movement in a first direction, a fourth fluid motor operatively connected to said second valve member for giving it movement in a second direction opposite to the direction of movement produced by the third fluid motor, a first assembly consisting of first and second compressed air valves and a fifth fluid motor means arranged for separately actuating said first and second compressed air valves, conduit means fluidly connecting said first and second compressed air valves with said first and second fluid motors respectively, a second assembly consisting of third and fourth compressed air valves and a sixth fluid motor means capable of separately actuating said third and fourth compressed air valves and conduits fluidly connecting said third and fourth valves with said third and fourth air motors respectively, conduit means fluidly connecting said fifth and sixth air motor means with a chamber and means operatively connecting said first and second assemblies to inactivate said sixth fluid motor means when said fifth fluid motor means actuates one of the compressed air valves in the first assembly.

3. A control system for regulating the flow of hydraulic fluid through a valve in response to changes in pressure in a fluid filled chamber comprising, in combination, a valve body, first and second cooperating valve members fluidly arranged in said valve body to vary the area of flow through the valve body, a first fluid motor operatively connected to the first valve member for giving it movement in a first direction, a second fluid motor operatively connected to said first valve member for giving it movement in a second direction opposite that produced by said first fluid motor, a third fluid motor operatively connected to the second valve member for giving it movement in a first direction, a fourth fluid motor operatively connected to the second valve member for giving it movement in a second direction opposite to that produced by the third fluid motor, a first assembly consisting of a first compressed air valve, a second compressed air valve and a fifth fluid motor means arranged for separately actuating said first and second compressed air valves, means fluidly connecting the first air valve of the said first assembly with said first fluid motor, means fluidly connecting said second compressed air valve of the first assembly with the second fluid motor, a second assembly consisting of a third compressed air valve, a fourth compressed air valve and a sixth fluid motor means arranged for separately actuating said third and fourth compressed air valves, means including a first periodic interrupter fluidly connecting the third compressed air valve with the third fluid motor, means including a second. periodic interrupter fluidly connecting the fourth compressed air valve with the fourth fluid motor, means fluidly connected with said first compressed air valve for inactivating said sixth fluid motor means when said first compressed air valve is actuated, means fluidly connected with said second compressed air valve for inactivating said sixth fluid motor means when said second compressed air valve isactuated and means fluidly connected said fifth and sixth fluid motor means with a chamber the pressure in which varies in response to a weighted member.

4. A control system for altering the flow of hydraulic fluid through a valve in response to changes in pressure in a fluid filled chamber comprising, in combination, a valve body, first and second cooperating valve members movably arranged in the valve body to vary the area of flow through the valve body, a first fluid motor operatively connected to the first valve member for giving it movement in a first direction, a second fluid motor operatively connected to the first valve member for giving it movement in a second direction opposite to that produced by the first fluid motor, a third fluid motor operatively connected to the second valve member for giving it movement in a first direction, a fourth fluid motor operatively connected to the second valve member for giving it movement in a second direction opposite to that produced by the third fluid motor, a first assembly consisting of first and second compressed air valves, and a fifth fluid motor consisting of first and second diaphragms separately arranged in chambers and mechanically connected and arranged for separately actuating said first and second valves, a second assembly consisting of third and fourth compressed air valves and a, sixth fluid motor means consisting of first and second diaphragms, arranged in separate chambers and mechanically connected and arranged for separately actuating said third and fourth compressed air valves, means including a periodic interrupter fluidly connecting the third compressed air valve with a third fluid motor, means including a second periodic interrupter fluidly connecting the fourth compressed air valve with the fourth connecting the chamber of the second'diaphragm of the first assembly and the chamber of the first diaphragm of the second assembly with the chamber of a weight signalling device, a conduit including an orifice member containing an orifice of substantially smaller flow area than the connecting conduits fluidly connecting the chambers of the first and second diaphragmsof the second assembly, a first pressure change actuated bypass valve arranged in a first bypass line connecting the chamber of the second diaphragm of the second assembly with said manifold, a second pressure change actuated bypass valve in a second bypass line fluidly connecting the chamber of the second diaphragm of the second assembly with said manifold, means fluidly connecting the actuating means of the first bypass valve with said first compressed air valve and means fluidly connecting the ac tuating means of the second bypass valve with said second compressed air valve.

No references cited.

fluid motor, a manifold fluidly