CA1131545A - Hydraulic actuator - Google Patents
Hydraulic actuatorInfo
- Publication number
- CA1131545A CA1131545A CA317,345A CA317345A CA1131545A CA 1131545 A CA1131545 A CA 1131545A CA 317345 A CA317345 A CA 317345A CA 1131545 A CA1131545 A CA 1131545A
- Authority
- CA
- Canada
- Prior art keywords
- piston
- drive shaft
- spring
- drive
- cam
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 230000033001 locomotion Effects 0.000 claims description 15
- 230000002829 reductive effect Effects 0.000 claims description 7
- 230000008878 coupling Effects 0.000 claims description 5
- 238000010168 coupling process Methods 0.000 claims description 5
- 238000005859 coupling reaction Methods 0.000 claims description 5
- 230000000670 limiting effect Effects 0.000 claims description 4
- 230000000717 retained effect Effects 0.000 claims description 3
- 230000003068 static effect Effects 0.000 abstract description 8
- 239000012530 fluid Substances 0.000 description 11
- 229910000831 Steel Inorganic materials 0.000 description 5
- 239000010959 steel Substances 0.000 description 5
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 230000006872 improvement Effects 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000036961 partial effect Effects 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B23/00—Apparatus for displacing, setting, locking, releasing or removing tools, packers or the like in boreholes or wells
- E21B23/08—Introducing or running tools by fluid pressure, e.g. through-the-flow-line tool systems
- E21B23/12—Tool diverters
Landscapes
- Life Sciences & Earth Sciences (AREA)
- Engineering & Computer Science (AREA)
- Geology (AREA)
- Mining & Mineral Resources (AREA)
- Physics & Mathematics (AREA)
- Environmental & Geological Engineering (AREA)
- Fluid Mechanics (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Actuator (AREA)
- Forging (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
ABSTRACT
A spring cushioned static seal hydraulically operated actuator is disclosed which contains a hydraulically driven piston arranged to reciprocate in a chamber. A spring couples the piston to a rotatable shaft which limits the torque placed on the shaft by the piston in its drive stroke. A return spring functions to return the piston and drive spring to their initial positions upon release of the hydraulic drive applied to the piston. A static seal on the piston seals at the completion of the drive stroke of the piston. The actuator may be used to operate a subsea diverter to direct "pump down" or through flow line (TFL tools) through wye-branched flow passageways formed in a diverter body member located on a submerged well head.
A spring cushioned static seal hydraulically operated actuator is disclosed which contains a hydraulically driven piston arranged to reciprocate in a chamber. A spring couples the piston to a rotatable shaft which limits the torque placed on the shaft by the piston in its drive stroke. A return spring functions to return the piston and drive spring to their initial positions upon release of the hydraulic drive applied to the piston. A static seal on the piston seals at the completion of the drive stroke of the piston. The actuator may be used to operate a subsea diverter to direct "pump down" or through flow line (TFL tools) through wye-branched flow passageways formed in a diverter body member located on a submerged well head.
Description
BACKGROUND OF THE INVENTION
16 Field of the Invention. The present invention concerns 17 hydraulically operated actuators and, particularly, such actuators 18 when used with diverters for directing the movement of tools used 19 in conducting various operations on remotely located oil and/or gas wells, such as wells-located subsea.
21 Desc~iption of the Prior Art. In performing completion 22 and wor~over operations in subsea wells, tools are moved hydraulic-23 ally into and out of well tubings through large radius flowline 24 loops mounted on the submerged wells. In one type of subsea production system one pair of pumpdown headers services several 26 wells. Each well tubing is provided with wye-branched flow 27 passageways to permit the conduct of operations either through a 28 vertical conduit or through loops. Hydraulically operated tool 29 diverters are required at each of the wells to enable the selec-tive deflection of tools into the desired wells. A hydraulically 31 operated TFL tool diverter designed to so direct passage of the 32 TFL tools is shown and described in U.S. Patent No. 3,881,516 33 entitled "Hydraulically Operated Diverter" by T. W. Childers et 34 al. The hydraulically operated actuator of the present inven-tion is an improvement in the actuator for such a diverter, 36 particularly in the means for limiting the torsional force that 11315~S
can be generated on the paddle drive shaft of the diverter and
16 Field of the Invention. The present invention concerns 17 hydraulically operated actuators and, particularly, such actuators 18 when used with diverters for directing the movement of tools used 19 in conducting various operations on remotely located oil and/or gas wells, such as wells-located subsea.
21 Desc~iption of the Prior Art. In performing completion 22 and wor~over operations in subsea wells, tools are moved hydraulic-23 ally into and out of well tubings through large radius flowline 24 loops mounted on the submerged wells. In one type of subsea production system one pair of pumpdown headers services several 26 wells. Each well tubing is provided with wye-branched flow 27 passageways to permit the conduct of operations either through a 28 vertical conduit or through loops. Hydraulically operated tool 29 diverters are required at each of the wells to enable the selec-tive deflection of tools into the desired wells. A hydraulically 31 operated TFL tool diverter designed to so direct passage of the 32 TFL tools is shown and described in U.S. Patent No. 3,881,516 33 entitled "Hydraulically Operated Diverter" by T. W. Childers et 34 al. The hydraulically operated actuator of the present inven-tion is an improvement in the actuator for such a diverter, 36 particularly in the means for limiting the torsional force that 11315~S
can be generated on the paddle drive shaft of the diverter and
2 in the means for effecting a static seal in the piston chamber.
3 SUMMARY OF THE INVENTION
4 In accordance with the teachings of the present inven-tion an actuator assembly includes a hydraulically operable 6 piston means including a chamber and a linearly movable piston 7 reciprocal in the chamber, a rotatable drive shaft, and means 8 connecting the piston to the drive shaft for converting linear 9 motion of the piston to rotary motion of the drive shaft and for limiting the torsional force capable of being generated on the 11 drive shaft by the piston. A static seal on the piston seals 12 against an end wall of the chamber at the end of the drive stroke 13 of the piston. The seal is an annular member, wedge-shaped in 14 cross section, having a deformable reduced contact area. In well operatons the drive shaft may be used to cause a diverter paddle 16 to pivot at the junction of wye-branched passageways for divert-17 ing TFL tools through either of the branched passageways. The 18 actuator assembly is sealingly connectable to the diverter body 19 member and is removable therefrom and replaceable thereon.
BRIEF DESCRIPTION OF THE DRAWINGS
21 Fig. 1 is a partial vertical section through the 22 actuator assembly of the invention and a tool diverter connected 23 thereto;
24 Fig. 2 is a view taken along lnes 2-2 of Fig. l; and Figs. 3, 4 and 5 are fragmentary views of the piston-chamber 26 illustrated in Fig. 1.
28 Referring to the figures there is shown a diverter 29 body 10 having wye-branched vertical bore 11 and a curved bore, not shown, which forms a smooth internal transition to a loop 31 section, not shown. Diverter body 10 is the same as the diverter 32 body shown and described in the aforementioned patent. A
33 diverter paddle 14 is shaped to conform to the curved bore on 3~ its one side and to vertical bore 11 on its other side. The free end 14a of paddle 14 is tapered on both sides and engages 36 the inner bore wall of the wye in each of its two positions.
37 Paddle 14 is non-rotatably mounted on one end of a shaft 17 which ~ 13~5~S
extends through the wall of diverter body 10 at the junction of 2 the bores. Shaft 17 serves as the axis of rotation for paddle 14.
3 Diverter body 10 is connected to a threaded receiver flange 20 by 4 threaded bolts 21. A threaded lock ring 22 is rotatably mounted on an operator or actuator assembly 23 and is connected by threads 6 to receiver flange 20. Actuator assembly 23 includes a housing 24 7 secured to a closure plate 25 at one end by threaded bolts 26 8 (only one is shown). An o-ring 27 seals off the connecting inner 9 surface of housing 24 and the outer surface of closure plate 25.
A large linearly movable piston 30 reciprocates in a 11 chamber 31 formed in a cylindrical body member 32 from one posi-12 tion, shown in Figs. 1 and 3, to another position, shown in 13 Figs. 4 and 5 (drive stroke) and from the other to the one posi-14 tion (return stroke). Piston 30 contains a static seal 30a which is an annular member, wedge-shaped in cross section, having a 16 deformable reduced contact area or edge. At the end of the drive 17 stroke of piston 30 the edge contacts and seals on seat 31a of 18 chamber 31. Under the compressive force of piston 30 the edge 19 yields or plastically deforms to conform to seat 31a, as indicated in Fig. 5, to achieve intimate contact and a better 21 seal. The quotient of piston force (pressure times piston area) 22 divided by the seal contact area is slightly greater than the 23 compressive strength of the piston material which results in the 24 plastic deformation of edge 30a. The piston preferably is con-structed of a soft malleable steel such as an annealed American 26 Iron and Steel Institute (AISI) 1015 steel with a hardness in the 27 range of 120 Brinnell Hardness Number (BHN). The cylinder and 28 static seat 31a are constructed of a harder steel such as AISI
29 4130 with a hardness in the range of 235 BHN. Preferably, the seal edge is blunted to prevent failure of the steel seal. The 31 reduced area (edge) of seal 30a also facilitates cutting through 32 any particles or debris which may be in the fluid in chamber 31 33 and adhere to seat 31a. Annular piston rings 30b surround 34 piston 30 but do not seal off the space between piston 30 and the wall of chamber 31. Piston 30 is connected to a drive plate 33 36 by means of a piston rod 34 which extends through an interior 37 wall of body member 32. Shaft seal 35 seals off the annulus 38 surrounding piston rod 34 within that wall. Drive plate 33, from 39 which a shaft 41 extends into a hollow output drive shaft 40, is 11315~5 ~ coupled to output shaft 40 by a cam or drive nut 43 and a cushion-2 ing coiled drive spring 44 positioned in body ~ember 32 between 3 plate 33 and one side of drive nut 43. Two external lugs or 4 pins 45 that ride in slots 46 formed in cylindrical body member 32 restrain drive nut 43 from rotating. Output drive shaft 40 has a 6 pair of helical slots 50 which are engaged by cam pins 51 on 7 drive nut 43. A coiled return spring 52 which has a lower spring 8 constant than drive spring 44 surrounds drive shaft 40 between an 9 end wall of body member 32 and the other side of cam nut 43 and urges drive nut 43 against the bias of drive spring 44. An open 11 window 53 in drive shaft 40 prevents trapping of fluid within 12 drive shaft 40.
13 Drive shaft 40 extends into closure plate 25 where it 14 is mounted for rotation within thrust bearings 55 and 56 on each side of a shoulder 57 and within a support bearing 58 threaded to 16 closure plate 25. The end of drive shaft 40 forms a socket 59 17 for receiving an end 60 of shaft 17. The interior cross section 18 of socket 59 is configured the same as the cross section of shaft 19 end 60. Such configuration is illustrated herein as square;
however, other suitable shapes may be used. The cross section of 21 the tip of shaft end 60 is reduced and configured as at 60a so 22 that socket 59 will pic~ up shaft 17 regardless of its rotational 23 position. ~ sleeve bushing 61 surrounds a portion of shaft 17 24 and a plate member 62 confines a retainer ring 63 against bushing 61. A pressure seal 65, retained in place by a plate 26 member 66, provides a pressure seal between shaft 40 and closure 27 plate inner wall 70. Other suitable pressure seals may be used.
28 A bleeder passageway 71 is positioned in closure plate 25 and, 29 communicates with the bore between o-ring seal 73 and seal 65 to prevent fluids which may escape by shaft seal 65 from entering 31 housing 24. Any fluids that may escape past seal 65 will leak 32 out between the course acme threads 23a and 23b. An annular 33 o-ring 75 on the face of closure plate 25 enables a manipulator, 34 not shown, to test the metal-to-metal ring seal 76 located between closure plate 25 and body 1~. Test pressure is applied 36 by the manipulator through a port 77 in housing 24 and fluid 37 pressure line 77a connected thereto and a passageway 77b in 38 closure plate 25 to which line 77a is connected. A port 86 in 39 cylindrical body member 32 fluidly communicates chamber 31 on the ` 1~315~5 1 exhaust side of piston 30 with a closed ambient pressure reser-2 voir system (not shown) through a fluid conduit 87, a threaded 3 connection 87a, a passageway 82, a poppet conne~tor 81 and a 4 condui 80. Poppet connector 81 includes a female portion 81b ' attached to closure plate 25 and a male portion 81a attached to 6 receiver flange 20. An o-ring 83 seals off the connection 7 between portion 81b and closure plate 25.
8 A diaphragm member, bellows or bladder 94 is connected 9 into a passageway 96 in the rear wall of housing 24 by means of a threaded connector 95. The interior of housing 24 is filled with 11 oil through plugged opening 97. The interior of the bellows is 12 open to ambient sea pressure (as is the a~orementioned fluid 13 reservoir system) and pressure is equalized inside and outside 14 housing 24. Instead of the bellows arrangement pressure equali-zation could be achieved inside and outside housing 24 by connect-16 ing the housing to the fluid reservoir system through another 17 conduit and connector in flange 20, closure plate 25 and another 18 poppet valve connector arrangement (such as 81). A conduit 85 19 conducts power fluid to cylinder 31 from the poppet valve through a poppet valve connection, not shown.
21 Diverter body 10 and the components associated there-22 with and the closed hydraulic system are permanently located 23 subsea adjacent the subsea wellhead. Actuator assembly 23 is 24 disconnectable and removable from and reconnectable to diverter body 10 using remotely controlled manipulators or divers. When 26 installing actuator assembly 23 it is positioned adjacent 27 diverter body 10 and properly aligned therewith. The end 60 of 28 shaft 17 enters socket 59 and, if necessary, is rotated as it 29 enters by the slanted surfaces 60a at the tip of the shaft. The two halves of each of the poppet valves 81 engage and when the 31 actuator assembly and diverter body 10 are positioned as shown in 32 Fig, 1 lock ring 22 is rotated to thread it to receiver flange 20.
33 Test pressure is then applied through port 77, hose 77a and 34 passageway 77b.
When the actuator assembly is connected to a diverter 36 and it is desired to divert tools from one bore of the diverter 37 to the other, power fluid is supplied from the reservoir through 38 conduit 8S to piston chamber 31 and piston 30 to move piston 30 39 in its drive stroke causing drive plate 33 to compress spring 44 which in turn acts on cam nut 43. As cam nut 43 is pushed axially 11315~5 by drive spring 44, drive shaft 40 is caused to rotate and return 2 spring 52 to be compressed. Since the return spring has a lower 3 spring constant than drive spring 44 cam nut 43 is moved linearly 4 in the direction of return spring 52 when piston 30 applies force to drive spring 44. When piston 30 seats on seat 31a, piston 6 rod 34 has moved the distance Dl. Biased by return spring 52 cam 7 nut 43 moves the distance D2, an approximate ratio of 1:2. As 8 shown, output shaft 40 rotates in a counter clockwise direction 9 when piston 30 moves from its right~hand to its left-hand posi-tion (drive stroke). At the end of the drive stroke the edge 11 of seal 30a seats on seat 31a as indicated in Fig. 5. The spring 12 coupling between the piston and the cam nut limits the torque on 13 the output shaft and, also, allows the output shaft to be rotated 14 in the opposite direction without moving the piston off its static seat. When power fluid is released from piston chamber 31 16 through conduit 85 to the reservoir, return spring 51 moves cam 17 nut 43 linearly in the direction of drive spring 44 and moves 18 piston 30 in its return stroke. Such movement causes output 19 shaft 40 to rotate in a cloc~wise direction, as shown in Fig. 2, until piston 30, drive plate 33, spring 44, cam nut 43 and return 21 spring 52 are positioned as shown in Fig. 1. In this arrangement 22 the diverter operator can try to overdrive the diverter paddle 14 23 so that it is firmly held in the extreme positions without over-24 stressing either the diverter paddle-shaft connection or the diverter paddle tip 14a. The actuator avoids causing damage to 26 the diverter paddle drive shaft connection if TFL tools should be 27 accidentally pushed under the paddle from the reverse direction 28 or if tools or debris are in the way when the diverter is operated.
29 It is designed to limit the torsional force that can be generated on the paddle drive shaft.
31 The actuator assembly shown and described herein limits 32 the total force applied by the output shaft and is, also, self-33 adjusting and provides a reliable seal on a static seat. Changes 34 and modifications may be made in the illustrative embodiments shown and deseribed herein without departing from the scope of 36 the invention as defined in the appended claims.
37 Having fully described the nature, objects, operation 38 and advantages of my invention I claim:
BRIEF DESCRIPTION OF THE DRAWINGS
21 Fig. 1 is a partial vertical section through the 22 actuator assembly of the invention and a tool diverter connected 23 thereto;
24 Fig. 2 is a view taken along lnes 2-2 of Fig. l; and Figs. 3, 4 and 5 are fragmentary views of the piston-chamber 26 illustrated in Fig. 1.
28 Referring to the figures there is shown a diverter 29 body 10 having wye-branched vertical bore 11 and a curved bore, not shown, which forms a smooth internal transition to a loop 31 section, not shown. Diverter body 10 is the same as the diverter 32 body shown and described in the aforementioned patent. A
33 diverter paddle 14 is shaped to conform to the curved bore on 3~ its one side and to vertical bore 11 on its other side. The free end 14a of paddle 14 is tapered on both sides and engages 36 the inner bore wall of the wye in each of its two positions.
37 Paddle 14 is non-rotatably mounted on one end of a shaft 17 which ~ 13~5~S
extends through the wall of diverter body 10 at the junction of 2 the bores. Shaft 17 serves as the axis of rotation for paddle 14.
3 Diverter body 10 is connected to a threaded receiver flange 20 by 4 threaded bolts 21. A threaded lock ring 22 is rotatably mounted on an operator or actuator assembly 23 and is connected by threads 6 to receiver flange 20. Actuator assembly 23 includes a housing 24 7 secured to a closure plate 25 at one end by threaded bolts 26 8 (only one is shown). An o-ring 27 seals off the connecting inner 9 surface of housing 24 and the outer surface of closure plate 25.
A large linearly movable piston 30 reciprocates in a 11 chamber 31 formed in a cylindrical body member 32 from one posi-12 tion, shown in Figs. 1 and 3, to another position, shown in 13 Figs. 4 and 5 (drive stroke) and from the other to the one posi-14 tion (return stroke). Piston 30 contains a static seal 30a which is an annular member, wedge-shaped in cross section, having a 16 deformable reduced contact area or edge. At the end of the drive 17 stroke of piston 30 the edge contacts and seals on seat 31a of 18 chamber 31. Under the compressive force of piston 30 the edge 19 yields or plastically deforms to conform to seat 31a, as indicated in Fig. 5, to achieve intimate contact and a better 21 seal. The quotient of piston force (pressure times piston area) 22 divided by the seal contact area is slightly greater than the 23 compressive strength of the piston material which results in the 24 plastic deformation of edge 30a. The piston preferably is con-structed of a soft malleable steel such as an annealed American 26 Iron and Steel Institute (AISI) 1015 steel with a hardness in the 27 range of 120 Brinnell Hardness Number (BHN). The cylinder and 28 static seat 31a are constructed of a harder steel such as AISI
29 4130 with a hardness in the range of 235 BHN. Preferably, the seal edge is blunted to prevent failure of the steel seal. The 31 reduced area (edge) of seal 30a also facilitates cutting through 32 any particles or debris which may be in the fluid in chamber 31 33 and adhere to seat 31a. Annular piston rings 30b surround 34 piston 30 but do not seal off the space between piston 30 and the wall of chamber 31. Piston 30 is connected to a drive plate 33 36 by means of a piston rod 34 which extends through an interior 37 wall of body member 32. Shaft seal 35 seals off the annulus 38 surrounding piston rod 34 within that wall. Drive plate 33, from 39 which a shaft 41 extends into a hollow output drive shaft 40, is 11315~5 ~ coupled to output shaft 40 by a cam or drive nut 43 and a cushion-2 ing coiled drive spring 44 positioned in body ~ember 32 between 3 plate 33 and one side of drive nut 43. Two external lugs or 4 pins 45 that ride in slots 46 formed in cylindrical body member 32 restrain drive nut 43 from rotating. Output drive shaft 40 has a 6 pair of helical slots 50 which are engaged by cam pins 51 on 7 drive nut 43. A coiled return spring 52 which has a lower spring 8 constant than drive spring 44 surrounds drive shaft 40 between an 9 end wall of body member 32 and the other side of cam nut 43 and urges drive nut 43 against the bias of drive spring 44. An open 11 window 53 in drive shaft 40 prevents trapping of fluid within 12 drive shaft 40.
13 Drive shaft 40 extends into closure plate 25 where it 14 is mounted for rotation within thrust bearings 55 and 56 on each side of a shoulder 57 and within a support bearing 58 threaded to 16 closure plate 25. The end of drive shaft 40 forms a socket 59 17 for receiving an end 60 of shaft 17. The interior cross section 18 of socket 59 is configured the same as the cross section of shaft 19 end 60. Such configuration is illustrated herein as square;
however, other suitable shapes may be used. The cross section of 21 the tip of shaft end 60 is reduced and configured as at 60a so 22 that socket 59 will pic~ up shaft 17 regardless of its rotational 23 position. ~ sleeve bushing 61 surrounds a portion of shaft 17 24 and a plate member 62 confines a retainer ring 63 against bushing 61. A pressure seal 65, retained in place by a plate 26 member 66, provides a pressure seal between shaft 40 and closure 27 plate inner wall 70. Other suitable pressure seals may be used.
28 A bleeder passageway 71 is positioned in closure plate 25 and, 29 communicates with the bore between o-ring seal 73 and seal 65 to prevent fluids which may escape by shaft seal 65 from entering 31 housing 24. Any fluids that may escape past seal 65 will leak 32 out between the course acme threads 23a and 23b. An annular 33 o-ring 75 on the face of closure plate 25 enables a manipulator, 34 not shown, to test the metal-to-metal ring seal 76 located between closure plate 25 and body 1~. Test pressure is applied 36 by the manipulator through a port 77 in housing 24 and fluid 37 pressure line 77a connected thereto and a passageway 77b in 38 closure plate 25 to which line 77a is connected. A port 86 in 39 cylindrical body member 32 fluidly communicates chamber 31 on the ` 1~315~5 1 exhaust side of piston 30 with a closed ambient pressure reser-2 voir system (not shown) through a fluid conduit 87, a threaded 3 connection 87a, a passageway 82, a poppet conne~tor 81 and a 4 condui 80. Poppet connector 81 includes a female portion 81b ' attached to closure plate 25 and a male portion 81a attached to 6 receiver flange 20. An o-ring 83 seals off the connection 7 between portion 81b and closure plate 25.
8 A diaphragm member, bellows or bladder 94 is connected 9 into a passageway 96 in the rear wall of housing 24 by means of a threaded connector 95. The interior of housing 24 is filled with 11 oil through plugged opening 97. The interior of the bellows is 12 open to ambient sea pressure (as is the a~orementioned fluid 13 reservoir system) and pressure is equalized inside and outside 14 housing 24. Instead of the bellows arrangement pressure equali-zation could be achieved inside and outside housing 24 by connect-16 ing the housing to the fluid reservoir system through another 17 conduit and connector in flange 20, closure plate 25 and another 18 poppet valve connector arrangement (such as 81). A conduit 85 19 conducts power fluid to cylinder 31 from the poppet valve through a poppet valve connection, not shown.
21 Diverter body 10 and the components associated there-22 with and the closed hydraulic system are permanently located 23 subsea adjacent the subsea wellhead. Actuator assembly 23 is 24 disconnectable and removable from and reconnectable to diverter body 10 using remotely controlled manipulators or divers. When 26 installing actuator assembly 23 it is positioned adjacent 27 diverter body 10 and properly aligned therewith. The end 60 of 28 shaft 17 enters socket 59 and, if necessary, is rotated as it 29 enters by the slanted surfaces 60a at the tip of the shaft. The two halves of each of the poppet valves 81 engage and when the 31 actuator assembly and diverter body 10 are positioned as shown in 32 Fig, 1 lock ring 22 is rotated to thread it to receiver flange 20.
33 Test pressure is then applied through port 77, hose 77a and 34 passageway 77b.
When the actuator assembly is connected to a diverter 36 and it is desired to divert tools from one bore of the diverter 37 to the other, power fluid is supplied from the reservoir through 38 conduit 8S to piston chamber 31 and piston 30 to move piston 30 39 in its drive stroke causing drive plate 33 to compress spring 44 which in turn acts on cam nut 43. As cam nut 43 is pushed axially 11315~5 by drive spring 44, drive shaft 40 is caused to rotate and return 2 spring 52 to be compressed. Since the return spring has a lower 3 spring constant than drive spring 44 cam nut 43 is moved linearly 4 in the direction of return spring 52 when piston 30 applies force to drive spring 44. When piston 30 seats on seat 31a, piston 6 rod 34 has moved the distance Dl. Biased by return spring 52 cam 7 nut 43 moves the distance D2, an approximate ratio of 1:2. As 8 shown, output shaft 40 rotates in a counter clockwise direction 9 when piston 30 moves from its right~hand to its left-hand posi-tion (drive stroke). At the end of the drive stroke the edge 11 of seal 30a seats on seat 31a as indicated in Fig. 5. The spring 12 coupling between the piston and the cam nut limits the torque on 13 the output shaft and, also, allows the output shaft to be rotated 14 in the opposite direction without moving the piston off its static seat. When power fluid is released from piston chamber 31 16 through conduit 85 to the reservoir, return spring 51 moves cam 17 nut 43 linearly in the direction of drive spring 44 and moves 18 piston 30 in its return stroke. Such movement causes output 19 shaft 40 to rotate in a cloc~wise direction, as shown in Fig. 2, until piston 30, drive plate 33, spring 44, cam nut 43 and return 21 spring 52 are positioned as shown in Fig. 1. In this arrangement 22 the diverter operator can try to overdrive the diverter paddle 14 23 so that it is firmly held in the extreme positions without over-24 stressing either the diverter paddle-shaft connection or the diverter paddle tip 14a. The actuator avoids causing damage to 26 the diverter paddle drive shaft connection if TFL tools should be 27 accidentally pushed under the paddle from the reverse direction 28 or if tools or debris are in the way when the diverter is operated.
29 It is designed to limit the torsional force that can be generated on the paddle drive shaft.
31 The actuator assembly shown and described herein limits 32 the total force applied by the output shaft and is, also, self-33 adjusting and provides a reliable seal on a static seat. Changes 34 and modifications may be made in the illustrative embodiments shown and deseribed herein without departing from the scope of 36 the invention as defined in the appended claims.
37 Having fully described the nature, objects, operation 38 and advantages of my invention I claim:
Claims (12)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. Apparatus comprising;
a hydraulically operable piston assembly having a chamber;
a linearly moveable piston means arranged to reciprocate in said chamber and having a drive stroke and a return stroke;
a rotatable drive shaft means;
at least one curved slot formed in said drive shaft means;
a linearly moveable cam means having pin means engageable in said curved slot for rotating said drive shaft means upon move-ment of said cam means;
a drive spring engaging said piston means and said cam means for moving said cam means in the direction of the drive stroke of said piston means upon movement of said piston means in said drive stroke; and a return spring engaging said cam means for urging said cam means in the direction of said return stroke of said piston means.
a hydraulically operable piston assembly having a chamber;
a linearly moveable piston means arranged to reciprocate in said chamber and having a drive stroke and a return stroke;
a rotatable drive shaft means;
at least one curved slot formed in said drive shaft means;
a linearly moveable cam means having pin means engageable in said curved slot for rotating said drive shaft means upon move-ment of said cam means;
a drive spring engaging said piston means and said cam means for moving said cam means in the direction of the drive stroke of said piston means upon movement of said piston means in said drive stroke; and a return spring engaging said cam means for urging said cam means in the direction of said return stroke of said piston means.
2. Apparatus as recited in claim 1 including:
seal means on said piston engageable with said chamber only at the end of the drive stroke of said piston, said seal means comprising an annular wedged shaped member having an inner de-formable reduced contact area.
seal means on said piston engageable with said chamber only at the end of the drive stroke of said piston, said seal means comprising an annular wedged shaped member having an inner de-formable reduced contact area.
3. Apparatus as recited in claim 1 in which said converting means includes:
at least one curved slot formed in said drive shaft;
a linearly movable cam nut having pin means engageable in said slot;
said spring means includes a drive spring coupling said piston and said cam nut for urging said cam nut in said one linear direction upon movement of said piston in said one direction;
a returned spring for urging said cam nut in a linear direction opposite to said one linear direction;
a cylindrical housing having at least one slot formed therein; and lug means formed on said cam nut retained in said slot to prevent rotation of said cam nut.
at least one curved slot formed in said drive shaft;
a linearly movable cam nut having pin means engageable in said slot;
said spring means includes a drive spring coupling said piston and said cam nut for urging said cam nut in said one linear direction upon movement of said piston in said one direction;
a returned spring for urging said cam nut in a linear direction opposite to said one linear direction;
a cylindrical housing having at least one slot formed therein; and lug means formed on said cam nut retained in said slot to prevent rotation of said cam nut.
4. Apparatus as recited in claim 1 in which said converting means includes:
at least one curved slot formed in said drive shaft;
a linearly movable cam nut having pin means engageable in said slot;
said spring means includes a drive spring coupling said piston and said cam nut for urging said cam nut in said one linear direction upon movement of said piston in said one direction;
a returned spring for urging said cam nut in a linear direction opposite to said one linear direction; said drive spring and said returned spring each comprising a linear extensible coiled spring, and said returned spring having a lower spring constant than said drive spring.
at least one curved slot formed in said drive shaft;
a linearly movable cam nut having pin means engageable in said slot;
said spring means includes a drive spring coupling said piston and said cam nut for urging said cam nut in said one linear direction upon movement of said piston in said one direction;
a returned spring for urging said cam nut in a linear direction opposite to said one linear direction; said drive spring and said returned spring each comprising a linear extensible coiled spring, and said returned spring having a lower spring constant than said drive spring.
5. Apparatus as recited in claim 4 including:
seal means on said piston engageable with said chamber only at the end of the drive stroke of said piston, said seal means comprising an annular member, wedge-shaped and cross section, having an annular deformable edge.
seal means on said piston engageable with said chamber only at the end of the drive stroke of said piston, said seal means comprising an annular member, wedge-shaped and cross section, having an annular deformable edge.
6. Apparatus as recited in claim 4 including thrust bearings surrounding said drive shaft,
7. Apparatus as recited in claim 6 including:
a diverter body member containing branched passageways joined together in a wye configuration;
a paddle arranged at the junction of said passageways and movable from one position in which passage through one of said passageways is blocked to another position in which said passage through said other passageway is blocked; and means connecting said paddle to said drive shaft to rotate said paddle in response to rotation of said drive shaft.
a diverter body member containing branched passageways joined together in a wye configuration;
a paddle arranged at the junction of said passageways and movable from one position in which passage through one of said passageways is blocked to another position in which said passage through said other passageway is blocked; and means connecting said paddle to said drive shaft to rotate said paddle in response to rotation of said drive shaft.
8. Apparatus comprising:
a hydraulically operable piston assembly having a chamber;
a linearly movable piston reciprocal in said chamber;
a rotatable drive shaft; and means for converting linear motion of said piston to rotary motion of said drive shaft and for limiting the torsional force capable of being generated on said drive shaft by said piston move-ment comprising:
at least one curved slot formed in said drive shaft;
a linearly movable cam nut having pin means engageable in said slot;
first biasing means coupling said piston and said cam nut for urging said cam nut in said one linear direction upon movement of said piston in said one direction; and second biasing means for urging said cam nut in a linear direction opposite to said one linear direction.
a hydraulically operable piston assembly having a chamber;
a linearly movable piston reciprocal in said chamber;
a rotatable drive shaft; and means for converting linear motion of said piston to rotary motion of said drive shaft and for limiting the torsional force capable of being generated on said drive shaft by said piston move-ment comprising:
at least one curved slot formed in said drive shaft;
a linearly movable cam nut having pin means engageable in said slot;
first biasing means coupling said piston and said cam nut for urging said cam nut in said one linear direction upon movement of said piston in said one direction; and second biasing means for urging said cam nut in a linear direction opposite to said one linear direction.
9. Apparatus as recited in claim 8 in which said first and second biasing means each comprises a linearly extensible coiled spring, said second coiled spring having a lower spring constant than said first coiled spring.
10. Apparatus as recited in claim 9 including:
seal means on said piston engageable with said chamber only at the end of the drive stroke of said piston, said seal means comprising an annular member, wedge-shaped and cross section, having an annular deformable reduced contact area.
seal means on said piston engageable with said chamber only at the end of the drive stroke of said piston, said seal means comprising an annular member, wedge-shaped and cross section, having an annular deformable reduced contact area.
11. Apparatus as recited in claim 10 including:
a flow diverter body member containing branched passageways joined together in a wye configuration;
a paddle arranged at the junction of said passageways and movable from one position in which passage through one of said passageways is blocked to another position in which passage through said other passageway is blocked, and means for connecting said paddle to said drive shaft for rotating said paddle in response to rotation of said drive shaft.
a flow diverter body member containing branched passageways joined together in a wye configuration;
a paddle arranged at the junction of said passageways and movable from one position in which passage through one of said passageways is blocked to another position in which passage through said other passageway is blocked, and means for connecting said paddle to said drive shaft for rotating said paddle in response to rotation of said drive shaft.
12. Apparatus comprising:
a hydraulically operable piston assembly having a chamber;
a linearly movable piston reciprocal in said chamber;
seal means on said piston engageable in said chamber only at the end of the drive stroke of said piston, said seal means comprising an annular wedge-shaped member having an annular reduced contact area;
a rotatable drive shaft;
means for converting linear motion of said piston to rotary motion of said drive shaft and for limiting the torsionally force that can be generated on said drive shaft by said piston;
at least one curved slot formed in said drive shaft;
linearly movable means engageable in said slot;
first biasing means coupling said piston and said linearly movable means for urging said linearly movable means in one linear direction upon movement of said piston in said one direction;
second biasing means for urging said linearly movable means in a linearly direction opposite to said one direction;
a housing having at least one slot formed therein; and means formed on said linearly movable means retained in said slot to prevent rotation of said linearly movable means en-gageable in said slot.
a hydraulically operable piston assembly having a chamber;
a linearly movable piston reciprocal in said chamber;
seal means on said piston engageable in said chamber only at the end of the drive stroke of said piston, said seal means comprising an annular wedge-shaped member having an annular reduced contact area;
a rotatable drive shaft;
means for converting linear motion of said piston to rotary motion of said drive shaft and for limiting the torsionally force that can be generated on said drive shaft by said piston;
at least one curved slot formed in said drive shaft;
linearly movable means engageable in said slot;
first biasing means coupling said piston and said linearly movable means for urging said linearly movable means in one linear direction upon movement of said piston in said one direction;
second biasing means for urging said linearly movable means in a linearly direction opposite to said one direction;
a housing having at least one slot formed therein; and means formed on said linearly movable means retained in said slot to prevent rotation of said linearly movable means en-gageable in said slot.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US86106177A | 1977-12-15 | 1977-12-15 | |
| US861,061 | 1977-12-15 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1131545A true CA1131545A (en) | 1982-09-14 |
Family
ID=25334768
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA317,345A Expired CA1131545A (en) | 1977-12-15 | 1978-12-04 | Hydraulic actuator |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPS5493776A (en) |
| AU (1) | AU526658B2 (en) |
| CA (1) | CA1131545A (en) |
| GB (1) | GB2010397B (en) |
| NO (1) | NO151945C (en) |
-
1978
- 1978-12-04 CA CA317,345A patent/CA1131545A/en not_active Expired
- 1978-12-13 GB GB7848280A patent/GB2010397B/en not_active Expired
- 1978-12-13 AU AU42463/78A patent/AU526658B2/en not_active Expired
- 1978-12-15 JP JP15567278A patent/JPS5493776A/en active Granted
- 1978-12-15 NO NO784227A patent/NO151945C/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| NO151945B (en) | 1985-03-25 |
| AU526658B2 (en) | 1983-01-27 |
| GB2010397A (en) | 1979-06-27 |
| AU4246378A (en) | 1979-06-21 |
| NO784227L (en) | 1979-06-18 |
| GB2010397B (en) | 1982-04-21 |
| NO151945C (en) | 1985-07-03 |
| JPS621070B2 (en) | 1987-01-10 |
| JPS5493776A (en) | 1979-07-25 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |