A remotely controlled variable-diameter stabilizer with clutch control

Abstract

The present invention discloses a remotely controlled variable-diameter stabilizer with clutch control, which includes a body, a mandrel, a return spring, an inclined block, a driving mechanism sequentially arranged in the annular cavity between the mandrel and the body from top to bottom, and a plurality of centralizing pistons radially distributed on the body wall. Each centralizing piston forms an axially sliding limit fit with the inclined surface on the corresponding inclined block. The mandrel is composed of an upper mandrel and a lower mandrel which are hermetically connected up and down to form a through pipe string. The driving mechanism is a stroke mechanism controlled by a one-way clutch, and includes a driving cam, a one-way clutch, a cam pin, an upper inlay, a lower inlay and a limit pin. The present invention can realize the switching of the working state of the variable-diameter stabilizer and multiple position exchanges in cooperation with a switched drilling pump. There are no complex curved surfaces on the driving cam, and the cam pin only drives the upper inlay to rotate circumferentially. The circumferential rotation only overcomes the frictional torque, with small force and small deformation. The outer diameter state of the variable-diameter stabilizer is monitored through the pump pressure of the surface drilling pump.

Description

Technical Field

[0001] The present invention belongs to a downhole tool for drilling in the field of drilling engineering equipment, and particularly relates to a remotely controlled variable diameter stabilizer controlled by a clutch used in directional wells, horizontal wells, and extended reach wells in the petroleum industry. Background Art

[0002] During the drilling process of directional wells, horizontal wells, and extended reach wells, in order to ensure that the actual drilling wellbore trajectory meets the requirements of the designed wellbore trajectory, one method is to use a remotely controlled variable diameter stabilizer controlled by switching the drilling pump. However, the currently developed such variable diameter stabilizers have the following problems:

[0003] (1) The upper curve and surface of the cam inside the control stabilizer for variable diameter are complex, and the machining is difficult;

[0004] (2) The cam pin is subject to large forces and is prone to deformation, which in turn leads to poor reliability of variable diameter control.

[0005] For example, the document with the application number 2013106914308 discloses a "hydromechanical variable diameter stabilizer". It includes a body, a mandrel, and a throttling mechanism. The mandrel and the throttling mechanism are both located inside the body. The mandrel is an integral mandrel. The mandrel is sleeved with an upper piston, a first return spring, a spring seat, an interference sleeve, a plurality of wedges, a cam stroke control mechanism, a balance piston, a positioning sleeve, a second return spring, a plug, and a throttling nozzle of the throttling mechanism from top to bottom. The spring seat is loosely sleeved on the mandrel, and a positioning pin is installed on the body relative to the position of the spring seat. The inner end of the positioning pin is inserted into the spring seat. The first return spring abuts between the upper piston and the spring seat. The plurality of wedges are all axially fixed on the mandrel. Three piston holes are circumferentially opened on the body relative to each wedge position, and a piston head is installed in each piston hole. The tail of the piston head has a dovetail track, and the dovetail track is slidably matched with the dovetail groove opened on the wedge. The cam stroke control mechanism includes a cam body. The cam body is rotatably supported on the mandrel. A cam pin is installed on the body relative to the position of the cam body. The inner end of the cam pin is inserted into the chute on the outer periphery of the cam body. The balance piston is loosely sleeved on the mandrel. The positioning sleeve is axially fixed on the mandrel and is located below the balance piston. The plug is loosely sleeved on the mandrel. A plug pin is installed on the body relative to the position of the plug. The inner end of the plug pin is inserted into the plug. The second return spring abuts between the positioning sleeve and the plug. A plurality of filter holes are opened on the body between the positioning sleeve and the plug, and filter plates are installed in the filter holes. The annular cavity formed by the body and the mandrel above the balance piston and below the upper piston is an oil cavity. The annular cavity between the balance piston and the plug is a low-pressure drilling fluid cavity. The inner cavities at the top, bottom of the body, and the inner cavity of the mandrel are all high-pressure drilling fluid cavities. Among them:

[0006] The cam stroke control mechanism further includes an upper bearing seat, two thrust bearings and a lower bearing seat. The two thrust bearings are respectively held at both ends of the cam body by the upper bearing seat and the lower bearing seat. The cam body is in the shape of a cylinder and is sleeved on the outer periphery of the mandrel. The chute on the outer periphery of the cam body extends in a broken line shape, and the depth of the chute changes regularly according to the cam. The rule for the depth change of the chute is as follows: the first high point - the first low point - the second high point - the second low point are successively deepened by 1.5 ± 0.2 mm, the third high point - the third low point - the fourth high point - the fourth low point are successively deepened by 1.5 ± 0.2 mm, the fourth low point - the third high point gradually changes from the deepest to the shallowest, and the first high point and the third high point have the same depth.

[0007] The throttling mechanism further includes a circlip, a positioning sleeve, a locking ring and a throttling head. The circlip, the positioning sleeve and the locking ring are installed on the body and axially fix the throttling head on the body. The outlet of the throttling nozzle installed at the bottom of the mandrel can be sleeved on the throttling head.

[0008] The wedge block is a cylinder. Three inclined surfaces are evenly distributed along the circumferential direction of 120° on the outer circle of the wedge block. A dovetail groove for installing the dovetail track of the piston head is opened on each of the three inclined surfaces. The opening at the starting end of the dovetail groove is wider than the dovetail track.

[0009] A retaining ring is also installed at the upper end of the mandrel.

[0010] In the cam mechanism adopted by this stabilizer, the cam structure is complex and the processing difficulty is large. Structurally, the cam pin bears the axial hydraulic force of the tool, with large force and easy deformation.

[0011] For another example, the document with the application number 2005201252862 discloses a "drilling remote-controlled variable-diameter stabilizer", which includes a housing, a pressing mechanism, a variable-diameter mechanism, a control mechanism and a signal mechanism. Its characteristics are that the housing is an integral type with spiral wing surfaces on the outer surface. The pressing mechanism consists of a pushing piston, an upper spindle, a lower spindle, a return spring and a spring seat. The variable-diameter mechanism consists of an inclined plane body, a radial piston and a sealing ring. The control mechanism consists of a cam body, a cam pin and a bearing. The signal mechanism consists of an orifice plate assembly and a mushroom head assembly. The upper spindle and the lower spindle are connected into one body by a threaded method. The pressing piston is installed at the uppermost end of the upper spindle, and the upper spindle and the lower spindle are installed successively from top to bottom: the return spring, the spring seat, the inclined plane body, the cam body, the balance piston, the plug and the orifice plate assembly. The spring seat is fixed to the housing with a fixing pin. Five inclined plane bodies are installed axially in turn in the inner cavity of the spiral wing surface part of the housing. Fifteen radial pistons are divided into three groups and are evenly installed axially on the three spiral wing surfaces of the housing, that is, five radial pistons are evenly installed on each spiral wing surface. The cam pin is installed radially under the spiral wing surface of the housing, the front end of the cam pin is inserted into the control chute on the outer surface of the cam body, and the bearing is installed at the upper and lower ends of the cam body. The plug is fixed to the housing with a fixing pin. The mushroom head assembly is installed on the inner wall of the lower end of the housing. Among the above components, the cam body can be driven to move up and down by the lower spindle and can also rotate. Other components installed on the upper and lower spindles can only be driven to move up and down by the upper and lower spindles and cannot rotate. The cavity below the pressing piston and above the balance piston is filled with lubricating oil. Among them: the housing in the above drilling remote-controlled variable-diameter stabilizer is in the shape of a cylinder. It has a cylindrical inner cavity, with internal threads at the upper and lower ends, and three evenly distributed spiral wing surfaces on the outer surface in the middle. The outer diameter of the spiral wing surface is larger than the outer diameter of the rest of the housing. Five through holes for installing radial pistons are evenly distributed axially on each spiral wing surface.

[0012] The inclined plane body in the above drilling remote-controlled variable-diameter stabilizer is in the shape of a cylinder and has an inner hole. Three inclined planes are evenly processed on the outer circle along a circumference of 120°, and there is an axial T-shaped groove or dovetail groove for installing a radial piston at the center of each of the three inclined planes.

[0013] The radial piston in the above drilling remote-controlled variable-diameter stabilizer is in the shape of a cylinder. Its front end is a cylindrical surface, which is inlaid with several hard alloy blocks like the outer surface of the spiral wing surface; its rear end is an inclined plane, and there is an axial T-shaped head or dovetail head at the center; there is a sealing ring groove on its outer circle.

[0014] The cam and the cam pin of the core cam control mechanism of this patent have the same problem.

[0015] Therefore, the applicant previously applied for and disclosed a saw gear-driven controllable variable diameter stabilizer (Patent No. 201510704745.0), which includes a body, a mandrel arranged in the body, a return spring, an inclined block, a driving mechanism, a balance piston, a differential pressure piston installed in the annular cavity between the mandrel and the body, a support cylinder and a signal column fixed at the lower end of the body, and a stabilizer body arranged on the body. A plurality of centralizing pistons are radially distributed on the wall of the stabilizer body, and the centralizing pistons and a plurality of inclined surfaces on the inclined block form a radial sliding limit fit; wherein: the mandrel is composed of an upper mandrel and a lower mandrel which are hermetically connected up and down to form a through pipe column. The top of the upper mandrel protrudes outward to form a piston which axially slides and seals with the inner wall of the body. The return spring is arranged in the annular cavity below the piston. The lower end of the return spring is fixedly connected with the body relatively through a spring seat. The inclined block is fixedly connected with the upper mandrel. The driving mechanism is located outside the lower mandrel below the inclined block; the driving mechanism includes an upper saw gear, an upper bearing, a middle saw gear, a lower bearing, an upper positioning pin, a lower saw gear, a sliding pin, a compression spring and a spring seat fixing pin. Among them, the upper saw gear is fixedly connected with the body. The upper bearing, the middle saw gear and the lower bearing are installed on the lower mandrel and form a rotational fit with the lower mandrel. The upper positioning pin is installed on the body at a position corresponding to the middle saw gear. The upper positioning pin is in limit fit with an upper positioning groove, a middle positioning groove and a lower positioning groove on the wall of the middle saw gear. The lower saw gear is arranged below the middle saw gear. An axial sliding groove is arranged on the outer wall of the lower saw gear. The sliding groove forms an axial sliding fit with a sliding pin installed on the body. The compression spring is installed between the lower saw gear and the compression spring seat. The upper end of the compression spring is in limit fit with a raised ring on the inner wall of the lower saw gear. The lower end of the compression spring is fixedly connected to the body through the compression spring seat and the spring seat fixing pin. The saw teeth at the lower end of the upper saw gear are completely meshed with the saw teeth at the upper end of the middle saw gear. The saw teeth at the lower end of the middle saw gear are completely meshed with the saw teeth at the upper end of the lower saw gear. The upper and lower ends of the middle saw gear each have saw teeth with different pitches; the signal column forms a plug-in fit with the lower end of the lower mandrel; an oil cavity is formed by the body and the mandrel above the balance piston. An annular hole communicating the inside and outside of the body is arranged on the body corresponding to the upper surface of the differential pressure piston.

[0016] The stabilizer further includes a boosting unit arranged at the upper part of the controllable variable diameter stabilizer. The boosting unit is cylindrical, with a boosting joint on the outside and a hollow boosting mandrel inside. The top of the boosting mandrel axially slides and seals with the inner wall of the boosting joint through an outward protruding piston. The lower part of the boosting mandrel axially slides and seals with a protruding edge arranged inside the boosting joint. The lower end of the boosting mandrel is butted against the upper mandrel. A boosting compression spring is installed below the boosting mandrel. The bottom of the boosting compression spring is in limit fit with the protruding edge arranged inside the boosting joint. A boosting annular hole penetrating through the inside and outside is arranged on the wall of the boosting joint.

[0017] After adopting the above solution, the variable diameter stabilizer switch drilling pump can realize the switching of the working state of the variable diameter stabilizer, achieve multiple position changes, there are no complex curved surfaces on the sawtooth gear, and the processing is simple. The positioning pin equivalent to the cam pin only plays a positioning role and will not wear, greatly enhancing the reliability of control. However, the driving mechanism part still adopts a spring-driven structure, and the controllability is relatively low during actual use. Summary of the Invention

[0018] In order to overcome the defects existing in the existing variable diameter stabilizers, the present invention provides a remotely controlled variable diameter stabilizer controlled by a clutch with stronger control reliability.

[0019] The technical solution of the present invention is: a remotely controlled variable diameter stabilizer controlled by a clutch, including a body, a mandrel arranged in the body, a return spring, an inclined block, a driving mechanism arranged in the annular cavity between the mandrel and the body from top to bottom in sequence, and a plurality of centralizing pistons radially distributed on the body wall; wherein, each centralizing piston and the inclined plane on the corresponding inclined block form an axial sliding limit fit, the mandrel is composed of an upper mandrel and a lower mandrel which are hermetically connected up and down to form a through pipe column, the outer convex platform at the top of the upper mandrel forms an axial sliding seal fit with the inner wall of the body, the return spring is arranged in the annular cavity below the outer convex platform of the upper mandrel, the lower end of the return spring is fixedly connected to the body relatively, the inclined block is fixedly connected to the outer wall of the upper mandrel below the return spring, and the driving mechanism is located in the annular cavity between the lower mandrel and the body below the inclined block; characterized in that: the driving mechanism is a stroke mechanism controlled by a one-way clutch, including a driving cam, a one-way clutch, a cam pin, an upper inlay, a lower inlay and a limit pin; wherein, the upper part of the upper inlay is rotationally sealed with the outer wall of the lower mandrel, and the lower part of the upper inlay has rectangular teeth with chamfers; the upper part of the lower inlay is provided with rectangular tooth grooves with chamfers that are axially intermittently engaged with the rectangular teeth of the upper inlay, and the lower part of the lower inlay has an annular groove, which is axially limited and matched with the limit pin fixed on the body; the outer circumference of the driving cam is provided with an L-shaped groove composed of a cam straight groove and a cam inclined groove, which is slidably limited and matched with the cam pin fixed on the body, and the sliding limit fit between the cam pin and the cam inclined groove converts the axial movement of the driving cam into circumferential rotation; the one-way clutch is a one-way clutch with the function of one-way torque transmission, and the one-way clutch is arranged in the preset annular cavity between the upper part of the upper inlay and the driving cam; the upper inlay and the driving cam are axially positioned on the lower mandrel, and the lower mandrel, the upper inlay and the driving cam can all rotate relatively; the lower mandrel and the driving cam have two kinds of strokes, long and short, the inclined block moves up or down with the upper mandrel, and drives the centralizing piston to change between three positions.

[0020] The above solution further includes:

[0021] A balance piston and a differential pressure piston are successively installed from top to bottom between the lower end of the lower mandrel and the body, and an annular hole is provided on the body pipe wall between the balance piston and the differential pressure piston and penetrates radially.

[0022] A signal body is arranged inside the lower end of the lower mandrel. The outer diameter of the signal body is smaller than the inner diameter of the lower mandrel. When the lower mandrel moves downward for a long stroke, the lower mandrel sleeves the signal body.

[0023] An upper thrust bearing is installed between the top of the driving cam and the lower mandrel, a middle thrust bearing is installed between the bottom of the driving cam and the upper fitting body, and a lower thrust bearing is installed between the upper fitting body and the locking nut.

[0024] An oil cavity is formed between the upper mandrel, the lower mandrel and the body; a needle bearing is also installed between the upper fitting body and the driving cam.

[0025] The one-way clutch mainly consists of a clutch cage and a clutch wedge.

[0026] The centering piston is connected with the inclined block through a T-shaped groove, and the centering piston limits the axial stroke of the inclined block.

[0027] A seal for increasing the rotational friction force is installed between the upper fitting body and the lower mandrel.

[0028] A plurality of L-shaped grooves on the driving cam are evenly distributed along the outer circumference of the driving cam; there are spiral wing belts on the body, and there are a plurality of centering pistons on each wing.

[0029] It also includes a spring seat and a locking nut. The lower end of the return spring is the spring seat, and the spring seat is clamped inside the upper end of the body; the upper fitting body and the driving cam are axially positioned on the lower mandrel through the locking nut.

[0030] The present invention has the following beneficial effects: The variable-diameter stabilizer switch drilling pump of the present invention can realize the switching of the working state of the variable-diameter stabilizer, realize multiple position exchanges, there are no complex curved surfaces on the driving cam, the processing is simple, the cam pin only drives the circumferential rotation of the upper fitting body, the circumferential rotation only overcomes the frictional torque, the force is small, the deformation is small, and the reliability of control is greatly enhanced. Description of the Drawings

[0031] Figure 1 It is a schematic cross-sectional view of the structure and non-working state of the remote-controlled variable-diameter stabilizer of the present invention.

[0032] Figure 2 It is a schematic cross-sectional view of the flush working state of the remote-controlled variable-diameter stabilizer of the present invention.

[0033] Figure 3 It is a schematic cross-sectional view of the extended working state of the remote-controlled variable-diameter stabilizer of the present invention.

[0034] Figure 4 It is Figure 1 The schematic cross-sectional view of the E-E section in

[0035] Figure 5 is Figure 2 the schematic diagram of the F-F cross-section in

[0036] Figure 6 is Figure 3 the schematic diagram of the G-G cross-section in

[0037] Figure 7 the schematic diagram of a one-way clutch structure of the present invention

[0038] Figure 8 the schematic diagram of the lower inlay structure of the present invention

[0039] Figure 9 the schematic diagram of the driving cam structure of the present invention

[0040] Figure 10 the schematic diagram of the upper inlay structure of the present invention

[0041] Figure 11 is Figure 1 the enlarged schematic diagram of part A in

[0042] Figure 12 the schematic diagram of the cross-section structure of the one-way clutch of the remote-controlled variable-diameter stabilizer of the present invention

[0043] The reference numerals are: 1. body, 2. upper mandrel, 3. return spring, 4. spring seat, 5. inclined block, 6. centralizing piston, 7. lower mandrel, 8. upper thrust bearing, 9. driving cam, 10. one-way clutch, 11. needle roller bearing, 12. cam pin, 13. seal, 14. middle thrust bearing, 15. lower thrust bearing, 16. locking nut, 17. upper inlay, 18. lower inlay, 19. limit pin, 20. balance piston, 21. annulus hole, 22. differential pressure piston, 23. signal body, 24. lower sub, 25. clutch cage, 26. clutch wedge, 27. top surface of the lower inlay, 28. rectangular tooth groove of the lower inlay, 29. bottom surface of the lower inlay, 30. straight groove of the cam, 31. inclined groove of the cam, 32. rectangular teeth of the upper inlay, 33. bottom surface of the upper inlay, 34. oil cavity Specific embodiments

[0044] The following further describes the specific embodiments of the present invention with reference to the drawings

[0045] Embodiment 1

[0046] Refer to the appendix Figure 1, A remotely controlled variable-diameter stabilizer controlled by a clutch, comprising a body 1, a mandrel disposed within the body 1, a return spring 3, an inclined block 5, a driving mechanism sequentially disposed from top to bottom within the annular cavity between the mandrel and the body 1, and a plurality of centralizing pistons 6 radially distributed on the wall of the body 1; wherein, each centralizing piston 6 forms an axially sliding limit fit with the inclined surface on the corresponding inclined block 5. The mandrel is composed of an upper mandrel 2 and a lower mandrel 7 which are hermetically connected up and down to form a through pipe string. The outer convex platform at the top of the upper mandrel 2 forms an axially sliding seal fit with the inner wall of the body 1. The return spring 3 is disposed within the annular cavity below the outer convex platform of the upper mandrel 2. The lower end of the return spring 3 is fixedly connected to the body 1 relatively. The inclined block 5 is fixedly connected to the outer wall of the upper mandrel 2 below the return spring 3. The driving mechanism is located within the annular cavity between the lower mandrel 7 below the inclined block 5 and the body 1. Refer to the attached Figure 11 , The driving mechanism is a stroke mechanism controlled by a one-way clutch, including a driving cam 9, a one-way clutch 10, a cam pin 12, an upper fitting body 17, a lower fitting body 18 and a limit pin 19.

[0047] Among them, refer to the attached Figure 10 , The upper part of the upper fitting body 17 is rotationally and hermetically fitted with the outer wall of the lower mandrel 7. The lower part of the upper fitting body 17 has rectangular teeth 32 with chamfers. Refer to the attached Figure 8 , The upper part of the lower fitting body 18 is provided with a rectangular tooth groove 28 with chamfers that axially intermittently engages with the rectangular teeth 32 of the upper fitting body. The lower part of the lower fitting body 18 is provided with an annular groove, which axially limits and cooperates with the limit pin 19 fixed on the body 1. Refer to the attached Figure 9 , The outer circumference of the driving cam 9 is provided with an L-shaped groove composed of a cam straight groove 30 and a cam inclined groove 31, which slidably limits and cooperates with the cam pin 12 fixed on the body 1. The sliding limit cooperation between the cam pin 12 and the cam inclined groove 31 converts the axial movement of the driving cam 9 into circumferential rotation. The one-way clutch 10 is a one-way clutch 10 with the function of one-way torque transmission. The one-way clutch 10 is disposed within a preset annular cavity between the upper part of the upper fitting body 17 and the driving cam 9. The upper fitting body 17 and the driving cam 9 are axially positioned on the lower mandrel 7. The lower mandrel 7, the upper fitting body 17 and the driving cam 9 can all rotate relatively; the lower mandrel 7 and the driving cam 9 have two kinds of strokes, long and short. The inclined block 5 moves up or down with the upper mandrel 2 and drives the centralizing piston 6 to change among three positions.

[0048] Embodiment 2

[0049] On the basis of Embodiment 1, it further includes:

[0050] A balance piston 20 and a differential pressure piston 22 are sequentially installed from top to bottom between the lower end of the lower mandrel 7 and the body 1. A radially penetrating annulus hole 21 is provided on the pipe wall of the body 1 between the balance piston 20 and the differential pressure piston 22.

[0051] A signal body 23 is arranged inside the body 1 at the lower end of the lower mandrel 7. The outer diameter of the signal body 23 is smaller than the inner diameter of the lower mandrel 7. When the lower mandrel 7 travels downward for a long stroke, the lower mandrel 7 sleeves the signal body 23.

[0052] An upper thrust bearing 8 is installed between the top of the driving cam 9 and the lower mandrel 7, a middle thrust bearing 14 is installed between the bottom of the driving cam 9 and the upper fitting body 17, and a lower thrust bearing 15 is installed between the upper fitting body 17 and the locking nut 16.

[0053] An oil cavity 34 is formed between the upper mandrel 2, the lower mandrel 7 and the body 1; A needle roller bearing 11 is also installed between the upper fitting body 17 and the driving cam 9.

[0054] Refer to the appendix Figure 7 The one-way clutch 10 mainly consists of a clutch cage 25 and a clutch wedge 26.

[0055] The centering piston 6 is connected to the inclined block 5 through a T-shaped groove, and the centering piston 6 limits the axial stroke of the inclined block 5.

[0056] A seal 13 for increasing the rotational friction is installed between the upper fitting body 17 and the lower mandrel 7.

[0057] A plurality of L-shaped grooves on the driving cam 9 are evenly distributed along the outer circumference of the driving cam 9; The body 1 is provided with a spiral wing band, and each wing is provided with a plurality of centering pistons 6.

[0058] The lower end of the return spring 3 is a spring seat 4, and the spring seat 4 is clamped inside the upper end of the body 1; The upper fitting body 17 and the driving cam 9 are axially positioned on the lower mandrel 7 through the locking nut 16.

[0059] Typical Embodiment 3

[0060] Refer to the appendix Figure 1The clutch-controlled remote control variable diameter stabilizer comprises a body 1, the lower end of the body 1 is connected to the lower joint 24, and the upper end of the body 1 and the lower end of the lower joint 24 are respectively connected to the upper and lower drill strings. The body 1 is equipped with an upper mandrel 2 and a lower mandrel 7, the upper mandrel 2 and the lower mandrel 7 are fixedly connected from top to bottom, and the inner cavity of the upper mandrel 2 and the lower mandrel 7 is a drilling fluid channel. A signal body 23 is arranged between the lower end of the lower mandrel 7 and the lower joint 24. A return spring 3 is arranged on the upper mandrel 2, the upper end of the return spring 3 is limited by the outer convex step at the top of the upper mandrel 2, and the lower end of the return spring 3 is a spring seat 4, and the spring seat 4 forms a limit fit with the body 1. Inside the body 1 below the spring seat 4, an inclined block 5 is externally arranged below the upper mandrel 2, and a radial piston hole is arranged on the body 1 corresponding to the outside of the inclined block 5, and a straightening piston 6 is installed in the piston hole, and the inner end of the straightening piston 6 is connected to the inclined block 5 through a T-shaped groove. The space between the upper mandrel 2, the lower mandrel 7 and the body 1 is an oil chamber 34, which is filled with oil. At the lower end of the lower mandrel 7, a balancing piston 20 and a differential pressure piston 22 are sequentially installed between the lower mandrel 7 and the body 1 from top to bottom, and a through annular hole 21 is provided on the tube wall of the body 1 between the balancing piston 20 and the differential pressure piston 22.

[0061] Refer to the attached Figure 11 and Figure 12 , a travel mechanism controlled by a one-way clutch is installed above the balance piston 20 outside the lower mandrel 7, and the travel mechanism controlled by the one-way clutch includes an upper thrust bearing 8, a driving cam 9, a needle bearing 11, a one-way clutch 10, a cam pin 12, a middle thrust bearing 14, an upper chimera 17, a lower thrust bearing 15, a locking nut 16, a lower chimera 18, and a limit pin 19. On the upper part of the lower mandrel 7, a locking nut 16, an upper chimera 17, a needle bearing 11, a one-way clutch 10, and a driving cam 9 are installed from inside to outside. Among them, an upper thrust bearing 8 is installed between the top of the driving cam 9 and the lower mandrel 7, a middle thrust bearing 14 is installed between the bottom of the driving cam 9 and the upper chimera 17, and a lower thrust bearing 15 is installed between the upper chimera 17 and the locking nut 16. The upper chimeric body 17 and the driving cam 9 are axially positioned on the lower mandrel 7 through the locking nut 16, and a seal 13 for increasing the rotational friction is installed between the upper chimeric body 17 and the lower mandrel 7. A needle bearing 11 and a one-way clutch 10 are installed between the upper chimeric body 17 and the driving cam 9. The one-way clutch 10 is embedded between the driving cam 9 and the upper chimeric body 17 to transmit torque in one direction, and has a function similar to a ratchet.

[0062] Refer to the attached Figure 7, the one-way clutch 10 mainly consists of a clutch cage 25 and a clutch wedge 26. When the drive cam 9 rotates unidirectionally, the clutch wedge 26 is in a locked state, and the drive cam 9 drives the upper fitting body 17 to rotate. When the drive cam 9 rotates in the reverse direction (clockwise when viewed from above), the upper fitting body 17 does not rotate with the drive cam 9. The needle bearing 11 precisely controls the mating clearance between the drive cam 9 and the upper fitting body 17 to ensure the stable operation of the one-way clutch 10. The cam pin 12 is fixed inside the body 1 and has a protruding pin shaft, and its pin shaft can slide in the cam straight groove 30 and the cam inclined groove 31 on the drive cam 9 (refer to the appendix Figure 9 ), and the sliding fit between the cam pin 12 and the cam inclined groove 31 converts the axial movement of the drive cam 9 into circumferential rotation. The lower mandrel 7, the upper fitting body 17, and the drive cam 9 can all rotate relative to each other. The lower fitting body 18 is installed below the upper fitting body 17 through a limit pin 19. The limit pin 19 is fixed on the body 1 and axially limits the lower fitting body 18, and the lower fitting body 18 can rotate relative to the limit pin 19. Each time the upper fitting body 17 rotates and descends to the lower fitting body 18 for limiting, the rectangular teeth 32 of the upper fitting body are intermittently engaged with the rectangular tooth grooves 28 of the lower fitting body.

[0063] Refer to the appendix Figure 1 , there is a spiral wing band on the body 1, and there are multiple centralizing pistons 6 on each wing. The centralizing piston 6 is pushed out or pulled back by the inclined block 5. When the inclined block 5 descends, it pushes the centralizing piston to extend outside the body, and the outer diameter of the tool becomes larger; when the inclined block ascends, since the inclined block 5 and the centralizing piston 6 are connected through a T-shaped groove structure, the inclined plane body pulls the piston back into the body 1, and the outer diameter of the tool becomes smaller. The diameter-changing range of the remotely controlled diameter-changing stabilizer is controlled by the descending distance of the inclined block 5. The greater the descending distance of the inclined block 5, the greater the extending length of the piston. The centralizing piston 6 also limits the axial stroke of the inclined block 5.

[0064] Application Example 4

[0065] The remotely controlled diameter-changing stabilizer controlled by the clutch of the present invention is connected in series to the drill string. The working process of the upper mandrel 2 and the lower mandrel 7 is as follows: When the pump is started and the drilling fluid flows through the drill string, the internal pressure of the drill tool is the pump pressure inside the diameter-changing stabilizer, and the pressure in the oil chamber 34 is the annulus pressure due to the annulus hole 21 at the lower part of the diameter-changing stabilizer. During drilling, there is a pressure drop between the drill tool and the drill bit at the lower part of the diameter-changing stabilizer. The pressure inside the drill tool is greater than the annulus pressure. Since the upper plane of the piston of the upper mandrel 2 is subjected to the pressure inside the drill tool and the lower plane is subjected to the annulus pressure, the upper mandrel 2 generates a downward driving force and descends to compress the return spring 3. At the same time, the lower mandrel 7 fixedly connected together also descends, and the stroke mechanism controlled by the one-way clutch acts accordingly. When the pump is stopped, the internal and external pressures of the diameter-changing stabilizer are balanced, the return spring 3 rebounds, pushes the upper mandrel 2 and the lower mandrel 7 to ascend, and the stroke mechanism controlled by the one-way clutch acts again.

[0066] The operation process of the stroke mechanism controlled by the one-way clutch in the remotely controlled variable-diameter stabilizer with clutch control is as follows: There are multiple L-shaped grooves composed of a cam straight groove 30 and a cam inclined groove 31 on the driving cam 9, which are evenly distributed along the outer circumference of the driving cam 9. After the first pump start, the driving cam 9 descends once with the lower mandrel 7. During the descending process, since the cam pin 12 moves relative to the L-shaped groove on the driving cam 9, the driving cam 9 will rotate counterclockwise (viewed from top to bottom) while descending. At this time, the clutch wedge 26 of the one-way clutch 10 rotates and expands radially, and the wedge 26 locks. The upper fitting body 17 will rotate with the rotation of the driving cam 9 (refer to the appendix Figure 12 ), until the cam pin 12 leaves the inclined groove 31 and enters the cam straight groove 30. At this time, the rectangular teeth 32 of the upper fitting body contact the top surface 27 of the lower fitting body, and the lower mandrel 7 can no longer descend. The centralizing piston 6 is flush with the outer cylindrical surface of the body 1. The descending distance of the upper mandrel 2 and the lower mandrel 7 is relatively short this time. Refer to the appendix Figure 2 and Figure 5 . When the pump stops and the return spring 3 rebounds to drive the upper mandrel 2 to ascend, refer to the appendix Figure 4 , the driving cam 9 will rotate clockwise (viewed from top to bottom) while ascending. At this time, the clutch wedge 26 of the one-way clutch 10 rotates and retracts radially, and the wedge 26 releases the lock. The upper fitting body 17 does not rotate with the rotation of the driving cam 9 until the inclined block 5 contacts the centralizing piston 6. At this time, the lower mandrel 7 can no longer ascend. The ascending distance of the upper mandrel 2 and the lower mandrel 7 is relatively short this time. The centralizing piston 6 retracts into the body 1. Refer to the appendix Figure 1 、 Figure 4 、and Figure 11 . When the pump starts again, the driving cam 9 descends with the lower mandrel 7. During the descending process, since the cam pin 12 moves relative to the L-shaped groove on the driving cam 9, the driving cam 9 will rotate counterclockwise (viewed from top to bottom) while descending. At this time, the clutch wedge 26 of the one-way clutch 10 rotates and expands radially, and the wedge 26 locks. The upper fitting body 17 will rotate with the rotation of the driving cam 9 until the cam pin 12 leaves the cam inclined groove 31 and enters the cam straight groove 30. Due to the rotation of the upper fitting body 17, the rectangular teeth 32 of the upper fitting body 17 can just mesh with the rectangular tooth grooves 28 of the lower fitting body 18 of the lower fitting body at this time. The lower mandrel 7 can continue to descend until the bottom surface 33 of the upper fitting body contacts the bottom surface 29 of the lower fitting body, and the lower mandrel 7 can no longer descend. At this time, the centralizing piston 6 extends out of the outer cylindrical surface of the body 1. The descending distance of the upper mandrel 2 and the lower mandrel 7 is relatively long this time. Refer to the appendix Figure 3 and Figure 6When the pump is stopped again, the return spring 3 rebounds and drives the upper mandrel 2 upward, and the driving cam 9 will not rotate during the upward process until the cam pin 12 leaves the cam straight groove 30 and enters the cam inclined groove 31, and the driving cam 9 starts to rotate clockwise (from top to bottom). At this time, the clutch wedge 26 of the one-way clutch 10 is in a free state, and the upper chimeric body 17 does not rotate with the rotation of the driving cam 9 until the inclined block 5 and the straightening piston 6 contact. At this time, the lower mandrel 7 can no longer go up, and the straightening piston 6 retracts into the body 1. This time, the upper mandrel 2 and the lower mandrel 7 move up a longer distance, refer to the attached Figure 1 , Figure 4 and Figure 11 .

[0067] In this way, the cycle continues. Each time the pump is turned on, the stroke mechanism controlled by the one-way clutch is actuated once, the upper core shaft 2 and the lower core shaft 7 move upward and downward, and have two long and short strokes. The inclined block 5 installed on the upper core shaft 2 drives the straightening piston 6 to change between three positions, and the outer diameter state of the variable diameter stabilizer is switched once, thereby realizing the switching of the outer diameter state of the variable diameter stabilizer.

[0068] The outer diameter status monitoring of the variable diameter stabilizer: The outer diameter of the signal body 23 is smaller than the inner diameter of the lower mandrel 7. Since the downward stroke of the lower mandrel 7 is different, when the downward stroke of the lower mandrel 7 is a short stroke, the lower mandrel 7 does not cover the signal body 23 at the end of the downward stroke, and the drilling fluid can hardly be throttled. Figure 2 When the lower mandrel 7 descends for a long distance, the lower mandrel 7 covers the signal body 23 at the end of the downward movement, and the drilling fluid flow area is significantly reduced, producing a throttling effect. Figure 3 , the pump pressure of the ground drilling pump increases. During the drilling process, the outer diameter state of the downhole variable diameter stabilizer is determined by the change of this pump pressure.

Claims

1. A remotely controlled variable-diameter stabilizer controlled by a clutch, comprising a body (1), a mandrel disposed within the body (1), a return spring (3), an inclined block (5), a drive mechanism successively disposed from top to bottom within the annular cavity between the mandrel and the body (1), and a plurality of centralizing pistons (6) radially distributed on the wall of the body (1); Wherein, Each centralizing piston (6) forms an axially sliding limit fit with the inclined surface on the corresponding inclined block (5). The mandrel is composed of an upper mandrel (2) and a lower mandrel (7) which are hermetically connected up and down to form a through pipe string. The outer convex platform at the top of the upper mandrel (2) forms an axially sliding seal fit with the inner wall of the body (1). The return spring (3) is disposed within the annular cavity below the outer convex platform of the upper mandrel (2). The lower end of the return spring (3) is fixedly connected to the body (1) relatively. The inclined block (5) is fixedly connected to the outer wall of the upper mandrel (2) below the return spring (3). The drive mechanism is located within the annular cavity between the lower mandrel (7) and the body (1) below the inclined block (5). It is characterized in that: the drive mechanism is a stroke mechanism controlled by a one-way clutch, including a drive cam (9), a one-way clutch (10), a cam pin (12), an upper fitting body (17), a lower fitting body (18) and a limit pin (19); wherein, the upper part of the upper fitting body (17) is rotationally sealed with the outer wall of the lower mandrel (7). The lower part of the upper fitting body (17) has rectangular teeth (32) with chamfers; the upper part of the lower fitting body (18) is provided with rectangular tooth grooves (28) with chamfers that are axially intermittently engaged with the rectangular teeth (32) of the upper fitting body. The lower part of the lower fitting body (18) is provided with an annular groove, which is axially limited and fitted with the limit pin (19) fixed on the body (1); on the outer circumference of the drive cam (9), there is an L-shaped groove composed of a cam straight groove (30) and a cam inclined groove (31), which is slidably limited and fitted with the cam pin (12) fixed on the body (1). The sliding limit fit between the cam pin (12) and the cam inclined groove (31) converts the axial movement of the drive cam (9) into circumferential rotation; the one-way clutch (10) is a one-way clutch (10) with the function of one-way torque transmission. The one-way clutch (10) is disposed within a preset annular cavity between the upper part of the upper fitting body (17) and the drive cam (9); the upper fitting body (17) and the drive cam (9) are axially positioned on the lower mandrel (7). The lower mandrel (7), the upper fitting body (17) and the drive cam (9) can all rotate relative to each other; the lower mandrel (7) and the drive cam (9) have two kinds of strokes, long and short. The inclined block (5) moves up or down with the upper mandrel (2) and drives the centralizing piston (6) to change among three positions; an upper thrust bearing (8) is installed between the top of the drive cam (9) and the lower mandrel (7), a middle thrust bearing (14) is installed between the bottom of the drive cam (9) and the upper fitting body (17), and a lower thrust bearing (15) is installed between the upper fitting body (17) and the lock nut (16); the centralizing piston (6) is connected to the inclined block (5) through a T-shaped groove, and the centralizing piston (6) limits the axial stroke of the inclined block (5).

2. The remotely controlled variable-diameter stabilizer with clutch control according to claim 1, characterized in that: a balance piston (20) and a differential pressure piston (22) are successively installed from top to bottom between the lower end of the lower mandrel (7) and the body (1), and an annular hole (21) penetrating radially is provided on the pipe wall of the body (1) between the balance piston (20) and the differential pressure piston (22).

3. The remotely controlled variable-diameter stabilizer with clutch control according to claim 2, characterized in that: a signal body (23) is arranged in the body (1) at the lower end of the lower mandrel (7), the outer diameter of the signal body (23) is smaller than the inner diameter of the lower mandrel (7), and when the lower mandrel (7) travels a long stroke downward, the lower mandrel (7) sleeves the signal body (23).

4. The remotely controlled variable-diameter stabilizer with clutch control according to claim 1 or 2, 3, characterized in that: an oil chamber (34) is formed between the upper mandrel (2), the lower mandrel (7) and the body (1); a needle roller bearing (11) is further installed between the upper fitting body (17) and the drive cam (9).

5. The remotely controlled variable-diameter stabilizer with clutch control according to claim 1 or 2, 3, characterized in that: the one-way clutch (10) is composed of a clutch cage (25) and a clutch wedge (26).

6. The remotely controlled variable-diameter stabilizer with clutch control according to claim 1 or 2, 3, characterized in that: a seal (13) for increasing the rotational frictional force is installed between the upper fitting body (17) and the lower mandrel (7).

7. The remotely controlled variable-diameter stabilizer with clutch control according to claim 1 or 2, 3, characterized in that: a plurality of L-shaped grooves on the drive cam (9) are evenly distributed along the outer circumference of the drive cam (9); the body (1) is provided with a spiral fin belt, and each fin is provided with a plurality of centralizing pistons (6).

8. The remotely controlled variable-diameter stabilizer with clutch control according to claim 1 or 2, 3, characterized in that: it further includes a spring seat (4) and a lock nut (16), the lower end of the return spring (3) is the spring seat (4), and the spring seat (4) is clamped and fixed inside the upper end of the body (1); the upper fitting body (17) and the drive cam (9) are axially positioned on the lower mandrel (7) through the lock nut (16).

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