CN103821821B - A kind of thrust bearing group of automatic adjustment turbodrill thrust load - Google Patents

Abstract

The present invention relates to a kind of thrust bearing group of automatic adjustment turbodrill thrust load, it is made up of upper bearing group and lower bearing group, and upper bearing group is installed on the top of turbine shaft, and lower bearing group is installed on the bottom of turbine shaft.Described upper bearing group is made up of 3 ~ 5 secondary upper bearings, and upper bearing is made up of upper bearing rotating ring and upper bearing stationary ring; Described lower bearing group is made up of 3 ~ 5 secondary lower bearings, and lower bearing is made up of lower bearing rotating ring and lower bearing stationary ring; Spindle nose locking nut, out splice going splice adopt with turbine shaft and are threaded, and are pressed on turbine shaft by upper bearing rotating ring and lower bearing rotating ring, and upper bearing rotating ring and lower bearing rotating ring are with turbine shaft synchronous axial system.The present invention is according to the size and Orientation of the thrust load of turbodrill, and automatically regulate the size that pod apertures is opened, the hydraulic load that turbine section is produced and the pressure of the drill are in transient equiliblium, and bearing no longer withstands shocks life-span of load, raising turbodrill.

Description

A Thrust Bearing Set Automatically Adjusting the Axial Load of a Turbodrill

technical field

The invention relates to a thrust bearing group for automatically adjusting the axial load of a turbine drilling tool, which belongs to the field of downhole power drilling tools for oil and gas.

Background technique

Turbodrilling tools have good development potential in ultra-deep well drilling and anti-deviation drilling, which can significantly increase the mechanical penetration rate and reduce drilling costs. With the development of drilling technology, the demand for turbodrills is increasing, but the service life of turbodrills is unstable, which limits the application and promotion of turbodrills. The service life of the turbodrill depends on the life of the thrust bearing group. The thrust bearing group works under high temperature, high speed and heavy load conditions. The thrust bearing group has a short life and is prone to failure. After the thrust bearing group fails, it is necessary to trip out the drill to replace the bearing, which is time-consuming and labor-intensive, and increases the cost. The existing thrust bearing group can only passively bear the downward hydraulic load and the upward drilling pressure, and cannot actively balance and adjust the axial load of the turbodrill, resulting in poor bearing capacity and short life of the thrust bearing group. Therefore, improving the structure of the thrust bearing group, improving the load-bearing performance of the thrust bearing group, reducing the impact load of the thrust bearing group, and increasing the life of the thrust bearing group are the keys to improving the life of the turbodrill.

Contents of the invention

The purpose of the present invention is to overcome the deficiencies of the prior art and provide a thrust bearing group that automatically adjusts the axial load of a turbodrill to realize the automatic adjustment of the axial load of a turbodrill so that the hydraulic load of the turbodrill and the weight-on-bit Being in dynamic balance, the thrust bearing group no longer bears the impact load, which improves the service life of the turbodrill.

Technical scheme of the present invention is:

The invention relates to a thrust bearing group for automatically adjusting the axial load of a turbo drilling tool, which is composed of an upper bearing group and a lower bearing group. The upper bearing group is installed on the top end of the turbine shaft, and the lower bearing group is installed on the bottom end of the turbine shaft. The upper bearing group is composed of 3 to 5 pairs of upper bearings, and the upper bearing is composed of the upper bearing dynamic ring and the upper bearing static ring; the lower bearing group is composed of 3 to 5 pairs of lower bearings, and the lower bearing is composed of the lower bearing dynamic ring and the upper bearing static ring. The lower bearing static ring is composed of; the shaft head lock nut, the output joint and the turbine shaft are connected by threads, and the upper bearing dynamic ring and the lower bearing dynamic ring are pressed on the turbine shaft, and the upper bearing dynamic ring and the lower bearing dynamic ring follow the turbine shaft. synchronous rotation. The upper joint and the lower joint are connected with the shell by threads, and the upper bearing static ring is pressed tightly in the pressure relief sleeve, and the lower bearing static ring is pressed tightly in the shell at the same time, the upper bearing static ring, the lower bearing static ring, and the pressure relief The sleeve and the housing remain stationary and do not rotate; the upper joint is connected with the drill string, and the output joint is connected with the drill bit.

The upper bearing group and the lower bearing group only bear unidirectional load, and the two do not work simultaneously. The upper bearing group relies on the circular diamond wear-resistant plates of the upper bearing dynamic ring and the upper bearing static ring to withstand the downward hydraulic load, and the lower bearing group relies on the lower bearing dynamic ring and the lower bearing static ring circular diamond wear-resistant plates to withstand the upward hydraulic load. drill pressure. According to the size and direction of the axial load of the turbine, the thrust bearing group automatically adjusts the opening size of the diversion holes of the upper bearing static ring and the lower bearing moving ring, and changes the hydraulic load of the turbine shaft, so that the hydraulic load on the turbine shaft It is in dynamic balance with the drilling weight, realizes the automatic adjustment of the axial load of the turbodrill, reduces the load and impact of the thrust bearing group, and prolongs the service life of the thrust bearing group.

The friction surface of the upper bearing moving ring is evenly inlaid with circular diamond wear-resistant sheets. The static ring of the upper bearing is composed of a static ring seat, a butterfly spring, a sliding body of the static ring, a positioning pin, and an O-shaped sealing ring. The static ring seat is evenly distributed with 4 diversion holes and 4 positioning pin holes along the circumferential direction, and 4 butterfly spring installation holes are evenly distributed on the inner bottom surface. The lower surface of the static ring sliding body is evenly distributed with 4 butterfly spring installation holes, and the upper surface is evenly inlaid with circular diamond wear-resistant sheets on the friction surface. The outer diameter of the static ring sliding body is provided with an O-ring ring groove and is evenly distributed 4 a limit slot. The O-shaped sealing ring is installed in the O-ring ring groove of the static ring sliding body, and is used to seal the static ring seat and the static ring sliding body, prevent drilling fluid particles from entering the sliding surface, and prevent the static ring sliding body from being trapped in the static ring. The seat cannot be moved. The belleville springs are combined and installed in the belleville spring mounting holes of the stationary ring seat and the stationary ring sliding body. The positioning pin is installed in the positioning pin hole and the limiting groove. Relying on the spring force of the butterfly spring and the limit of the positioning pin, the static ring seat, the butterfly spring and the sliding body of the static ring are fixed as a whole to form the upper bearing static ring. The compression deformation of the butterfly spring can allow the sliding body of the static ring to move axially in the seat of the static ring, and the movement of the sliding body of the static ring can realize the opening and closing of the diversion hole.

The friction surface of the static ring of the lower bearing is evenly inlaid with circular diamond wear-resistant sheets. The moving ring of the lower bearing is composed of a moving ring seat, a butterfly spring, a sliding body of the moving ring, a positioning pin, and first and second O-rings. The moving ring seat has 4 diversion holes and 4 positioning pin holes evenly distributed along the circumference, and 4 butterfly spring installation holes are evenly distributed on the inner bottom surface. The lower surface of the moving ring sliding body is evenly distributed with 4 butterfly spring installation holes, the upper surface is a friction surface evenly inlaid with circular diamond wear-resistant sheets, and the outer and inner diameters of the moving ring sliding body are equipped with O-rings Ring groove, 4 limit grooves are evenly distributed on the outer diameter of the sliding ring of the moving ring. The first and second O-rings are installed in the O-ring groove of the sliding body of the moving ring, used to seal the moving ring seat and the sliding body of the moving ring, prevent drilling fluid particles from entering the sliding surface, and prevent the sliding of the moving ring The body cannot move in the moving ring seat. The butterfly springs are combined and installed in the butterfly spring mounting holes of the moving ring base and the sliding body of the moving ring. The positioning pin is installed in the positioning pin hole and the limiting groove. Relying on the spring force of the butterfly spring and the limit of the positioning pin, the moving ring seat, the butterfly spring and the sliding body of the moving ring are fixed together to form the lower bearing moving ring. The compression deformation of the butterfly spring can allow the moving ring sliding body to move axially in the moving ring seat, and the movement of the moving ring sliding body can realize the opening and closing of the diversion hole.

The upper disk and the lower ring of the pressure relief sleeve are uniformly provided with 4 drilling fluid passages along the circumferential direction, and the pressure relief passages are provided radially on the upper disk. 12 to 20 diversion holes are evenly distributed on the pressure relief sleeve. The diversion hole of the pressure relief sleeve communicates with the diversion hole of the upper bearing static ring, and the diameter of the diversion hole of the pressure relief sleeve is 4 to 6 mm larger than the diameter of the diversion hole of the upper bearing static ring. Misalignment due to axial compression of the turbodrill. The inner surface of the upper disc is inlaid with a ring-shaped diamond wear-resistant sheet. The drilling fluid channel is used to guide the drilling fluid into the turbine stator and the turbine rotor.

The housing is provided with 2 pressure relief holes, the pressure relief holes of the housing communicate with the pressure relief channel of the pressure relief sleeve, and the diameter of the pressure relief hole of the housing is 4~ 6 mm, to avoid misalignment of the pressure relief hole and the pressure relief flow channel due to the axial compression of the turbodrill. The pressure relief hole facilitates the discharge of drilling fluid to the drilling annulus.

The turbine shaft is evenly distributed with 12 to 20 diversion holes along the circumference, and the turbine shaft communicates with the diversion holes of the lower bearing moving ring, and the diameter of the diversion holes of the turbine shaft is 4 to 30 times larger than the diameter of the diversion holes of the lower bearing moving ring. 6 mm, to avoid misalignment of the diversion hole due to the axial compression of the turbodrill.

The top of the turbine shaft is inlaid with a ring-shaped diamond wear-resistant sheet. After the top of the turbine shaft and the ring-shaped diamond wear-resistant plate on the inner surface of the upper disc are loaded, the overload of the lower bearing group can be avoided, and the butterfly spring of the moving ring of the lower bearing can be prevented from failing due to flattening. The friction surfaces of the overload protection moving ring and the overload protection static ring are inlaid with ring-shaped diamond wear-resistant sheets. The annular diamond wear-resistant plates of the overload protection moving ring and the overload protection static ring can avoid the overload of the upper bearing group and prevent the flattening failure of the butterfly spring of the upper bearing static ring.

Compared with the prior art, the present invention has the following advantages: 1. With the change of drilling conditions, the thrust bearing group automatically adjusts the opening size of the diversion hole according to the size and direction of the axial load of the turbodrill, so that the turbine section produces The hydraulic load and drilling pressure are in dynamic balance, and the bearing no longer bears the impact load, which improves the life of the turbodrill. 2. The thrust bearing set adopts the installation method of the upper bearing set and the lower bearing set, and the disassembly, maintenance and installation of the thrust bearing set are convenient.

Description of drawings

Fig. 1 is a schematic diagram of a thrust bearing group in a turbodrill that automatically adjusts the axial load of a turbodrill of the present invention;

Fig. 2 is a three-dimensional solid sectional view of the upper bearing of the present invention;

Fig. 3 is a three-dimensional solid sectional view of the lower bearing of the present invention;

Fig. 4 is a three-dimensional solid assembly sectional view of the upper bearing of the present invention;

Fig. 5 is a three-dimensional solid assembly sectional view of the lower bearing of the present invention;

Fig. 6 is a three-dimensional solid sectional view of the pressure relief sleeve of the present invention;

Fig. 7 is a schematic diagram of the structure when the present invention is installed in a turbodrill and the drilling pressure is less than the hydraulic load;

Fig. 8 is a schematic diagram of the structure when the present invention is installed in a turbodrill and the drilling pressure is greater than the hydraulic load.

In the figure: 1. Upper bearing group, 2. Lower bearing group, 3. Turbine shaft, 4. Upper bearing, 5. Lower bearing, 6. Upper bearing moving ring, 7. Upper bearing stationary ring, 8. Lower bearing moving ring , 9. The static ring of the lower bearing, 10. The shaft head lock nut, 11. The output joint, 12. The upper joint, 13. The lower joint, 14. The shell, 15. The pressure relief sleeve, 16. The circular diamond wear-resistant Sheet, 17. Static ring seat, 18. Butterfly spring, 19. Static ring sliding body, 20. Locating pin, 21. O-ring, 22. Diversion hole, 23. Locating pin hole, 24. Butterfly spring Mounting hole, 25. Butterfly spring mounting hole, 26. Round diamond wear-resistant sheet, 27. O-ring ring groove, 28. Limit groove, 29. Moving ring seat, 30. Butterfly spring, 31. Moving Ring sliding body, 32. positioning pin, 33. first O-ring, 34. second O-ring, 35. diversion hole, 36. positioning pin hole, 37. butterfly spring mounting hole, 38. butterfly Spring mounting hole, 39. Round diamond wear-resistant sheet, 40. O-ring ring groove, 41. Limit groove, 42. O-ring ring groove, 43. Round diamond wear-resistant sheet, 44. Upper part Disc, 45. lower ring, 46. drilling fluid flow channel, 47. pressure relief flow channel, 48. diversion hole, 49. annular diamond wear plate, 50. turbine stator, 51. turbine rotor, 52. discharge Pressure hole, 53. diversion hole, 54. annular diamond wear-resistant plate, 55. overload protection moving ring, 56. overload protection static ring, 57. annular diamond wear-resistant plate, 58. annular diamond wear-resistant plate.

detailed description

Below in conjunction with accompanying drawing and embodiment the present invention will be further described:

As shown in Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5 and Fig. 6, a thrust bearing group for automatically adjusting the axial load of a turbodrill in the present invention is composed of an upper bearing group 1 and a lower bearing group 2 , The upper bearing set 1 is installed on the top end of the turbine shaft 3, and the lower bearing set 2 is installed on the bottom end of the turbine shaft 3. The upper bearing group 1 is composed of 3 to 5 pairs of upper bearings 4, and the upper bearing 4 is composed of an upper bearing moving ring 6 and an upper bearing static ring 7; the lower bearing group 2 is composed of 3 to 5 pairs of lower bearings 5, and the lower The bearing 5 is composed of the lower bearing moving ring 8 and the lower bearing static ring 9; the shaft head lock nut 10, the output joint 11 and the turbine shaft 3 are threadedly connected, and the upper bearing moving ring 6 and the lower bearing moving ring 8 are pressed against the turbine shaft. On the shaft 3, the upper bearing moving ring 6 and the lower bearing moving 8 ring rotate synchronously with the turbine shaft 3. The upper joint 12 and the lower joint 13 are threadedly connected with the housing 14, and the upper bearing static ring 7 is pressed in the pressure relief sleeve 15, and the lower bearing static ring 9 is pressed in the housing 14 at the same time, and the upper bearing static ring 7. The static ring 9 of the lower bearing, the pressure relief sleeve 15 and the housing 14 remain stationary and do not rotate. The upper joint 12 is connected with the drill string, and the output joint 11 is connected with the drill bit.

As shown in Fig. 1, Fig. 2 and Fig. 3, the upper bearing set 1 and the lower bearing set 2 only bear unidirectional load, and the two do not work simultaneously. The upper bearing group 1 relies on the circular diamond wear-resistant plate 16 of the upper bearing dynamic ring 6 and the circular diamond wear-resistant plate 26 of the upper bearing static ring 7 to bear the downward hydraulic load; the lower bearing group 2 relies on the lower bearing dynamic ring 8 The circular diamond wear-resistant plate 43 of the lower bearing static ring 9 and the circular diamond wear-resistant plate 39 of the lower bearing static ring 9 are used to withstand the upward drilling pressure; the thrust bearing group automatically adjusts the upper bearing static ring 7 according to the size and direction of the axial load of the turbine The size of the opening of the guide hole 22 and the guide hole 35 of the lower bearing moving ring 8 changes the size of the hydraulic load on the turbine shaft 3, so that the hydraulic load on the turbine shaft 3 and the drilling pressure are in a dynamic balance.

As shown in Figure 2 and Figure 4, the friction surface of the upper bearing moving ring 6 is evenly inlaid with a circular diamond wear-resistant sheet 16; body 19, locating pin 20, O-ring 21; the static ring seat 17 is evenly distributed along the circumference of the four diversion holes 22 and four locating pin holes 23, the inner bottom surface is evenly distributed four butterfly spring mounting holes 24. Four butterfly spring installation holes 25 are evenly distributed on the lower surface of the static ring sliding body 19, and the upper surface is a friction surface evenly inlaid with a circular diamond wear-resistant sheet 26; the outer diameter of the static ring sliding body 19 is provided with O-shaped Sealing ring groove 27 and 4 limit grooves 28 are evenly distributed; the O-ring sealing ring 21 is installed in the O-ring sealing ring groove 27 of the static ring sliding body 19, and the O-ring sealing ring 21 is used to seal the static ring seat 17 and the static ring sliding body 19 prevent drilling fluid particles from entering the sliding subsurface, and prevent the static ring sliding body 19 from being unable to move in the static ring seat 17.

Described disc spring 18 is a pairing combination, is installed in the disc spring mounting hole 24 of static ring seat 17 and the disc spring mounting hole 25 of static ring sliding body 19; Described locating pin 20 is installed in locating pin hole 23 and In the limit groove 28, rely on the spring force of the butterfly spring 18 and the limit of the positioning pin 20, the static ring seat 17, the butterfly spring 18 and the static ring sliding body 19 are fixed as one to form the upper bearing static ring 7; The compression deformation of the spring 18 allows the static ring sliding body 19 to move axially in the static ring seat 17, and the movement of the static ring sliding body 19 can realize the opening and closing of the flow guide hole 22.

As shown in FIG. 3 and FIG. 5 , the friction surface of the lower bearing static ring 9 is evenly inlaid with circular diamond wear-resistant plates 39 . The lower bearing moving ring 8 is composed of a moving ring seat 29, a butterfly spring 30, a moving ring sliding body 31, a positioning pin 32, first and second O-ring seals (33, 34); the moving ring seat 29 Four guide holes 35 and four positioning pin holes 36 are evenly distributed along the circumference, and four butterfly spring installation holes 37 are evenly distributed on the inner bottom surface; four butterfly spring installation holes 38 are evenly distributed on the lower surface of the moving ring sliding body 31 , the upper surface of which is a friction surface evenly inlaid with a circular diamond wear-resistant sheet 43; the outer diameter of the moving ring sliding body 31 is provided with an O-ring ring groove 40 and four limit grooves 41 are evenly distributed, and the moving ring sliding body 31 There is an O-ring ring groove 42 on the inner diameter of the inner diameter; the first O-ring 33 is installed in the O-ring groove 40 of the moving ring sliding body 31, and the second O-ring 34 is installed in the moving In the O-shaped sealing ring groove 42 of the ring sliding body 31, the first and second O-ring sealing rings (33, 34) are used to seal the moving ring seat 29 and the moving ring sliding body 31 to prevent drilling fluid particles from entering the sliding surface. Avoid that the moving ring sliding body 31 cannot move in the moving ring seat 29 .

The butterfly spring 30 is a combination, installed in the butterfly spring mounting hole 36 of the moving ring seat 29 and the butterfly spring mounting hole 37 of the moving ring sliding body 31; the positioning pin 32 is mounted in the positioning pin hole 36 And in the limit groove 41, rely on the spring force of the butterfly spring 30 and the limit of the positioning pin 32, the moving ring seat 29, the butterfly spring 30 and the moving ring sliding body 31 are fixed as one to form the lower bearing moving ring 8; The compression deformation of the butterfly spring 30 allows the moving ring sliding body 31 to move axially in the moving ring seat 29 , and the movement of the moving ring sliding body 31 can realize the opening and closing of the diversion hole 35 .

As shown in Figures 1 and 6, the upper disk 44 and the lower ring 45 of the pressure relief sleeve 15 are evenly provided with four drilling fluid flow channels 46 along the circumferential direction, and the upper disk 44 is provided with a discharge channel in the radial direction. Pressure flow channel 47; 12 diversion holes 48 are evenly distributed on the pressure relief sleeve 15; the inner surface of the upper disc 44 is inlaid with annular diamond wear-resistant plates 49; the drilling fluid flow channel 46 is used to guide the drilling fluid into the turbine The stator 50 and the turbine rotor 51; the diversion hole 48 of the pressure relief sleeve 15 communicates with the diversion hole 22 of the upper bearing stationary ring 7, and the diameter of the diversion hole 48 of the pressure relief sleeve 15 is smaller than the diversion hole 48 of the upper bearing stationary ring 7 The diameter of the hole 22 is 4 to 6 millimeters larger, so as to avoid misalignment of the diversion hole 48 and the diversion hole 22 due to the axial compression of the turbodrill.

As shown in Figure 1, the housing 14 is provided with two pressure relief holes 52, the pressure relief holes 52 of the housing 14 communicate with the pressure relief channel 47 of the pressure relief sleeve 15, and the pressure relief holes 52 of the housing 14 The diameter is 4 to 6 millimeters larger than the diameter of the relief flow channel 47 of the pressure relief sleeve 15, so as to avoid misalignment of the pressure relief hole 52 and the pressure relief flow path 47 due to the axial compression of the turbodrill. The pressure relief hole 52 facilitates the discharge of drilling fluid to the drilling annulus.

As shown in Figure 1, the hollow shaft section of the turbine shaft 3 is evenly distributed with 12 guide holes 53 along the circumference, the turbine shaft 3 communicates with the guide holes 35 of the lower bearing moving ring 8, and the guide holes 53 of the turbine shaft 3 The diameter is 4-6 millimeters larger than the diameter of the diversion hole 35 of the lower bearing moving ring 8, so as to avoid misalignment of the diversion hole 53 and the diversion hole 35 due to the axial compression of the turbodrill.

As shown in Figures 1 and 6, the top of the turbine shaft 3 is inlaid with a ring-shaped diamond wear-resistant sheet 54, and the ring-shaped diamond wear-resistant sheet 54 at the top of the turbine shaft 3 and the ring-shaped diamond wear-resistant sheet 49 on the inner surface of the upper disc 44 are loaded. , can avoid the overload of the lower bearing group 2, and prevent the butterfly spring 30 of the lower bearing moving ring 8 from being flattened and failing. The friction surface of the overload protection moving ring 55 is inlaid with an annular diamond wear-resistant sheet 57 , and the friction surface of the overload protection static ring 56 is inlaid with an annular diamond wear-resistant sheet 58 . After the annular diamond wear-resistant plate 57 of the overload protection moving ring 55 and the annular diamond wear-resistant plate 58 of the overload protection static ring 56 are loaded, the overload of the upper bearing group 1 can be avoided, and the butterfly spring 18 of the static ring 7 of the upper bearing can be prevented from being flattened invalidated.

As shown in Figure 1, the thrust bearing group is installed in the initial position of the turbodrill, and the distance between the annular diamond wear-resistant plate 54 at the top of the turbine shaft 3 and the annular diamond wear-resistant plate 49 of the pressure relief sleeve 15 is D1 The distance between the annular diamond wear-resistant sheet 57 of the overload protection moving ring 55 and the annular diamond wear-resistant sheet 58 of the overload protection static ring 56 is D2; the upper bearing group 1 and the lower bearing group 2 of the thrust bearing group only bear Small preload, the diversion holes 22 and the diversion holes 35 of the upper bearing stationary ring 7 and the lower bearing moving ring 8 are all closed.

As shown in Figure 1, when the WOB is less than the hydraulic load, the turbine shaft 3 moves downward relative to the initial position under the action of the hydraulic load, and D2 gradually decreases. The circular diamond wear-resistant plate 16 of the upper bearing dynamic ring 6 and the circular diamond wear-resistant plate 26 of the upper bearing static ring 7 begin to load and rub; the circular diamond wear-resistant plate 43 of the lower bearing dynamic ring 8 and the lower bearing static The circular diamond wear-resistant plates 39 of the ring 9 are separated from each other and do not bear the load; the diversion holes 35 of the lower bearing moving ring 8 are all closed. The upper bearing moving ring 6 moves downward with the turbine shaft 3, and the butterfly spring 18 is compressed by the static ring sliding body 19 of the upper bearing static ring 7, so that the static ring sliding body 19 moves downward relative to the static ring seat 17, and the upper bearing When the diversion hole 22 of the static ring 7 is opened, the drilling fluid flows into the cavity of the pressure relief sleeve 15 and the upper bearing group 1 through the diversion hole 48 of the pressure relief sleeve 15 and the diversion hole 22 of the upper bearing static ring 7 , and finally enter the drilling annulus through the relief channel 47 and the relief hole 52. As part of the drilling fluid enters the drilling annulus, the inlet pressure of the turbine stator 50 and the turbine rotor 51 decreases, and the hydraulic load generated by the turbine decreases. When the hydraulic load decreases to be equal to the drilling pressure, the turbine shaft is in balance again.

The opening size of the diversion hole 22 of the upper bearing static ring 7 is directly proportional to the difference between drilling pressure and hydraulic load. When the guide hole 22 of the upper bearing static ring 7 is fully opened, the reduced hydraulic load is still greater than the drilling pressure, and the turbine shaft 3 will continue to move downward. When D2 decreases to zero, the annular diamond wear-resistant surface 57 of the overload protection moving ring 55 and the annular diamond wear-resistant surface 58 of the overload protection static ring 56 begin to bear load and friction occurs, the turbine shaft 3 stops moving downward, and the thrust bearing The position in the turbodrill is shown in Figure 7; the upper bearing set 1, the overload protection moving ring 55 and the overload protection static ring 56 are simultaneously loaded, which can effectively avoid the flattening failure of the upper bearing set 1 butterfly spring 18.

As shown in Figure 1, when the WOB is greater than the hydraulic load, the turbine shaft 3 moves upward relative to the initial position under the effect of the WOB, and D1 gradually decreases. The circular diamond wear-resistant plate 43 of the lower bearing dynamic ring 8 and the circular diamond wear-resistant plate 39 of the lower bearing static ring 9 begin to bear and rub; the circular diamond wear-resistant plate 16 of the upper bearing dynamic ring 6 and the upper bearing static The circular diamond wear-resistant plates 26 of the ring 7 are separated from each other and do not bear the load; the guide holes 22 of the static ring 7 of the upper bearing are all closed. The lower bearing moving ring 8 moves upwards, and the butterfly spring 30 is compressed by the moving ring sliding body 31 of the lower bearing moving ring 8, so that the moving ring sliding body 31 moves downward relative to the moving ring seat 29, and the lower bearing moving ring 8 moves downward. When the diversion hole 35 is opened, the drilling fluid flows into the cavity of the lower bearing group 2 through the diversion hole 53 of the turbine shaft 3 and the diversion hole 35 of the lower bearing moving ring 8, and passes through the load protection moving ring 55 and the overload protection static ring 56 into the drilling annulus. Part of the drilling fluid enters the lower bearing group 2, causing the downward hydraulic load to increase. When the hydraulic load increases to be equal to the weight on bit, the axial load of the turbodrill returns to balance.

The opening size of the diversion hole 35 of the lower bearing moving ring 8 is directly proportional to the difference between drilling pressure and hydraulic load. When the guide hole 35 of the lower bearing moving ring 8 was fully opened, the increased hydraulic load was still less than the weight on bit, and the turbine shaft 3 would continue to move upward. When D1 is reduced to zero, the annular diamond wear-resistant plate 54 on the top of the turbine shaft 3 and the annular diamond wear-resistant plate 49 of the pressure relief sleeve 15 begin to load and rub against each other, the turbine shaft 3 stops moving upward, and the thrust bearing assembly The location in the turbodrill is shown in Figure 8. The pressure relief sleeve 15 and the lower bearing group 2 are loaded at the same time. On the one hand, the overload protection at the top of the turbine shaft 3 can effectively avoid the flattening failure of the butterfly spring 30 of the lower bearing group 2. On the other hand, the top of the turbine shaft 3 and the pressure relief The sleeve 15 forms a sealing surface to block the drilling fluid pressure relief channel 47, preventing the drilling fluid from entering the drilling annulus, further increasing the hydraulic load, and promoting the recovery of the balance of the axial load of the turbodrill.

Claims (3)

1. one kind regulates the thrust bearing group of turbodrill thrust load automatically, be made up of upper bearing group (1) and lower bearing group (2), it is characterized in that: upper bearing group (1) is installed on the top of turbine shaft (3), lower bearing group (2) is installed on the bottom of turbine shaft (3), described upper bearing group (1) is made up of 3 ~ 5 secondary upper bearings (4), and upper bearing (4) is made up of upper bearing rotating ring (6) and upper bearing stationary ring (7); Described lower bearing group (2) is made up of 3 ~ 5 secondary lower bearings (5), and lower bearing (5) is made up of lower bearing rotating ring (8) and lower bearing stationary ring (9); Spindle nose locking nut (10), out splice going splice (11) adopt with turbine shaft (3) and are threaded, be pressed on turbine shaft (3) by upper bearing rotating ring (6) and lower bearing rotating ring (8), upper bearing rotating ring (6) and lower bearing rotating ring (8) are with turbine shaft (3) synchronous axial system; Top sub (12) and lower connector (13) adopt with housing (14) and are threaded, upper bearing stationary ring (7) is pressed in pressure release sleeve (15), be pressed in housing (14) by lower bearing stationary ring (9), upper bearing stationary ring (7), lower bearing stationary ring (9), pressure release sleeve (15) and housing (14) keep static and do not rotate simultaneously; Described top sub (12) is connected with drill string, and out splice going splice (11) is connected with drill bit; Described upper bearing group (1) and lower bearing group (2) only bear unidirectional load, and work when both are different; Upper bearing group (1) relies on the circular diamond wear proof sheet (16) of upper bearing rotating ring (6) to bear downward hydraulic load with the circular diamond wear proof sheet (26) of upper bearing stationary ring (7); Lower bearing group (2) relies on the circular diamond wear proof sheet (43) of lower bearing rotating ring (8) to bear the pressure of the drill upwards with the circular diamond wear proof sheet (39) of lower bearing stationary ring (9); Thrust bearing group is according to the size and Orientation of axial turbine load, the unlatching size of the pod apertures (22) of automatic adjustment upper bearing stationary ring (7) and the pod apertures (35) of lower bearing rotating ring (8), change the size of the hydraulic load of turbine shaft (3), make the hydraulic load suffered by turbine shaft (3) and the pressure of the drill be in transient equiliblium.

2. the thrust bearing group of a kind of automatic adjustment turbodrill thrust load according to claim 1, is characterized in that: the rubbing surface of described upper bearing rotating ring (6) evenly inlays circular diamond wear proof sheet (16); Described upper bearing stationary ring (7) is made up of stationary seat (17), butterfly spring (18), stationary ring slide mass (19), positioning dowel (20), O-ring seals (21); Described stationary seat (17) is uniformly distributed circumferentially 4 pod apertures (22) and 4 positioning pin holes (23), and inner bottom surface is uniformly distributed 4 butterfly spring mounting holes (24); Described stationary ring slide mass (19) lower surface is uniformly distributed 4 butterfly spring mounting holes (25), and its upper surface is that rubbing surface evenly inlays circular diamond wear proof sheet (26); Stationary ring slide mass (19) external diameter is provided with O-ring seals annular groove (27) and uniform 4 restraining grooves (28); Described O-ring seals (21) is arranged in the O-ring seals annular groove (27) of stationary ring slide mass (19), O-ring seals (21) is for stationary seal ring seat (17) and stationary ring slide mass (19), prevent drilling fluid particle from entering sliding pair surface, avoid stationary ring slide mass (19) cannot move in stationary seat (17).

3. the thrust bearing group of a kind of automatic adjustment turbodrill thrust load according to claim 1, it is characterized in that: the rubbing surface of described lower bearing stationary ring (9) evenly inlays circular diamond wear proof sheet (39), described lower bearing rotating ring (8) is made up of rotating seat (29), butterfly spring (30), rotating ring slide mass (31), positioning dowel (32), the first and second O-ring seals (33,34); Described rotating seat (29) is uniform 4 pod apertures (35) and 4 locating stud nail (36) circumferentially, and inner bottom surface is uniformly distributed 4 butterfly spring mounting holes (37); Described rotating ring slide mass (31) lower surface is laid with 4 butterfly spring mounting holes (38), and its upper surface is that rubbing surface evenly inlays circular diamond wear proof sheet (43); The external diameter of rotating ring slide mass (31) is provided with O-ring seals annular groove (40) and uniform 4 restraining grooves (41), and the internal diameter of rotating ring slide mass (31) is provided with O-ring seals annular groove (42); Described first O-ring seals (33) is arranged in the O V-shaped ring groove (40) of rotating ring slide mass (31), described second O-ring seals (34) is arranged in the O V-shaped ring groove (42) of rotating ring slide mass (31), first and second O-ring seals (33,34) are for moving sealing ring seat (29) and rotating ring slide mass (31), prevent drilling fluid particle from entering sliding pair surface, avoid rotating ring slide mass (31) rotating seat (29) in cannot move.