Highly stable and reliable deep well electric submersible pump

Abstract

This invention relates to the field of submersible pump technology, specifically disclosing a highly stable and reliable deep-well electric submersible pump, comprising: a pump body, including a suction section and a guide fluid connected to one end of the suction section; a rotor assembly disposed within the pump body, the rotor assembly including a pump shaft, an impeller mounted on the pump shaft, and a final-stage impeller; a thrust bearing assembly mounted at the end of the guide fluid away from the suction section and connected to one end of the pump shaft; a check valve assembly mounted at the end of the thrust bearing assembly away from the guide fluid; a connecting frame mounted at the end of the suction section away from the guide fluid; a submersible motor mounted at the end of the connecting frame away from the suction section; a motor coupling having a first elastic ring; a pump coupling having a second elastic ring; and an elastic ring installed in the first and second elastic rings. This highly stable and reliable deep-well electric submersible pump can withstand the back thrust generated by the pumped medium, has vibration reduction and noise reduction effects, and ensures stable operation.

Description

Technical Field

[0001] This invention relates to the field of submersible pump technology, and in particular to a highly stable and reliable deep-well electric submersible pump. Background Technology

[0002] Deep-well electric submersible pumps are widely used in various industries as general-purpose machinery. Currently, submersible pumps lack independent thrust bearing assemblies, and the pump shaft and motor shaft are rigidly connected via a coupling, with the pump shaft acting directly on the motor shaft. Submersible pumps cannot withstand the axial movement of the rotor components during pump startup, causing excessive upward instantaneous displacement of the rotor components. This leads to impact and friction damage to the impellers and wear rings at each stage. Furthermore, since the pump shaft and motor shaft form a rigid unit, all axial movement of the rotor components acts on the submersible motor, resulting in impact and friction damage to the motor. Furthermore, the mutual transmission of pump body vibration and submersible motor vibration can cause resonance, severely damaging the service life of the electric submersible pump. As the rotor component of the electric submersible pump becomes longer, its rigidity decreases. The rotor component uses the bearing at the bottom of the submersible motor as a support point, making the entire rotor component a bottom-up fulcrum structure. When the pump rotates at high speed, the weight of the multiple impellers and the medium being transported within the impellers is greater than the weight of the motor rotor, causing the entire rotor component to form an amplified rotational swing state from bottom to top, which intensifies the vibration of the electric submersible pump and severely reduces its service life. Summary of the Invention

[0003] The purpose of this invention is to provide a highly stable and reliable deep-well electric submersible pump that can withstand the reverse thrust generated by the pumped medium, has the effect of vibration reduction and noise reduction, and ensures stable operation.

[0004] To achieve the above objectives, the present invention provides a highly stable and reliable deep-well electric submersible pump, comprising: The pump body includes a suction section and a fluid guide connected to one end of the suction section; A rotor assembly is disposed within the pump body, the rotor assembly including a pump shaft, an impeller mounted on the pump shaft, and a final stage impeller; a thrust bearing assembly is mounted at the end of the guide fluid away from the suction section and connected to one end of the pump shaft; A check valve assembly is installed at the end of the thrust bearing assembly away from the fluid guide; A connecting bracket is installed at the end of the suction section away from the fluid guide; A submersible motor is installed at the end of the connecting frame away from the suction section, and the submersible motor has a submersible motor shaft; a motor coupling is disposed in the connecting frame and is connected to the submersible motor shaft, and the motor coupling has a first elastic ring. A water pump coupling, connected to the motor coupling and installed at the other end of the pump shaft, the water pump coupling having a second elastic ring, the second elastic ring being correspondingly arranged to the first elastic ring; and An elastic ring is installed in the first elastic ring position and the second elastic ring position.

[0005] In some embodiments, the thrust bearing assembly includes a guide bearing housing, a guide rib, a guide cone, a guide shield, a thrust disk, a thrust bearing, and a main anti-slip bearing. The guide cone is connected to the guide bearing housing via the guide rib. The guide shield is mounted on the guide cone. The thrust disk is spaced apart within the guide cone and mounted on the pump shaft. The thrust bearing is located on the inner wall of the guide cone and mounted on the pump shaft. The main anti-slip bearing is mounted on the inner wall of the guide shield and located between the guide shield and the thrust disk.

[0006] In some embodiments, a balance cavity is formed between the thrust disk and the thrust bearing, the thrust bearing has a main flow channel, the guide cone has a liquid collection cavity, and the balance cavity is connected to the liquid collection cavity through the main flow channel; The flow guide shroud has a liquid collection chamber, and an auxiliary flow channel is formed between the main anti-slip bearing and the thrust plate. The liquid collection chamber is connected to the liquid receiving chamber through the auxiliary flow channel. The thrust bearing assembly includes a balance tube, the guide cone has a pressure relief chamber, the pressure relief chamber is connected to the liquid collection chamber through a flow channel, one end of the balance tube is connected to the pressure relief chamber, and the other end of the balance tube is used to connect to the jet hole of the suction section.

[0007] In some embodiments, the thrust bearing includes a bearing skeleton and a bearing body, the bearing body being mounted on the bearing skeleton, the bearing skeleton being mounted on the inner wall of the guide cone, and the bearing body being mounted on the pump shaft; The bearing body has a first radial lubrication groove, a balance ring groove, and a first axial force-bearing surface at one end near the thrust plate. The bearing body has a radial force-bearing surface in the middle. The first axial force-bearing surface is located on the outer periphery of the balance ring groove. The first radial lubrication groove is located on both sides of the balance ring groove and the first axial force-bearing surface. The first radial lubrication groove has a mounting hole. The radial force-bearing surface has an axial lubrication groove. The first radial lubrication groove has a first axial force-bearing surface end edge and a first axial force-bearing surface start edge on both sides, and a first lubrication slope is formed between the first axial force-bearing surface start edge and the first axial force-bearing surface.

[0008] In some embodiments, the main anti-slip bearing has a second axial force-bearing surface and a second radial lubrication groove distributed alternately at one end near the thrust disk, and the second axial force-bearing surface is spaced apart from the thrust disk; The second radial lubrication groove has screw holes, and the second radial lubrication groove has a second axial force-bearing surface end edge and a second axial force-bearing surface start edge on both sides. A second lubrication slope is formed between the second axial force-bearing surface start edge and the second axial force-bearing surface.

[0009] In some embodiments, the thrust disk includes: The disc body has a first through hole in the middle, and the inner wall of the disc body has a main flat keyway and a sealing ring groove. The front side of the disc body has an auxiliary axial force-bearing surface, and the rear side of the disc body has a main axial force-bearing surface with a balance ring groove. A cylindrical body is disposed on the main axial force-bearing surface. The middle part of the cylindrical body has a second through hole, which communicates with the first through hole. The inner wall of the cylindrical body has an auxiliary flat keyway. The cylindrical body is configured to be installed in a thrust bearing, and the main axial force-bearing surface is spaced apart from the thrust bearing. The first through hole and the second through hole are used to install the pump shaft.

[0010] In some embodiments, the main axial force-bearing surface is parallel to the auxiliary axial force-bearing surface; the front side of the disc body also has a forward-extending arc surface and an end face, the arc surface being located between the auxiliary axial force-bearing surface and the end face, and the end face being parallel to the auxiliary axial force-bearing surface; the front end of the main flat keyway extends out of the end face; the outer diameter of the arc surface near the end face is smaller than the outer diameter of the arc surface near the auxiliary axial force-bearing surface.

[0011] In some embodiments, the upper part of the motor coupling has a first torque transmission block that is alternately distributed with the first elastic ring, the water pump coupling has a second torque transmission block that is alternately distributed with the second elastic ring, the outer periphery of the elastic ring has elastic blocks that are spaced apart, and the elastic blocks are installed one-to-one in the first elastic ring and the second elastic ring.

[0012] In some embodiments, the outer peripheral wall of the motor coupling has speed measuring teeth, and a submersible speed probe is installed on the connecting frame. The submersible speed probe is used to measure the speed of the speed measuring teeth. The outer peripheral wall of the water pump coupling has a sand-throwing ring, the outer edge of which is bent downwards and extends downwards; the lower surface of the sand-throwing ring forms a downward measuring surface, and a submerged axial force probe is installed in the suction section, the submerged axial force probe being in contact with the downward measuring surface; The bottom of the water pump coupling has an upward measuring surface, and the suction section is equipped with a submerged liquid vertical displacement probe, which is in contact with the upward measuring surface. A submersible temperature probe is installed inside the connecting frame, and a submersible vibration probe is installed on the outer wall of the connecting frame.

[0013] In some embodiments, a sliding bearing is provided inside the guide fluid, and the sliding bearing is installed between the guide fluid and the pump shaft.

[0014] This invention provides a highly stable and reliable deep-well electric submersible pump. Compared with the prior art, its advantages are as follows: The pump body includes a suction section and a guide fluid connected to one end of the suction section. A rotor assembly is disposed within the pump body, and the rotor assembly includes a pump shaft, an impeller mounted on the pump shaft, and a final stage impeller. A thrust bearing assembly is mounted at the end of the guide fluid away from the suction section and connected to one end of the pump shaft. A check valve assembly is mounted at the end of the thrust bearing assembly away from the guide fluid. A connecting bracket is mounted at the end of the suction section away from the guide fluid. At one end of the fluid, a submersible motor is mounted on the connecting frame at the end away from the suction section. The submersible motor has a submersible motor shaft, and a motor coupling is disposed within the connecting frame and connected to the submersible motor shaft. The motor coupling has a first elastic ring. A water pump coupling is connected to the motor coupling and mounted on the other end of the pump shaft. The water pump coupling has a second elastic ring, which corresponds to the first elastic ring. The elastic rings are installed in both the first and second elastic rings. Thus, through the combined use of the thrust bearing and the main anti-slip bearing, the reverse thrust generated by the pumping medium from the running rotor components can be withstood, ensuring stable operation. The elastic rings achieve a flexible connection between the motor coupling and the water pump coupling, thereby compensating for displacement deviations and providing vibration reduction and noise reduction effects. Attached Figure Description

[0015] Figure 1 This is a cross-sectional structural schematic diagram of a highly stable and reliable deep well electric submersible pump provided in some embodiments of the present invention.

[0016] Figure 2 This is an enlarged schematic diagram of point A in Figure 1.

[0017] Figure 3 This is an enlarged schematic diagram of point B in Figure 1.

[0018] Figure 4 This is an enlarged schematic diagram of point C in Figure 1.

[0019] Figure 5 This is an enlarged schematic diagram of point D in Figure 1.

[0020] Figure 6 This is an enlarged schematic diagram of the guide bearing housing of a high-stability and reliable deep-well electric submersible pump provided in some embodiments of the present invention.

[0021] Figure 7 This is an enlarged schematic diagram of the suction section of a highly stable and reliable deep-well electric submersible pump provided in some embodiments of the present invention.

[0022] Figure 8 This is an enlarged schematic diagram of the connecting frame of a highly stable and reliable deep well electric submersible pump provided in some embodiments of the present invention.

[0023] Figure 9 This is an enlarged schematic diagram of the flow guide cover of a high-stability and reliable deep-well electric submersible pump provided in some embodiments of the present invention.

[0024] Figure 10a This is an enlarged schematic diagram of the thrust bearing of a high-stability and reliable deep-well electric submersible pump provided in some embodiments of the present invention.

[0025] Figure 10b This is a top-view enlarged schematic diagram of the thrust bearing of a high-stability and reliable deep-well electric submersible pump provided in some embodiments of the present invention.

[0026] Figure 11a This is an enlarged schematic diagram of the main anti-slip bearing of a high-stability and reliable deep-well electric submersible pump provided in some embodiments of the present invention.

[0027] Figure 11b This is a top-view enlarged schematic diagram of the main anti-slip bearing of a high-stability and reliable deep-well electric submersible pump provided in some embodiments of the present invention.

[0028] Figure 12 This is an enlarged schematic diagram of the thrust plate of a highly stable and reliable deep-well electric submersible pump provided in some embodiments of the present invention.

[0029] Figure 13 This is an enlarged schematic diagram of the isolation bushing of a high-stability and reliable deep-well electric submersible pump provided in some embodiments of the present invention.

[0030] Figure 14a This is an enlarged schematic diagram of the pump coupling of a high-stability and reliable deep-well electric submersible pump provided in some embodiments of the present invention.

[0031] Figure 14b This is a bottom-view enlarged schematic diagram of the pump coupling of a high-stability and reliable deep-well electric submersible pump provided in some embodiments of the present invention.

[0032] Figure 15a This is an enlarged schematic diagram of the motor coupling of a highly stable and reliable deep-well electric submersible pump provided in some embodiments of the present invention.

[0033] Figure 15b This is a top-view enlarged schematic diagram of the motor coupling of a high-stability and reliable deep-well electric submersible pump provided in some embodiments of the present invention.

[0034] Figure 16 This is an enlarged schematic diagram of the pump shaft of a highly stable and reliable deep well electric submersible pump provided in some embodiments of the present invention.

[0035] In the diagram: 1. Submersible motor; 2. Connecting frame; 3. Suction section; 4. Impeller; 5. Guide fluid; 6. Balance pipe; 7. Bearing sleeve; 8. Sliding bearing; 9. Interstage sleeve; 10. Thrust bearing assembly; 11. Check valve assembly; 12. Last stage impeller; 13. Rear inlet ring; 14. Pump shaft; 15. First submersible vibration probe; 16. Second submersible vibration probe; 17. Isolation sleeve; 18. First O-ring; 19. Pressure relief chamber; 20. Submersible pressure probe; 21. First screw; 22. Main flow channel; 23. Balance chamber; 24. Second O-ring; 25. Round nut; 26. Check valve cover; 27. Guide shield; 28. Main key; 29. ​​Thrust washer; 30. Third submersible vibration probe; 31. Thrust plate; 32. High 33. Molecular soft packing; 34. Second screw; 35. Third O-ring; 36. Second submersible temperature probe; 37. Flow guide bearing seat; 38. Fourth submersible vibration probe; 39. Liquid collection chamber; 40. Third screw; 41. Main anti-slip bearing; 42. Thrust bearing; 43. Fourth O-ring; 44. Auxiliary flat key; 45. Fifth O-ring; 46. Fourth screw; 47. Auxiliary anti-slip bearing; 48. Fifth screw; 49. Front ring; 50. Submersible motor shaft; 51. Motor coupling; 52. Elastic ring; 53. Submersible axial force probe; 54. Water pump coupling; 55. Suction bushing; 56. Sixth O-ring; 57. Submersible vertical displacement probe; 58. Fifth submersible vibration probe; 59. Submersible speed probe; 6 0. First submersible temperature probe; 61. First guide rib; 62. Liquid collection tank; 63. Pressure relief hole; 64. Liquid collection tank; 65. Pressure measuring hole; 66. First O-ring; 67. Second O-ring; 68. Temperature measuring hole; 69. Flow channel; 70. First guide cone; 71. Bearing surface; 72. Axial force probe mounting slot; 73. Jet hole; 74. Displacement probe mounting slot; 75. First vibration measuring hole; 76. Velocity measuring hole; 77. First screw hole; 78. Second guide rib; 79. Third O-ring; 80. Bearing skeleton; 81. Mounting hole; 82. First radial lubrication groove; 83. First lubrication slope; 84. First balance ring groove; 85. Bearing body; 86. Axial lubrication groove; 87. First axial force bearing surface; 88. 89. End edge of the first axial force-bearing surface; 90. Start edge of the first axial force-bearing surface; 91. Second screw hole; 92. Second axial force-bearing surface; 93. Start edge of the second axial force-bearing surface; 94. Second radial lubrication groove; 95. Second lubrication inclined surface; 96. Balance ring groove; 97. Auxiliary axial force-bearing surface; 98. O-ring groove; 99. First main flat keyway; 100. Main axial force-bearing surface; 101. First auxiliary flat keyway; 102. Isolation ring; 103. Filter hole; 104. Second guide cone; 105. First elastic ring; 106. Upward measuring surface; 107. Downward measuring surface; 108. Sand-throwing ring; 109. First torque transmission block; 110. Third axial force-bearing surface; 111. Second elastic ring;112. Second torque transmission block; 113. Fourth axial force-bearing surface; 114. Axial force-bearing groove surface; 115. Speed ​​measuring gear; 116. Second main keyway; 117. Second auxiliary keyway; 118. Shaft extension; 119. Fifth axial force-bearing surface; 120. Balance hole; 121. Liquid collection chamber; 122. Auxiliary flow channel; 123. Return hole; 124. Third vibration measuring hole; 125. Radial force-bearing surface; 126. Bearing mounting position; 127. Vibration measuring hole; a. Jet angle; b. Placement angle; F. First axial clearance; G. Second axial clearance; H. Third axial clearance; I. Fourth axial clearance; J. Fifth axial clearance; L. Sixth axial clearance; N. Seventh axial clearance; O. Eighth axial clearance; K. Ninth axial clearance; X. Tenth axial clearance; M. Eleventh axial clearance. Detailed Implementation

[0036] The technical solutions in the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments.

[0037] It should be understood that in the description of this application, the terms "upper," "lower," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are used solely for the convenience of describing this application and for simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application. The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. That is, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. Furthermore, unless otherwise stated, "a plurality of" means two or more.

[0038] Furthermore, the technical features involved in the different embodiments of this application described below can be combined with each other as long as they do not conflict with each other.

[0039] like Figures 1-16As shown, some embodiments of the present invention include a highly stable and reliable deep well electric submersible pump, comprising: a submersible motor 1, a connecting frame 2, a suction section 3, an impeller 4, a guide tube 5, a balance pipe 6, a bearing sleeve 7, a sliding bearing 8, an interstage sleeve 9, a thrust bearing assembly 10, a check valve assembly 11, a final stage impeller 12, a rear inlet ring 13, a pump shaft 14, a first submersible vibration probe 15, a second submersible vibration probe 16, a third submersible vibration probe 30, a fourth submersible vibration probe 37, a fifth submersible vibration probe 58, an auxiliary anti-slip bearing 46, a front inlet ring 48, a motor coupling 51, an elastic ring 52, a submersible axial force probe 53, a pump coupling 54, a suction sleeve 55, a submersible vertical displacement probe 57, a submersible speed probe 59, a first submersible temperature probe 60, and a second submersible temperature probe 35.

[0040] The rotor assembly includes a pump shaft 14, an impeller 4, and a final stage impeller 12. The rotor assembly is placed inside the guide fluid 5 and the suction section 3. The thrust bearing assembly 10 is connected to the guide fluid 5 and the rotor assembly. The check valve assembly 11 is connected to the thrust bearing assembly 10 to form the submersible pump body. The submersible pump body is connected to the submersible motor 1 through the motor coupling 51, the elastic ring 52, and the connecting frame 2 to form a highly stable and reliable deep well electric submersible pump.

[0041] like Figure 2 As shown, the thrust bearing assembly 10 includes an isolation bushing 17, a first O-ring 18, a balance tube 6, a submersible pressure probe 20, a first screw 21, a second O-ring 24, a round nut 25, a flow guide 27, a main flat key 28, a thrust washer 29, a third submersible vibration probe 30, a thrust disc 31, a polymer soft filler 32, a second screw 33, a third O-ring 34, a second submersible temperature probe 35, a flow guide bearing seat 36, a fourth submersible vibration probe 37, a third screw 39, a main anti-slip bearing 40, a thrust bearing 41, a fourth O-ring 42, an auxiliary flat key 43, and a fifth O-ring 44.

[0042] like Figure 6 As shown, the guide bearing housing 36 is provided with a first guide rib 61, a liquid collection tank 62, a pressure relief hole 63, a liquid receiving tank 64, a pressure measuring hole 65, a first O-ring 66, a third vibration measuring hole 124, a second O-ring 67, a temperature measuring hole 68, a flow channel 69, a first guide cone 70, and a bearing surface 71. The number of first guide ribs 61 is ≥3, the number of flow channels 69 is ≥1, the pressure relief hole 63, the pressure measuring hole 65, and the temperature measuring hole 68 are respectively provided on the first guide ribs 61, and the liquid collection tank 62 is connected to the liquid receiving tank 64 through the flow channel 69.

[0043] like Figure 7As shown, the suction section 3 is provided with an axial force probe mounting groove 72, a jet hole 73, a displacement probe mounting groove 74, a jet angle α, and a placement angle b. The jet angle α has an angle value of 6°-30°, the number of jet angles α is ≥1, and the placement angle b has an angle value of 12°-85°.

[0044] like Figure 8 As shown, the connecting frame 2 is provided with a first vibration measuring hole 75 and a speed measuring hole 76.

[0045] like Figure 9 As shown, the flow guide shroud 27 is provided with a return hole 123, a first screw hole 77, a second flow guide rib 78, and a third O-ring 79. The number of return holes 123 is ≥1, and the number of second flow guide ribs 78 is ≥3.

[0046] like Figure 10a and Figure 10b As shown, the thrust bearing 41 is provided with a bearing skeleton 80, mounting hole 81, first radial lubrication groove 82, first lubrication inclined surface 83, radial force surface 125, first balance ring groove 84, first axial force surface 87, bearing body 85, axial lubrication groove 86, end edge 88 of the first axial force surface and start edge 89 of the first axial force surface. The end edge 88 and start edge 89 of the first axial force surface form the first radial lubrication groove 82. The first lubrication inclined surface 83 is located at the intersection of the start edge 89 of the first axial force surface and the first axial force surface 87. The end edge 88 and start edge 89 of the first axial force surface are in a circular arc rotation shape. The circular arc rotation direction of the end edge 88 and start edge 89 of the first axial force surface is the same as the rotation direction of the rotor component. A first radial lubrication groove 82, a first lubrication inclined surface 83, a first balance ring groove 84, a first axial force-bearing surface 87, and an axial lubrication groove 86 are provided on the bearing body 85. The axial lubrication groove 86 is connected to the first radial lubrication groove 82, and the first radial lubrication groove 82 is connected to the first balance ring groove 84. The bearing body 85 is installed and fixed on the bearing frame 80. The bearing body 85 is made of a high molecular polymer material. The mounting hole 81 is provided in the first radial lubrication groove 82. The number of axial lubrication grooves 86 is ≥3, and the number of axial lubrication grooves 86 is equal to that of the first radial lubrication groove 82, the first lubrication inclined surface 83, and the first axial force-bearing surface 87.

[0047] like Figure 11a and Figure 11bAs shown, the main anti-slip bearing 40 is provided with a second screw hole 90, a second axial force-bearing surface 91, a starting edge 92 of the second axial force-bearing surface, an ending edge 93 of the second axial force-bearing surface, a second radial lubrication groove 94, and a second lubrication inclined surface 95. The ending edge 93 of the second axial force-bearing surface and the starting edge 92 of the second axial force-bearing surface form the second radial lubrication groove 94. The second lubrication inclined surface 95 is located at the intersection of the starting edge 92 of the second axial force-bearing surface and the second axial force-bearing surface 91. The ending edge 93 of the second axial force-bearing surface and the starting edge 92 of the second axial force-bearing surface are in a circular arc rotation shape. The circular arc rotation direction of the ending edge 93 of the second axial force-bearing surface and the starting edge 92 of the second axial force-bearing surface is the same as the rotation direction of the rotor component. The main anti-slip bearing 40 is made of a high molecular polymer material. The second screw hole 90 is located in the second radial lubrication groove 94. The number of second radial lubrication grooves 94 is ≥3. The number of first radial lubrication grooves 82 is equal to the number of second lubrication inclined surfaces 95 and second axial force-bearing surfaces 91.

[0048] like Figure 12 As shown, the thrust disk 31 is provided with a second balance ring groove 96, an auxiliary axial force-bearing surface 97, an O-ring groove 98, a first main flat keyway 99, a main axial force-bearing surface 100, and a first auxiliary flat keyway 101. The main axial force-bearing surface 100 and the auxiliary axial force-bearing surface 97 are made of high-melting-point wear-resistant alloy.

[0049] like Figure 13 As shown, the isolation bushing 17 is provided with an isolation ring 102, a filter hole 103 and a second guide cone 104. The taper angle of the second guide cone 104 is equal to the taper angle of the first guide cone 70 provided on the guide bearing seat 36.

[0050] like Figure 14a and Figure 14b As shown, the water pump coupling 54 is provided with a first elastic ring 105, an upper measuring surface 106, a lower measuring surface 107, a sand-throwing ring 108, a first torque transmission block 109, and a third axial force-bearing surface 110. The number of the first elastic rings 105 is ≥2, and the number of the first elastic rings 105 is equal to the number of the first torque transmission blocks 109.

[0051] like Figure 15a and Figure 15b As shown, the motor coupling 51 is provided with a speed measuring tooth 115, a second elastic ring 111, a fourth axial force-bearing surface 113, an axial force-bearing groove surface 114, and a second torque transmission block 112. The number of teeth of the speed measuring tooth 115 is selected according to actual needs. The number of the second elastic ring 111 and the axial force-bearing groove surface 114, as well as the number of the first elastic ring 105 and the number of the first torque transmission block 109 provided on the water pump coupling 54, are equal.

[0052] like Figure 16As shown, the pump shaft 14 is provided with a second main flat keyway 116, a second auxiliary flat keyway 117, a shaft extension 118, and a fifth axial force-bearing surface 119.

[0053] During assembly, the rear inlet ring 13 is installed on the guide fluid 5 by the fourth screw 45, the auxiliary anti-slip bearing 46 is installed on the final stage impeller 12 by the fifth screw 47, the front inlet ring 48 is installed on the guide fluid 5 and the suction section 3 by the sixth screw 49 respectively, and the sliding bearing 8 is installed on the guide fluid 5.

[0054] During assembly, the pump coupling 54 is installed on the pump shaft 14, and the bearing sleeve 7 is installed on the pump shaft 14 and mates with the pump coupling 54. The pump shaft 14 is installed on the suction section 3 so that the bearing sleeve 7 mates with the sliding bearing 8. The sixth O-ring 56 is fitted on the pump shaft 14 and mates with the bearing sleeve 7. The suction sleeve 55 is fitted on the pump shaft 14 and mates with the sixth O-ring 56. The impeller 4, bearing sleeve 7, sixth O-ring 56, interstage sleeve 9 and final stage impeller 12 are installed on the pump shaft 14 in sequence. At the same time, multiple guide tubes 5 are installed on the outside of the impeller 4 and the final stage impeller 12 on the pump shaft 14 in sequence so that the impeller 4 and the final stage impeller 12 mate with the front inlet ring 48 and the rear inlet ring 13, respectively.

[0055] During assembly, the sixth O-ring 56 is fitted onto the pump shaft 14 and then mates with the bearing sleeve 7. The fourth O-ring 42 is installed in the second O-ring position 67. The thrust bearing 41 mates with the bearing surface 71 and the fourth O-ring 42 respectively, and is then installed in the guide bearing seat 36 through the mounting hole 81 by the first screw 21.

[0056] During assembly, the isolation bushing 17 is fitted onto the pump shaft 14 and then mates with the sixth O-ring 56. The first O-ring 18 is fitted onto the pump shaft 14 and then mates with the isolation bushing 17. The guide bearing seat 36 is installed on the guide fluid 5. The second O-ring 24 is installed in the O-ring groove 98. The auxiliary flat key 43 is installed in the second auxiliary flat key groove 117. The main flat key 28 is installed in the second main flat key groove 116. After the thrust disc 31 is fitted onto the pump shaft 14, the auxiliary flat key 43 mates with the first auxiliary flat key groove 101, the main flat key 28 mates with the first main flat key groove 99, the thrust disc 31 mates with the first O-ring 18, and the main axial force-bearing surface 100 mates with the first axial force-bearing surface 87.

[0057] During assembly, the thrust washer 29 is installed on the pump shaft 14 and then mates with the thrust plate 31. The round nut 25 is installed on the pump shaft 14 and then presses the thrust plate 31 with the thrust washer 29. The main anti-slip bearing 40 is installed on the bearing mounting position 126 and fixed with the third screw 39 through the second screw hole 90. The third O-ring 34 is installed on the third O-ring position 79. The flow guide shroud 27 is installed on the flow guide bearing seat 36, so that the third O-ring 34 mates with the first O-ring position 66 and is fixed with the second screw 33 through the first screw hole 77. The polymer soft filler 32 is filled into the first screw hole 77 to form a smooth flow surface.

[0058] During assembly, the check valve assembly 11 is installed on the flow guide bearing seat 36. When the check valve cover 26 of the check valve assembly 11 falls into the flow guide bearing seat 36 due to failure after long-term use, it can be effectively prevented from entering the flow channel of the flow guide bearing seat 36 by the second flow guide rib 78.

[0059] During assembly, the balance tube 6 is installed in the pressure relief hole 63 and the jet hole 73, the third submersible vibration probe 30 is installed in the third vibration measuring hole 124, the submersible pressure probe 20 is installed in the pressure measuring hole 65, the second submersible temperature probe 35 is installed in the temperature measuring hole 68, and the fourth submersible vibration probe 37 is installed in the second vibration measuring hole 127 to form a submersible pump.

[0060] During assembly, the motor coupling 51 is installed on the submersible motor shaft 50, the connecting frame 2 is installed on the submersible motor 1, the elastic ring 52 is installed in the second elastic ring position 111, and the submersible pump is installed on the connecting frame 2, so that the pump coupling 54 cooperates with the elastic ring 52 and the motor coupling 51, and the shaft extension 118 cooperates with the axial force groove surface 114 to form a flexible connection.

[0061] The first submersible temperature probe 60 is installed on the submersible motor 1 and the connecting frame 2. The submersible speed probe 59 is installed on the speed measuring hole 76 and then engages with the speed measuring gear 115. The fifth submersible vibration probe 58 is installed on the first vibration measuring hole 75. The submersible axial force probe 53 is installed on the axial force probe mounting groove 72 and then contacts the downward measuring surface 107. The submersible vertical displacement probe 57 is installed on the displacement probe mounting groove 74 and then contacts the upward measuring surface 106. In this way, a highly stable and reliable deep well electric submersible pump is formed.

[0062] Among them, the axial lubrication groove 86, the first balance ring groove 84, the second balance ring groove 96, and the first radial lubrication groove 82 form a balance cavity 23. The main axial force-bearing surface 100, together with the first axial force-bearing surface 87, the first radial lubrication groove 82, and the first lubrication inclined surface 83, forms a main flow channel 22. The auxiliary axial force-bearing surface 97, together with the second axial force-bearing surface 91, the second radial lubrication groove 94, and the second lubrication inclined surface 95, forms an auxiliary flow channel 122. The guide shield 27, together with the round nut 25, the thrust plate 31, and the auxiliary flow channel 122, forms a liquid collection cavity 121. The liquid tank 64, together with the thrust bearing 41, the main flow channel 22, the thrust disk 31, the liquid collection chamber 121, and the guide shroud 27, forms the liquid collection chamber 38. The liquid collection tank 62 and the thrust bearing 41 form the pressure relief chamber 19. The balance chamber 23 is connected to the liquid collection chamber 38 through the main flow channel 22. The liquid collection chamber 38 is connected to the liquid collection chamber 121 through the auxiliary flow channel 122. The liquid collection chamber 121 is connected to the liquid collection chamber 38 through the return hole 123. The liquid collection chamber 38 is connected to the pressure relief chamber 19 through the flow channel 69. The pressure relief chamber 19 is connected to the jet hole 73 through the balance pipe 6.

[0063] During operation, the high-pressure medium in the guide fluid 5 flows into the balance chamber 23 after being filtered through the filter hole 103. After entering the balance chamber 23, the high-pressure medium lifts the rotor component of the submersible pump upward. The high-pressure medium lubricates the thrust bearing 41 and thrust disc 31 through the main flow channel 22, which can effectively reduce friction. The high-pressure medium flows into the liquid collection chamber 38 through the main flow channel 22. The high-pressure medium in the liquid collection chamber 38 flows into the liquid collection chamber 121 through the auxiliary flow channel 122. It then flows into the liquid collection chamber 38 through the return hole 123 to achieve circulation and cooling. The high-pressure medium in the liquid collection chamber 38 flows into the pressure relief chamber 19 through the flow channel 69. The high-pressure medium in the pressure relief chamber 19 flows into the jet hole 73 through the balance pipe 6. The high-pressure medium in the jet hole 73 is jetted at high pressure through the jet hole 73 and finally enters the suction port of the impeller 4, achieving the balance of axial force and high cavitation resistance.

[0064] Based on the above structural configuration, the thrust bearing assembly 10 vertically suspends the rotor of the submersible pump within the pump body, allowing the submersible pump to withstand both axial and radial forces simultaneously. The bearing bushing 7, pump coupling 54, elastic ring 52, suction bushing 55, sixth O-ring 56, interstage bushing 9, isolation bushing 17, first O-ring 18, and thrust disc 31 prevent complete isolation between the pumped medium and the pump shaft 14, ensuring that the medium or impurities within the medium do not damage the pump shaft 14.

[0065] The balance chamber 23, together with the balance pipe 6, the jet hole 73, and the balance holes 120 on the submersible pump impeller 4 and the final stage impeller 12, forms a dual axial force balance capability for the submersible pump. The sand-throwing ring 108 enables the rotor component to resist sand throwing, preventing impurities or silt in the medium from entering the submersible motor 1 and causing damage to the submersible motor 1. The elastic ring 52 enables the pump shaft 14 and the submersible motor shaft 50 to have a flexible connection, so that the vibration of the pump rotor component will not be transmitted to the submersible motor 1, or the vibration of the submersible motor 1 will not be transmitted to the rotor component, ensuring the safe and reliable operation of the submersible pump. The main anti-slip bearing 40 and the auxiliary anti-slip bearing 46 enable the submersible pump to independently withstand the instantaneous axial upward movement of the rotor component at the moment of pump start-up, and at the same time, to independently withstand the instantaneous downward movement of the rotor component under the counter-thrust of the medium after the pump starts running, ensuring that the main shaft of the submersible motor will not be driven by the rotor component to move instantaneously upward or downward, ensuring the safe and reliable operation of the submersible motor.

[0066] In some embodiments, the thrust bearing 41 and the thrust disc 31 form a first axial clearance F; the thrust bearing 41 and the isolation ring 102 provided on the isolation bushing 17 form a second axial clearance G; the rear end ring 13 and the auxiliary anti-slip bearing 46 form a third axial clearance H; the rear end ring 13 and the impeller 4 and the final stage impeller 12 form equal axial clearances, which are all fourth axial clearances I; the impeller 4 and the suction section 3 form a fifth axial clearance J; the sand-throwing ring 108 provided on the pump coupling 54 and the submerged axial force probe 53 form a sixth axial clearance L; and the third axial force-bearing surface 110 provided on the pump coupling 54... The fourth axial force-bearing surface 113 of the motor coupling 51 forms a seventh axial clearance N; the fifth axial force-bearing surface 119 of the pump shaft 14 and the axial force-bearing groove surface 114 of the motor coupling 51 form an eighth axial clearance O; the sand-throwing ring 108 of the water pump coupling 54 and the top of the submersible vertical displacement probe 57 form a ninth axial clearance K; the sand-throwing ring 108 of the water pump coupling 54 and the submersible vertical displacement probe 57 form a tenth axial clearance X; and the submersible vertical displacement probe 57 and the upward measuring surface 106 of the water pump coupling 54 form an eleventh axial clearance M.

[0067] The above-mentioned clearances satisfy the following relationships: First axial clearance F < Second axial clearance G, First axial clearance F = Third axial clearance H, Second axial clearance G > Fourth axial clearance I, Fourth axial clearance I = Fifth axial clearance J, Fifth axial clearance J > Sixth axial clearance L, Fifth axial clearance J > Ninth axial clearance K, Ninth axial clearance K = Eighth axial clearance O, Eleventh axial clearance M > First axial clearance F, Tenth axial clearance X > Ninth axial clearance K.

[0068] Based on the above structural configuration, the thrust bearing assembly 10, the rear end ring 13, and the auxiliary anti-slip bearing 46 bear the axial displacement force of the submersible pump rotor component moving upward, and the thrust bearing assembly 10 bears the axial displacement force of the submersible pump rotor component moving downward, ensuring that the submersible motor does not bear axial force; the submersible axial force probe 53 detects the axial force of the submersible pump in real time, and the submersible vertical displacement probe 57 detects the axial upward displacement of the rotor component caused by the start-up and operation of the submersible pump in real time. When the axial upward displacement reaches the set limit value, it is determined that the thrust bearing assembly 10, the rear end ring 13, and the auxiliary anti-slip bearing 46 need to be repaired or replaced; the submersible vertical displacement probe 57 also detects the axial downward displacement of the rotor component during long-term operation of the submersible pump in real time, and when the axial downward .... When the downward displacement reaches the set controllable value, it is determined that the axial displacement force of the submersible pump rotor component begins to be borne by the submersible motor. At the same time, it can be considered that the thrust bearing assembly needs to be repaired or replaced. When the axial downward displacement reaches the set limit value, it is determined that the thrust bearing assembly 10 and the submersible motor need to be maintained, repaired or replaced. The pump coupling 54 cooperates with the elastic ring 52 and the motor coupling 51, and the shaft extension 118 cooperates with the axial force groove surface 114 to form a flexible connection, so that the vibration of the pump rotor component will not be transmitted to the submersible motor 1, or the vibration of the submersible motor 1 will not be transmitted to the rotor component. At the same time, it can ensure that the weight of the submersible pump rotor component and the water thrust are fully applied to the axial positioning surface of the submersible motor shaft 50 of the submersible motor 1.

[0069] During use, the third submersible vibration probe 30 detects the axial vibration value of the submersible pump in real time, and the submersible pressure probe 20 detects the balance pressure value at the balance chamber 23 of the thrust bearing assembly 10 in real time. When the pressure value is low, it can be determined that the filter hole 103 of the isolation bushing 17 is blocked, or that the submersible pump is operating with a low head. The second submersible temperature probe 35 detects the operating temperature value at the thrust bearing 41 of the thrust bearing assembly 10 in real time, the fourth submersible vibration probe 37 detects the radial vibration value of the submersible pump in real time, the fifth submersible vibration probe 58 detects the radial vibration value at the connection between the submersible pump and the submersible motor 1 in real time, the first submersible temperature probe 60 detects the operating temperature value of the submersible motor 1 in real time, the first submersible vibration probe 15 detects the radial vibration value at the bottom of the submersible motor 1 in real time, and the second submersible vibration probe 16 detects the axial vibration value at the bottom of the submersible motor 1 in real time.

[0070] Based on the above embodiments, the high-stability and reliable deep-well electric submersible pump provided by this invention allows for the installation of more impellers (up to 80 or more) in series, enabling the pump flow rate to reach 5000 m³ / h or more, and the pump head to reach 4000 m or more. This ensures the high-stability and reliable deep-well electric submersible pump can independently withstand the weight of the pump rotor assembly and the counter-thrust generated by the pumped medium, preventing the rotor assembly's weight and counter-thrust from acting on the submersible motor and damaging it. Furthermore, the pump has the dual capability of independently withstanding the instantaneous axial upward movement of the rotor assembly at the moment of pump start-up, and simultaneously, independently withstanding the instantaneous downward movement of the rotor assembly under the counter-thrust of the medium after the pump's instantaneous start-up, ensuring that the submersible motor's main shaft is not driven by the rotor assembly to move instantaneously upward or downward, guaranteeing the safe and reliable operation of the submersible motor.

[0071] Submersible pumps have the ability to balance dual axial forces and prevent the rotor components from shifting downwards during operation. They have the ability to completely balance residual axial forces, ensuring that the rotor components and submersible motors operate safely without bearing any axial forces. Submersible pumps also have the ability to resist cavitation with high-pressure jets, which can effectively ensure the reliable suction capacity of the pump and prevent vibration and impeller cavitation damage caused by cavitation during pump operation, effectively extending the service life of deep well electric submersible pumps.

[0072] It has the ability to flexibly connect the pump shaft and the motor shaft, preventing the vibration of the pump rotor components from being transmitted to the motor or the vibration of the motor rotor from being transmitted to the pump rotor components, thus ensuring the safe and reliable operation of the submersible motor and the submersible pump; it has the ability to measure in real time the minute axial force caused by changes in operating conditions during the operation of the submersible pump, the ability to measure in real time the minute axial movement caused by changes in operating conditions during the operation of the submersible pump, the ability to measure in real time the wear of the thrust bearing caused by long-term use of the submersible pump requiring maintenance and replacement, and the ability to measure in real time the wear of the thrust bearing caused by long-term use of the submersible motor requiring maintenance and replacement.

[0073] It has the ability to completely isolate the pumped medium from the main shaft, ensuring that impurities in the medium do not wear down the main shaft; it has the ability to prevent debris or sand from being thrown from the rotor components, preventing impurities or silt in the medium from entering the submersible motor and damaging it; it has the ability to measure the speed of the deep well electric submersible pump in real time, and can determine the impact of the power grid on the pump, such as voltage phase loss or unstable power grid frequency, on the damage to the submersible motor, and can also determine the damage caused by the submersible motor stalling due to the pump's ultra-high flow rate operation; it has the ability to measure the axial and radial vibration of the submersible pump in real time, and the axial and radial vibration of the submersible motor in real time, and the temperature of the submersible pump and submersible motor in real time, effectively improving the service life and safety, stability and reliability of the deep well electric submersible pump, and reducing the pump's operation, maintenance and repair costs.

[0074] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and substitutions can be made without departing from the technical principles of the present invention, and these improvements and substitutions should also be considered within the scope of protection of the present invention.

Claims

1. A highly stable and reliable deep-well electric submersible pump, characterized in that, include: The pump body includes a suction section and a fluid guide connected to one end of the suction section; A rotor assembly is disposed within the pump body, the rotor assembly including a pump shaft, an impeller mounted on the pump shaft, and a final stage impeller; A thrust bearing assembly is installed at the end of the guide fluid away from the suction section and connected to one end of the pump shaft; A check valve assembly is installed at the end of the thrust bearing assembly away from the fluid guide; A connecting bracket is installed at the end of the suction section away from the fluid guide; A submersible motor is mounted on the end of the connecting frame away from the suction section, and the submersible motor has a submersible motor shaft; A motor coupling is disposed within the connecting frame, the motor coupling is connected to the submersible motor shaft, and the motor coupling has a first elastic ring. A water pump coupling, connected to the motor coupling and installed at the other end of the pump shaft, the water pump coupling having a second elastic ring, the second elastic ring being correspondingly arranged to the first elastic ring; and An elastic ring is installed in the first elastic ring position and the second elastic ring position; The thrust bearing assembly includes a guide bearing housing, a guide rib, a guide cone, a guide shield, a thrust disk, a thrust bearing, and a main anti-slip bearing. The guide cone is connected to the guide bearing housing through the guide rib. The guide shield is installed on the guide cone. The thrust disk is spaced apart inside the guide cone and installed on the pump shaft. The thrust bearing is located on the inner wall of the guide cone and installed on the pump shaft. The main anti-slip bearing is installed on the inner wall of the guide shield and is located between the guide shield and the thrust disk. A balance cavity is formed between the thrust disk and the thrust bearing. The thrust bearing has a main flow channel, and the guide cone has a liquid collection cavity. The balance cavity is connected to the liquid collection cavity through the main flow channel. The flow guide shroud has a liquid collection chamber, and an auxiliary flow channel is formed between the main anti-slip bearing and the thrust plate. The liquid collection chamber is connected to the liquid receiving chamber through the auxiliary flow channel. The thrust bearing assembly includes a balance tube, the guide cone has a pressure relief chamber, the pressure relief chamber is connected to the liquid collection chamber through a flow channel, one end of the balance tube is connected to the pressure relief chamber, and the other end of the balance tube is used to connect to the jet hole of the suction section; The thrust bearing includes a bearing frame and a bearing body. The bearing body is mounted on the bearing frame, the bearing frame is mounted on the inner wall of the guide cone, and the bearing body is mounted on the pump shaft. The bearing body has a first radial lubrication groove, a balance ring groove, and a first axial force-bearing surface at one end near the thrust plate. The bearing body has a radial force-bearing surface in the middle. The first axial force-bearing surface is located on the outer periphery of the balance ring groove. The first radial lubrication groove is located on both sides of the balance ring groove and the first axial force-bearing surface. The first radial lubrication groove has a mounting hole. The radial force-bearing surface has an axial lubrication groove. The first radial lubrication groove has a first axial force-bearing surface end edge and a first axial force-bearing surface start edge on both sides, and a first lubrication slope is formed between the first axial force-bearing surface start edge and the first axial force-bearing surface.

2. The highly stable and reliable deep-well electric submersible pump according to claim 1, characterized in that, The main anti-slip bearing has a second axial force-bearing surface and a second radial lubrication groove that are staggered at one end near the thrust plate, and the second axial force-bearing surface is spaced apart from the thrust plate; The second radial lubrication groove has screw holes, and the second radial lubrication groove has a second axial force-bearing surface end edge and a second axial force-bearing surface start edge on both sides. A second lubrication slope is formed between the second axial force-bearing surface start edge and the second axial force-bearing surface.

3. The highly stable and reliable deep-well electric submersible pump according to claim 1, characterized in that, The thrust disk includes: The disc body has a first through hole in the middle; the inner wall of the disc body has a main flat keyway and a sealing ring groove; the front side of the disc body has an auxiliary axial force-bearing surface; the rear side of the disc body has a main axial force-bearing surface; the main axial force-bearing surface has a balance ring groove; and A cylindrical body is provided on the main axial force-bearing surface. The middle part of the cylindrical body has a second through hole, which communicates with the first through hole. The inner wall of the cylindrical body has an auxiliary flat keyway. The cylindrical body is configured to be installed in a thrust bearing, and the main axial force-bearing surface is spaced apart from the thrust bearing. The first through hole and the second through hole are used to install the pump shaft.

4. The highly stable and reliable deep-well electric submersible pump according to claim 3, characterized in that, The main axial force-bearing surface is parallel to the auxiliary axial force-bearing surface; the front side of the disc body also has a forward-extending arc surface and an end face, the arc surface is located between the auxiliary axial force-bearing surface and the end face, and the end face is parallel to the auxiliary axial force-bearing surface; the front end of the main flat keyway extends out of the end face; the outer diameter of the arc surface near the end face is smaller than the outer diameter of the arc surface near the auxiliary axial force-bearing surface.

5. The highly stable and reliable deep-well electric submersible pump according to claim 1, characterized in that, The upper part of the motor coupling has a first torque transmission block that is alternately distributed with the first elastic ring, and the water pump coupling has a second torque transmission block that is alternately distributed with the second elastic ring. The outer periphery of the elastic ring has elastic blocks that are spaced apart, and the elastic blocks are installed one-to-one in the first elastic ring and the second elastic ring.

6. The highly stable and reliable deep-well electric submersible pump according to claim 1, characterized in that, The outer peripheral wall of the motor coupling has speed measuring teeth, and a submersible speed probe is installed on the connecting frame. The submersible speed probe is used to measure the speed of the speed measuring teeth. The outer peripheral wall of the water pump coupling has a sand-throwing ring, the outer edge of which is bent downwards and extends; the lower surface of the sand-throwing ring forms a downward measuring surface, and a submerged axial force probe is installed in the suction section, the submerged axial force probe being in contact with the downward measuring surface; The bottom of the water pump coupling has an upward measuring surface, and the suction section is equipped with a submerged liquid vertical displacement probe, which is in contact with the upward measuring surface. A submersible temperature probe is installed inside the connecting frame, and a submersible vibration probe is installed on the outer wall of the connecting frame.

7. The highly stable and reliable deep-well electric submersible pump according to claim 1, characterized in that, The guide fluid is equipped with a sliding bearing, which is installed between the guide fluid and the pump shaft.

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