Dual channel hydraulic lift pump

Abstract

This invention relates to a dual-channel hydraulic lift pump for solid fluidized bed exploitation of marine natural gas hydrates, comprising a pump section, a turbine section, a bridge-type channel assembly, an upper connector, a housing, and a lower connector. The pump section mainly consists of a pump impeller, a guide wheel, a pump shaft, and a pump housing. The turbine section mainly consists of a stator, a rotor, a turbine shaft, and a turbine housing. The bridge-type channel assembly mainly consists of a bridge-type channel connector, an intermediate connecting shaft, and a sealing assembly. The pump section and turbine section are connected as a unit via the bridge-type channel assembly and held in place in the middle of the housing by a centralizing block. During operation, the turbine section converts hydraulic energy into mechanical energy, which is transmitted to the pump shaft via the intermediate connecting shaft. The pump shaft drives the pump impeller to continuously draw back the fluid from the wellbore, performs work on the back fluid, and then discharges it. This invention controls and reduces the pressure of the fluid column on the formation during operation, solves the problem of wellbore leakage in solid fluidized bed exploitation, and greatly improves exploitation efficiency.

Description

Technical Field

[0001] This invention relates to a dual-channel hydraulic lift pump used for solid fluidized bed extraction of marine natural gas hydrates, belonging to the field of marine natural gas hydrate extraction equipment. Background Technology

[0002] Solid-state fluidized bed extraction of marine natural gas hydrates is a development technique addressing issues such as natural gas escape and formation collapse encountered in other extraction methods. During operation, rotary drilling is first used to mechanically break up the solid natural gas hydrate in situ within the reservoir, creating a borehole. Then, high-pressure water jets are used to further break up the solid hydrate and mix it with drilling fluid. The circulating drilling fluid, containing hydrate solid particles, is brought back to the surface from the seabed, achieving green extraction of seabed natural gas hydrates. However, due to the narrow equivalent density window and low fracturing pressure of hydrate reservoirs, formation leakage is extremely common. Most of the drilling fluid pumped into the hydrate reservoir from the surface is lost and cannot return, hindering effective hydrate extraction. Reducing the pressure of the wellbore fluid column on the hydrate reservoir and controlling formation leakage is an effective method to solve these problems. In wellbores containing hydrated solid particles, lifting pumps can be used to pump drilling fluid to the sea surface, effectively solving the leakage problem of hydrated reservoirs and improving extraction efficiency. Summary of the Invention

[0003] The purpose of this invention is to meet the requirements of solid fluidized bed extraction technology for marine natural gas hydrates by providing a dual-channel hydraulic lift pump to achieve green and efficient extraction of marine natural gas hydrates.

[0004] The technical solution adopted in this invention is:

[0005] This invention discloses a dual-channel hydraulic lifting pump, comprising a pump section, a turbine section, a bridge-type channel assembly, an upper connector, a housing, and a lower connector. The pump section mainly consists of a pump impeller, a guide wheel, a radial bearing, a thrust bearing assembly, a pump shaft, a pump housing, an upper connector for the pump housing, a lower connector for the pump housing, a clamping nut, a flow sleeve, and a stop pin. The pump impeller is fitted onto the pump shaft with a clearance fit. To meet different head requirements, multiple pump impellers are mounted on the pump shaft. Guide wheels are installed after each pump impeller, alternating with the pump impellers to form a series connection of pumps. During operation, the pump impeller drives the flow of the return fluid in its flow channel, performing work on the return fluid and converting mechanical energy into the return fluid's energy. After being discharged by the pump impeller, the return fluid enters the guide wheel, where it is decelerated and its flow direction is changed. Then, it enters the next stage pump impeller at a suitable speed and direction, where its energy is further increased. After being decelerated and guided by the next stage guide wheel, it enters subsequent pump impellers and guide wheels again until the last stage guide wheel. After the return fluid's energy has increased to the required level, it flows out of the pump section. Radial bearings are installed at both ends of the pump shaft to keep it aligned, preventing eccentricity during rotation. A thrust bearing assembly is installed at the bottom of the pump shaft to bear the axial load generated by the pump impeller during operation and to transfer the axial load to the pump casing. The lower section of the pump shaft is hollow, extending upwards within the shaft to the lower end of the pump impeller inlet. Grooves are evenly distributed circumferentially at the top of the corresponding hollow section, forming a continuous flow channel to allow the return fluid from the lower end of the pump shaft to smoothly pass through the hollow section and enter the pump impeller. The upper and lower joints of the pump casing are threaded to the pump casing, securing the pump section components within the casing. Circumferentially distributed centering blocks are located on the outer wall of the pump casing corresponding to the positions where the radial bearings are placed.

[0006] The turbine section mainly consists of a stator, rotor, centralizing bearing, thrust bearing, turbine shaft, turbine housing, spline joint, flow positioning sleeve, upper turbine housing joint, and lower turbine housing joint. The rotors are mounted on the turbine shaft with a clearance fit. Since the output torque of a single rotor is limited, multiple rotors are mounted on the turbine shaft to meet torque requirements. The stator is installed in front of each rotor, alternating with it. During operation, the hydraulic fluid first enters the stator, where it is accelerated and guided in the stator flow channels before entering the rotor at a specific direction and speed. As it flows through the rotor blades, it generates lift and impact forces, driving the rotor to rotate, thus converting the hydraulic energy of the hydraulic fluid into mechanical energy. After exiting the rotor, the hydraulic fluid enters the next stage stator, where it is again accelerated and guided before entering the next stage rotor. The fluid energy of the hydraulic fluid is again converted into mechanical energy, repeating this energy conversion process until the hydraulic fluid exits the last stage rotor. Centralizing bearings are installed at both ends of the turbine shaft to withstand the radial load generated during turbine shaft rotation, preventing eccentricity. A thrust bearing is installed at the lowest end of the turbine shaft to bear the axial load on the turbine shaft. The lower section of the turbine shaft is hollow, with uniformly spaced grooves along the circumference near the top of the last stage rotor to allow the kinetic fluid flowing from the last stage rotor to exit through the hollow section of the turbine shaft. A spline joint is threaded to the turbine shaft, clamping and securing the components mounted on the turbine shaft. Both the upper and lower turbine housing joints are threaded to the turbine housing, fixing the turbine section components within the turbine housing. The turbine housing has circumferentially distributed centering blocks corresponding to the location of the centering bearing. The lower turbine housing joint has a tapered section and groove at its end to transmit axial load and counter-torque, and its lower half is designed to be flat to allow fluid passage.

[0007] The bridge-type channel assembly mainly consists of a bridge-type channel connector, an intermediate connecting shaft, and a sealing assembly. The bridge-type channel connector has a double-layer structure, consisting of a central tube and a shell. Five independent flow channels are evenly arranged circumferentially. Two channels are used to deliver power fluid to the lower turbine section, and the other three channels are used to deliver return fluid from the pump section upwards. The inlet and outlet of the channels delivering power fluid and return fluid are opposite, and they are alternately arranged circumferentially to ensure uniform stress on the bridge-type channel assembly. The intermediate connecting shaft has a threaded upper end and an internal spline at the lower end, and its upper half is hollow, with evenly spaced grooves along the circumference at the bottom of the hollow section. The sealing assembly mainly consists of a gap sealing sleeve, a Chevron seal, a spacer ring, a gland, an O-ring, a wear ring, and screws. The gap sealing sleeve is threaded into the central tube of the bridge-type channel connector, and the intermediate connecting shaft passes through the center of the sealing assembly. The sealing assembly divides the inner cavity of the bridge-type channel joint's intermediate tube into an upper chamber and a lower chamber. The upper chamber is the return fluid chamber, and the lower chamber is the dynamic fluid chamber. The lower end of the gap sealing sleeve has a groove to collect solid particles brought in from the gap.

[0008] Furthermore, the pump casing lower joint of the pump section and the bridge channel joint of the bridge channel assembly are connected together by threads. The bridge channel joint of the bridge channel assembly and the turbine housing upper joint of the turbine section are also connected together by threads. The pump shaft is directly connected to the intermediate connecting shaft by threads, and the turbine shaft is connected to the intermediate connecting shaft by a spline joint. This achieves the fixed connection of the pump section, bridge channel assembly, and turbine section into a single assembly. The assembly is centered within the housing by the centralizing blocks outside the pump casing and turbine housing. The power generated by the turbine section is transmitted from the turbine shaft to the intermediate connecting shaft via the spline joint, and then from the intermediate connecting shaft to the pump shaft, which in turn drives the pump impeller. The pump section's counter-torque and axial load during operation are borne by the pump casing, while the turbine section's counter-torque and axial load are borne by the turbine housing. The pump casing transmits the counter-torque and axial load to the bridge-type channel joint via the lower pump casing connector. The bridge-type channel joint then transmits the pump section's counter-torque and axial load to the turbine housing via the upper turbine housing connector. The turbine housing then transmits the counter-torque and axial load from both the pump and turbine sections to the lower turbine housing connector. The conical section of the lower turbine housing connector sits on the conical surface of the lower connector, transmitting the axial load from the assembly to the lower connector and then to the housing. Simultaneously, a key within the lower connector engages in a groove within the lower turbine housing connector to transmit the counter-torque.

[0009] Furthermore, the lower end face of the upper connector is closely attached to the centering block of the upper connector on the pump casing, fixing the assembly in the casing and achieving axial positioning.

[0010] Working principle of the invention:

[0011] The high-pressure hydrant delivered from the top enters the bridge-type channel assembly through the annular channel between the pump section and the housing. From there, it flows through the hydrant channel within the bridge-type channel assembly into the turbine section. In the turbine section, after being accelerated by the stator guide, it enters the rotor, where its fluid energy is converted into mechanical energy, driving the rotor to rotate. The hydrant then enters the next stage stator, and this process repeats. After passing through multiple stages of stators and rotors, the hydrant exits from the turbine section. The multi-stage rotors drive the turbine shaft to rotate, which transmits power to the pump shaft via an intermediate connecting shaft. The rotating pump shaft drives the pump impeller on it to rotate. The impeller performs work on the return fluid, which, after being decelerated and guided by the guide wheel, flows to the next stage pump impeller. This process repeats, and after passing through multiple stages of pump impellers and guide wheels, the return fluid exits the pump section. Simultaneously, the pump impeller continuously draws in the lower return fluid. The lower return fluid enters the bridge-type channel assembly through the annular channel between the turbine section and the housing. From there, it flows through the return fluid channel within the bridge-type channel assembly into the hollow section of the pump shaft and reaches the pump impeller inlet, where it is drawn in by the pump impeller.

[0012] The beneficial effects of the present invention are as follows: (1) The lift pump reduces the pressure of the wellbore fluid column on the hydrate reservoir, avoiding the problem of drilling fluid loss caused by the fracturing of the hydrate reservoir. This allows a normal circulation to be established in the wellbore when drilling into the seabed natural gas hydrate layer, bringing the broken solid particles of natural gas hydrate from the formation back to the sea surface, which greatly improves the production capacity of the marine natural gas hydrate solid fluidized mining method; (2) By changing the flow rate of the power fluid entering the lift pump at the sea surface, the rotation speed of the rotor in the turbine section is adjusted, which changes the rotation speed of the pump wheel in the pump section, thereby adjusting the lift pump head. The change in the lift pump head adjusts the pressure of the wellbore fluid column on the bottom of the well, thus achieving the purpose of pressure controlled drilling, which can meet the drilling needs of formations with different leakage pressures. Attached Figure Description

[0013] Figure 1 This is a schematic diagram of the structure of a dual-channel hydraulic lifting pump according to the present invention;

[0014] Figure 2 yes Figure 1 Cross-sectional view of AA;

[0015] Figure 3 yes Figure 1 Cross-sectional view of BB;

[0016] Figure 4 yes Figure 1 Cross-sectional view of CC;

[0017] Figure 5 yes Figure 1 Cross-sectional view of DD;

[0018] Figure 6 yes Figure 1 Cross-sectional view of EE;

[0019] Figure 7 yes Figure 1 Cross-sectional view of FF;

[0020] Figure 8 yes Figure 1 Cross-sectional view of GG;

[0021] Figure 9 yes Figure 1 A partial enlarged view of the central sealing assembly;

[0022] Figure 10 yes Figure 1 The working principle diagram of a dual-channel hydraulic lifting pump is described above.

[0023] In the diagram: 1. Upper connector, 2. Housing, 3. Pump housing upper connector, 4. Stop pin, 5. Compression nut, 6. Pump housing, 7. Radial bearing, 8. Guide wheel, 9. Pump impeller, 10. Pump shaft, 11. Flow sleeve, 12. Radial bearing, 13. Thrust bearing assembly, 14. Pump housing lower connector, 15. Intermediate connecting shaft, 16. Bridge-type channel connector, 17. Screw, 18. Gland, 19. O-ring, 20. Wear ring, 21. Chevron seal, 22. Spacer ring, 23. Chevron seal, 24. Gap sealing sleeve, 25. Turbine housing upper connector, 26. Spline connector, 27. Turbine shaft, 28. Turbine housing, 29. Centralizing bearing, 30. Stator, 31. Rotor, 32. Centralizing bearing, 33. Flow positioning sleeve, 34. Thrust bearing, 35. Turbine housing lower connector, 36. Lower connector. Detailed Implementation

[0024] The specific embodiments of the present invention will be further described below with reference to the accompanying drawings.

[0025] like Figure 1 , Figure 2 , Figure 3 , Figure 4 , Figure 5 , Figure 6 , Figure 7 , Figure 8As shown, this invention discloses a dual-channel hydraulic lifting pump, comprising a pump section, a bridge-type channel assembly, a turbine section, an upper connector 1, a housing 2, and a lower connector 36. The pump section mainly consists of a pump impeller 9, a guide wheel 8, radial bearings 7 and 12, a thrust bearing assembly 13, a pump shaft 10, a pump housing 6, an upper connector 3 for the pump housing, a lower connector 14 for the pump housing, a clamping nut 5, a flow sleeve 11, and a stop pin 4. The pump impeller 9 is fitted onto the pump shaft 10 with a clearance fit. To meet different head requirements, multiple pump impellers 9 are installed on the pump shaft 10. The guide wheel 8 is installed after each pump impeller 9, alternating with the pump impellers 9 to form a series connection of the pumps. During operation, the pump shaft 10 rotates, and the pump impeller 9 rotates accordingly. The pump impeller 9 drives the flow of the return fluid in its flow channel and performs work on the return fluid, converting mechanical energy into the energy of the return fluid. After being discharged by the pump impeller 9, the return fluid enters the guide impeller 8, where it is decelerated and its flow direction is changed. Then, it enters the next stage pump impeller 9 at a suitable speed and direction, where its energy is further increased. After being decelerated and guided by the next stage guide impeller 8, it enters the subsequent pump impellers 9 and guide impellers 8 again, until the last stage guide impeller 8. After the energy of the return fluid increases to the required level, it flows out of the pump section. Radial bearings 7 and 12 are installed at both ends of the pump shaft 8 to straighten the pump shaft 10, preventing eccentricity during rotation. A thrust bearing assembly 13 is installed at the lowest end of the pump shaft 10 to bear the axial load generated by the pump impeller 9 during operation and to transfer the axial load to the pump casing 6. The lower section of the pump shaft 10 is hollow, extending upwards to the lower end of the pump impeller 9's suction inlet. Grooves ① are evenly distributed circumferentially at the top of the corresponding hollow section of the pump shaft 10, aligning with holes on the flow sleeve 11 to form a through-flow channel, allowing the return fluid from the lower end of the pump shaft 10 to smoothly pass through the hollow section and enter the pump impeller 9. The outer wall of the pump casing 6 has circumferentially distributed centering blocks b and c corresponding to the positions where radial bearings 7 and 12 are placed. The cross-sections of centering blocks b and c are fan-shaped to facilitate fluid passage. Components mounted on the pump shaft 10 are positioned by the lower step of the pump shaft 10, secured by clamping nuts 5, and prevented from loosening by locking pins 4. The upper connector 3 and lower connector 14 of the pump casing are threadedly connected to the pump casing 6. Components mounted on the inner wall of the pump casing 6 are secured by the upper connector 3 and lower connector 14, and are integrally connected to the pump casing 6. The straightening blocks b and c on the outer wall of the pump casing 6, together with the straightening block a on the upper connector 3 of the pump casing, straighten the pump section to the center of the casing 2.

[0026] like Figure 1 , Figure 6 , Figure 7 , Figure 8The turbine section shown mainly consists of a stator 30, a rotor 31, centralizing bearings 29 and 32, a thrust bearing 34, a turbine shaft 27, a turbine housing 28, a spline joint 26, a flow positioning sleeve 33, an upper turbine housing joint 25, and a lower turbine housing joint 35. The rotor 31 is mounted on the turbine shaft 27 with a clearance fit. Since the output torque of a single rotor 31 is limited, multiple rotors 31 are mounted on the turbine shaft 27 to meet torque requirements. The stator 30 is installed in front of each rotor 31, alternating with the rotors. During operation, the motive fluid first enters the stator 30, is accelerated and guided in the stator 30's flow channels, and then enters the rotor 31 at a certain direction and speed. As it flows through the rotor 31's blades, it generates lift and impact forces on the rotor 31's blades, driving the rotor 31 to rotate, thus converting the fluid energy of the motive fluid into mechanical energy. After the motive fluid flows out of the rotor 31, it enters the next stage stator 30. In the next stage stator 30, it is accelerated and guided again before entering the next stage rotor 31. The fluid energy of the motive fluid is converted into mechanical energy again, and this energy conversion process is repeated until the motive fluid flows out of the last stage rotor 31. Steering bearings 29 and 32 are installed at both ends of the turbine shaft 27 to bear the radial load generated during the rotation of the turbine shaft 27, preventing it from becoming eccentric. A thrust bearing 34 is installed at the lowest end of the turbine shaft 27 to bear the axial load on the turbine shaft 27. The lower section of the turbine shaft 27 is hollow, and grooves ⑤ are evenly distributed along the circumference near the top of the last stage rotor 31 in the hollow section. The grooves ⑤ are aligned with the holes on the flow positioning sleeve 33 so that the motive fluid flowing out from the last stage rotor 31 can flow out through the hollow section of the turbine shaft 27. The turbine housing 28 has circumferentially distributed steering blocks d and e corresponding to the positions where the steering bearings 29 and 32 are placed. The cross-sections of the steering blocks d and e are fan-shaped to allow fluid passage. The lower turbine housing connector 35 has a conical section and a groove at its end to transmit axial load and counter-torque, and its lower half is flattened to allow fluid passage. Components mounted on the turbine shaft 27 are positioned by a step at the lower end of the turbine shaft 27. The spline connector 26 is threadedly connected to the turbine shaft 27 and clamps and secures the components mounted on the turbine shaft 27, making them integrally connected to the turbine shaft 27. The upper turbine housing connector 25 and the lower turbine housing connector 35 are both threadedly connected to the turbine housing 28. Components mounted on the inner wall of the turbine housing 28 are clamped and secured by the upper turbine housing connector 25 and the lower turbine housing connector 35, and are integrally connected to the turbine housing 28. The centering blocks d and e on the outer wall of the turbine housing 28 center the turbine joint at the center of the housing 2.

[0027] like Figure 1 , Figure 5 , Figure 9As shown, the bridge-type channel assembly mainly consists of a bridge-type channel connector 16, an intermediate connecting shaft 15, and a sealing assembly. The bridge-type channel connector 16 has a double-layer structure, consisting of an intermediate pipe and an outer shell. Five independent flow channels α, β, γ, δ, and ε are evenly arranged circumferentially on its surface. Flow channel α connects to the upper cavity of the intermediate pipe of the bridge-type channel connector 16 via slot ③ and the corresponding slots of flow channels β and δ, for conveying the pump section's return fluid upwards. Flow channel γ connects to the lower cavity of the intermediate pipe of the bridge-type channel connector 16 via slot ④ and the corresponding slot of flow channel ε, for conveying the power fluid downwards into the turbine section. The flow channels α, β, and δ for conveying the return fluid have inlets and outlets opposite to those of the flow channels γ and ε for conveying the power fluid, and are arranged alternately circumferentially to ensure uniform stress on the bridge-type channel assembly. The intermediate connecting shaft 15 has a threaded upper end and an internal spline at the lower end. Its upper half is hollow, with a uniformly spaced circumferential groove at the bottom of the hollow section ② to connect the inner cavity of the intermediate tube of the bridge-type channel joint 16 and the hollow section of the lower part of the pump shaft 10, thereby introducing the return fluid into the pump section. The sealing assembly mainly consists of a gap sealing sleeve 24, Chevron seals 21 and 23, a spacer ring 22, a gland 18, an O-ring 19, a wear ring 20, and screws 17. The gap sealing sleeve 24 is threaded into the intermediate tube of the bridge-type channel joint 16, and the intermediate connecting shaft 15 passes through the center of the sealing assembly. Chevron seals 21 and 23 and spacer ring 22 are installed at the upper end of the gap sealing sleeve 24, and the O-ring 19 and wear ring 20 are installed in the groove of the gland 18. Finally, they are fixed to the gap sealing sleeve 24 by screws 17. The sealing assembly divides the inner cavity of the intermediate tube of the bridge-type channel connector 16 into an upper cavity and a lower cavity. The upper cavity is the return fluid cavity, and the lower cavity is the power fluid cavity. The lower end of the gap sealing sleeve 24 has a groove for collecting solid particles brought in from the gap.

[0028] Furthermore, the pump housing lower connector 14 of the pump section and the bridge channel connector 16 of the bridge channel assembly are connected together by threads. The bridge channel connector 16 of the bridge channel assembly and the turbine housing upper connector 25 of the turbine section are also connected together by threads. The pump shaft 10 is directly connected to the intermediate connecting shaft 15 by threads, and the turbine shaft 27 is connected to the intermediate connecting shaft 15 through a spline connector 26. This achieves the fixed connection of the pump section, the bridge channel assembly, and the turbine section into a single assembly. The centralizing blocks b and c outside the pump housing 6 and the centralizing blocks d and e outside the turbine housing 28 ensure that the assembly is located at the center of the housing 2. The power generated by the turbine section is transmitted from the turbine shaft 27 to the intermediate connecting shaft 15 through the spline connector 26, and then from the intermediate connecting shaft 15 to the pump shaft 10. The pump shaft 10 then drives the pump wheel 9 to work. The pump section's counter-torque and axial load during operation are borne by the pump casing 6, while the turbine section's counter-torque and axial load are borne by the turbine casing 28. The pump casing 6 transmits the counter-torque and axial load to the bridge-type channel joint 16 via the lower pump casing connector 14. The bridge-type channel joint 16 then transmits the pump section's counter-torque and axial load to the turbine casing 28 via the upper turbine casing connector 25. The turbine casing 28 transmits the counter-torque and axial load of both the pump and turbine sections to the lower turbine casing connector 35. The conical section of the lower turbine casing connector 35 sits on the conical surface of the lower connector 36, transmitting the axial load from the assembly to the lower connector 36 and then to the casing 2. Simultaneously, a key within the lower connector 36 engages in the groove of the lower turbine casing connector 35 to transmit the counter-torque.

[0029] Furthermore, the lower end face of the upper connector 1 is closely attached to the straightening block a of the upper connector 3 of the pump casing, fixing the assembly in the housing 2 to achieve axial positioning.

[0030] like Figure 10The diagram shows the working principle of a dual-channel hydraulic lifting pump according to the present invention. The thin single arrow indicates the flow diagram of the power fluid, and the thick double arrow indicates the flow diagram of the return fluid. The power fluid delivered from the top enters the bridge channel assembly through the annular channel between the pump section and the housing 2. After passing through the power fluid flow channels γ and ε in the bridge channel assembly, it enters the turbine section. In the turbine section, after being guided and accelerated by the stator 30, it enters the rotor 31, where the fluid energy is converted into mechanical energy, driving the rotor 31 to rotate. The power fluid then enters the next stage stator 30, and so on. After passing through multiple stages of stators 30 and rotors 31, the power fluid is discharged from the turbine section. The multi-stage rotors 31 drive the turbine shaft 27 to rotate, and the turbine shaft 27 transmits the power to the pump shaft 10 through the intermediate connecting shaft 15. The pump shaft 10 rotates, driving the pump wheel 9 on the pump shaft 10 to rotate. The pump wheel 9 does work on the return liquid, and after being decelerated and guided by the guide wheel 8, it flows to the next stage pump wheel 9. This process is repeated. After passing through multiple stages of pump wheels 9 and guide wheels 8, the return liquid flows out of the pump section. At the same time, the pump wheel 9 continuously draws in the lower return liquid. The lower return liquid enters the bridge channel assembly through the annular channel between the turbine section and the housing 2. It then enters the hollow section of the pump shaft 10 through the return liquid flow channels α, β, and δ in the bridge channel assembly and reaches the suction port of the pump wheel 9, where it is drawn in by the pump wheel 9.

[0031] The foregoing has shown and described the basic features and principles of the present invention. The descriptions of orientation, such as "up," "down," "inner," and "outer," indicate the orientation or positional relationship shown in the accompanying drawings. These descriptions are merely for the purpose of describing the present invention. The above embodiments are only for illustrating the technical concept and features of the present invention. Their purpose is to enable those skilled in the art to understand the content of the present invention and implement it, and they are not intended to limit the scope of protection of the present invention.

Claims

1. A dual-channel hydraulic lifting pump, comprising a pump section, a turbine section, a bridge-type channel assembly, an upper connector (1), a housing (2), and a lower connector (36), characterized in that: The pump section mainly consists of a pump impeller (9), a guide wheel (8), radial bearings (7, 12), a thrust bearing assembly (13), a pump shaft (10), an upper pump housing connector (3), and a lower pump housing connector (14); the turbine section mainly consists of a stator (30), a rotor (31), a centralizing bearing (29, 32), a thrust bearing (34), a turbine shaft (27), a turbine housing (28), a spline connector (26), an upper turbine housing connector (25), and a lower turbine housing connector (35); the bridge-type channel assembly mainly consists of a bridge-type channel connector (16), an intermediate connecting shaft (15), and a sealing assembly; the pump section and the turbine section are connected as a combined unit through the bridge-type channel assembly, wherein the pump shaft (10) and the intermediate connecting shaft (15) are connected as a combined unit. The connecting shaft (15) is connected by a thread, the intermediate connecting shaft (15) is connected to the spline joint (26) by a spline, and then the spline joint (26) is connected to the turbine shaft (27) by a thread to form a whole. At the same time, the pump section is connected to the pump housing lower joint (14) and the bridge channel joint (16), and the turbine section is connected to the turbine housing upper joint (25) and the bridge channel joint (16). The assembly is aligned in the middle of the housing (2) by the straightening blocks (b, c) outside the pump housing (6) and the straightening blocks (d, e) outside the turbine housing (28), and sits on the lower joint (36) through the turbine housing lower joint (35). The upper joint (1) presses the pump housing upper joint (3) to achieve axial positioning of the assembly in the housing (2). The bridge-type channel joint (16) has a double-layer structure, consisting of a middle pipe and an outer shell. Five independent flow channels (α, β, γ, δ, ε) are evenly arranged around its circumference. Two of the flow channels (γ, ε) are used to transport power fluid to the lower turbine section, and the other three flow channels (α, β, δ) are used to transport the pump section's return fluid upwards. The inlet and outlet of the flow channels (γ, ε) for transporting power fluid and the flow channels (α, β, δ) for transporting return fluid are opposite and are arranged alternately around the circumference. The sealing assembly is mainly composed of a gap sealing sleeve (24), Chevron seals (21, 23), spacer ring (22), gland (18), O-ring (19), wear ring (20), and screw (17). The gap sealing sleeve (24) is threaded into the middle tube of the bridge-type channel joint (16), and the middle connecting shaft (15) passes through the center of the sealing assembly.

2. The dual-channel hydraulic lifting pump according to claim 1, characterized in that: The conical section of the turbine housing lower connector (35) sits on the conical surface of the lower connector (36), and the key of the lower connector (36) is engaged in the groove of the turbine housing lower connector (35).

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