Vortex mixed-pushing multiphase booster impeller and multiphase booster pump

Abstract

The vortex mixed pushing multiphase pressurizing impeller comprises an impeller body, a shaft hole is formed in the impeller body in the axis direction of the impeller body, and pressurizing blades are evenly distributed on the outer side face of the impeller body; a pressurizing blade on the impeller body forms an axial flow vortex pressurizing blade flow channel and a centrifugal vortex pressurizing blade flow channel from an inlet to an outlet, the axial flow vortex pressurizing blade flow channel is an outer-circle inner-cone gradually-shrinking flow channel, the outer edge of the pressurizing blade of the axial flow vortex pressurizing blade flow channel is cylindrical, and the outer edge of the centrifugal vortex pressurizing blade flow channel is cylindrical. The root of the section of pressurizing blade is in a cone shape formed by a plurality of sections of arcs in a tangent mode, the centrifugal vortex pressurizing blade flow channel is a centrifugal gradually-expanding flow channel, and the outer edge diameter and the root diameter of the pressurizing blade of the centrifugal vortex pressurizing blade flow channel are gradually increased in the direction from an inlet to an outlet. The vortex mixed pushing multiphase pressurizing impeller and the multiphase pressurizing pump have the advantages of being high in gas content of a conveying medium, low in maintenance cost and long in service life.

Description

Technical Field

[0001] The present invention belongs to the technical field of booster pumps, and particularly relates to a vortex mixed-push multiphase booster impeller and a multiphase booster pump. Background Art

[0002] Multiphase mixing and transportation technology is a key technology for onshore and deep-sea oil and gas exploitation engineering projects, and its key equipment is a multiphase booster pump. So far, the performance of multiphase booster pumps far from meets the actual needs of oilfield sites. On the one hand, due to the complexity of multiphase flow and the dependence of the pump on the flow pattern and gas holdup, the application range of current multiphase pumps is still restricted to a certain extent; on the other hand, the performance and efficiency of multiphase pumps under high inlet gas-liquid ratio conditions need to be improved. When the volume content of inlet gas reaches 50%, the best efficiency of a screw axial flow pump is only about 45%. Currently, domestic multiphase booster pumps have technical problems such as low gas holdup of the transported medium, unstable pressure during medium transportation, high maintenance costs, and short service life. Summary of the Invention

[0003] The purpose of the present invention is to provide a vortex mixed-push multiphase booster impeller and a multiphase booster pump to solve the above problems existing in the prior art.

[0004] To achieve the above purpose, the present invention adopts the following technical solutions: A vortex mixed-push multiphase booster impeller includes an impeller body. An axial hole is formed in the impeller body along its axis direction, and booster blades are evenly arranged on the outer side surface of the impeller body. The booster blades on the impeller body form an axial vortex booster blade flow channel and a centrifugal vortex booster blade flow channel from the inlet to the outlet. The shape of the axial vortex booster blade flow channel is a tapered flow channel with a circular outer and conical inner shape. The outer edge of the booster blade in the axial vortex booster blade flow channel is cylindrical, and the root of this section of the booster blade is a cone composed of multiple arcs tangent to each other. The shape of the centrifugal vortex booster blade flow channel is a centrifugal expanding flow channel. The outer diameter and root diameter of the booster blade in the centrifugal vortex booster blade flow channel gradually increase from the inlet to the outlet direction. The flow area of the flow passage between the blades of the booster impeller shows a trend of gradually decreasing and then gradually increasing. The flow area of the flow passage between the booster impellers at the intersection of the axial vortex booster blade flow channel and the centrifugal vortex booster blade flow channel is the smallest.

[0005] The working process and principle of the above structure are as follows: When the multiphase supercharging impeller conveys multiphase media with a high gas content, the media first flows through the axial-flow vortex supercharging blade flow passage part. Under the axial thrust of some supercharging blades in the axial-flow vortex supercharging blade flow passage, after the gas phase is compressed and heat-transfered, its volume shrinks. The reduction in the volume of the mixed media matches the gradually shrinking flow passage of the axial-flow vortex supercharging blade flow passage part, ensuring the filling and stability of the media in the flow passage. After the media flows out of the axial-flow vortex supercharging blade flow passage part, the pressure of the multiphase media increases significantly, ensuring that after the multiphase media enters the centrifugal flow passage of the centrifugal vortex supercharging blade flow passage, the generation of backflow in the turning flow passage of the centrifugal vortex supercharging blade flow passage section is effectively inhibited, ensuring the uniform and stable increase of the media pressure in the flow passage, and effectively improving the stability and reliability of the equipment for conveying multiphase media.

[0006] Further, the shaft hole includes a positioning section and a threaded section. A nut is provided at the smaller outer diameter end of the shaft hole close to the impeller body. The end of the shaft hole close to the nut is the threaded section, and the end of the shaft hole away from the nut is the positioning section.

[0007] Through the setting of the positioning section, it is convenient to quickly position and dock the shaft hole with the pump shaft, improving the assembly efficiency. The setting of the threaded section facilitates the threaded connection between the shaft hole and the pump shaft. The nut is used to screw the supercharging impeller during installation.

[0008] Further, the number of the supercharging blades does not exceed 10.

[0009] The limitation of the number of supercharging blades facilitates the compact setting of the structure of the supercharging impeller and reduces the volume of the multiphase supercharging pump.

[0010] A multiphase supercharging pump applying a vortex mixing and pushing multiphase supercharging impeller includes a pump body and a supercharging impeller arranged in the pump body. An outlet pipe is provided on the pump body. The front and rear ends of the pump body are respectively connected with a front pump cover and a rear pump cover. An internal guide wheel is arranged in the front pump cover. A bearing seat is coaxially connected to the rear pump cover. A pump shaft is rotatably arranged in the bearing seat. The pump shaft passes through the rear pump cover and is coaxially connected with the supercharging impeller. A gap is left between the supercharging impeller and the rear pump cover. A decompression hole is opened on the rear pump cover. One end of the decompression hole is communicated with the gap, and the other end is connected with a decompression pipe. The other end of the decompression pipe is connected to the front pump cover.

[0011] The working process and principle of the above structure are as follows: The pump shaft drives the booster impeller to rotate, creating a negative pressure at the inlet of the booster pump. The conveyed medium enters the guide vane flow passage of the built-in guide wheel in the front pump cover through the inlet of the booster pump. Under the guiding action of the guide vanes of the built-in guide wheel, the conveyed medium forms a pre-whirl flow; the medium with pre-whirl enters the booster impeller at an excellent attack angle. Under the dual effects of the convergent-divergent flow passage and vortex boosting in the booster impeller, the pressure of the medium in the impeller is effectively increased evenly and stably; a part of the medium at the outlet of the booster impeller flows through the gap between the rear pump cover and the booster impeller, and then flows back into the pump inlet of the front pump cover through the decompression hole of the rear pump cover and the decompression pipe, thereby effectively reducing the axial thrust of the booster impeller facing the pump inlet and improving the stability and service life of the equipment; the main booster medium flowing through the booster impeller is discharged from the booster pump after the guiding and secondary boosting effects of the pump body.

[0012] Further, a sealing sleeve is provided between the bearing seat and the rear pump cover. The sealing sleeve is sleeved on the pump shaft, and the sealing sleeve is connected to the bearing in the bearing seat and rotates with the bearing. The sealing sleeve is in sealing contact with the rear pump cover.

[0013] The setting of the sealing sleeve ensures the sealing between the bearing seat and the rear pump cover and ensures the pumping efficiency of the gas-liquid two-phase medium.

[0014] Further, a first sealing ring is provided at the connection between the front pump cover and the pump body. A guide sleeve matching the outer edge contour of the front part of the booster impeller is provided in the pump body. A second sealing ring is provided between the guide sleeve and the pump body. A third sealing ring is provided at the connection between the rear pump cover and the pump body.

[0015] The setting of the first sealing ring ensures the connection sealing between the front pump cover and the pump body. The setting of the guide sleeve facilitates ensuring an effective medium passage space when the booster impeller is working, ensuring its pumping pressure. The third sealing ring is used to ensure the connection sealing between the rear pump cover and the pump body.

[0016] Further, a first connection component is connected between the front pump cover and the pump body, a second connection component is connected between the rear pump cover and the pump body, a third connection component is connected between the bearing seat and the rear pump cover, and a set screw is connected between the guide sleeve and the pump body.

[0017] Beneficial effects: Through the design of the booster impeller structure, the present invention provides a new solution and technical support for the multi-phase booster pump to transport multi-phase flow with a high gas content rate, greatly expanding the application parameter range of the booster impeller during gas-containing transportation; significantly reducing the equipment failure losses caused by low system inlet pressure, extending the system maintenance cycle and service life, and reducing the equipment maintenance cost; effectively improving the stability and reliability of the equipment in transporting multi-phase media. This multi-phase booster pump impeller can transport multi-phase flow media with a gas content rate of up to 50% or higher. Description of the Drawings

[0018] Figure 1 Schematic three-dimensional structure diagram of the supercharging impeller according to the present invention; Figure 2 Front view of the overall structure of the supercharging impeller according to the present invention; Figure 3 Main sectional view of the supercharging impeller according to the present invention; Figure 4 Meridional plane projection structure diagram of the supercharging impeller flow path in the present invention; Figure 5 Meridional plane flow-through area diagram of the supercharging impeller flow path in the present invention; Figure 6 Meridional plane projection example diagram of the supercharging impeller flow path in the present invention; Figure 7 Meridional plane flow-through area example diagram of the supercharging impeller flow path in the present invention; Figure 8 Sectional structure diagram of the multiphase supercharging pump in the present invention; Figure 9 Schematic diagram of the structure of the inner guide wheel and the supercharging impeller in the front pump cover according to the present invention.

[0019] Reference numerals: 1. Front pump cover; 2. Supercharging impeller; 3. First sealing ring; 4. First connection assembly; 5. Set screw; 6. Second sealing ring; 7. Pump body; 8. Third sealing ring; 9. Rear pump cover; 10. Second connection assembly; 11. Sealing sleeve; 12. Pump shaft; 13. Bearing seat; 14. Third connection assembly; 15. Pressure reducing pipe; 16. Flow guiding sleeve; 17. Impeller body; 18. Supercharging blade; 19. Shaft hole; 20. Positioning section; 21. Thread section; 22. Nut; 23. Outlet pipe; 24. Inner guide wheel; 25. Pressure reducing hole; Axial-vortex supercharging blade flow path δ2; Centrifugal-vortex supercharging blade flow path δ3. Detailed implementation manners

[0020] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the present invention in combination with the accompanying drawings and the descriptions of the embodiments or the prior art. Obviously, the following descriptions of the structures of the accompanying drawings are only some embodiments of the present invention. For those of ordinary skill in the art, other accompanying drawings can be obtained based on these drawings without creative efforts. It should be noted here that the descriptions of these embodiments are used to help understand the present invention, but do not constitute a limitation to the present invention.

[0021] Embodiment: As Figure 1As shown in the figure, this embodiment provides a vortex mixed-push multiphase supercharging impeller, which includes an impeller body 17. An axial hole 19 is provided along the axis direction of the impeller body 17, and supercharging blades 18 are evenly arranged on the outer side surface of the impeller body 17. The supercharging blades 18 on the impeller body 17 form an axial vortex supercharging blade flow passage δ2 and a centrifugal vortex supercharging blade flow passage δ3 from the inlet to the outlet. The outer shape of the axial vortex supercharging blade flow passage δ2 is an outer-circle inner-conical gradually shrinking flow passage. The outer edge of the supercharging blade 18 in the axial vortex supercharging blade flow passage δ2 is cylindrical, and the root of this section of the supercharging blade 18 is a cone composed of multiple tangent arcs. The outer shape of the centrifugal vortex supercharging blade flow passage δ3 is a centrifugal gradually expanding flow passage. The outer edge diameter and root diameter of the supercharging blade 18 in the centrifugal vortex supercharging blade flow passage δ3 gradually increase from the inlet to the outlet direction. The flow passage area between the blades of the supercharging impeller 2 gradually decreases and then gradually increases. The flow passage area between the supercharging impellers 2 at the intersection of the axial vortex supercharging blade 18 flow passage and the centrifugal vortex supercharging blade 18 flow passage is the smallest.

[0022] Set the distance from the impeller inlet to the midpoint of the impeller outlet as δ1, that is, δ1 = δ2 + δ3. The length of the middle streamline of the meridian plane projection of the δ2 part of the flow passage is L2, and the length of the middle streamline of the meridian plane projection of the δ3 part of the flow passage is L3. The total length of the middle streamline of the meridian plane projection of the δ1 part of the flow passage L1 = L2 + L3. The dimensional relationship between the axial δ2 and δ1 of the multiphase supercharging impeller is: 0.4 ≤ δ2 / δ1 ≤ 0.8; the dimensional relationship of the length of the middle streamline of the meridian plane projection of the flow passage is: 0.3 ≤ L2 / L1 ≤ 0.7.

[0023] Specifically, the length of δ1 is 70 mm, the length of δ2 is 40 mm, and δ2 / δ1 = 0.57, which conforms to the above relationship.

[0024] The radius of the outer cylinder of the blade in the δ2 part of the multiphase supercharging impeller is Rα1, and the outlet radius of the blade in the δ3 part is Rα4. The relationship between them is: Rα4 / Rα1 > 1; the diameters of the first end and the last end of the root of the blade in the δ2 part are Rα2 and Rα3 respectively. The relationship between them is: Rα3 / Rα2 ≥ 1.1.

[0025] Specifically, Rα1 is 45 mm, Rα2 is 10 mm, Rα3 is 24 mm, and Rα4 is 75 mm. Rα4 / Rα1 = 1.66, and Rα3 / Rα2 = 2.4, which conforms to the above relationship.

[0026] Such as Figure 4 and Figure 6As shown, b is the outlet width, b = 16 mm, θ1 is the horizontal angle of the outer edge of the blade at the outlet, with a specific value of 82°, and θ2 is the horizontal angle of the root of the blade at the outlet, with a specific value of 93°; Ra is the bending radius of the outer edge of the δ3 part of the blade, with a specific value of 20 mm, Rb is the bending radius of the root of the δ3 part of the blade, with a specific value of 37 mm, Rc is the bending radius of the root of the δ2 part of the blade away from the inlet, with a specific value of 50 mm, and Rd is the bending radius of the root of the δ2 part of the blade close to the inlet, with a specific value of 225 mm; attached Figure 6 Among them, R45 means the radius here is 45 mm, R10 means the radius here is 10 mm, R225 means the radius here is 225 mm, R50 means the radius here is 50 mm, R24 means the radius here is 24 mm, R20 means the radius here is 20 mm, R37 means the radius here is 37 mm, and R75 means the radius here is 75 mm; As Figure 5 and Figure 7 shown, Sa, Sb, and Sc are three standard values of the flow cross-sectional area, which are 5000 mm², 6000 mm², and 7000 mm² respectively. L refers to the relative meridian length of the meridional plane projection of the flow channel, and LMAX refers to the maximum relative meridian length of the meridional plane projection of the flow channel.

[0027] The working process and principle of the above structure are as follows: When the multiphase booster impeller 2 conveys the multiphase medium with a high gas content, the medium first flows through the δ2 part of the axial-flow vortex booster blade flow channel. Under the axial thrust of some booster blades 18 in the δ2 part of the axial-flow vortex booster blade flow channel, its gas phase contracts in volume after compression and heat transfer. The reduction in the volume of the mixed medium matches the gradually shrinking flow channel of the δ2 part of the axial-flow vortex booster blade flow channel, ensuring the filling and stability of the medium in the flow channel. After the medium flows out of the δ2 part of the axial-flow vortex booster blade flow channel, the pressure of the multiphase medium increases significantly, ensuring that after the multiphase medium enters the centrifugal flow channel of the centrifugal vortex booster blade flow channel δ3, the generation of backflow in the turning flow channel of the δ3 section of the centrifugal vortex booster blade flow channel is effectively suppressed, ensuring the uniform and stable increase of the medium pressure in the flow channel, and effectively improving the stability and reliability of the equipment for conveying the multiphase medium.

[0028] In another embodiment of the present invention, as Figures 1-7 shown, the shaft hole 19 includes a positioning section 20 and a threaded section 21. A nut 22 is provided at the smaller outer diameter end of the shaft hole 19 close to the impeller body 17. The end of the shaft hole 19 close to the nut 22 is the threaded section 21, and the end of the shaft hole 19 away from the nut 22 is the positioning section 20.

[0029] Through the setting of the positioning section 20, it is convenient to quickly position and dock the shaft hole 19 with the pump shaft 12, improving the assembly efficiency and accuracy. The setting of the threaded section 21 facilitates the firm connection of the shaft hole 19 and the pump shaft 12 through threads. The nut 22 is used to screw and boost the impeller 2 during installation.

[0030] In another embodiment of the present invention, as Figures 1-7 shown, the number of boosting vanes 18 does not exceed 10.

[0031] The limitation of the number of boosting vanes 18 facilitates the compact setting of the boosting impeller 2 and reduces the volume of the multiphase boosting pump.

[0032] As Figure 8 and Figure 9 shown, a multiphase boosting pump applying a vortex mixing and pushing multiphase boosting impeller includes a pump body 7 and a boosting impeller 2 arranged in the pump body 7. An outlet pipe 23 is arranged on the pump body 7, and the outlet pipe 23 has a flared structure. The front and rear ends of the pump body 7 are respectively connected with a front pump cover 1 and a rear pump cover 9. An internal guide wheel 24 is arranged in the front pump cover 1. A bearing seat 13 is coaxially connected to the rear pump cover 9. A pump shaft 12 is rotatably arranged in the bearing seat 13. The pump shaft 12 passes through the rear pump cover 9 and is coaxially connected with the boosting impeller 2. A gap is left between the boosting impeller 2 and the rear pump cover 9. A decompression hole 25 is opened on one side of the rear pump cover 9 away from the outlet pipe 23. The decompression hole 25 is inclined. One end of the decompression hole 25 is communicated with the gap, and the other end is connected with a decompression pipe 15. The other end of the decompression pipe 15 is connected to the front pump cover 1.

[0033] The working process and principle of the above structure are as follows: The pump shaft 12 drives the boosting impeller 2 to rotate, forming a negative pressure at the inlet of the boosting pump. The conveying medium enters the guide vane flow passage of the internal guide wheel 24 in the front pump cover 1 through the inlet of the boosting pump. Under the guiding action of the guide vanes of the internal guide wheel 24, the conveying medium forms a pre-whirl flow; the medium with pre-whirl enters the boosting impeller 2 with an excellent attack angle. Under the dual effects of the convergent-divergent flow passage and vortex boosting in the boosting impeller 2, the pressure of the medium in the impeller is effectively increased evenly and stably; a part of the medium at the outlet of the boosting impeller 2 flows through the gap between the rear pump cover 9 and the boosting impeller 2, and then flows back into the pump inlet of the front pump cover 1 through the decompression hole of the rear pump cover 9 and the decompression pipe 15, thereby effectively reducing the axial thrust of the boosting impeller 2 facing the pump inlet and improving the stability and service life of the equipment; the main boosting medium flowing through the boosting impeller 2 is discharged from the boosting pump after the guiding and secondary boosting effects of the pump body 7.

[0034] In another embodiment of the present invention, as Figure 8 shown, a sealing sleeve 11 is arranged between the bearing seat 13 and the rear pump cover 9. The sealing sleeve 11 is sleeved on the pump shaft 12. The sealing sleeve 11 is connected to the bearing in the bearing seat 13 and rotates with the bearing. The sealing sleeve 11 is in sealing contact with the rear pump cover 9.

[0035] The setting of the sealing sleeve 11 ensures the sealing between the bearing housing 13 and the rear pump cover 9, and ensures the pumping efficiency of the gas-liquid two-phase medium.

[0036] In another embodiment of the present invention, as Figure 8 shown, a first sealing ring 3 is provided at the connection between the front pump cover 1 and the pump body 7. A guide sleeve 16 is provided inside the pump body 7, and the inner wall of the guide sleeve 16 matches the front outer edge contour of the booster impeller 2. The outer part of the guide sleeve 16 is in a cylindrical structure, the inner wall of the guide sleeve 16 is a curved surface, a second sealing ring 6 is provided between the guide sleeve 16 and the pump body 7, and a third sealing ring 8 is provided at the connection between the rear pump cover 9 and the pump body 7.

[0037] The setting of the first sealing ring 3 ensures the connection sealing between the front pump cover 1 and the pump body 7. The setting of the guide sleeve 16 facilitates ensuring an effective medium passage space when the booster impeller 2 is working, ensuring its pumping pressure. The third sealing ring 8 is used to ensure the connection sealing between the rear pump cover 9 and the pump body 7.

[0038] In another embodiment of the present invention, as Figure 8 shown, a first connection assembly 4 is connected between the front pump cover 1 and the pump body 7, a second connection assembly 10 is connected between the rear pump cover 9 and the pump body 7, a third connection assembly 14 is connected between the bearing housing 13 and the rear pump cover 9, and a set screw 5 is connected between the guide sleeve 16 and the pump body 7. The first connection assembly 4, the second connection assembly 10, and the third connection assembly 14 are all connecting bolts.

[0039] Finally, it should be noted that the above are only the preferred embodiments of the present invention and are not used to limit the protection scope of the present invention. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A vortex hybrid multiphase booster impeller, characterized in that: It comprises an impeller body (17), wherein the impeller body (17) is provided with an axial hole (19) along the axial direction thereof, and booster blades (18) are evenly distributed on the outer side surface of the impeller body (17); The booster blades (18) on the impeller body (17) form an axial vortex booster blade flow channel (δ2) and a centrifugal vortex booster blade flow channel (δ3) from the inlet to the outlet. The outer shape of the axial vortex booster blade flow channel (δ2) is an outer circular inner conical tapered flow channel. The outer edge of the booster blade (18) of the axial vortex booster blade flow channel (δ2) is cylindrical. The root of the booster blade (18) is a cone formed by multiple tangent arcs. The centrifugal vortex booster blade flow channel (δ2) is a cone formed by multiple tangent arcs. The appearance of the vortex booster blade flow channel (δ3) is a centrifugal gradually expanding flow channel. The outer edge diameter and the root diameter of the booster blade (18) of the centrifugal vortex booster blade flow channel (δ3) gradually increase from the inlet to the outlet. The flow channel area between the blades of the booster impeller gradually decreases and then gradually increases. The flow channel area between the booster impellers at the intersection of the axial vortex booster blade flow channel (δ2) and the centrifugal vortex booster blade flow channel (δ3) is the smallest.

2. The vortex hybrid multiphase booster impeller according to claim 1, characterized in that: The shaft hole (19) comprises a positioning section (20) and a threaded section (21); a nut (22) is provided at an end of the shaft hole (19) with a smaller outer diameter close to the impeller body (17); an end of the shaft hole (19) close to the nut (22) is the threaded section (21); and an end of the shaft hole (19) away from the nut (22) is the positioning section (20).

3. The vortex hybrid multi-phase boost impeller according to claim 1, characterized in that: The number of the booster blades (18) does not exceed 10.

4. A multiphase booster pump using the vortex hybrid multiphase booster impeller as claimed in claim 1, characterized in that: The invention comprises a pump body (7) and a booster impeller (2) arranged in the pump body (7), wherein the pump body (7) is provided with an outlet pipe (23), the front and rear ends of the pump body (7) are respectively connected to a front pump cover (1) and a rear pump cover (9), the front pump cover (1) is provided with a built-in guide wheel (24), the rear pump cover (9) is coaxially connected to a bearing seat (13), a pump shaft (12) is rotatably arranged in the bearing seat (13), the pump shaft (12) passes through the rear pump cover (9) and is coaxially connected to the booster impeller, a gap is left between the booster impeller and the rear pump cover (9), a pressure reducing hole (25) is opened on the rear pump cover (9), one end of the pressure reducing hole (25) is connected to the gap, and the other end is connected to a pressure reducing pipe (15), and the other end of the pressure reducing pipe (15) is connected to the front pump cover (1).

5. The multiphase booster pump using a vortex hybrid multiphase booster impeller according to claim 4, characterized in that: A sealing sleeve (11) is provided between the bearing seat (13) and the rear pump cover (9); the sealing sleeve (11) is sleeved on the pump shaft (12); the sealing sleeve (11) is connected to the bearing in the bearing seat (13) and rotates with the bearing; the sealing sleeve (11) is in sealing contact with the rear pump cover (9).

6. The multiphase booster pump using a vortex hybrid multiphase booster impeller according to claim 4, characterized in that: A first sealing ring (3) is provided at the connection between the front pump cover (1) and the pump body (7); a guide sleeve (16) matching the outer edge profile of the front part of the booster impeller is provided in the pump body (7); a second sealing ring (6) is provided between the guide sleeve (16) and the pump body (7); and a third sealing ring (8) is provided at the connection between the rear pump cover (9) and the pump body (7).

7. The multiphase booster pump using a vortex hybrid multiphase booster impeller according to claim 4, characterized in that: A first connecting assembly (4) is connected between the front pump cover (1) and the pump body (7), a second connecting assembly (10) is connected between the rear pump cover (9) and the pump body (7), a third connecting assembly (14) is connected between the bearing seat (13) and the rear pump cover (9), and a set screw (5) is connected between the guide sleeve (16) and the pump body (7).

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