Multi-component cooperative optimization composite gas-liquid centrifugal pump

Abstract

The present application relates to the field of fluid machinery design, specifically relates to a kind of multi-component collaborative optimization's composite gas-liquid centrifugal pump;Including impeller, flow guide component and volute;The impeller includes cover plate and is arranged on the hub of cover plate, hub is installed with blade, blade is divided into front impeller section and rear impeller section along radial direction, wherein segmented gap is formed between front impeller section and rear impeller section, the cover plate is symmetrically provided with a plurality of backflow holes, wherein impeller is provided with impeller inlet and impeller outlet;The cover plate is provided with spoiler structure away from the side of blade;In the design optimization of centrifugal pump, the composite structure of multi-component coupling can effectively improve its gas-liquid mixed transport performance;Using segmented blade, the synergistic effect of flow guiding of segmented gap and backflow hole circulation can form three-dimensional rotational cutting flow field in the impeller, can efficiently break up stagnant gas mass, effectively suppresses gas phase aggregation, creates good conditions for gas-liquid mixed transport.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of fluid machinery design, in particular to a multi-component collaborative optimization composite gas-liquid centrifugal pump. BACKGROUND

[0002] Unlike the single medium delivery of centrifugal pumps, when the centrifugal pump is used to deliver gas-liquid two-phase incompatible fluid, due to the order difference between the gas phase and the liquid phase, gas-liquid separation phenomenon will occur under the action of centrifugal force, which will make the gas phase migrate to the low pressure core area to form a gas phase aggregation area, and the liquid phase will be squeezed to the blade working surface area. This separation phenomenon will cause the following problems: (1) the retention of gas bubbles occupies the flow passage space, reduces the effective cross-sectional area of the flow passage, causes the relative velocity of the liquid phase to increase sharply, induces the increase of turbulent kinetic energy dissipation, and reduces the hydraulic efficiency; (2) the periodic generation or collapse of gas clusters produces pressure pulsation, induces axial force fluctuation, aggravates rotor system vibration, and even causes flow passage blockage or operation instability in severe cases; (3) the compressibility of gas makes the flow of fluid in the impeller more complex, and with the increase of gas content, the flow instability caused by gas-liquid interaction is significantly amplified, further reducing the head and efficiency of the pump, and threatening the safe operation of the pump and system.

[0003] In order to improve the gas-liquid delivery performance of the centrifugal pump, the commonly used methods at present include: (1) gas phase pretreatment: a gas-liquid separation device is arranged in front of the centrifugal pump, and through centrifugal separation, filtration or cyclone separation, etc., the gas and liquid are separated in advance, and the gas phase ratio entering the pump body is reduced; (2) impeller structure optimization: adopting double suction impeller design or special blade type design, so that the gas bubbles are uniformly distributed and accelerated to escape; (3) active exhaust control: installing an automatic exhaust valve system, setting a pressure sensitive exhaust valve at the top of the pump cavity, when the gas aggregation amount detected exceeds a certain value, the automatic exhaust valve is opened, and the retention of gas bubbles is discharged outside the pump.

[0004] However, the pretreatment method is difficult to adapt to the rapid fluctuation of gas content; the double suction impeller design scheme has high sensitivity to non-design conditions, and lacks adaptability to complex conditions; the active exhaust system has response lag and sealing reliability problems. SUMMARY

[0005] In view of the problems mentioned in the prior art, the present application proposes a multi-component collaborative optimization composite gas-liquid centrifugal pump, by constructing a multi-component coupled composite structure of impeller-vane-volute, realizing dynamic breaking of gas clusters, pressure pulsation suppression and axial force self-balancing, weakening the aggregation phenomenon of gas bubbles in the impeller flow passage, reducing the high gas content area in the flow passage, improving the gas-liquid two-phase distribution in the flow passage, and further improving the pressure boosting capacity and delivery performance of the centrifugal pump under high gas content.

[0006] In order to achieve the above purpose, the present application adopts the following technical scheme:

[0007] The present invention proposes a multi-component collaboratively optimized compound gas-liquid centrifugal pump, comprising an impeller, a flow guide assembly and a volute;

[0008] The impeller includes a cover plate and a hub disposed on the cover plate, blades are mounted on the hub, and the blades are radially divided into a front impeller section and a rear impeller section, a segmented gap is formed between the front impeller section and the rear impeller section, a plurality of return holes are symmetrically provided on the cover plate, and the impeller is provided with an impeller inlet and an impeller outlet; a turbulence structure is provided on a side of the cover plate away from the blades;

[0009] The flow guide assembly includes a guide vane arranged in a transition area, and the transition area is arranged between the impeller outlet and the inlet of the volute; wherein the inlet width of the volute is greater than the impeller outlet width.

[0010] As a further improvement of the present invention, the diameter of the center of the segmented gap is determined by the impeller inlet diameter and the impeller outlet diameter, satisfying:

[0011]

[0012] Where: is the impeller inlet diameter, unit: mm; is the impeller outlet diameter, unit: mm; is the diameter of the center of the segment gap;

[0013] The width of the segment gap is 1% to 5% of the hub diameter.

[0014] As a further improvement of the present invention, the number of the reflow holes is equal to the number of the blades;

[0015] Methods for determining the location of the return hole include:

[0016] Construct a positioning circle with the center of the segment gap as the center and the length of the segment gap as the radius;

[0017] The center of the reflow hole is arranged on the positioning circumference, and the distances between the center of the reflow hole, the center of the segmented gap and the blades are equal.

[0018] As a further improvement of the present invention, the radial cross-sectional diameter of the reflow hole is 1% to 3% of the hub diameter.

[0019] As a further improvement of the present invention, the flow-disturbing structure includes a plurality of flow-disturbing blades extending from the outer edge of the impeller circumference toward the center of the impeller, wherein the flow-disturbing blades are arranged at intervals along the circumferential direction.

[0020] As a further improvement of the present invention, the width of the spoiler blade is 3% to 6% of the impeller outlet diameter;

[0021] The thickness of the turbulent blade is 1% to 3% of the impeller outlet diameter;

[0022] The ratio of the number of the spoiler blades to the number of blades is 0.5-1.

[0023] As a further improvement of the present invention, the guide vanes are arranged to be deflected in a clockwise direction along the transition region, and adjacent guide vanes are arranged at equal intervals;

[0024] Among them, the guide vanes are wedge-shaped structures, and the ratio of the number of guide vanes to the number of blades is 1.8 to 2.2.

[0025] As a further improvement of the present invention, the ratio of the height of the guide vane to the impeller outlet diameter is 1 to 1.2;

[0026] The circumferential deflection angle of the guide vane is between 5° and 15°;

[0027] The minimum spacing between adjacent guide vanes is 10% to 20% of the base diameter of the volute.

[0028] As a further improvement of the present invention, the volute is designed with a gradually diverging flow channel, and the ratio of the volute inlet width to the impeller outlet width is 1.1 to 1.4.

[0029] As a further improvement of the present invention, the impeller is a semi-open impeller.

[0030] Compared with the prior art, the present invention has achieved the following technical effects:

[0031] In the design optimization of the centrifugal pump, the present invention can effectively improve the gas-liquid mixed transportation performance of the centrifugal pump through a composite structure coupled with multiple components; by adopting segmented blades and utilizing the synergistic effect of the flow guidance of the segmented gaps and the circulation of the return holes, a three-dimensional rotary shear flow field can be formed inside the impeller. This flow field can efficiently break up retained air masses, effectively inhibit gas phase aggregation, and create good conditions for gas-liquid mixed transportation.

[0032] The present invention helps to reduce the low-pressure area on the suction surface of the impeller by providing a return hole on the cover plate, thereby reducing the occurrence of cavitation from the root. At the same time, it can also realize automatic compensation of the pressure difference before and after the cover plate, greatly reduce the axial force imbalance, alleviate the force burden of the impeller during operation, and thus significantly extend the service life of the impeller.

[0033] The guide vanes of the present invention adopt a deflection design to make the outlet flow field distribution more uniform, greatly improving the operating stability of the centrifugal pump. Combined with the control of the volute inlet width, it effectively reduces the energy loss of the fluid in the volute and improves the energy conversion efficiency of the centrifugal pump. In addition, the design of the spoiler blades greatly enhances the turbulence intensity, further suppresses gas aggregation, and comprehensively improves the gas-liquid two-phase flow characteristics inside the impeller, so that the centrifugal pump can still maintain excellent conveying capacity and efficient operation under high gas content conditions, meeting the use requirements under complex working conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] Figure 1 Schematic diagram of the impeller structure model of this embodiment;

[0035] Figure 2 This is a cross-sectional view of the 1 / 2 impeller of the overall structure of this embodiment;

[0036] Figure 3 This is an enlarged schematic diagram of 1 / 4 of the impeller of the overall structure of this embodiment;

[0037] Figure 4 Schematic diagram of the spoiler blades of this embodiment;

[0038] Figure 5 Schematic diagram of the overall structural model of this embodiment.

[0039] Figure numerals: 1, impeller; 2, blade; 3, return hole; 4, segmented gap; 5, spoiler blade; 6, guide vane; 7, volute. DETAILED DESCRIPTION

[0040] Hereinafter, only certain exemplary embodiments are briefly described. As will be appreciated by those skilled in the art, the described embodiments may be modified in various ways without departing from the spirit or scope of the present invention. Therefore, the drawings and description are to be considered as illustrative in nature and not restrictive.

[0041] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0042] Furthermore, 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 the technical features being referred to. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, "plurality" means two or more, unless otherwise specifically defined.

[0043] In the present invention, unless otherwise expressly specified or limited, terms such as "mounted," "connected," "connect," and "fixed" should be understood broadly. For example, they may refer to fixed connection, detachable connection, or integration; mechanical connection, electrical connection, or communication; direct connection or indirect connection through an intermediate medium; and internal communication between two components or interaction between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0044] In the present invention, unless otherwise expressly specified or limited, a first feature being "above" or "below" a second feature may include the first and second features being in direct contact, or may include the first and second features being in contact not directly but through another feature between them. Furthermore, a first feature being "above," "above," and "above" a second feature may include the first feature being directly above or obliquely above the second feature, or may simply mean that the first feature is higher in level than the second feature. A first feature being "below," "below," and "below" a second feature may include the first feature being directly above or obliquely above the second feature, or may simply mean that the first feature is lower in level than the second feature.

[0045] It will be understood that when used in this specification and the appended claims, the terms “comprises” and “comprising” indicate the presence of described features, integers, steps, operations, elements and / or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components and / or groups thereof.

[0046] It should also be understood that the terms used in the present specification are only for the purpose of describing particular embodiments and are not intended to limit the present invention. As used in the present specification and the appended claims, the singular forms "a", "an", and "the" are intended to include the plural forms unless the context clearly indicates otherwise.

[0047] It should be further understood that the term "and / or" used in the present description and the appended claims refers to and includes any and all possible combinations of one or more of the associated listed items.

[0048] The accompanying drawings illustrate various schematic diagrams of structures according to embodiments disclosed herein. These figures are not drawn to scale; for clarity, some details are exaggerated and some details may be omitted. The shapes of the various regions and layers shown in the figures, as well as their relative sizes and positional relationships, are merely exemplary and may deviate in practice due to manufacturing tolerances or technical limitations. Those skilled in the art may design regions / layers with different shapes, sizes, and relative positions as needed.

[0049] The present invention proposes a multi-component collaboratively optimized compound gas-liquid centrifugal pump, comprising an impeller 1, a flow guide assembly and a volute 7;

[0050] The impeller 1 includes a cover plate and a hub disposed on the cover plate, on which blades 2 are mounted. The blades 2 are radially divided into a front impeller section and a rear impeller section, with a segmented gap 4 formed between the front impeller section and the rear impeller section. A plurality of reflow holes 3 are symmetrically provided on the cover plate. The impeller 1 is provided with an impeller inlet and an impeller outlet. A side of the cover plate away from the blades 2 is provided with a flow-turbulating structure.

[0051] The flow guide assembly includes a guide vane 6 provided in a transition area, wherein the transition area is provided between the impeller outlet and the inlet of the volute 7; wherein the inlet width of the volute 7 is greater than the impeller outlet width.

[0052] The embodiments of the present invention are described in detail below with reference to the accompanying drawings.

[0053] When improving and optimizing a centrifugal pump, the present invention first needs to obtain the basic parameters and operating requirements of the centrifugal pump. The basic parameters include the impeller inlet diameter, impeller outlet diameter, impeller width, hub diameter, number of impeller blades, base circle diameter of the volute, and other parameters. Based on these parameters, the structure of the centrifugal pump is improved.

[0054] See also Figure 1 The impeller 1 of this embodiment preferably adopts a semi-open impeller, wherein a cover plate is provided on one side of the semi-open impeller and blades 2 are provided on the other side. The blades 2 are mounted on the hub, wherein an axial flow channel can be formed between the multiple blades 2 and the cover plate. The axial flow channel of this embodiment can enable the fluid to migrate from the pressure surface of the blade 2 to the negative pressure surface, and bring out the air mass retained in the impeller 1, thereby reducing the occurrence of gas retention inside the impeller 1.

[0055] The blades 2 of this embodiment preferably adopt binary cylindrical blades, and the blades 2 are segmented into a front impeller segment and a rear impeller segment, and a segmented gap 4 is formed between the front impeller segment and the rear impeller segment; the position of the segmented gap 4 can be adjusted according to the specific structural parameters of the centrifugal pump and the ratio and flow characteristics of the gas-liquid mixture. The segmented gap 4 of this embodiment can optimize the flow path of the fluid to reduce the possibility of gas accumulation, thereby achieving the best conveying effect.

[0056] In this embodiment, the center position of the segmented gap 4 is determined based on the impeller inlet diameter and the impeller outlet diameter. The diameter range of the center of the segmented gap 4 is:

[0057]

[0058] Where: is the impeller inlet diameter, unit: mm; is the impeller outlet diameter, unit: mm; is the diameter of the center of the segment gap.

[0059] In the embodiment, the width of the segment gap 4 is set to 1% to 5% of the hub diameter in order to ensure efficiency and safety.

[0060] In this embodiment, the same number of reflow holes 3 as the number of blades 2 are arranged on the cover plate. In the embodiment, the reflow holes 3 are hollow cylinders of equal diameter. By utilizing the pressure difference between the pump chamber and the axial flow channel, the fluid can flow through the reflow holes 3 at a higher speed, increase the local turbulence intensity in the axial flow channel, and use the jet effect to break up the local air mass into bubbles that are easier to transport, thereby improving the performance and operating stability of the centrifugal pump.

[0061] The return hole 3 of the embodiment is arranged in front of the segmented gap 4 and close to the suction side of the front impeller section. The method for determining the center of the return hole 3 is: a positioning circle is constructed with the center of the segmented gap as the center and the length of the segmented gap as the radius. The center of the return hole 3 is located on the circle and meets the distance constraint condition, that is, it is ensured that the distances between the center of the return hole 3, the center of the segmented gap 4, and the blade 2 remain equal, thereby ensuring that the flow characteristics of the fluid when passing through the return hole 3 are optimized.

[0062] In the embodiment, the radial cross-sectional diameter of the return hole 3 is 1% to 3% of the hub diameter. The position and size of the return hole 3 can be optimized according to actual working conditions, fluid properties and system performance requirements. For centrifugal pumps with poor gas-liquid transportation performance, a radial cross-sectional diameter of 3% of the hub diameter is preferably selected to improve the working efficiency and stability of the centrifugal pump.

[0063] See also Figure 4 The back of the cover plate of the present invention is provided with a plurality of spoiler blades 5 evenly distributed in a circumferential array, and the spoiler blades 5 extend from the outer edge of the impeller circumference toward the center of the impeller; in the optimized design of the spoiler blades 5 of this embodiment, the following are satisfied:

[0064] The width of the spoiler blade 5 ranges from 3% to 6% of the impeller outlet diameter.

[0065] The thickness of the spoiler blade 5 is in the range of 1% to 3% of the impeller outlet diameter.

[0066] The number of the spoiler blades 5 is 0.3 to 1 times the number of the blades 2.

[0067] The thickness of the spoiler blades 5 is selected based on the fluid properties, the actual operating conditions of the pump, and the structural parameters of the pump. For example, high-viscosity fluids require wider spoiler blades 5 to provide sufficient disturbance, while low-viscosity fluids may require thinner spoiler blades 5 to reduce energy loss.

[0068] See also Figure 5 The guide vane 6 of this embodiment is a wedge-shaped structure, and the guide vane 6 is deflected in the clockwise direction and is arranged in the transition area between the impeller outlet and the volute inlet. The spacing between adjacent guide vanes 6 is the same to achieve uniform distribution of radial velocity and airflow angle at the guide vane outlet, thereby reducing the risk of flow separation.

[0069] The guide vane 6 of this embodiment satisfies the following requirements during the optimized design:

[0070] The ratio of the number of guide vanes 6 to the number of blades 2 is 1.8 to 2.2 to enhance the air mass breaking capability.

[0071] The ratio of the height of the guide vane 6 to the impeller outlet diameter is usually 1 to 1.2.

[0072] To avoid flow blockage and ensure that the fluid can flow smoothly out of the impeller and into the guide vane 6, during design, it is ensured that the guide vane 6 should match the shape and size of the impeller outlet. Therefore, the guide vane inlet is aligned with the axial flow channel outlet, and the circumferential deflection angle of the guide vane 6 ranges from 5° to 15°.

[0073] The minimum spacing between adjacent guide vanes 6 is 10% to 20% of the base diameter of the volute to ensure sufficient flow area, while avoiding backflow of fluid between the guide vanes due to excessive spacing, preventing the bubble retention area in the impeller 1 from extending to the volute 7, and improving the head performance of the centrifugal pump under low flow conditions.

[0074] The volute 7 of this embodiment is designed with a gradually expanding flow channel, which can ensure the smooth continuity of the internal flow channel of the centrifugal pump. The ratio of the inlet width of the volute 7 to the width of the impeller outlet is 1.1 to 1.4, which can increase the speed of the fluid entering the volute 7 and improve the aggregation of bubbles.

[0075] This embodiment provides a specific implementation process of a multi-component collaboratively optimized compound gas-liquid centrifugal pump. The design flow rate of the centrifugal pump in this embodiment is Q = 16m 3 / h, design head H = 20m, rated speed n = 1450r / min, specific speed n s =37.

[0076] Step 1: According to the design conditions and operating conditions of the centrifugal pump, the basic structural parameters of the centrifugal pump are obtained as follows: the impeller inlet diameter D1 is 76mm, the impeller outlet diameter The impeller outlet width is 247mm is 11mm, the number of impeller blades Z is 12, and the hub diameter The base diameter of the volute is 20mm. It is 287mm.

[0077] Step 2: Design the blade 2 in sections. Due to the diameter of the inlet center of the section gap 4 The value range is , see Figure 2 , substituting into The value range is 133mm 190mm, then take It is 170mm, and the length of segment gap 4 is 5% of the hub diameter. Substituting it into the length of segment gap 4 is 4mm.

[0078] Step 3: Arrange multiple reflow holes 3 on the cover plate to increase the local turbulence intensity in the axial flow channel, so as to improve the flow field distribution and the flow trajectory of the air mass; in this embodiment, the number of reflow holes 3 is the same as the number of blades 2, both 12, and the reflow holes 3 are arranged in front of the segmented gap 4 and close to the suction side of the front impeller section.

[0079] See also Figure 2 According to the method for determining the center of the reflux hole 3, determine the diameter of the center of the reflux hole 3 The relative position of the reflux hole 3 and the segment gap 4 is 152 mm. Figure 3 The radial cross-sectional diameter of the return hole 3 is 5% of the impeller inlet diameter, which is 4 mm.

[0080] Step 4: See Figure 4 On the back of the cover plate, a spoiler blade 5 is arranged, which extends from the outer edge of the impeller circumference toward the center of the impeller. The width of the spoiler blade 5 is 3% of the impeller outlet diameter, which is 8 mm. The thickness of the spoiler blade 5 is 1% of the impeller outlet diameter, which is 3 mm. The number of spoiler blades 5 is equal to the number of blades 2, both 12, and multiple spoiler blades 5 are evenly distributed, which can further increase the symmetry of the flow.

[0081] Step 5: See Figure 5 In the transition region between the impeller outlet and the volute inlet, multiple guide vanes 6 are evenly arranged at equal intervals in the clockwise direction. The number of guide vanes 6 is 1.8 times the number of blades 2, which is 22. The height of the guide vanes 6 needs to match the width of the impeller outlet to avoid flow blockage. Therefore, h / b2 is taken as 1.1, and the height of the guide vanes 6 is 12 mm. In this embodiment, the circumferential deflection angle γ of the guide vanes 6 is 10°. The minimum spacing between adjacent guide vanes is 10-20% of the base circle diameter of the volute. In this embodiment, 10% is taken as the minimum spacing, which is 30 mm.

[0082] Step six, the ratio of the inlet width b3 and the outlet width b2 of the volute of the embodiment b3 / b2=1.4, substituting b3=15mm, by increasing the inlet width of the volute to increase the speed of fluid into the volute, improve the aggregation of bubbles.

[0083] The above shows and describes the basic principles and main features of the present application and the advantages of the present application, for those skilled in the art, it is obvious that the present application is not limited to the details of the above exemplary embodiments, and the present application can be realized in other specific forms without departing from the spirit or essential characteristics of the present application. Therefore, in any respect, the embodiments should be regarded as exemplary and non-limiting, the scope of the present application is defined by the appended claims rather than the above description, therefore all changes falling within the meaning and scope of the equivalent elements of the claims are intended to be included in the present application. Any reference signs in the claims should not be regarded as limiting the claims involved.

[0084] In addition, it should be understood that although the present specification is described in terms of embodiments, not every embodiment contains only one independent technical solution, and the description of the specification is only for the sake of clarity, those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be combined appropriately to form other embodiments that those skilled in the art can understand. The above is only to illustrate the technical idea of the present application, and cannot limit the protection scope of the present application. Any modification made on the basis of the technical solutions of the present application falls within the protection scope of the claims of the present application.

Claims

1. A multi-component collaboratively optimized compound gas-liquid centrifugal pump, characterized in that: It includes an impeller (1), a flow guide assembly, and a volute (7); The impeller (1) comprises a cover plate and a hub disposed on the cover plate, blades (2) are mounted on the hub, the blades (2) are radially divided into a front impeller section and a rear impeller section, a segmented gap (4) is formed between the front impeller section and the rear impeller section, a plurality of reflow holes (3) are symmetrically disposed on the cover plate, and the impeller (1) is provided with an impeller inlet and an impeller outlet; a side of the cover plate away from the blades (2) is provided with a flow turbulence structure; the number of the reflow holes (3) is equal to the number of the blades (2); Methods for determining the position of the reflux hole (3) include: Constructing a positioning circle with the center of the segment gap (4) as the center and the length of the segment gap (4) as the radius; The center of the reflow hole (3) is located on the positioning circle, and the distances between the center of the reflow hole (3), the center of the segmented gap (4), and the blade (2) are equal; The flow guide assembly comprises a guide vane (6) provided in a transition area, wherein the transition area is provided between the outlet of the impeller (1) and the inlet of the volute (7); wherein the inlet width of the volute (7) is greater than the outlet width of the impeller.

2. A multi-component collaboratively optimized compound gas-liquid centrifugal pump according to claim 1, characterized in that: The diameter of the center of the segmented gap (4) is determined by the impeller inlet diameter and the impeller outlet diameter, and satisfies: Where: is the impeller inlet diameter, unit: mm; is the impeller outlet diameter, unit: mm; is the diameter of the center of the segment gap; The width of the segment gap (4) is 1% to 5% of the hub diameter.

3. The multi-component collaboratively optimized compound gas-liquid centrifugal pump according to claim 1, characterized in that: The radial cross-sectional diameter of the reflow hole (3) is 1% to 3% of the hub diameter.

4. The multi-component collaboratively optimized compound gas-liquid centrifugal pump according to claim 1, characterized in that: The flow-disturbing structure comprises a plurality of flow-disturbing blades (5) extending from the outer edge of the impeller circumference toward the center of the impeller, wherein the flow-disturbing blades (5) are arranged at intervals along the circumferential direction.

5. The multi-component collaboratively optimized compound gas-liquid centrifugal pump according to claim 4, characterized in that: The width of the flow-disturbing blade (5) is 3% to 6% of the impeller outlet diameter; The thickness of the flow-disturbing blade (5) is 1% to 3% of the impeller outlet diameter; The ratio of the number of the spoiler blades (5) to the number of the blades (2) is 0.5 to 1.

6. The multi-component collaboratively optimized compound gas-liquid centrifugal pump according to claim 1, characterized in that: The guide vanes (6) are arranged in a clockwise deflection along the transition region, and adjacent guide vanes (6) are arranged at equal intervals; The guide vanes (6) are wedge-shaped structures, and the ratio of the number of the guide vanes (6) to the number of the blades (2) is 1.8 to 2.

2.

7. A multi-component collaboratively optimized compound gas-liquid centrifugal pump according to claim 6, characterized in that: The ratio of the height of the guide vane (6) to the impeller outlet diameter is 1 to 1.2; The circumferential deflection angle of the guide vane (6) is between 5° and 15°; The minimum spacing between adjacent guide vanes (6) is 10% to 20% of the base circle diameter of the volute (7).

8. The multi-component collaboratively optimized compound gas-liquid centrifugal pump according to claim 1, characterized in that: The volute (7) is designed as a gradually expanding flow channel, and the ratio of the inlet width of the volute (7) to the width of the impeller outlet is 1.1 to 1.

4.

9. The multi-component collaboratively optimized compound gas-liquid centrifugal pump according to claim 1, characterized in that: The impeller (1) is a semi-open impeller.

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