Skirted blade for multiphase pump

Abstract

The utility model discloses a blade with a skirt edge for a multiphase pump, which comprises an impeller blade body and a skirt edge structure arranged on the back surface of the working surface of the impeller blade body, the skirt edge structure is a bulge arranged on the back surface of the working surface of the impeller blade body, and the skirt edge structure is distributed along the radian of the impeller blade body. The side, away from the multiphase pump impeller, of the skirt edge structure is aligned with the edge of the corresponding impeller blade body. According to the utility model, the skirt structure is additionally arranged on the back surface of the working surface of the blade, so that the leakage flow at the gap is effectively reduced, an inflow medium does not generate an obvious liquid gathering phenomenon, the speed distribution and the gas distribution are more uniform, the gas transmission capacity of the multiphase pump is improved, and the operation efficiency and the operation stability of the pump are improved.

Description

Technical Field

[0001] The utility model belongs to the technical field of fluid mechanical equipment and relates to a blade with a skirt used for a mixed delivery pump. Background Art

[0002] Gas-liquid mixed transportation is the core technology of oil and natural gas extraction and transportation. The vane-type mixed pump has the advantages of compact structure, wide operating conditions, and wear resistance. The vane-type mixed pump is usually composed of multiple compression stages, each of which contains an impeller and a guide vane segment. The impeller converts mechanical energy into kinetic energy of the working fluid through high-speed rotation, and the guide vane segment converts the kinetic energy of the working fluid into pressure energy to achieve pressurization.

[0003] As the core component of the vane-type gas-liquid mixed pump, the impeller has a vital impact on the mixed performance and stable operation of the pump. The ordinary blade structure used on the impeller generally has defects such as uneven gas-liquid mixing and unstable flow conditions, which have a certain impact on the pump performance, such as reducing the head and efficiency, generating noise and vibration, and reducing the stability of equipment operation. Therefore, it is necessary to optimize the design of the impeller blades to improve the pump performance. Utility Model Content

[0004] The purpose of the utility model is to provide a blade with a skirt for a mixed flow pump. By adding a skirt structure on the back of the working surface of the blade, the leakage flow at the gap is effectively reduced, so that the inflow medium does not produce obvious liquid aggregation phenomenon, the velocity distribution and the gas distribution are more uniform, the gas delivery capacity of the mixed flow pump is improved, and the efficiency and stability of the pump operation are increased.

[0005] The technical solution adopted by the utility model is that a blade with a skirt for a mixed flow pump includes an impeller blade body and a skirt structure arranged on the back side of the working surface of the impeller blade body. The skirt structure is a protrusion arranged on the back side of the working surface of the impeller blade body. The skirt structure is distributed along the curvature of the impeller blade body, and the side of the skirt structure away from the mixed flow pump impeller is aligned with the edge of the corresponding impeller blade body.

[0006] The utility model is also characterized in that:

[0007] The skirt structure is distributed in an arc shape along the curvature of the impeller blade body, and the length of the skirt structure is consistent with the length of the impeller blade body.

[0008] The thickness d2 of the skirt structure is 60% of the thickness d1 of the impeller blade body.

[0009] The cross section of the skirt structure is a rectangular structure, the width of the rectangle is d2, the length of the rectangle is d3, and the calculation formulas of d2 and d3 are shown as follows:

[0010] d3=3d2 (1)

[0011] Both ends of the skirt structure are welded to the two ends of the working surface of the impeller blade body.

[0012] The distance from the center of the skirt structure to the center of the hybrid pump impeller is 1.2 times the diameter of the hybrid pump impeller.

[0013] The inner circle radius r2 of the skirt structure is 1.1 times the radius r of the hybrid pump impeller.

[0014] The total length of the skirt structure is 0.25 times the diameter of the hybrid pump impeller.

[0015] The length d3 of the rectangle in the cross-section of the skirt structure is 0.48 times the length L of the cross-section of the impeller blade body.

[0016] The beneficial effects of the present utility model are as follows:

[0017] By adding a skirt structure at the end of the back of the blade working surface, the present utility model effectively reduces the leakage flow at the gap, so that there is no obvious liquid accumulation phenomenon in the inflow medium, the overall density of the mixed fluid changes little, the velocity distribution and gas distribution are more uniform, the gas transportation capacity of the hybrid pump is improved, the head and efficiency of the hybrid pump can also be improved, and the efficiency and stability of the pump operation are increased. Description of the Drawings

[0018] Figure 1 is a schematic structural diagram of the blade with a skirt for the hybrid pump of the present utility model;

[0019] Figure 2 is a schematic cross-sectional structural diagram of the impeller blade body and the skirt structure in the blade with a skirt for the hybrid pump of the present utility model;

[0020] Figure 3 is a radian distribution diagram of the skirt structure in the blade with a skirt for the hybrid pump of the present utility model.

[0021] Figure 4 is a curve graph showing the change of efficiency with gas volume fraction in Embodiment 4 of the present utility model;

[0022] Figure 5 is a curve graph showing the change of head with gas volume fraction in Embodiment 4 of the present utility model.

[0023] In the figure: 1. Hybrid pump impeller, 2. Impeller blade body, 3. Skirt structure. Detailed Implementation Modes

[0024] The present utility model will be described in detail below in conjunction with the drawings and specific implementation modes.

[0025] Embodiment 1

[0026] The blade with a skirt for the hybrid pump of the present utility model has a structure as Figure 1As shown, it includes the impeller blade body 2, and a skirt structure 3 provided on the back of the working surface of the impeller blade body 2. The skirt structure 3 is a protrusion provided on the back of the working surface of the impeller blade body 2. The skirt structure 3 is distributed along the arc of the impeller blade body 2. The side of the skirt structure 3 facing away from the hybrid pump impeller 1 is aligned with the edge of the corresponding impeller blade body 2.

[0027] The working principle of this embodiment is as follows:

[0028] During operation, the fluid enters the impeller through the inlet pipe. The impeller drives the fluid to rotate, and the fluid obtains energy due to the action of centrifugal force. On the back of the pressure surface, the skirt structure 3 can further break the diameter of the bubbles in the fluid flowing into the impeller blade body 2, effectively reducing the leakage flow at the gap, and making the pressure and gas content distribution more uniform. The skirt structure 3 can delay the fluid passing through the impeller blade body 2 from entering the next flow channel and be carried into the outlet of the next flow channel to form a high-pressure area, increasing the pressure on the suction surface of the impeller blade body 2 and reducing the separation of the boundary layer on the suction surface of the main impeller blade body 2. On the working surface side, due to the presence of the skirt structure 3 on its back, on the one hand, it can improve the flow condition and enhance the gas-liquid mixing degree, and on the other hand, it changes the blade structure, increases the blade strength, reduces the additional losses generated by the blade rotation, and thus increases the reliability and working life of the hybrid pump.

[0029] Embodiment 2

[0030] The blade with a skirt for a hybrid pump of the present utility model has a structure as Figure 1 shown, including the impeller blade body 2, and a skirt structure 3 provided on the back of the working surface of the impeller blade body 2. The skirt structure 3 is a protrusion provided on the back of the working surface of the impeller blade body 2. The skirt structure 3 is distributed along the arc of the impeller blade body 2. The side of the skirt structure 3 facing away from the hybrid pump impeller 1 is aligned with the edge of the corresponding impeller blade body 2; the skirt structure 3 is arc-shaped along the arc of the impeller blade body 2, and the length of the skirt structure 3 is the same as the length of the impeller blade body 2.

[0031] Embodiment 3

[0032] The blade with a skirt for a hybrid pump of the present utility model has a structure as Figure 1 shown, including the impeller blade body 2, and a skirt structure 3 provided on the back of the working surface of the impeller blade body 2. The skirt structure 3 is a protrusion provided on the back of the working surface of the impeller blade body 2. The skirt structure 3 is distributed along the arc of the impeller blade body 2. The side of the skirt structure 3 facing away from the hybrid pump impeller 1 is aligned with the edge of the corresponding impeller blade body 2; the skirt structure 3 is arc-shaped along the arc of the impeller blade body 2, and the length of the skirt structure 3 is the same as the length of the impeller blade body 2;

[0033] The thickness d2 of the skirt structure 3 is 60% of the thickness d1 of the impeller blade body 2. This proportional relationship helps to reasonably distribute materials while ensuring the structural strength. It will neither increase unnecessary weight and cost due to excessive thickness nor fail to meet the strength requirements due to excessive thinness.

[0034] As Figure 2 shown, the cross-section of the skirt structure 3 is a rectangular structure. The width of the rectangle is d2, which is the thickness of the skirt structure 3, and the length of the rectangle is d3. The calculation formulas for d2 and d3 are shown in Equation 2 below:

[0035] d3 = 3d2 (2)

[0036] For the length d3 of the rectangular skirt structure 3, the relatively large length-to-thickness ratio enables the skirt structure to play a better role in guiding and stabilizing the fluid. The longer side can, to a certain extent, guide the fluid flow direction, reduce fluid turbulence, and improve the gas-liquid mixing ability of the hybrid pump.

[0037] Both ends of the skirt structure 3 are welded to the two ends of the working surface of the impeller blade body 2.

[0038] The distance from the center of the skirt structure 3 to the center of the hybrid pump impeller 1 is 1.2 times the diameter of the hybrid pump impeller 1. This distance can place the skirt structure in a more appropriate hydrodynamic position in the theory of fluid mechanics. On the one hand, it can avoid excessive interference with the main fluid at the center of the impeller, and on the other hand, it can effectively guide and assist the fluid at the edge of the impeller, enhancing the fluid transmission and mixing effect.

[0039] As Figure 3 shown, the inner circle radius r2 of the skirt structure 3 is 1.1 times the radius r of the hybrid pump impeller 1. This dimension design forms a specific flow channel space between the skirt and the impeller. When the fluid enters the pump, the skirt structure can guide the fluid to pass through the impeller area more smoothly, reducing fluid vortex and turbulence phenomena.

[0040] The total length of the skirt structure 3 is 0.25 times the diameter of the hybrid pump impeller 1. It can prevent the fluid from excessive diffusion or backflow in the axial direction.

[0041] The length d3 of the rectangle in the cross-section of the skirt structure 3 is 0.48 times the cross-section length L of the impeller blade body 2. Such a dimensional proportional relationship enables the skirt structure to play a certain role in pre-whirl and rectification at the impeller blade inlet, which is beneficial to improving the operation stability of the entire hybrid pump.

[0042] The working principle of this embodiment is as follows:

[0043] During operation, the fluid enters the impeller through the inlet pipe. The impeller drives the fluid to rotate, and the fluid obtains energy due to the action of centrifugal force. On the back of the pressure surface, the skirt structure 3 can further break the diameter of the air bubbles in the fluid flowing into the impeller blade body 2, effectively reducing the leakage flow at the gap, making the pressure and gas content distribution more uniform. The skirt structure 3 can delay the fluid passing through the impeller blade body 2 from entering the next flow channel, and is brought into the outlet of the next flow channel with the water flow to form a high-pressure area, increasing the pressure on the suction surface of the impeller blade body 2 and reducing the separation of the boundary layer on the suction surface of the main impeller blade body 2. On the working surface side, due to the existence of the skirt structure 3 on its back, on the one hand, it can improve the flow condition and enhance the gas-liquid mixing degree, and on the other hand, it changes the blade structure, increases the blade strength, reduces the additional losses generated by the blade rotation, and thus increases the reliability and working life of the hybrid pump.

[0044] Example 4

[0045] On the basis of Example 3, taking the gas-liquid hybrid pump as the research object, using the Mixture mixing model and the k-epsilon standard turbulence model, by adding the skirt structure 3 of Example 3 of the present invention at the back of the working surface of the impeller blade, the performance curves of the gas-liquid hybrid pump with the "skirt" structure are obtained through numerical simulation under the working conditions of gas content 0, 0.1, 0.3, 0.5, and 0.7 as Figure 4 , Figure 5 shown.

[0046] Through experimental comparison, it can be seen that for the hybrid pump with the blade structure with the skirt structure 3 in the present invention, compared with the hybrid pump with the conventional blade structure, its pressure rise is increased by 2.3% and the efficiency is increased by 3.4%.

Claims

1. The vane with a skirt for a hybrid pump, characterized in that, It includes an impeller blade body (2) and a skirt structure (3) provided on the back of the working surface of the impeller blade body (2). The skirt structure (3) is a protrusion provided on the back of the working surface of the impeller blade body (2). The skirt structure (3) is distributed along the arc of the impeller blade body (2). The side of the skirt structure (3) facing away from the hybrid pump impeller (1) is aligned with the edge of the corresponding impeller blade body (2).

2. The skirted vane for a hybrid pump according to claim 1, characterized in that, The skirt structure (3) is arc-shaped along the arc of the impeller blade body (2), and the length of the skirt structure (3) is the same as the length of the impeller blade body (2).

3. The vane with a skirt for a hybrid pump according to claim 2, wherein, The thickness d2 of the skirt structure (3) is 60% of the thickness d1 of the impeller blade body (2).

4. The vane with a skirt for a hybrid pump according to claim 3, wherein The cross-section of the skirt structure (3) is a rectangular structure. The width of the rectangle is d2, and the length of the rectangle is d3. The calculation formulas for d2 and d3 are shown in the following formula (1): d3 = 3d2 (1).

5. The vane with a skirt for a hybrid pump according to claim 4, characterized in that, Both ends of the skirt structure (3) are welded to both ends of the working surface of the impeller blade body (2).

6. The vane with a skirt for a hybrid pump according to claim 5, wherein, The distance from the center of the skirt structure (3) to the center of the hybrid pump impeller (1) is 1.2 times the diameter of the hybrid pump impeller (1).

7. The skirted vane for a hybrid pump according to claim 6, wherein, The inner radius r2 of the skirt structure (3) is 1.1 times the radius r of the hybrid pump impeller (1).

8. The skirted vane for a hybrid pump according to claim 7, wherein The total length of the skirt structure (3) is 0.25 times the diameter of the hybrid pump impeller (1).

9. The vane with a skirt for a hybrid pump according to claim 8, characterized in that, The length d3 of the rectangle of the cross-section of the skirt structure (3) is 0.48 times the cross-section length L of the impeller blade body (2).

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