Impeller structure of a vortex pump

Abstract

The utility model belongs to the technical field of vortex pump hydraulic design relates to a vortex pump's impeller structure, including pump body and impeller, the pump body includes water inlet, water outlet, snail room flow channel and pump end, the impeller includes wheel disc and blade, the impeller sets up in pump end, its blade bottom protrudes into the snail room flow channel of pump body, the structural design of impeller satisfies following condition: b2: the numerical range of D2 is 0.2 0.24, L: the numerical range of D2 is 0.33 0.41, wherein, b2 is the height of impeller blade, D2 is the outer diameter of impeller, L is the vertical distance of blade bottom end to water inlet. The vortex pump's impeller structure provided by the utility model can improve the hydraulic performance of vortex pump, shorten the development cycle and save the development cost.

Description

Technical Field

[0001] This utility model belongs to the technical field of hydraulic design of vortex pumps, and relates to an impeller structure of a vortex pump. Background Technology

[0002] Currently, there is no mature design method for cyclone pumps on the market. Due to their large throughput capacity and different impeller structures and spacings, the performance and design values ​​of ordinary centrifugal pumps differ greatly when applied to cyclone pump design, and they cannot meet the design requirements.

[0003] Chinese invention patent CN103742417A (publication date: 2014-04-23) discloses a hydraulic design method for a high-efficiency, large-flow vortex pump, specifically relating to a hydraulic design method for the impeller and vortex chamber of the vortex pump. It provides design formulas for the bladeless cavity width, bladeless cavity inlet diameter, number of blades, blade wrap angle, blade inlet angle, and blade outlet angle. The vortex pump designed according to this method can effectively ensure the non-clogging nature of the vortex pump, achieving ideal head, efficiency, and operational stability with minimal hydraulic losses.

[0004] The aforementioned patent provides a quantitative design of the impeller parameters for the vortex pump, but does not address the spatial relationship between the impeller and the volute. In actual use, through flow and vortices will be generated between the impeller blades and the volute flow channel. These factors will also cause energy loss and have a significant impact on the hydraulic performance of the vortex pump. Utility Model Content

[0005] This invention addresses the shortcomings of existing technologies by providing an impeller structure for a vortex pump, which can improve the hydraulic performance of the vortex pump, shorten the research and development cycle, and save research and development costs.

[0006] To solve the above-mentioned technical problems, the objective of this utility model is achieved through the following technical solution:

[0007] A cyclone pump impeller structure includes a pump body and an impeller. The pump body includes an inlet, an outlet, a volute flow channel, and a pump end. The impeller includes a disc and blades. The impeller is disposed at the pump end, with the bottom of its blades extending forward into the volute flow channel of the pump body. The structural design of the impeller satisfies the following conditions:

[0008] b2: The numerical range of D2 is 0.2-0.24; L: The numerical range of D2 is 0.33-0.41;

[0009] Where b2 is the height of the impeller blade, D2 is the outer diameter of the impeller, and L is the vertical distance from the bottom of the blade to the inlet.

[0010] In the impeller structure of the aforementioned cyclone pump, the impeller is an open impeller, and the impeller, pump body, and inlet are all coaxially arranged.

[0011] In the impeller structure of the aforementioned cyclone pump, the upper end face of the impeller is lower than the upper end face of the pump end and higher than the upper end face of the volute flow channel; the axial distance of the blade extending into the volute flow channel is greater than half of the blade's axial dimension.

[0012] This utility model also provides specific design parameters for cyclone pumps that meet some common design requirements:

[0013] An impeller structure for a cyclone pump, the design flow rate of which is 6m³ / s. 3 The pump has a design head of 4m and a specific speed of 150 Ns. The impeller structure is designed to meet the following requirements: b2 = 18mm, D2 = 80mm, and L = 32mm. In the cyclone pump, the ratio of b2 to D2 is 0.23, and the ratio of L to D2 is 0.4.

[0014] An impeller structure for a cyclone pump, the design flow rate of which is 12 m³ / s. 3 The pump has a design head of 6m and a specific speed of 157 Ns. The impeller structure is designed to meet the following requirements: b2 = 18mm, D2 = 92mm, and L = 35mm. In the cyclone pump, the ratio of b2 to D2 is 0.2, and the ratio of L to D2 is 0.38.

[0015] An impeller structure for a cyclone pump, the design flow rate of which is 15 m³ / s. 3 The pump has a design head of 7m and a specific speed of 156 Ns. The impeller structure is designed to meet the following requirements: b2 = 24mm, D2 = 100mm, and L = 35mm. In the cyclone pump, the ratio of b2 to D2 is 0.24, and the ratio of L to D2 is 0.35.

[0016] An impeller structure for a cyclone pump, the design flow rate of which is 15 m³ / s. 3 / h, with a design head of 8.5m and a Ns (specific speed) value of 135, the impeller structure design meets the following requirements: b2 is 24mm, D2 is 100mm, and L is 35mm; in the cyclone pump, the value of b2:D2 is 0.23; and the value of L:D2 is 0.33.

[0017] An impeller structure for a cyclone pump, the cyclone pump having a design flow rate of 20 m³ / h 3 The pump has a design head of 8m and a specific speed of 163 Ns. The impeller structure is designed to meet the following requirements: b2 = 27mm, D2 = 113mm, and L = 46mm. In the cyclone pump, the ratio of b2 to D2 is 0.24, and the ratio of L to D2 is 0.41.

[0018] An impeller structure for a cyclone pump, the design flow rate of which is 25 m³ / s. 3 The pump has a design head of 9m and a specific speed of 166 Ns. The impeller structure is designed to meet the following requirements: b2 = 27mm, D2 = 120mm, and L = 46mm. In the cyclone pump, the ratio of b2 to D2 is 0.23, and the ratio of L to D2 is 0.38.

[0019] An impeller structure for a cyclone pump, the design flow rate of which is 30 m³ / s. 3 The pump has a design head of 13m and a specific speed of 138 Ns. The impeller structure is designed to meet the following requirements: b2 is 30mm, D2 is 125mm, and L is 46mm. In the cyclone pump, the ratio of b2 to D2 is 0.24, and the ratio of L to D2 is 0.37.

[0020] Compared with the prior art, this utility model has the following advantages:

[0021] This invention provides an impeller structure for a cyclone pump. The optimized design of the impeller structure significantly improves the overall performance of the cyclone pump: by reducing the impeller outer diameter to decrease disc friction loss, and simultaneously increasing the blade height to increase flow capacity, reduce through-flow, and suppress vortex generation, the hydraulic efficiency is optimally improved when the proportional parameter b2:D2 = 0.2-0.24. Combined with the proportional constraint of the bladeless cavity inlet depth to the impeller outer diameter (L:D2 = 0.33-0.41), the flow field distribution is optimized while ensuring the pump's flow capacity. This empirical parameter system can quickly pinpoint design objectives, reduce the number of prototype trials, significantly shorten the R&D cycle, and reduce development costs. Attached Figure Description

[0022] Figure 1 This is a schematic diagram of the structure of Embodiment 1 of this utility model;

[0023] Figure 2 This is a hydraulic performance diagram of Embodiment 2 of this utility model;

[0024] Reference numerals: 1. Pump body; 11. Inlet; 12. Outlet; 13. Volute flow channel; 14. Pump end; 2. Impeller; 21. Disc; 22. Blade; b2. Impeller blade height; D2. Impeller outer diameter; L. Vertical distance from the bottom of the blade to the inlet. Detailed Implementation

[0025] The present invention will be further described below with reference to the accompanying drawings and specific embodiments. See also: Figure 1-2 :

[0026] Example 1

[0027] A cyclone pump impeller structure includes a pump body and an impeller. The pump body includes an inlet, an outlet, a volute flow channel, and a pump end. The impeller includes a disc and blades. The impeller is disposed at the pump end, with the bottom of its blades extending forward into the volute flow channel of the pump body. The structural design of the impeller satisfies the following conditions:

[0028] b2: The numerical range of D2 is 0.2-0.24; L: The numerical range of D2 is 0.33-0.41;

[0029] Where b2 is the height of the impeller blade, D2 is the outer diameter of the impeller, and L is the vertical distance from the bottom of the blade to the inlet.

[0030] In the impeller structure of the aforementioned cyclone pump, the impeller is an open impeller, and the impeller, pump body, and inlet are all coaxially arranged.

[0031] In the impeller structure of the aforementioned cyclone pump, the upper end face of the impeller is lower than the upper end face of the pump end and higher than the upper end face of the volute flow channel; the axial distance of the blade extending into the volute flow channel is greater than half of the blade's axial dimension.

[0032] Example 2

[0033] Two impeller structures were designed, and their parameters are shown in the table below:

[0034] Table 1

[0035] b2(mm) D2 (mm) Number of leaves b2 / D2 Impeller 1 24 105 8 0.23 Impeller 2 18 115 8 0.16

[0036] The hydraulic performance test results of the two impellers are attached. Figure 2 As shown in the figure, the curves are Qh (flow rate-head), Q-η (flow rate-efficiency), and QP (flow rate-power), respectively. The horizontal axis represents the flow rate (m³ / s). 3 / h), the left vertical axis represents the head (m) and the right vertical axis represents the power (%): by reducing the impeller outer diameter D2 and increasing the impeller blade height b2, the hydraulic performance is significantly improved. The smaller the impeller outer diameter, the less the impeller disc friction loss. The increased blade height increases the amount of liquid passing through the impeller and reduces the through flow.

[0037] Example 3

[0038] An impeller structure for a cyclone pump, the design flow rate of which is 6m³ / s. 3 The pump has a design head of 4m and a specific speed of 150 Ns. The impeller structure is designed to meet the following requirements: b2 = 18mm, D2 = 80mm, and L = 32mm. In the cyclone pump, the ratio of b2 to D2 is 0.23, and the ratio of L to D2 is 0.4. Through testing, the efficiency of the electric pump in this embodiment is 17.2%.

[0039] Example 4

[0040] An impeller structure for a cyclone pump, the design flow rate of which is 12 m³ / s. 3 The pump has a design head of 6m and a specific speed of 157 Ns. The impeller structure is designed to meet the following requirements: b2 = 18mm, D2 = 92mm, and L = 35mm. In the cyclone pump, the ratio of b2 to D2 is 0.2, and the ratio of L to D2 is 0.38. Through testing, the efficiency of the electric pump in this embodiment is 29.4%.

[0041] Example 5

[0042] An impeller structure for a cyclone pump, the design flow rate of which is 15 m³ / s. 3 The pump has a design head of 7m and a specific speed of 156 Ns. The impeller structure is designed to meet the following requirements: b2 = 24mm, D2 = 100mm, and L = 35mm. In the cyclone pump, the ratio of b2 to D2 is 0.24, and the ratio of L to D2 is 0.35. Through testing, the efficiency of the electric pump in this embodiment is 30.1%.

[0043] Example 6

[0044] An impeller structure for a cyclone pump, the design flow rate of which is 15 m³ / s. 3 The pump has a design head of 8.5m and a specific speed (Ns) of 135. The impeller's structural design satisfies the following parameters: b2 = 24mm, D2 = 100mm, and L = 35mm. In the cyclone pump, the ratio of b2 to D2 is 0.23, and the ratio of L to D2 is 0.33. Through testing, the pump efficiency of this embodiment is 33.6%.

[0045] Example 7

[0046] An impeller structure for a cyclone pump, the cyclone pump having a design flow rate of 20 m³ / h 3 The pump has a design head of 8m and a specific speed of 163 Ns. The impeller structure is designed to meet the following requirements: b2 = 27mm, D2 = 113mm, and L = 46mm. In the cyclone pump, the ratio of b2 to D2 is 0.24, and the ratio of L to D2 is 0.41. Through testing, the efficiency of the electric pump in this embodiment is 28.3%.

[0047] Example 8

[0048] An impeller structure for a cyclone pump, the design flow rate of which is 25 m³ / s. 3The pump has a design head of 9m and a specific speed of 166 Ns. The impeller structure is designed to meet the following requirements: b2 = 27mm, D2 = 120mm, and L = 46mm. In the cyclone pump, the ratio of b2 to D2 is 0.23, and the ratio of L to D2 is 0.38. Through testing, the efficiency of the electric pump in this embodiment is 30.5%.

[0049] Example 9

[0050] An impeller structure for a cyclone pump, the design flow rate of which is 30 m³ / s. 3 The pump has a design head of 13m and a specific speed of 138 Ns. The impeller structure is designed to meet the following requirements: b2 = 30mm, D2 = 125mm, and L = 46mm. In the cyclone pump, the ratio of b2 to D2 is 0.24, and the ratio of L to D2 is 0.37. Through testing, the efficiency of the electric pump in this embodiment is 38.8%.

[0051] Examples 3-9 show cyclone pumps (specifically, non-clogging submersible cyclone pumps) with different design parameters. Comprehensive experiments demonstrate that a value range of b2:D2 of 0.2-0.24 and a value range of L:D2 of 0.33-0.41 exhibit good hydraulic performance. These empirical values ​​allow for the rapid acquisition of cyclone pump impeller design parameters, reducing the number of prototype trials, significantly shortening the R&D cycle, and lowering development costs.

[0052] The above embodiments are merely preferred embodiments of the present utility model and are not intended to limit the scope of protection of the present utility model. Therefore, all equivalent changes made to the structure, shape, and principle of the present utility model should be covered within the scope of protection of the present utility model.

Claims

1. An impeller structure for a cyclone pump, comprising a pump body (1) and an impeller (2), wherein the pump body (1) includes an inlet (11), an outlet (12), a volute flow channel (13), and a pump end (14), and the impeller (2) includes a disc (21) and blades (22), characterized in that, The impeller (2) is located at the pump end (14), and the bottom of its blades (22) extends forward into the volute flow channel (13) of the pump body (1). The structural design of the impeller (2) satisfies the following conditions: b2: The numerical range of D2 is 0.2-0.24; L: The numerical range of D2 is 0.33-0.41; Where b2 is the height of the blade (22) of the impeller (2), D2 is the outer diameter of the impeller (2), and L is the vertical distance from the bottom of the blade (22) to the inlet (11).

2. The impeller structure of a cyclone pump according to claim 1, characterized in that, The impeller (2) is an open impeller, and the impeller (2), pump body (1) and water inlet (11) are all coaxially arranged.

3. The impeller structure of a cyclone pump according to claim 2, characterized in that, The upper end face of the wheel (21) is lower than the upper end face of the pump end (14) and higher than the upper end face of the volute flow channel (13); the axial distance of the blade (22) extending into the volute flow channel (13) is greater than half of the axial dimension of the blade (22).

4. The impeller structure of a cyclone pump according to claim 1, characterized in that, The design flow rate of the cyclone pump is 6m³ / h. 3 / h, with a design head of 4m and a Ns value of 150, the impeller (2) has a structural design that satisfies: b2 is 18mm, D2 is 80mm, and L is 32mm.

5. The impeller structure of a cyclone pump according to claim 1, characterized in that, The design flow rate of the cyclone pump is 12m³ / h. 3 / h, the design head is 6m, the Ns value is 157, and the structural design of its impeller (2) meets the following requirements: b2 is 18mm, D2 is 92mm, and L is 35mm.

6. The impeller structure of a cyclone pump according to claim 1, characterized in that, The design flow rate of the cyclone pump is 15m³ / h. 3 / h, with a design head of 7m and a Ns value of 156, the impeller (2) has a structural design that satisfies the following: b2 is 24mm, D2 is 100mm, and L is 35mm.

7. The impeller structure of a cyclone pump according to claim 1, characterized in that, The design flow rate of the cyclone pump is 15m³ / h. 3 / h, the design head is 8.5m, the Ns value is 135, and the structural design of its impeller (2) meets the following requirements: b2 is 24mm, D2 is 100mm, and L is 35mm.

8. The impeller structure of a cyclone pump according to claim 1, characterized in that, The design flow rate of the cyclone pump is 20m³. 3 / h, the design head is 8m, the Ns value is 163, and the structural design of its impeller (2) meets the following requirements: b2 is 27mm, D2 is 113mm, and L is 46mm.

9. The impeller structure of a cyclone pump according to claim 1, characterized in that, The design flow rate of the cyclone pump is 25m³ / h. 3 / h, the design head is 9m, the Ns value is 166, and the structural design of its impeller (2) meets the following requirements: b2 is 27mm, D2 is 120mm, and L is 46mm.

10. The impeller structure of a cyclone pump according to claim 1, characterized in that, The design flow rate of the cyclone pump is 30m³. 3 / h, the design head is 13m, the Ns value is 138, and the structural design of its impeller (2) meets the following requirements: b2 is 30mm, D2 is 125mm, and L is 46mm.

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