Rib plate, pump and design method of pump

Abstract

The invention relates to a rib plate, a pump and a pump design method.The pump comprises a pump shell, the rib plate and an impeller, the pump shell comprises an inlet and an impeller cavity which are communicated, the impeller is rotationally arranged in the impeller cavity, the rib plate is arranged on the inner wall of the inlet, and the rib plate is formed by thickening a filling base plane in the normal direction of the filling base plane; the boundary of the filling base plane comprises an outer boundary, an inner boundary, a front boundary and a rear boundary, the outer boundary, the front boundary, the inner boundary and the rear boundary are sequentially connected to form a closed boundary, the outer boundary extends in the axial direction of the inlet, and the spatial positions (x, y and z) of all points on the outer boundary and the inner boundary meet a double-twist-line equation. The design method of the pump comprises the following steps of defining parameters of the rib plate, generating a filling base plane, generating a rib plate main body, chamfering and installing the rib plate into a pump shell. Due to the unique shape design of the rib plates, the flow guide effect of the pump at the inlet is good, the hydraulic efficiency of the pump is improved, prerotation can be restrained, and the cavitation resistance of the pump is improved.

Description

Technical Field

[0001] This invention relates to the field of pump technology, and more particularly to a rib plate, a pump, and a pump design method. Background Technology

[0002] In practical applications, due to limited installation space or improper pipeline design, non-uniform inflows such as deflection, vortex, and pre-swirling flow often form at the pump inlet. These non-uniform inflows disrupt the symmetry of the internal flow of the pump impeller, resulting in uneven load on the impeller blades. This leads to problems such as deterioration of cavitation resistance, damage to the impeller blades, and reduced hydraulic efficiency of the pump.

[0003] Therefore, there is an urgent need for a design method for ribs, pumps, and pumps to solve the above-mentioned technical problems. Summary of the Invention

[0004] The purpose of this invention is to provide a rib plate to at least solve one of the above-mentioned problems.

[0005] To achieve the above objectives, the present invention provides a rib plate, which is formed by thickening a filling base surface along the normal direction of the filling base surface. The boundary of the filling base surface includes an outer boundary, an inner boundary, a front boundary, and a rear boundary. The outer boundary, the front boundary, the inner boundary, and the rear boundary are sequentially connected to form a closed boundary. The spatial positions (x, y, z) of each point on the outer boundary satisfy the first double-twisted line equation: ; ; ; The spatial positions (x, y, z) of each point on the inner boundary satisfy the second bitwist equation: ; ; ; In the formula, R is half of the radial height H of the rib, and L is the axial length of the rib. Let be the torsion angle, and t be a variable parameter, with a value ranging from 0 to 1.

[0006] Furthermore, the twist angle The range is 25°-40°.

[0007] The object of this invention is to provide a pump that at least solves one of the above-mentioned problems.

[0008] To achieve the above objectives, the present invention provides a pump, comprising: Pump casing, which includes a communicating inlet and a wheel chamber; As described in any of the above embodiments, the rib is disposed on the inner wall of the inlet, and the outer boundary extends along the axial direction of the inlet; The impeller rotates within the impeller cavity.

[0009] Furthermore, the radial height H of the rib is 0.06 to 0.09 times the diameter D of the inlet.

[0010] Furthermore, the axial length L of the rib plate is 0.82 to 0.96 times the length of the straight pipe section of the inlet.

[0011] Furthermore, the rib thickness T of the rib plate is 2.4%-4% of the diameter D of the inlet.

[0012] Furthermore, the number of ribs is N, and each of the ribs is spaced apart on the inner wall of the inlet along the circumferential direction of the inlet.

[0013] Furthermore, the number N of the ribs is 3-6.

[0014] The purpose of this invention is to provide a pump design method to at least solve one of the above-mentioned problems.

[0015] To achieve the above objectives, the present invention provides a pump design method as described in any of the above embodiments, comprising the following steps: Define the parameters of the rib: radial height H, axial length L, and torsion angle. The rib thickness T and the number of ribs N are known parameters, while t is a variable; Generate the filling base surface: Based on the known parameters, variables, and hyoid equations of the inner and outer boundaries of the rib, create the inner and outer boundaries of the filling base surface in the 3D modeling software; based on the endpoints of the inner and outer boundaries, create the front and rear boundaries of the filling base surface in the 3D modeling software; fill the filling base surface by filling its closed boundaries. Forming the rib body: The filling base surface is thickened along the normal direction of the filling base surface to form the rib body; Rounding: Round the corner of the rib body facing the inlet to form a rounded corner, thus forming the rib; Install the ribs into the pump casing: Insert N ribs into the pump model and evenly arrange each rib on the inner wall of the pump casing inlet.

[0016] Furthermore, the size of the rounded corner is equal to the rib thickness T of the rib plate.

[0017] The beneficial effects of this invention are as follows: The pump provided by this invention includes a pump casing, ribs, and an impeller. The pump casing includes a connected inlet and a wheel cavity. The impeller is rotatably disposed within the wheel cavity. The ribs are disposed on the inner wall of the inlet and are formed by thickening a filling base surface along the normal direction of the filling base surface. The boundary of the filling base surface includes an outer boundary, an inner boundary, a front boundary, and a rear boundary. The outer boundary, front boundary, inner boundary, and rear boundary are sequentially connected to form a closed boundary. The outer boundary extends along the axial direction of the inlet. The spatial position (x, y, z) of each point on the outer boundary satisfies the first double-twisted line equation: ; ; ; The spatial positions (x, y, z) of each point on the inner boundary satisfy the second bitwist equation: ; ; ; In the formula, R is half of the radial height H of the rib, and L is the axial length of the rib. Let be the torsion angle, and t be a variable parameter, with a value ranging from 0 to 1.

[0018] The unique shape of the ribs forms a guide channel opposite to the impeller's rotation direction, and the torsion of the ribs increases the guiding force of the fluid, suppresses pre-swirling incoming flow, makes the incoming flow more uniform, reduces the generation of local low-pressure areas on the impeller, and improves the pump's anti-cavitation performance. The ribs, generated using the nylontilinear equation, have a flow-guiding effect, transforming the fluid flow from passive interception to active guidance. This more effectively cuts and disperses vortices, actively guiding the fluid to recombine into a more uniform and orderly flow, thereby homogenizing the velocity distribution. This makes the fluid entering the impeller smoother and axially symmetrical, reducing energy loss and improving the pump's hydraulic efficiency. The uniform inlet flow field makes the radial force acting on the impeller more balanced, reducing pump vibration and noise, improving pump operational stability and reliability, and extending pump service life. The ribs at the pump inlet have a simple structure, requiring only minor modifications to the existing pump body casting mold. These minor modifications are low-cost, requiring no additional parts and increasing manufacturing costs almost nothing, yet improving the pump's hydraulic efficiency.

[0019] The pump design method provided by this invention includes the following steps: Define the parameters of the rib: radial height H, axial length L, and torsion angle. The rib thickness T and the number of ribs N are known parameters, while t is a variable; Generate the filling base surface: Based on the known parameters, variables, and hyoid equations of the inner and outer boundaries of the rib, create the inner and outer boundaries of the filling base surface in the 3D modeling software; based on the endpoints of the inner and outer boundaries, create the front and rear boundaries of the filling base surface in the 3D modeling software; fill the filling base surface by filling its closed boundaries. Forming the rib body: The filling base surface is thickened along the normal direction of the filling base surface to form the rib body; Rounding: The end of the rib body facing the inlet is rounded to form a rounded corner, thus ultimately forming the rib; Install the ribs into the pump casing: Insert N ribs into the pump model and evenly arrange each rib on the inner wall of the pump casing inlet.

[0020] This pump design method results in a pump with good flow guidance at the inlet, which can more effectively cut and disperse vortices, reduce energy loss, improve pump hydraulic efficiency, reduce pump vibration and noise, improve pump operation stability and reliability, extend pump service life, and suppress pre-swirl, thereby improving the pump's anti-cavitation performance. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the pump provided in an embodiment of the present invention; Figure 2 This is a top view of the pump provided in an embodiment of the present invention; Figure 3 yes Figure 1 A magnified view of a section at point A in the middle; Figure 4 This is a schematic diagram of the rib plate provided in an embodiment of the present invention; Figure 5 This is a structural schematic diagram of the rib plate from another angle provided in an embodiment of the present invention; Figure 6 This is a schematic diagram of the pump provided in the comparative example of the present invention; Figure 7 This is a top view of the pump provided as a comparative example of the present invention; Figure 8 This is a comparison chart of flow rate and hydraulic efficiency obtained by simulating the pump provided in the embodiment of the present invention and the pump provided in the comparative example; Figure 9 This is a velocity vector cloud map obtained from pump simulation provided in this embodiment of the invention; Figure 10 This is a velocity vector cloud diagram obtained from pump simulation provided in the comparative example of this invention; Figure 11 This is a line graph of axial length versus hydraulic efficiency obtained from simulation of the pump provided in this embodiment of the invention. Figure 12This is a line graph of radial height versus hydraulic efficiency obtained from simulation of the pump provided in this embodiment of the invention; Figure 13 This is a line graph of torsion angle versus hydraulic efficiency obtained from simulation of the pump provided in this embodiment of the invention; Figure 14 This is a line graph of rib thickness versus hydraulic efficiency obtained from simulation of the pump provided in this embodiment of the invention.

[0022] In the picture: 1. Pump casing; 11. Inlet; 12. Impeller cavity; 13. Outlet; 2. Rib; 21. Filler base surface; 211. Outer boundary; 212. Inner boundary; 213. Front boundary; 214. Rear boundary; 22. Rounded corner; 3. Impeller; 100. Pump casing; 101. Inlet; 102. Impeller cavity; 103. Outlet; 200, Rib plate; 300, Impeller. Detailed Implementation

[0023] The technical solution of the present invention will be further described below with reference to the accompanying drawings and specific embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and not intended to limit it. Furthermore, it should be noted that, for ease of description, only the parts relevant to the present invention are shown in the accompanying drawings, not all of them.

[0024] This invention defines certain directional terms. Unless otherwise stated, the directional terms used, such as "up," "down," "left," "right," "inner," and "outer," are used for ease of understanding and therefore do not constitute a limitation on the scope of protection of this invention.

[0025] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0026] In the description of this invention, unless otherwise explicitly specified and limited, the terms "connected," "linked," and "fixed" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0027] like Figure 1 and Figure 5 As shown, this embodiment provides a pump, which includes a pump casing 1, a rib plate 2, and an impeller 3. The pump casing 1 includes a connected inlet 11 and a wheel cavity 12. The impeller 3 is rotatably disposed within the wheel cavity 12. The rib plate 2 is disposed on the inner wall of the inlet 11. The rib plate 2 is formed by thickening the filling base surface 21 along the normal direction of the filling base surface 21. The boundary of the filling base surface 21 includes an outer boundary 211, an inner boundary 212, a front boundary 213, and a rear boundary 214. The outer boundary 211, the front boundary 213, the inner boundary 212, and the rear boundary 214 are connected sequentially to form a closed boundary. The outer boundary 211 extends along the axial direction of the inlet 11. The spatial positions (x, y, z) of each point on the outer boundary 211 satisfy the first double-twisted line equation: ; ; ; The spatial positions (x, y, z) of each point on the inner boundary 212 satisfy the second bitwist equation: ; ; ; In the formula, R is half of the radial height H of rib 2, i.e., R = H / 2; L is the axial length of rib 2. Let be the torsion angle, and t be a variable parameter, with a value ranging from 0 to 1.

[0028] The unique shape of rib 2 forms a guide channel with the opposite rotation direction to impeller 3, and the torsion of rib 2 increases the guiding force of the fluid, suppresses the pre-swirling incoming flow, makes the incoming flow more uniform, reduces the generation of local low-pressure areas in impeller 3, and improves the pump's anti-cavitation performance. Rib 2, generated using the nylonite equation, has a flow-guiding effect, which changes the fluid flow from passive interception to active guidance, and can more effectively cut and disperse vortices, actively guiding the fluid to recombine into a more uniform and orderly flow, thereby homogenizing the velocity distribution, making the fluid entering impeller 3 smoother and axially symmetrical, reducing energy loss, and improving the pump's hydraulic efficiency. The uniform inlet flow field makes the radial force acting on impeller 3 more balanced, reducing pump vibration and noise, improving pump operation stability and reliability, and extending pump service life. Setting rib 2 at the pump inlet 11 has a simple structure, which can be achieved with only minor modifications to the existing pump body casting mold. The modification is small and the cost is low. No additional parts are needed, and the manufacturing cost is almost negligible, yet the pump's hydraulic efficiency is improved.

[0029] Furthermore, the pump casing 1 also includes an outlet 13, which is connected to the impeller cavity 12. After the incoming flow enters the inlet 11, it is cut and dispersed by the action of the rib plate 2, actively guiding the fluid to recombine into a more uniform and orderly flow. Then, under the rotation of the impeller 3, it is sucked into the impeller cavity 12 and pumped out of the pump through the outlet 13.

[0030] like Figures 4-5 As shown, the radial height of rib 2 refers to the farthest distance of the outer contour of rib 2 in the radial direction of inlet 11.

[0031] Furthermore, the axial length of rib 2 refers to the farthest distance of the outer contour of rib 2 in the axial direction of inlet 11.

[0032] Furthermore, the rib 2 is formed by thickening the rib thickness T along the normal direction of the filling base surface 21, and the filling base surface 21 is a curved surface.

[0033] The unique shape of the rib 2 is determined by the hyoid equation. Both the inner boundary 212 and the outer boundary 211 are part of the hyoid equation. The difference between the two is a 180° phase difference. This phase difference makes the inner boundary 212 and the outer boundary 211 non-parallel in three-dimensional space, thus forming a guide channel opposite to the rotation direction of the impeller 3. This has a good guiding effect while also suppressing the pre-swirling flow, making the flow more uniform, reducing the generation of local low-pressure areas in the impeller 3, and improving the pump's anti-cavitation performance.

[0034] To demonstrate the beneficial effects of the unique shape of rib 2, a comparative example is provided for comparison with the pump provided in this embodiment. The pump provided in the comparative example is as follows: Figures 6-7As shown, the pump provided in the comparative example includes a pump casing 100, a rib plate 200, and an impeller 300. The pump casing 100 has an inlet 101, an impeller cavity 102, and an outlet 103. The inlet 101 and the impeller cavity 102 are interconnected, and the outlet 103 and the impeller cavity 102 are interconnected. The impeller 300 is rotatably disposed within the impeller cavity 102. The rib plate 200 is disposed on the inner wall of the inlet 101. The inner and outer boundaries of the rib plate 200 are parallel, and the variation of the outer boundary conforms to the Archimedean spiral. That is to say, the pump provided in the comparative example differs from the pump provided in this embodiment in that the shape of the rib plate is different, and the rib plate 200 in the comparative example does not have torsion.

[0035] Figure 8 The figure shows a comparison of the hydraulic efficiency of the pumps provided in the comparative example and this embodiment at different flow rates, obtained by simulation with only the shape of the ribs changed while keeping other parameters constant. Figure 8 It is evident that the hydraulic efficiency of the pump provided in this embodiment is significantly higher than that of the pump provided in the comparative example. In other words, while both the pumps in the comparative example and this embodiment can reduce vortices and impeller inlet pre-swirl, thus improving the pump's cavitation resistance, the pump provided in this embodiment has a higher hydraulic efficiency. This is because the pump provided in this embodiment has a torsion effect in the ribs, resulting in better flow guidance and higher hydraulic efficiency. Furthermore, it also reduces vortices, lowers impeller inlet pre-swirl, and improves the pump's cavitation resistance.

[0036] Depend on Figure 9 and Figure 10 The comparison shows that the pump provided in the comparative example exhibits flow separation at the location highlighted in red, resulting in increased flow loss and reduced hydraulic efficiency.

[0037] Therefore, the unique shape of rib 2 cannot be achieved simply by replacing different equations.

[0038] While ensuring other parameters (rib thickness T is 1.2mm, torsion angle) With the axial angle of 30°, the radial height H of 4mm, and the straight pipe section length of inlet 11 of 23mm remaining constant, simulation analysis was performed on a water pump with ribs 2 having different axial lengths L, and the results were as follows: Figure 11The line graph shown represents the axial length L on the horizontal axis and the hydraulic efficiency on the vertical axis. As can be seen from the graph, with other parameters remaining constant, the hydraulic efficiency varies significantly within the range of 19mm-22mm for the axial length L. Specifically, the hydraulic efficiency is most noticeable and higher within the range of 0.82-0.96 times the length of the straight pipe section of inlet 11, especially when the axial length L is 0.87 times the length of the straight pipe section of inlet 11 (i.e., an axial length of 20mm). In other words, the preferred range for the axial length L is 0.82-0.96 times the length of the straight pipe section of inlet 11, with 0.87 times the length of the straight pipe section of inlet 11 being the preferred value. Within this preferred range, the closer the axial length L is to the preferred value, the higher the hydraulic efficiency. When the axial length L is too large, the straight pipe section exceeding the inlet 11 will interfere with the impeller 3, resulting in reduced hydraulic efficiency and unstable hydraulic efficiency with fluctuations. When the axial length L is too short, insufficient correction of the fluid flow will also lead to reduced hydraulic efficiency. Therefore, the axial length L of the rib plate 2 is 0.82 to 0.96 times the length of the straight pipe section of the inlet 11.

[0039] Preferably, the axial length L of the rib plate 2 is 0.87 times the length of the straight pipe section of the inlet 11.

[0040] While ensuring other parameters (rib thickness T is 1.2mm, torsion angle) With the axial angle constant at 30°, the axial length L constant at 20mm, and the inlet diameter D constant at 50mm, a simulation analysis was performed on a water pump with ribs 2 having different radial heights H. The results are as follows: Figure 12 The line graph shown represents the radial height H on the horizontal axis and the hydraulic efficiency on the vertical axis. As can be seen from the graph, with other parameters remaining constant, the hydraulic efficiency varies significantly within the range of 3mm-4.5mm for the radial height H. Specifically, the hydraulic efficiency varies significantly and is relatively high within the range of 0.06-0.09 times the diameter D of the pump inlet 11, especially when the radial height H is 0.08 times the diameter D of the pump inlet 11 (radial height of 4mm). In other words, the preferred range for the radial height H is 0.06-0.09 times the diameter D of the pump inlet 11, with 0.08 times the diameter D of the pump inlet 11 being the preferred value. Within the preferred range of the radial height H, the closer the radial height H is to the preferred value, the higher the hydraulic efficiency. When the radial height H is too large, it will block the flow channel, causing the hydraulic efficiency to fluctuate unstablely. When the radial height H is too small, it can only guide the boundary layer near the inner wall of inlet 11, and cannot affect the deflection and vortex at the center of inlet 11, thus reducing the hydraulic efficiency. Therefore, the radial height H of rib 2 is 0.06 to 0.09 times the diameter D of inlet 11.

[0041] Preferably, the radial height H of the rib 2 is 0.08 times the diameter D of the inlet 11.

[0042] While keeping other parameters (axial length L = 20 mm, rib thickness T = 1.2 mm, radial height H = 4 mm, inlet diameter D = 50 mm) constant, simulation analysis was performed on water pumps with ribs 2 including different torsion angles θ, and the results are as follows: Figure 13 The line graph shown represents the torsion angle θ on the horizontal axis and hydraulic efficiency on the vertical axis. As can be seen from the graph, with other parameters remaining constant, the hydraulic efficiency varies significantly within the torsion angle θ range of 25° to 40°, and is relatively high, especially between 25° and 30°. When the torsion angle θ is too large, it over-corrects the anti-pre-spinning effect, leading to a decrease in hydraulic efficiency and unstable fluctuations. Conversely, when the torsion angle θ is too small, the correction of anti-pre-spinning is insufficient, resulting in a decrease in hydraulic efficiency. Therefore, the torsion angle... The range is 25°-40°.

[0043] Preferably, the twist angle It is 30°.

[0044] While keeping other parameters constant (axial length L = 20mm, torsion angle θ = 30°, radial height H = 4mm, inlet diameter D = 50mm), a simulation analysis was conducted on a water pump with ribs 2 of varying thicknesses T, and the results are as follows: Figure 14 The line graph shown represents the rib thickness T on the horizontal axis and the hydraulic efficiency on the vertical axis. As can be seen from the graph, with other parameters remaining constant, the hydraulic efficiency varies significantly within the range of 1.2mm-2mm when the rib thickness T is 2.4%-4% of the diameter D of inlet 11. The hydraulic efficiency is also relatively high within this range, especially when the rib thickness T is 2.4% of the diameter D of inlet 11. Therefore, a rib thickness T of 2.4%-4% of the diameter D of inlet 11 is considered the preferred range, with 2.4% of the diameter D of inlet 11 being the preferred value. Within this preferred range, the closer the rib thickness T is to the preferred value, the higher the hydraulic efficiency. When the rib thickness T is too large, it increases the contact area between the rib 2 and the fluid, increasing flow resistance and flow loss, and thus reducing hydraulic efficiency. When the rib thickness T is too small, it cannot meet the strength requirements of the rib 2, increasing the risk of the rib 2 breaking due to fluid impact, and the hydraulic efficiency fluctuates unstablely. Therefore, the rib thickness T of the rib 2 is 2.4%-4% of the diameter D of the inlet 11.

[0045] Preferably, the rib thickness T of rib 2 is 2.4% of the diameter D of inlet 11.

[0046] Furthermore, there are N ribs 2, and each rib 2 is spaced apart on the inner wall of the inlet 11 along the circumference of the inlet 11. Specifically, each rib 2 is evenly arranged along the circumference of the inlet 11.

[0047] Furthermore, the number N of ribs 2 is 3-6. If the number N of ribs 2 is too small, it will lead to uneven division and dispersion of vortices by ribs 2, and may also generate new, unsuppressed vortices; if the number N of ribs 2 is too large, it will significantly increase the contact area between the fluid and ribs 2, increase the friction loss between the fluid and ribs 2, and reduce the hydraulic efficiency of the pump.

[0048] Preferably, the number N of ribs 2 is 4, and each rib 2 is evenly arranged along the circumference of the inlet 11, with the angle between two adjacent ribs 2 being 90°.

[0049] This embodiment also provides a pump design method, including the following steps: Define the parameters of rib 2: radial height H of rib 2, axial length L of rib 2, and torsion angle. The thickness T of rib 2 and the number N of rib 2 are known parameters, and t is a variable; Generate the filling base surface 21: Based on the known parameters and variables of the rib 2, as well as the hyoid equations of the inner boundary 212 and the outer boundary 211, create the inner boundary 212 and the outer boundary 211 of the filling base surface 21 in the 3D modeling software; based on the endpoints of the inner boundary 212 and the outer boundary 211, create the front boundary 213 and the rear boundary 214 of the filling base surface 21 in the 3D modeling software; fill the closed boundary of the filling base surface 21 to form the filling base surface 21; Generate the rib body: Thicken the filling base surface 21 along the normal direction of the filling base surface 21 to form the rib body; Rounding: Rounding the corner of the rib body facing the inlet 11 to form a rounded corner 22, thus forming the rib 2; Install the ribs 2 into the pump casing 1: Insert N ribs 2 into the water pump model and evenly arrange each rib 2 on the inner wall of the inlet 11 of the pump casing 1.

[0050] This pump design method results in a pump with good flow guidance at inlet 11, which can more effectively cut and disperse vortices, reduce energy loss, improve pump hydraulic efficiency, reduce pump vibration and noise, improve pump operation stability and reliability, extend pump service life, and suppress pre-swirl, thereby improving pump anti-cavitation performance.

[0051] Furthermore, the size of the rounded corner 22 is equal to the rib thickness T of the rib 2. This arrangement reduces the impact loss between the fluid and the rib 2, thereby improving the hydraulic efficiency of the pump.

[0052] Furthermore, when generating the rib body, the filling base surface 21 can be used as the center surface, and the thickness can be symmetrically increased on both sides of the filling base surface 21 along the normal direction of the filling base surface 21. Alternatively, the filling base surface 21 can be used as the surface of the rib 2, and the thickness can be increased on one side of the filling base surface 21 along the normal direction of the filling base surface 21.

[0053] Furthermore, the N ribs 2 can be formed by arraying.

[0054] Furthermore, in the step of installing the rib plate 2 into the pump casing 1, the outer boundary 211 intersects with the inner wall of the inlet 11. Since the side surface formed by the two outer boundaries 211 of the rib plate 2 is a curved surface, this curved surface may not completely fit with the inner wall of the inlet 11, that is, there will be a gap between the curved surface and the inner wall of the inlet 11. In order to ensure the strength of the rib plate 2, the gap needs to be filled into a solid. When filling, the solid needs to be filled according to the direction of the curved surface formed by the two outer boundaries 211 of the rib plate 2. Since this curved surface is a side surface, the filling base surface 21 plays a dominant role in guiding the fluid. Therefore, the filling has little effect on the shape of the filling base surface 21, and the main shape of the rib plate 2 will not change much. Therefore, it will not have a key impact on the fluid flow.

[0055] In this embodiment, the rib plate 2 is generated by creating a boundary - filling the boundary to form a filling base surface 21 - thickening the filling base surface 21. This is because the filling base surface 21 is an irregular curved surface in three-dimensional space, which cannot be formed into a solid by simple stretching. Moreover, the curvature of the curved surface formed by the filling base surface 21 formed by the boundary filling is continuous, and the solid formed by thickening is also smoother.

[0056] Furthermore, 3D modeling software can be Solidworks.

[0057] The following is a specific example illustrating the design method of this pump, including the following steps: Define the parameters of rib 2: define the radial height H of rib 2 as 4mm, the axial length L of rib 2 as 20mm, and the torsion angle as... The angle is 30°, the thickness T of rib 2 is 1.2 mm, and the number of ribs 2 is 4, that is, R is 2 mm; t starts from 0 and takes 11 values ​​in sequence: 0, 0.1, 0.2, 0.3...1. Generate the filled base surface 21: Substitute the 11 values ​​of t into the first hyoid line equation to obtain the spatial coordinates of 11 points on the outer boundary 211. Insert the spatial coordinates of the 11 points on the outer boundary 211 into Solidworks to create the outer boundary 211. When t is 0, the obtained point is the front endpoint of the outer boundary 211. When t is 1, the obtained point is the rear endpoint of the outer boundary 211. Substituting the 11 values ​​of t into the second hyoid line equation, we obtain the spatial coordinates of 11 points on the inner boundary 212. Inserting the spatial coordinates of the 11 points on the inner boundary 212 into Solidworks will create the inner boundary 212. When t is 0, the obtained point is the front endpoint of the inner boundary 212, and when t is 1, the obtained point is the rear endpoint of the inner boundary 212. By inserting the coordinates of the front endpoint of the inner boundary 212 and the coordinates of the front endpoint of the outer boundary 211 into Solidworks, the front boundary 213 can be created. By inserting the coordinates of the rear end point of the inner boundary 212 and the coordinates of the rear end point of the outer boundary 211 into Solidworks, the rear boundary 214 can be created. The filling base surface 21 is formed by filling the closed boundary formed by the sequential connection of the outer boundary 211, the front boundary 213, the inner boundary 212 and the rear boundary 214. Generate the rib body: Thicken the filling base surface 21 along the normal direction of the filling base surface 21 to form the rib body; Rounding: Rounding the corner of the rib body facing the inlet 11 to form a rounded corner 22, thus forming the rib 2; Install the ribs 2 into the pump casing 1: Insert N ribs 2 into the water pump model and evenly arrange each rib 2 on the inner wall of the inlet 11 of the pump casing 1.

[0058] Although the present invention has been described in detail above with general descriptions, specific embodiments, and experiments, modifications or improvements can be made to it, which will be obvious to those skilled in the art. Therefore, all such modifications or improvements made without departing from the spirit of the present invention fall within the scope of protection claimed by the present invention.

Claims

1. A rib plate, characterized in that, The rib is formed by thickening the filling base surface (21) along the normal direction of the filling base surface (21). The boundary of the filling base surface (21) includes an outer boundary (211), an inner boundary (212), a front boundary (213), and a rear boundary (214). The outer boundary (211), the front boundary (213), the inner boundary (212), and the rear boundary (214) are connected in sequence to form a closed boundary. The spatial positions (x, y, z) of each point on the outer boundary (211) satisfy the first double twist line equation: ； ； ； The spatial positions (x, y, z) of each point on the inner boundary (212) satisfy the second double twist line equation: ； ； ； In the formula, R is half of the radial height H of the rib (2), and L is the axial length of the rib (2). Let be the torsion angle, and t be a variable parameter, with a value ranging from 0 to 1.

2. The rib plate according to claim 1, characterized in that, Twist angle The range is 25°-40°.

3. A pump, characterized in that, include: Pump housing (1), which includes a communicating inlet (11) and a wheel cavity (12); The rib (2) as described in any one of claims 1-2 is provided on the inner wall of the inlet (11), and the outer boundary (211) extends along the axial direction of the inlet (11); The impeller (3) rotates within the wheel cavity (12).

4. The pump according to claim 3, characterized in that, The radial height H of the rib (2) is 0.06 to 0.09 times the diameter D of the inlet (11).

5. The pump according to claim 3, characterized in that, The axial length L of the rib (2) is 0.82 to 0.96 times the length of the straight pipe section of the inlet (11).

6. The pump according to claim 3, characterized in that, The rib thickness T of the rib (2) is 2.4%-4% of the diameter D of the inlet (11).

7. The pump according to claim 3, characterized in that, The number of ribs (2) is N, and each of the ribs (2) is arranged at intervals along the circumference of the inlet (11) on the inner wall of the inlet (11).

8. The pump according to claim 7, characterized in that, The number N of the ribs (2) is 3-6.

9. A design method for a pump as described in any one of claims 3-8, characterized in that, Includes the following steps: Define the parameters of rib (2): radial height H of rib (2), axial length L of rib (2), and torsion angle. The thickness T of the rib (2) and the number N of the rib (2) are known parameters, and t is a variable; Generate the filling base surface (21): Based on the known parameters and variables of the rib (2) and the hyoid equations of the inner boundary (212) and outer boundary (211), create the inner boundary (212) and outer boundary (211) of the filling base surface (21) in the 3D modeling software; based on the endpoints of the inner boundary (212) and the outer boundary (211), create the front boundary (213) and rear boundary (214) of the filling base surface (21) in the 3D modeling software; fill the filling base surface (21) with the closed boundary of the filling base surface (21) to form the filling base surface (21); Generate the rib body: The filling base surface (21) is thickened along the normal of the filling base surface (21) to form the rib body; Rounding: Rounding the corner of the rib body facing the inlet (11) to form a rounded corner (22), thereby finally forming the rib (2); Install the ribs (2) into the pump casing (1): Insert N ribs (2) into the pump model and arrange each rib (2) evenly on the inner wall of the inlet (11) of the pump casing (1).

10. The pump design method according to claim 9, characterized in that, The size of the rounded corner (22) is equal to the rib thickness T of the rib (2).

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