Design method of high-lift vortex pump

Abstract

The invention relates to the technical field of pumps, and discloses a high-lift vortex pump design method which comprises the following steps: designing a vortex pump structure; a pump cavity of the vortex pump protrudes outwards, and the protruding direction is the direction of the water inlet side of the vortex pump. The shape of a blade on an impeller of the vortex pump is set to be a bent wedge shape; parameters of the vortex pump are calculated; the parameters of the vortex pump comprise the number of blades of an impeller, the outer diameter of the impeller and the width of a bladeless cavity in a pump cavity; according to the pump, the outlet pressure of the constant-pressure pump is increased, the lift and efficiency are improved, and meanwhile the problems that an existing vortex pump is large in friction and short in service life are solved.

Description

Technical Field

[0001] The invention relates to the technical field of pump design, and in particular to a design method for a high-lift vortex pump. Background Art

[0002] At present, traditional centrifugal pumps still dominate the water pumps produced and used in my country. However, in some special fields, such as industry, agriculture, fire hydraulics, etc., traditional centrifugal pumps have some limitations. In order to overcome these limitations, swirl constant pressure pumps came into being and have gradually been widely used.

[0003] Compared with traditional centrifugal pumps, vortex pumps have the following characteristics: simple structure, easy to manufacture, and stable operation; there is no clearance between the impeller and the pump body, and there is no problem of wear causing the clearance to increase and causing performance degradation; most of the solid particles do not pass through the impeller, so there is no clogging performance, and the impeller wear is relatively reduced. However, because most of the transported material flows out under the drive of the vortex without the blade cavity, the non-destructiveness is poor, and there is a certain degree of damage to the transported material.

[0004] With the advancement of technology and the growth of demand, the existing spiral flow constant pressure pump technology can no longer meet the requirements of the nuclear industry and high-rise building fire protection because of its insufficient flow, limited head and low efficiency. Especially with the acceleration of urbanization, the density and height of buildings are increasing, and the fire situation is becoming more and more complicated, while the existing high-rise fire protection technology cannot keep up with the growth rate of high-rise buildings. Summary of the invention

[0005] In order to solve the above problems, the present invention provides a design method for a high-lift vortex pump.

[0006] A method for designing a high-lift vortex pump comprises the following steps:

[0007] S1. Design the swirl pump structure;

[0008] The vortex pump comprises a horizontally arranged pump body, a horizontally arranged pump shaft, an impeller located inside the pump body and mounted on the pump shaft, and a bearing body sleeved on the pump shaft and rotatably connected to the pump shaft through a bearing;

[0009] The pump chamber of the vortex pump is configured to protrude outward, and the protruding direction is the direction of the water inlet side of the vortex pump;

[0010] The blade shape on the impeller of the swirl pump is set to a bent wedge shape, the thickness of the blade located at the center of the impeller of the swirl pump is greater than the thickness of the blade located at the edge of the impeller, and the width of the blade located at the center of the impeller is greater than the width of the blade located at the edge of the impeller;

[0011] S2, calculate the parameters of the swirl pump;

[0012] The swirl pump parameters include the number of impeller blades, the outer diameter of the impeller, and the width of the bladeless cavity in the pump cavity;

[0013] First, the number of impeller blades is calculated based on the outer diameter of the impeller, the diameter of the water inlet of the swirl pump, the blade inlet angle, and the blade outlet angle;

[0014] Then, the outer diameter of the impeller is calculated according to the head and the speed of the swirl pump;

[0015] Finally, the impeller-free width of the pump cavity is calculated based on the impeller outer diameter.

[0016] Description: Since the flow channel between the blades of the vortex pump diffuses more seriously, when slip is not considered, the relative velocity is equal to the axial velocity, so the diffusion of the relative velocity is also very serious, and the axial vortex flow between the blades is very strong, causing flow turbulence between the blades and generating considerable additional hydraulic losses. The present invention can improve this flow state and improve the efficiency of the pump through the above-mentioned design method. And through the settings of the blade shape, etc., the work done by the blade on the liquid is increased, the degree of circulation flow is relatively reduced, and the vortex loss at the leading edge of the blade is reduced, thereby improving the pump efficiency.

[0017] Furthermore, the water inlet of the swirl pump is parallel to the horizontal plane, the water outlet of the swirl pump is perpendicular to the ground, and the number of blades of the impeller is 14.

[0018] Note: Through the above-mentioned setting, the vortex loss at the leading edge of the blade can be reduced while ensuring the strength of the blade.

[0019] Furthermore, the number of blades of the impeller is calculated by formula (1):

[0020]

[0021] In formula (1), Z is the number of impeller blades, D2 is the outer diameter of the impeller, D1 is the diameter of the water inlet of the swirl pump, and β b1 is the blade inlet angle, β b2 is the blade outlet angle.

[0022] Furthermore, the outer diameter of the impeller is calculated by formula (2):

[0023]

[0024] In formula (2), D2 is the outer diameter of the impeller, K is the empirical coefficient, the value range is 15-18, g is the acceleration of gravity, H is the head of the swirl pump, and n is the speed of the swirl pump.

[0025] Note: The impeller outer diameter obtained by the above method is suitable for the setting in this scheme.

[0026] Furthermore, the width of the bladeless cavity in the pump cavity is calculated by formula (3):

[0027] L=(0.25~0.35)D2 (3)

[0028] In formula (3), L is the width of the impeller chamber in the pump cavity, and D2 is the outer diameter of the impeller.

[0029] Note: The above spacing is more appropriate. If it exceeds this range, it may affect the internal flow of the vortex pump and thus affect the efficiency of the pump.

[0030] Furthermore, the inner wall structure of the water outlet is set to a conical diffuser tubular structure; the unilateral diffusion angle θ of the conical diffuser tubular structure satisfies Where D 出 is the outlet diameter of the vortex pump, F8 is the inlet area of ​​the conical expansion tubular structure, L 扩 is the length of the conical diffuser tubular structure.

[0031] Note: By setting the unilateral diffusion angle of the inner wall of the water outlet, hydraulic losses can be reduced: the design of the diffusion angle helps to smoothly guide the fluid to transition from the high-speed area (impeller outlet) to the low-speed area (pipeline), reducing the turbulence and friction losses of the fluid at the water outlet. By optimizing the diffusion angle, the backflow and vortex of the fluid at the water outlet can be reduced, thereby improving the overall efficiency of the pump; at the same time, the flow of the fluid at the water outlet is made more uniform, reducing local pressure fluctuations, reducing hydraulic losses and avoiding fluid impact, which can reduce the wear of the internal components of the pump and extend the service life of the pump.

[0032] Further, the bent wedge-shaped structure is:

[0033] Each blade comprises a main blade section near the center of the impeller and a bent section near the edge of the impeller, the axis of the main blade section passes through the center of the impeller, the axis of the bent section is 30° with the axis of the main blade section, the inclination angle of the blade side surface is 3-4°, and the inclination angle of the blade end face wedge is 1-2°;

[0034] Wherein, the main leaf segment occupies 2 / 3 to 3 / 4 of the total length of the leaf;

[0035] The axis of the main blade segment is a line parallel to and running through the length direction of the main blade segment;

[0036] The axis of the bending section is a line parallel to and running through the length direction of the bending section.

[0037] Description: Through the above-mentioned improved blade setting, the fluid flow can be guided more effectively, energy loss can be reduced, thereby improving the efficiency of the pump. At the same time, it helps the fluid to form a smoother streamline, reduce fluid separation and vortex, improve fluid dynamics, enhance anti-cavitation ability, and optimize energy conversion.

[0038] Furthermore, the inclination angle of the blade side is set to 3-4°, that is, the angle formed by connecting the blade end point at the center of the impeller and the blade end point at the edge of the impeller with the vertical direction is 3-4°;

[0039] The inclination angle of the blade end wedge is 2°, that is, the angle between the blade end edge and the axis of the main blade section is 2°.

[0040] Furthermore, the width b2 of the blade at the edge of the impeller satisfies: Where b2 is the width of the blade at the edge of the impeller, D2 is the impeller diameter, and n is s is the rotation speed.

[0041] Note: The above setting can reduce the vortex loss at the leading edge of the blade.

[0042] Furthermore, the water pressure chamber is configured as an annular water pressure chamber.

[0043] Description: The annular water pressure chamber mentioned above has the characteristics of increased flow head curve and high efficiency value at the highest efficiency point.

[0044] Further, the gap e between the outer diameter of the impeller and the highest point of the pump chamber is: e=(0.1-0.3)D2; the highest point of the pump chamber refers to the inner wall of the pump chamber on the same plane as the impeller;

[0045] The gap between the bottom end face of the blade and the front end of the pump body is maintained at 3 to 6 mm; the bottom end face of the blade refers to the end face installed with the impeller disk of the impeller, and the front end of the pump body refers to the inner wall of the pump cavity facing the bottom end face of the blade.

[0046] Note: By setting the above-mentioned gap, the backflow and vortex of the fluid at the water outlet can be reduced, thereby improving the overall efficiency of the pump; in addition, the leakage of the fluid between the impeller and the pump chamber can be reduced, thereby improving the efficiency of the pump; at the same time, the friction between the impeller and the pump chamber can be reduced, the pressure distribution can be optimized, and the risk of cavitation can be reduced.

[0047] The beneficial effects of the present invention are:

[0048] The design method of the present invention can improve the occurrence of flow channel diffusion between blades of the swirl pump, avoid flow turbulence between blades, and thus improve the efficiency of the pump. Through the settings of the blade shape and other settings, it can more effectively guide the fluid flow while improving the head and efficiency, reduce the energy loss caused by the vortex at the leading edge of the blade, and at the same time help the fluid to form smoother streamlines, reduce fluid separation and vortices, improve fluid dynamics performance, enhance anti-cavitation ability, and optimize energy conversion. BRIEF DESCRIPTION OF THE DRAWINGS

[0049] Figure 1 is a schematic structural diagram of a swirl pump according to an embodiment of the present invention;

[0050] Figure 2 is a two-dimensional front view of a swirl pump according to an embodiment of the present invention;

[0051] Figure 3 is a two-dimensional front view of the swirl pump impeller of an embodiment of the present invention;

[0052] Figure 4 is a diagram of the shape of an impeller blade according to an embodiment of the present invention;

[0053] Figure 5 Schematic diagram of the gap between the bottom end surface of the blade and the front end of the pump body in an embodiment of the present invention;

[0054] Figure 6 2 is a schematic diagram showing the principle of the width of the bladeless cavity and the relative position of the impeller in an embodiment of the present invention;

[0055] 1- pump body, 2- pump cover, 3- impeller, 4- pump shaft, 5- sealing ring, 6- impeller bolt, 7- bearing, 8- bearing body, 9- bearing cover, 10- bracket, 11- keyway, 12- mechanical seal ring, 100- water inlet, 110- water outlet, 120- pump chamber, 130- partition, 300- blade, 310- wheel disc, 320- balance hole, 330- wheel hub. DETAILED DESCRIPTION

[0056] In order to further illustrate the method adopted by the present invention and the effect achieved, the technical solution of the present invention will be clearly and completely described in combination with experiments below.

[0057] The working principle of the vortex pump is that when the impeller rotates, the energy of the medium increases due to the centrifugal force, and the medium entering between the blades is pushed by the blades and moves with the impeller. The medium near the top of the impeller outlet forms a through flow due to the large centrifugal force, and the medium in the middle of the impeller forms a circulating flow. The through flow flows out through the pump cavity outlet, forming a certain head; the solid particles and fibers in the medium gain energy under the action of the circulating flow, and most of them do not pass through the impeller, but move in the bladeless cavity and are discharged through the pump outlet, thereby achieving the purpose of conveying complex media or fluids containing impurities.

[0058] Compared with other pumps, vortex pumps have the advantages of good blocking performance and good pump suction performance. However, due to the existence of circulating flow, the internal hydraulic loss is large, the pump efficiency is basically below 60% and its dimensionless specific speed range is 60 to 130. Therefore, its efficiency is low and the head needs to be improved.

[0059] In this regard, the embodiments of the present invention can solve the above-mentioned problems of low efficiency and low head by designing the structure and parameters of the vortex pump; the details are as follows:

[0060] Embodiment 1: A method for designing a high-lift vortex pump, comprising the following steps:

[0061] S1. Design the swirl pump structure;

[0062] The vortex pump comprises a horizontally arranged pump body 1, a horizontally arranged pump shaft 4, an impeller 3 located inside the pump body 1 and mounted on the pump shaft 4, a bearing body 8 sleeved on the pump shaft 4 and rotatably connected to the pump shaft 4 through a bearing 7, and a bracket 10 assembled and connected to the bearing body 8; the pump body 1 is provided with a water inlet for water inlet and a water outlet for water outlet, the impeller 3 is mounted on one end of the pump shaft 4 through an impeller bolt 6, and the other end of the pump shaft 4 is provided with a keyway 11; a pump cover 2 is assembled and connected to the pump body 1, and a sealing ring 5 is provided between the pump body 1 and the pump cover 2; one end of the bearing body 8 is connected to the other end of the pump cover 2, and the other end of the bearing body 8 is provided with a bearing gland 9;

[0063] The pump chamber of the swirl pump is configured to protrude outward, and the protruding direction is the direction of the water inlet side of the swirl pump;

[0064] The blade shape on the impeller 3 of the swirl pump is set to a bent wedge shape, the thickness of the blade located at the center of the impeller 3 of the swirl pump is greater than the thickness of the blade located at the edge of the impeller 3, and the width of the blade located at the center of the impeller 3 is greater than the width of the blade located at the edge of the impeller 3;

[0065] S2, calculate the parameters of the swirl pump;

[0066] The swirl pump parameters include the number of blades of the impeller 3, the outer diameter of the impeller 3 and the width of the bladeless cavity in the pump cavity;

[0067] The number of blades of the impeller 3 is calculated by formula (1):

[0068]

[0069] In formula (1), Z is the number of impeller blades, D2 is the outer diameter of the impeller, D1 is the diameter of the water inlet of the swirl pump, and β b1 is the blade inlet angle, β b2 is the blade outlet angle.

[0070] The water inlet is arranged horizontally on the ground, the water outlet of the swirl pump is arranged vertically on the ground, and the number of blades of the impeller is 14.

[0071] The outer diameter of the impeller 3 is calculated by formula (2):

[0072]

[0073] In formula (2), D2 is the outer diameter of the impeller, K is the empirical coefficient, the value range is 15-18, g is the acceleration of gravity, H is the head of the swirl pump, and n is the speed of the swirl pump.

[0074] The width of the bladeless chamber in the pump chamber is calculated by formula (3):

[0075] L=(0.25~0.35)D2 (3)

[0076] In formula (3), L is the width of the impeller chamber in the pump cavity, and D2 is the outer diameter of the impeller.

[0077] The inner wall structure of the water outlet is set to a conical diffuser tubular structure; the unilateral diffusion angle θ of the conical diffuser tubular structure satisfies Where D 出 is the outlet diameter of the vortex pump, F8 is the inlet area of ​​the conical expansion tubular structure, L 扩 is the length of the tapered diffuser tubular structure;

[0078] The bent wedge-shaped structure is:

[0079] Each blade comprises a main blade section near the center of the impeller and a bent section near the edge of the impeller, the axis of the main blade section passes through the center of the impeller, the axis of the bent section is 30° with the axis of the main blade section, the inclination angle of the blade side surface is 3-4°, and the inclination angle of the blade end face wedge is 1-2°;

[0080] Wherein, the main leaf segment occupies 2 / 3 to 3 / 4 of the total length of the leaf;

[0081] The axis of the main blade segment is a line parallel to and running through the length direction of the main blade segment;

[0082] The axis of the bending section is a line parallel to and running through the length direction of the bending section.

[0083] The inclination angle of the blade side is set to 3-4°, that is, the angle formed by connecting the end point of the blade located at the center of the impeller and the end point of the blade located at the edge of the impeller with the vertical direction is 3-4°;

[0084] The inclination angle of the blade end wedge is 2°, that is, the angle between the blade end edge and the axis of the main blade section is 2°;

[0085] The width b2 of the blade at the edge of the impeller satisfies: Where b2 is the width of the blade at the edge of the impeller, D2 is the impeller diameter, and n is s is the rotation speed.

[0086] The water pressure chamber is set to be an annular water pressure chamber;

[0087] The gap e between the outer diameter of the impeller and the highest point of the pump chamber is set to: e=(0.1-0.3)D2; the highest point of the pump chamber refers to the inner wall of the pump chamber on the same plane as the impeller;

[0088] Keep the gap between the bottom end of the blade and the front end of the pump body at 3 to 6 mm (such as Figure 5 The middle arrow points to a gap); the bottom end face of the blade refers to the end face installed with the impeller disc of the impeller, and the front end of the pump body refers to the inner wall of the pump chamber facing the bottom end face of the blade.

[0089] The head of the vortex pump obtained by the above design method is stable at more than 289m, while the vortex pumps of the same type and specification in the prior art are difficult to achieve this head.

[0090] Experimental example

[0091] Based on the design method of Example 1, the present invention provides a vortex pump device such as Figure 1 As shown, the vortex pump of the present invention comprises a pump body 1, a pump cover 2, an impeller 3, a pump shaft 4, an impeller bolt 6, a bearing 7, a bearing body 8 and a bracket 10;

[0092] The pump body 1 is provided with a water inlet for water inlet and a water outlet for water outlet. The impeller 3 is located inside the pump body 1. The impeller 3 is mounted on one end of the pump shaft 4 through an impeller bolt 6. The other end of the pump shaft 4 is provided with a keyway 11. The pump body 1 is assembled and connected with one end of the pump cover 2, and the pump body 1 and the pump cover 2 are directly provided with a sealing ring 5.

[0093] The pump shaft 4 passes through the bearing body 8, and the pump shaft 4 is rotatably connected to the bearing body 8 through the bearing 7, the bearing body 8 is assembled and connected to the bracket 10, one end of the bearing body 8 is connected to the other end of the pump cover 2, and the other end of the bearing body 8 is provided with a bearing pressure cover 9;

[0094] like Figure 1 As shown, from Figure 1The pump body 1 is placed at the left end, and the axis of the pump body 1 coincides with the axis of the pump shaft 4; the pump cover 2 is connected to the pump body 1 through 24 hexagonal bolts; the impeller 3 is matched with the impeller key in the pump shaft through the impeller bolt 6 to fix the impeller 3 on the pump shaft 4;

[0095] The gap between the impeller 3 and the pump cover 2 is sealed by the sealing ring 5, which can reduce the wear of the pump cover and avoid leakage, thereby improving the volumetric efficiency; the pump cover 2 and the sealing ring 5 are connected by 12 hexagon socket head cylindrical screws; since the mechanical seal ring 12 has the advantages of less leakage and long life, the mechanical seal ring 12 is used on the pump shaft 4 of the impeller 3 and the pump cover 2; the bearing body 8 is installed on the pump shaft 4 through the bearing 7 and connected to the pump cover 2 through 12 hexagon socket head cylindrical screws. The hole at the lower end of the bearing body 8 and the hole at the upper end of the bracket 10 are connected by hexagon socket head cylindrical screws.

[0096] like Figure 1 As shown, the pump body 1 is provided with a pump chamber 120 protruding to the left, and the impeller 3 is fully extended into the pump chamber 120, until the width of the impeller chamber is 1 / 4 to 1 / 3 of the impeller blades. Figure 6 As shown in the diagram c, the through flow flows directly out through the impeller, reducing the circulating flow and the hydraulic loss caused by the circulating flow, and improving the pump head and efficiency.

[0097] like Figure 6 As shown in the figure, the relative positions of the bladeless cavity and the impeller 3 are divided into three types, the impeller 3 is completely retracted to the bladeless cavity, partially extended to the bladeless cavity, and fully extended to the bladeless cavity. The present invention selects the third mode c in the figure, from Figure 6 It can be seen that the bladeless chamber is a pump chamber 120 protruding to the left, which can avoid reducing blockage and reduce the circulating flow and water loss caused by the circulating flow, thereby improving the pump head and efficiency.

[0098] like Figure 1 As shown, the gap e between the outer diameter of the impeller 3 and the pump chamber 120 is 15 mm, and the gap between the bottom of the blade 300 and the front end surface of the pump cover is 3 to 6 mm, that is, the gap between the bottom end surface of the blade 300 and the front end of the pump body. The gap allows the fluid to flow smoothly to the front end surface of the pump cover without causing circulation loss, thereby improving the pump efficiency.

[0099] like Figure 2As shown, the water pressure chamber adopts an annular water pressure chamber, which has the characteristics of an increased flow head curve and a high efficiency value at the highest efficiency point. The water pressure type is divided into three types: spiral, quasi-spiral, and annular. For example, the present invention uses the same impeller to conduct experimental comparisons in three types of spiral, quasi-spiral, and annular water pressure chambers, and obtains the following findings: Spiral water pressure chamber: the flow head curve decreases, the power curve increases, the efficiency decreases, but the high efficiency range is wider. Quasi-spiral water pressure chamber: the flow head curve increases, the power curve decreases, and the efficiency is significantly improved. Annular water pressure chamber: the flow head curve is similar to that of the quasi-spiral water pressure chamber, the efficiency value of the highest efficiency point is high, and the high efficiency point moves toward the direction of small flow.

[0100] like Figure 2 As shown, the internal structure of the water outlet 110 opened on the inner wall of the upper end of the pump body 1 is a tapered diffuser structure, and the unilateral diffusion angle of the tapered diffuser is 5-6°; the water inlet 100 and the water outlet 110 of the pump body 1, the rear end of the pump body 1 and the front end of the pump cover 2 are connected to form a pump cavity 120. Among them, two partitions 130 are provided at the water inlet 100 of the pump body 1, and the thickness of the partition 130 gradually transitions from 12mm to 6mm from the edge of the pump body 1 to the center, and the length of the partition 130 is 105mm. Such a setting can reduce the turbulence of the inlet flow and improve the cavitation performance.

[0101] like Figure 3 As shown, the impeller 3 includes a hub 330 and a disk 310 connected to the inner side of the blade 300 and 14 blades 300 located on the front side of the disk 310, and the disk 310 is provided with 14 balancing holes 320. The hub 330 and the disk 310 connected to the inner side of the blade 300 are connected as a whole by a smooth arc; the above-mentioned balancing holes 320 can reduce the axial force and ensure the stability of the pump during operation.

[0102] like Figure 4 As shown, each blade 300 includes a main blade section and a bending section, and each blade starts to tilt at the second section at 2 / 3 to 3 / 4 of the total length of the blade to form a bending section; the main blade section blade bone line forms a first angle with the radial direction of the hub, that is, the axis of the main blade section is set through the center of the impeller, and the axis of the main blade section is a line parallel to the length direction of the main blade section. Therefore, the axis of the main blade section forms a first angle of 0° with the radial direction of the hub, and the first angle is 0°. The bending section extends obliquely in the same direction as the rotation direction of the impeller 3 and forms a second angle with the main blade section. The second angle is 30°, that is, the axis of the bending section is 30° with the axis of the main blade section.

[0103] The centrifugal force at the inlet end of the blade 300 close to the hub 330 is greater than the centrifugal force at the outlet end of the blade 300, so that the pressure of the liquid flow at the outlet 110 is greater than the pressure of the liquid flow at the inlet 100, and radial rotating radial flow is generated between the blades 300, so that a constant pressure high-lift drain pump characteristic can be obtained during drainage.

[0104] like Figure 3 and 4 As shown, the inner width of the blade 300 near the hub 330 is greater than the outer width of the blade 300, forming an inclination angle of 3° to 4°. The blade 300 is wedge-shaped, and the inclination angle of the inclined surface of the wedge 300 is 1° to 2°, preferably 2°. Two adjacent blades 300 construct the flow channel of the impeller 3. The above-mentioned wedge shape can, on the one hand, reduce the thickness of the blade, increase the head and efficiency of the pump, and on the other hand, reduce the vortex loss at the leading edge of the blade.

[0105] like Figure 3 and Figure 4 As shown, the number of blades is preferably 14. Generally speaking, the flow channel diffusion between the 300 blades of the swirl pump is very serious. When slip is not considered, the relative velocity is equal to the axial velocity, so the diffusion of the relative velocity is also very serious. The axial vortex flow between the 300 blades is very strong, causing the flow turbulence between the 300 blades, and thus generating considerable additional hydraulic losses. The number of 14 blades and the wedge-shaped blades are equivalent to increasing the number of blades and reducing the thickness of the blades, which greatly improves the head and efficiency of the pump.

[0106] In addition, in the existing technology, the number of blades generally does not exceed 10, and exceeding 10 may cause poor pump efficiency and head. However, this study found that the efficiency of the 14-blade pump designed by the present invention has not decreased. It can be seen that the head and efficiency data corresponding to different numbers of blades in the following Table 1 are higher than the average level; and the front and rear cover plates are not set in this solution, and the probability of clogging is small; this embodiment is an open impeller, and the corresponding maintenance cost and process are relatively simple compared to traditional centrifugal pumps.

[0107] Table 1 Head and efficiency of swirl pumps with various blade numbers

[0108] Number of blades Speed ​​(r / min) <![CDATA[Flow rate (m 3 / h)]]> Lift(m) efficiency(%) 7 2950 130 240.18 47.52 10 2950 130 262.78 51.42 14 2950 130 289.32 61.89

[0109] The above embodiments are not limitations of the present invention. Ordinary technicians in the relevant technical field can make various changes and modifications without departing from the spirit and scope of the present invention. Therefore, all equivalent technical solutions should also fall within the scope of the present invention. The patent protection scope of the present invention should be defined by the claims.

Claims

1. A method for designing a high-lift swirl pump, characterized in that: The following steps are involved: S1. Design the structure of the swirl pump: The vortex pump comprises a horizontally arranged pump body (1), a horizontally arranged pump shaft (4), an impeller (3) located inside the pump body (1) and mounted on the pump shaft (4), and a bearing body (8) sleeved on the pump shaft (4) and rotatably connected to the pump shaft (4) via a bearing (7); The pump chamber (3) of the vortex pump is arranged to protrude outward, and the protruding direction is consistent with the water inlet direction of the vortex pump; The blades on the impeller (3) of the swirl pump are in the shape of a bent wedge, and the thickness of the blades located at the center of the impeller (3) of the swirl pump is greater than the thickness of the blades located at the edge of the impeller, and the width of the blades located at the center of the impeller (3) is greater than the width of the blades located at the edge of the impeller (3); S2. Calculate the parameters of the swirl pump: The swirl pump parameters include the number of impeller blades, the outer diameter of the impeller, and the width of the bladeless cavity in the pump cavity; First, the number of blades of the impeller (3) is calculated based on the outer diameter of the impeller (3), the diameter of the water suction port of the swirl pump, the blade inlet angle, and the blade outlet angle; Then, the outer diameter of the impeller (3) is calculated according to the head of the swirl pump and the rotation speed of the swirl pump; Finally, the impeller-free width of the pump cavity is calculated based on the outer diameter of the impeller (3).

2. A high-lift vortex pump design method as claimed in claim 1, characterized in that: The water inlet of the swirl pump is parallel to the horizontal plane, the water outlet of the swirl pump is perpendicular to the ground, and the impeller has 14 blades.

3. A high-lift vortex pump design method as claimed in claim 2, characterized in that: The number of blades of the impeller (3) is calculated by formula (1): In formula (1), Z is the number of impeller blades, D2 is the outer diameter of the impeller, D1 is the diameter of the water inlet of the swirl pump, and β b1 is the blade inlet angle, β b2 is the blade outlet angle.

4. A high-lift vortex pump design method as claimed in claim 2, characterized in that: The outer diameter of the impeller (3) is calculated by formula (2): In formula (2), D2 is the outer diameter of the impeller, K is the empirical coefficient, the value range is 15-18, g is the acceleration of gravity, H is the head of the swirl pump, and n is the speed of the swirl pump.

5. A high-lift vortex pump design method as claimed in claim 2, characterized in that: The width of the bladeless chamber in the pump chamber is calculated by formula (3): L=(0.25~0.35)D2 (3) In formula (3), L is the width of the impeller chamber in the pump cavity, and D2 is the outer diameter of the impeller.

6. A high-lift vortex pump design method as claimed in claim 2, characterized in that: The inner wall structure of the water outlet is a conical diffuser tubular structure; the unilateral diffusion angle θ of the conical diffuser tubular structure satisfies Where D 出 is the outlet diameter of the vortex pump, F8 is the inlet area of ​​the conical expansion tubular structure, L 扩 is the length of the conical diffuser tubular structure.

7. A high-lift vortex pump design method as claimed in claim 2, characterized in that: The bent wedge-shaped structure is: Each blade comprises a main blade section near the center of the impeller and a bent section near the edge of the impeller, the axis of the main blade section passes through the center of the impeller, the axis of the bent section is 30° with the axis of the main blade section, the inclination angle of the blade side surface is 3-4°, and the inclination angle of the blade end face wedge is 1-2°; Wherein, the main leaf segment occupies 2 / 3 to 3 / 4 of the total length of the leaf; The axis of the main blade segment is a line parallel to and running through the length direction of the main blade segment; The axis of the bending section is a line parallel to and running through the length direction of the bending section.

8. A method for designing a high-lift vortex pump as claimed in claim 7, characterized in that: The width b2 of the blade at the edge of the impeller satisfies: Where b2 is the width of the blade at the edge of the impeller, D2 is the impeller diameter, and n is s is the rotation speed.

9. A high-lift vortex pump design method as claimed in claim 2, characterized in that: The water pressure chamber is an annular water pressure chamber.

10. A high-lift vortex pump design method as claimed in claim 2, characterized in that: The clearance e between the outer diameter of the impeller and the highest point of the pump chamber is: e=(0.1-0.3)D2; the highest point of the pump chamber refers to the inner wall of the pump chamber on the same plane as the impeller; The gap between the bottom end face of the blade and the front end of the pump body is maintained at 3 to 6 mm; the bottom end face of the blade refers to the end face installed with the impeller disk of the impeller, and the front end of the pump body refers to the inner wall of the pump cavity facing the bottom end face of the blade.

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