Centrifugal hydraulic fan

Abstract

The invention relates to a centrifugal hydraulic fan which comprises a pump body provided with a first cavity, the first cavity is provided with an axial first opening, and the cavity wall of the first cavity is provided with a water inlet and a water outlet; the pump cover is used for blocking the first opening; the hydraulic impeller is rotatably arranged in the first cavity; the pump shaft is connected with the hydraulic impeller; the wind impeller is connected with the pump shaft; the hydraulic impeller comprises a front cover plate and a rear cover plate, a hydraulic impeller outlet is formed in the center of the front cover plate, a plurality of first hydraulic blades are arranged between the front cover plate and the rear cover plate, a hydraulic impeller inlet is formed between the front cover plate and the rear cover plate, and a pressure relief hole is formed in the rear cover plate and used for balancing pressure on the two sides of the rear cover plate. The centrifugal hydraulic fan has the following advantages that due to the design of the pressure relief holes, water flow can enter the other side of the rear cover plate from one side of the rear cover plate through the pressure relief holes, it is guaranteed that the pressure on the two sides of the rear cover plate is kept balanced, the rotating resistance of the hydraulic impeller is reduced, and the working efficiency is guaranteed.

Description

Technical Field

[0001] The present invention relates to the technical field of hydraulic application, in particular to a centrifugal hydraulic fan. Background Art

[0002] In the prior art, when a centrifugal hydraulic fan is working, the water flow drives the hydraulic impeller to rotate, which in turn drives the wind blades to rotate. However, the water flow presses the hydraulic impeller inward, resulting in an unbalanced pressure on both sides of the hydraulic impeller, which increases the rotational resistance of the hydraulic impeller and reduces the working efficiency of the hydraulic impeller. Summary of the Invention

[0003] An object of the present application is to provide a centrifugal hydraulic fan that can maintain the working efficiency of the hydraulic impeller.

[0004] The technical solution adopted in this application is: a centrifugal hydraulic fan, comprising: The pump body is provided with a first cavity with a circular cross section, the first cavity is provided with a first axial opening, and the cavity wall of the first cavity is provided with a water inlet and a water outlet; a pump cover, used to seal the first opening and detachably connected to the pump body; a hydraulic impeller rotatably disposed in the first cavity and coaxially arranged with the first cavity; Pump shaft, connected to the hydraulic impeller; A wind impeller connected to the pump shaft; A second axial opening is provided on the pump cover, and the pump shaft is passed through the second opening; the hydraulic impeller includes a front cover plate and a rear cover plate, a hydraulic impeller outlet is provided at the center of the front cover plate, the hydraulic impeller outlet is connected with the water outlet, a plurality of first hydraulic blades are provided between the front cover plate and the rear cover plate, a hydraulic impeller inlet is formed between the front cover plate and the rear cover plate, the hydraulic impeller inlet is connected with the water inlet, and a pressure relief hole is provided on the rear cover plate, which is used to balance the pressure on both sides of the rear cover plate.

[0005] Compared with the existing technology, the advantage of this application lies in the design of the pressure relief hole, which allows water to flow from one side of the rear cover plate through the pressure relief hole into the other side of the rear cover plate, ensuring that the pressure on both sides of the rear cover plate remains balanced, reducing the rotational resistance of the hydraulic impeller, and ensuring work efficiency.

[0006] In some embodiments of the present application, a water guide groove is provided on the first cavity, and the water guide groove is arranged around the cavity wall of the first cavity. The top of the water guide groove is open and connected to the first cavity. The width of the top opening of the water guide groove is the same as the width of the hydraulic impeller inlet, and the water inlet is connected to the water guide groove; the cross-sectional area of ​​the water guide groove gradually decreases from the outside to the inside; the cross-sectional area of ​​the water guide groove gradually decreases along the circumference of the first cavity, and the cross-sectional area at the connection between the water guide groove and the water inlet is the largest.

[0007] Furthermore, the water inlet direction of the water inlet is tangent to the bottom of the water guide groove; the water inlet is located above the center of the hydraulic impeller; and the highest point of the hydraulic impeller inlet is higher than the lowest point of the water inlet.

[0008] In some embodiments of the present application, the first hydraulic blades are arranged perpendicular to the front cover plate, and extend from the outermost side of the front cover plate or the outermost side of the rear cover plate toward the center; the plurality of first hydraulic blades are in a vortex shape toward the outlet of the hydraulic impeller.

[0009] In some embodiments of the present application, a second hydraulic blade is provided between adjacent first hydraulic blades, and the second hydraulic blade extends from the outermost side of the front cover plate or the outermost side of the rear cover plate toward the center; the second hydraulic blade is in a vortex shape toward the hydraulic impeller outlet.

[0010] In some embodiments of the present application, the pump body is provided with an outwardly extending water inlet pipe, the water inlet pipe is provided with a water inlet channel, the water inlet channel is connected to the water inlet through a conical surface, and the radial cross-sectional area of ​​the conical surface gradually increases from the inside to the outside; the pump body is provided with an outwardly extending water outlet pipe, the water outlet pipe is provided with a water outlet channel, the water outlet channel is connected to the water outlet, and the radial cross-sectional area of ​​the water outlet channel gradually increases from the inside to the outside.

[0011] In some embodiments of the present application, a mounting sleeve is provided on the rear cover plate, and the mounting sleeve is connected to the pump shaft; a step is provided on the pump shaft, and a shaft sleeve is provided on the pump shaft, one end of the shaft sleeve abuts the mounting sleeve, and the other end abuts the step; a mechanical seal is used between the pump cover and the shaft sleeve.

[0012] In some embodiments of the present application, a second cavity is provided on the pump cover, and the second cavity is connected to the first cavity through a pressure relief hole.

[0013] In some embodiments of the present application, the wind impeller includes a wind blade and a connecting sleeve, the inner side of the wind blade is connected to the connecting sleeve, and the connecting sleeve is connected to the pump shaft.

[0014] In some embodiments of the present application, a bearing box is provided between the pump cover and the wind impeller, one end of the bearing box is connected to the pump cover, and the other end is provided with a bearing cover, the bearing cover and the bearing box are detachably connected, a third opening is provided on the bearing cover, and the pump shaft is passed through the third opening; a bearing is provided between the pump shaft and the bearing box, and both sides of the bearing are respectively abutted against the pump shaft and the bearing box; and an outwardly extending mounting foot is provided on the pump body.

[0015] In some embodiments of the present application, the diameter D of the hydraulic impeller outlet is j =54.9mm, the diameter of the rear cover D2=265mm, the width of the hydraulic impeller inlet b2=8mm, the inlet angle β2 of the first hydraulic blade=31°, the outlet angle β1 of the first hydraulic blade=31°, and eight first hydraulic blades are provided.

[0016] In some embodiments of the present application, the pump body is a volute, the first cavity is a volute chamber, the base circle diameter D3 of the first cavity is 275 mm, the inlet width b3 of the first cavity is 8 mm; a tongue is provided in the first cavity, and the placement angle of the tongue is =25°. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 is a schematic structural diagram of embodiment 1 of the present invention; Figure 2 is a cross-sectional view of Example 1 of the present invention; Figure 3 yes Figure 2 Cross-sectional view in the AA direction; Figure 4 This is a schematic structural diagram of a hydraulic impeller according to embodiment 1 of the present invention; Figure 5 is a cross-sectional view of a hydraulic impeller according to embodiment 1 of the present invention; Figure 6 is a cross-sectional view of a pump body according to embodiment 1 of the present invention; Figure 7 is a cross-sectional view of the cochlear chamber of Example 1 of the present invention; Figure 8 The embodiment 1 of the present invention is at a flow rate of 30m 3 / h state of the middle section pressure distribution cloud diagram; Figure 9 The embodiment 1 of the present invention is at a flow rate of 25m 3 / h state of the middle section pressure distribution cloud diagram; Figure 10 The embodiment 1 of the present invention is at a flow rate of 30m 3 / h state of the middle section velocity streamline diagram; Figure 11 The embodiment 1 of the present invention is at a flow rate of 25m 3 Velocity streamline diagram of the middle section under the condition of / h; Figure 12 The embodiment 1 of the present invention is at a flow rate of 30m 3 / h state of the flow field velocity distribution cloud diagram of the middle section; Figure 13 The embodiment 1 of the present invention is at a flow rate of 25m 3 / h state of the flow field velocity distribution cloud diagram of the middle section; Figure 14 This is the external characteristic curve of Example 1 of the present invention at 1500 r / min.

[0018] In the figure: 1. Pump body; 2. First cavity; 3. First opening; 4. Water inlet; 5. Water outlet; 6. Pump cover; 7. Hydraulic impeller; 8. Pump shaft; 9. Wind impeller; 10. Second opening; 11. Front cover; 12. Rear cover; 13. Hydraulic impeller outlet; 14. First hydraulic blade; 15. Hydraulic impeller inlet; 16. Pressure relief hole; 17. Water guide groove; 18. Second hydraulic blade; 19. Water inlet pipe; 20 , water inlet channel; 21. Conical surface; 22. Water outlet pipe; 23. Water outlet channel; 24. Mounting sleeve; 25. Step; 26. Bushing; 27. Second cavity; 28. Wind blade; 29. ​​Connecting sleeve; 30. Bearing box; 31. Bearing cover; 32. Third opening; 33. Bearing; 34. Mounting foot; 35. Stationary ring assembly; 36. Dynamic ring assembly; 37. Inlet flange; 38. Outlet flange; 39. Partition tongue. DETAILED DESCRIPTION

[0019] In order to further illustrate the technical means and effects adopted by the present invention to achieve the predetermined purpose of the invention, the specific implementation methods, structures, features and effects of the present invention are described in detail below in conjunction with the accompanying drawings and preferred embodiments.

[0020] Example 1: This embodiment provides a centrifugal hydraulic fan, such as Figure 1-Figure 5 As shown, including: The pump body 1 is provided with a first cavity 2 with a circular cross section, the first cavity 2 is provided with a first axial opening 3, and the cavity wall of the first cavity 2 is provided with a water inlet 4 and a water outlet 5; A pump cover 6 is used to seal the first opening 3 and is detachably connected to the pump body 1; The hydraulic impeller 7 is rotatably disposed in the first cavity 2 and is coaxially arranged with the first cavity 2; The pump shaft 8 is connected to the hydraulic impeller 7; The wind impeller 9 is connected to the pump shaft 8; A second axial opening 10 is provided on the pump cover 6, and the pump shaft 8 is passed through the second opening 10; the hydraulic impeller 7 includes a front cover plate 11 and a rear cover plate 12, and a hydraulic impeller outlet 13 is provided at the center of the front cover plate 11, and the hydraulic impeller outlet 13 is communicated with the water outlet 5, and a plurality of first hydraulic blades 14 are provided between the front cover plate 11 and the rear cover plate 12, and a hydraulic impeller inlet 15 is formed between the front cover plate 11 and the rear cover plate 12, and the hydraulic impeller inlet 15 is communicated with the water inlet 4, and a pressure relief hole 16 is provided on the rear cover plate 12, and the pressure relief hole 16 is used to balance the pressure on both sides of the rear cover plate 12.

[0021] The design of the pressure relief hole 16 allows water to flow from one side of the rear cover plate 12 through the pressure relief hole 16 into the other side of the rear cover plate 12, ensuring that the pressure on both sides of the rear cover plate 12 remains balanced, reducing the lateral pressure on the hydraulic impeller 7, and thereby reducing the rotational resistance of the hydraulic impeller 7 and improving work efficiency.

[0022] In order to ensure reliable water inlet, a water guide groove 17 is provided on the first cavity 2, and the water guide groove 17 is arranged around the cavity wall of the first cavity 2. The top of the water guide groove 17 is open and connected to the first cavity 2. The width of the top opening of the water guide groove 17 is the same as the width of the hydraulic impeller inlet 15, so that most of the water flow is used to drive the hydraulic impeller 7, so that its energy utilization rate of the water flow is high, and the water inlet 4 is connected to the water guide groove 17; the cross-sectional area of ​​the water guide groove 17 gradually decreases from the outside to the inside, so that the water flow velocity flowing out of the top opening of the water guide groove 17 is large, increasing the driving force on the hydraulic impeller 7; the cross-sectional area of ​​the water guide groove 17 gradually decreases along the circumference of the first cavity 2, and the cross-sectional area of ​​the water guide groove 17 is the largest at the connection between the water guide groove 17 and the water inlet 4, ensuring the water flow velocity at the end of the water guide groove 17, so that the water flow flowing out of the end water guide groove 17 also has a driving force on the hydraulic impeller 7. The design of the water guide groove 17 ensures that the water entering from the water inlet 4 will first enter the water guide groove 17. The water guide groove 17 guides the water flow to flow around the wall of the first cavity 2. At the same time, part of the water flows out from the top opening of the water guide groove 17 to drive the hydraulic impeller 7 to rotate. That is, the outflowing water pushes the hydraulic impeller 7 around the circumference of the hydraulic impeller 7, with a large pushing range and balanced pushing force.

[0023] In order to ensure reliable water inlet, the water inlet direction of the water inlet 4 is tangent to the bottom of the water guide groove 17 to ensure smooth water inlet; the water inlet 4 is located above the center of the hydraulic impeller 7, so that the incoming water flow will also flow downward, utilizing gravitational potential energy; the highest point of the hydraulic impeller inlet 15 is higher than the lowest point of the water inlet 4.

[0024] To ensure the reliability of the hydraulic impeller 7, the first hydraulic blades 14 are arranged perpendicular to the front shroud 11, extending from the outermost side of the front shroud 11 or the outermost side of the rear shroud 12 toward the center. The plurality of first hydraulic blades 14 are arranged in a spiral shape toward the hydraulic impeller outlet 13. In this embodiment, the front shroud 11 and the rear shroud 12 have the same diameter, that is, the first hydraulic blades 14 extend from the outermost side of the front shroud 11 and the rear shroud 12 toward the center.

[0025] To ensure the reliability of the hydraulic impeller 7, a second hydraulic blade 18 is provided between adjacent first hydraulic blades 14. The second hydraulic blade 18 extends from the outermost side of the front cover plate 11 or the outermost side of the rear cover plate 12 toward the center; the second hydraulic blade 18 is in a vortex shape toward the hydraulic impeller outlet 13.

[0026] To ensure reliable water inlet, the pump body 1 is provided with an outwardly extending water inlet pipe 19, which is provided with a water inlet channel 20. This water inlet channel 20 communicates with the water inlet 4 via a conical surface 21, the radial cross-sectional area of ​​which gradually increases from the inside outward. The cross-sectional area of ​​the water inlet channel 20 is larger than that of the water inlet 4, ensuring a sufficient water flow rate. The design of the conical surface 21 increases the water inlet pressure, thereby enhancing the driving force of the water flow on the hydraulic impeller 7.

[0027] To ensure reliable water flow, the pump body 1 is provided with an outwardly extending water outlet pipe 22. The water outlet pipe 22 is provided with a water outlet channel 23. The water outlet channel 23 is connected to the water outlet 5. The radial cross-sectional area of ​​the water outlet channel 23 gradually increases from the inside to the outside. The cross-sectional area of ​​the water outlet channel 23 is larger than that of the water outlet 5 to ensure the water flow rate.

[0028] In this embodiment, the outer end of the water inlet pipe 19 is provided with an inlet flange 37, which can be easily connected to the external water inlet pipe; the outer end of the water outlet pipe 22 is provided with an outlet flange 38, which can be easily connected to the external water outlet pipe.

[0029] To ensure the reliability of the rear cover plate 12, a mounting sleeve 24 is provided on the rear cover plate 12, which is connected to the pump shaft 8. A step 25 is provided on the pump shaft 8, and a shaft sleeve 26 is sleeved on the pump shaft 8. One end of the shaft sleeve 26 abuts the mounting sleeve 24, and the other end abuts the step 25. A mechanical seal is used between the pump cover 6 and the shaft sleeve 26. Specifically, the mechanical seal includes a stationary ring assembly 35 and a dynamic ring assembly 36. The stationary ring assembly 35 is fixedly connected to the pump cover 6 and sleeved on the shaft sleeve 26. The dynamic ring assembly 36 is arranged between the stationary ring assembly 35 and the rear cover plate 12 and sleeved on the shaft sleeve 26. The mechanical seal has good sealing performance.

[0030] To facilitate installation, the pump cover 6 is provided with a second cavity 27, which communicates with the first cavity 2 via the pressure relief hole 16. The second cavity 27 is used to install a mechanical seal to ensure a reliable seal between the pump shaft 8 and the pump cover 6; the pressure relief hole 16 communicates with the second cavity 27 to ensure the pressure relief effect of the pressure relief hole 16.

[0031] In order to ensure the reliability of the wind impeller 9, the wind impeller 9 includes a wind blade 28 and a connecting sleeve 29. The inner side of the wind blade 28 is connected to the connecting sleeve 29, and the connecting sleeve 29 is connected to the pump shaft 8. The wind blade 28 is used to rotate to generate wind power.

[0032] For reliable connection, a bearing box 30 is provided between the pump cover 6 and the wind impeller 9. One end of the bearing box 30 is connected to the pump cover 6, and the other end is provided with a bearing cover 31. The bearing cover 31 is detachably connected to the bearing box 30. The bearing cover 31 is provided with a third opening 32, and the pump shaft 8 is passed through the third opening 32. A bearing 33 is provided between the pump shaft 8 and the bearing box 30, and the two sides of the bearing 33 are respectively in contact with the pump shaft 8 and the bearing box 30. The pump body 1 is provided with mounting feet 34 extending outward. The design of the bearing box 30 can improve protection and prevent debris from entering and contacting the pump shaft 8. The design of the bearing 33 can make the rotation of the pump shaft 8 smoother, and the support of the bearing box 30 on the bearing 33 further supports the pump shaft 8. The mounting feet 34 can facilitate installation.

[0033] In this embodiment, the rated design parameters of the centrifugal hydraulic fan are shown in Table 1 below: Table 1 flow Maximum recovery head Speed Shaft power Maximum outer diameter Design pressure medium 28m3 / h <90 m 1500 r / min 2.5kW 805mm 4Mpa 25° clean water The water inlet pipe diameter of the water inlet channel 20 is 80 mm, and the water outlet pipe diameter of the water outlet channel 23 is 80 mm.

[0034] The diameter D of the hydraulic impeller outlet 13 j Determination: Calculate the effective diameter D0 of the impeller inlet, taking Q = 28m 3 / h, n=1500 rpm, K0=3.9, we get:

[0035]

[0036] where d h is the impeller hub diameter. The hub diameter is not considered here and is taken as 0, so:

[0037] Determination of the diameter D2 of the rear cover plate 12:

[0038] where K D Taking 15.3, we get:

[0039] Determination of the width b2 of the hydraulic impeller inlet 15:

[0040] where k b Taking 0.46, we get:

[0041] Take b2=8mm.

[0042] The inlet angle β2 of the first hydraulic blade 14 is set to 31°, and the outlet angle β1 of the first hydraulic blade 14 is set to 31°.

[0043] Determination of the number of blades Z of the hydraulic impeller 7:

[0044] Among them, R2-R1 is the expanded length of the center line of the impeller flow channel axial projection, is the radius of the center of gravity of the median, is the average value of the blade inlet and outlet angles, K is the empirical coefficient, and here K=4.4.

[0045] From the known parameters, we can conclude that: R2-R1=0.0583m, R2+R1=0.2067m.

[0046]

[0047] Eight first hydraulic blades 14 are provided, and eight second hydraulic blades 18 are provided. The maximum thickness of the first hydraulic blades 14 and the second hydraulic blades 18 is 6.1 mm.

[0048] like Figure 6 As shown, in this embodiment, the pump body 1 is a volute, the first cavity 2 is a volute chamber; a partition tongue 39 is provided in the first cavity 2; and the water inlet pipe 19 is a volute chamber contraction pipe.

[0049] The cross-sectional shape of the volute chamber includes rectangular, pear-shaped, trapezoidal and circular. The cross-sectional shape of the volute chamber has little effect on the performance and can be selected based on the structure and manufacturing convenience. In this embodiment, a trapezoidal volute chamber is used.

[0050] To facilitate calculation and drawing, Figure 7 As shown in the figure, the volute chamber is usually cut into 8 sections at 45 degrees to each other. That is, the volute chamber is cut into 8 axial planes to determine the shape and area of ​​each section. When designing, the 8th section is calculated first, and the other sections are determined based on the 8th section.

[0051] The circle cut at the starting point of the helical line in section 8 (or at the tip of the tongue 39) is called the base circle. There should be a certain clearance between the base circle and the hydraulic impeller 7. Too small a clearance can easily cause noise and vibration due to flow blockage. A larger clearance can reduce flow unevenness around the positive guide vanes, lowering noise and vibration and slightly improving efficiency. In this embodiment, the base circle diameter of the first cavity 2 is D3 = 275 mm.

[0052] The inlet width b3 of the first cavity 2 is usually larger than the width b2 of the hydraulic impeller inlet 15 , and usually b3=b2+(5-10). In this embodiment, the inlet width of the first cavity 2 is b3=8 mm.

[0053] The tongue 39 is located at the beginning or slightly behind the beginning of the spiral part of the vortex chamber, separating the spiral part from the contraction tube. The section through the head of the tongue 39 is usually called the 0 section, and the angle between the tongue 39 and the 8th section is the tongue placement angle, which is expressed as express. The size of the spacer 39 should ensure smooth connection between the spiral portion and the shrink tube, and minimize the radial size. =25°.

[0054] The outlet of the contraction tube can be approximately considered as the 8th section of the volute chamber. The main structural parameters of the contraction tube are: the suction diameter D of the water inlet pipe 19 d =50mm, the height L of the water inlet pipe 19 = 345mm, and the diffusion angle θ of the water inlet pipe 19 is 7°~13°.

[0055] In this embodiment, the developed hydraulic turbine has a specific speed of only 20, which is an ultra-low specific speed type.

[0056] like Figure 8 、 Figure 9 As shown, at a flow rate of 30m 3 / h and flow rate 25m 3 / h There is no obvious high-pressure area in the hydraulic impeller 7 area under the two operating points, and the pressure distribution in the entire flow area is uniform.

[0057] like Figure 10 、 Figure 11 As shown, at a flow rate of 30m 3 / h and flow rate 25m 3 / h Under the two operating points, the velocity streamline distribution inside the pump body 1 and the water inlet pipe 19 is very uniform, while the velocity streamline distribution inside the hydraulic impeller 7 is not uniform enough. This is due to the dynamic and static interference between the pump body 1 and the hydraulic impeller 7 on the inlet section of the hydraulic impeller 7.

[0058] like Figure 12 、 Figure 13 As shown, due to the interference between dynamic and static, a non-uniform flow field can still be observed in the hydraulic impeller 7. Since the designed hydraulic turbine has an ultra-low specific speed, the width of the hydraulic impeller outlet 13 is relatively small, and the appearance of high-pressure fluid can also be observed at each section of the pump body 1. However, the internal flow field of the hydraulic impeller 7 is relatively uniform as a whole, thereby ensuring that the flow conditions in the turbine are more stable.

[0059] Table 2 shows the theoretically calculated values ​​of the axial force acting on the hydraulic turbine under different operating conditions. As can be seen, within a given flow range, the axial force acting on hydraulic impeller 7 initially increases, reaching a maximum of 443.68 N at around 28 m³, before decreasing to 328.55 N at 33.6 m³. This is related to the angle at which the liquid exits hydraulic impeller 7. Comparing theoretical formulas with calculations shows that the axial force acting on hydraulic impeller 7 is very small, having minimal impact on turbine operation and resolving the issue of unstable operation at ultra-low specific speeds.

[0060] Table 2 Flow rate Q / / h 22.4 28 33.6 F / N 305.558 443.68 328.55 Table 3 shows the CFD calculation results of the efficiency, shaft power and recovery pressure head of the designed turbine at different flow rates at 1500r / min. Figure 14 It can be seen that the developed turbine has a given parameter range of 25m 3 / h to 30m 3 / h range, its output power fully meets the shaft power required to drive the wind impeller 9. At the same time, the theoretically predicted efficiency is relatively high in the turbine operating range, breaking through the difficulty of the narrow high-efficiency zone of ultra-low specific speed hydraulic turbines. 3 Although it is less than 2.5kW at 1000 rpm / h, the wind impeller 9 only needs 2.2kW of power for normal operation, and this single-stage hydraulic turbine can fully meet the operation needs.

[0061] Table 3

[0062] The above description is merely a preferred embodiment of the present invention and does not constitute any form of limitation to the present invention. Although the present invention has been disclosed as above in terms of a preferred embodiment, it is not intended to limit the present invention. Any person skilled in the art can, without departing from the scope of the technical solution of the present invention, make some changes or modifications to equivalent embodiments using the technical contents disclosed above. However, any brief modifications, equivalent changes and modifications made to the above embodiments based on the technical essence of the present invention without departing from the content of the technical solution of the present invention are still within the scope of the technical solution of the present invention.

Claims

1. A centrifugal hydraulic fan, characterized in that: include: The pump body (1) is provided with a first cavity (2) having a circular cross section, the first cavity (2) is provided with a first axial opening (3), and a water inlet (4) and a water outlet (5) are provided on the cavity wall of the first cavity (2); A pump cover (6) is used to seal the first opening (3) and is detachably connected to the pump body (1); A hydraulic impeller (7) is rotatably disposed in the first cavity (2) and is coaxially arranged with the first cavity (2); A pump shaft (8) connected to the hydraulic impeller (7); A wind impeller (9) connected to the pump shaft (8); A second axial opening (10) is provided on the pump cover (6), and the pump shaft (8) is passed through the second opening (10); the hydraulic impeller (7) includes a front cover plate (11) and a rear cover plate (12); a hydraulic impeller outlet (13) is provided at the center of the front cover plate (11), and the hydraulic impeller outlet (13) is communicated with the water outlet (5); a plurality of first hydraulic blades (14) are provided between the front cover plate (11) and the rear cover plate (12); a hydraulic impeller inlet (15) is formed between the front cover plate (11) and the rear cover plate (12), and the hydraulic impeller inlet (15) is communicated with the water inlet (4); a pressure relief hole (16) is provided on the rear cover plate (12), and the pressure relief hole (16) is used to balance the pressure on both sides of the rear cover plate (12).

2. A centrifugal hydraulic fan according to claim 1, characterized in that: A water guide groove (17) is provided on the first cavity (2), and the water guide groove (17) is arranged around the cavity wall of the first cavity (2). The top of the water guide groove (17) is open and communicates with the first cavity (2). The width of the top opening of the water guide groove (17) is the same as the width of the hydraulic impeller inlet (15), and the water inlet (4) is communicated with the water guide groove (17); the cross-sectional area of ​​the water guide groove (17) gradually decreases from the outside to the inside; the cross-sectional area of ​​the water guide groove (17) gradually decreases along the circumference of the first cavity (2), and the cross-sectional area at the connection between the water guide groove (17) and the water inlet (4) is the largest.

3. A centrifugal hydraulic fan according to claim 2, characterized in that: The water inlet direction of the water inlet (4) is tangent to the bottom of the water guide groove (17); the water inlet (4) is located above the center of the hydraulic impeller (7); and the highest point of the hydraulic impeller inlet (15) is higher than the lowest point of the water inlet (4).

4. A centrifugal hydraulic fan according to claim 1, characterized in that: The first hydraulic blades (14) are arranged perpendicular to the front cover plate (11), and the first hydraulic blades (14) extend from the outermost side of the front cover plate (11) or the outermost side of the rear cover plate (12) toward the center; the plurality of first hydraulic blades (14) are in a vortex shape toward the hydraulic impeller outlet (13).

5. The centrifugal hydraulic fan according to claim 1, characterized in that: A second hydraulic blade (18) is provided between adjacent first hydraulic blades (14), and the second hydraulic blade (18) extends from the outermost side of the front cover plate (11) or the outermost side of the rear cover plate (12) toward the center; the second hydraulic blade (18) is in a vortex shape toward the hydraulic impeller outlet (13).

6. A centrifugal hydraulic fan according to claim 1, characterized in that: The pump body (1) is provided with an outwardly extending water inlet pipe (19), the water inlet pipe (19) is provided with a water inlet channel (20), the water inlet channel (20) is connected to the water inlet (4) through a conical surface (21), and the radial cross-sectional area of ​​the conical surface (21) gradually increases from the inside to the outside; the pump body (1) is provided with an outwardly extending water outlet pipe (22), the water outlet pipe (22) is provided with a water outlet channel (23), the water outlet channel (23) is connected to the water outlet (5), and the radial cross-sectional area of ​​the water outlet channel (23) gradually increases from the inside to the outside.

7. The centrifugal hydraulic fan according to claim 1, characterized in that: A second cavity (27) is provided on the pump cover (6), and the second cavity (27) is communicated with the first cavity (2) through the pressure relief hole (16).

8. The centrifugal hydraulic fan according to claim 1, characterized in that: A bearing box (30) is provided between the pump cover (6) and the wind impeller (9), one end of the bearing box (30) is connected to the pump cover (6), and the other end is provided with a bearing cover (31), the bearing cover (31) and the bearing box (30) are detachably connected, a third opening (32) is provided on the bearing cover (31), and the pump shaft (8) is passed through the third opening (32); a bearing (33) is provided between the pump shaft (8) and the bearing box (30), and two sides of the bearing (33) are respectively in contact with the pump shaft (8) and the bearing box (30); and a mounting foot (34) extending outward is provided on the pump body (1).

9. The centrifugal hydraulic fan according to claim 1, characterized in that: The diameter D of the hydraulic impeller outlet (13) j =54.9mm; the diameter D2 of the rear cover plate (12) is 265mm; the width b2 of the hydraulic impeller inlet (15) is 8mm; the inlet angle β2 of the first hydraulic blade (14) is 31°; the outlet angle β1 of the first hydraulic blade (14) is 31°; and eight first hydraulic blades (14) are provided.

10. The centrifugal hydraulic fan according to claim 1, characterized in that: The pump body (1) is a volute, and the first cavity (2) is a volute chamber; the base circle diameter D3 of the first cavity (2) is 275 mm; the inlet width b3 of the first cavity (2) is 8 mm; a partition tongue (39) is provided in the first cavity (2), and the placement angle of the partition tongue (39) is =25°.

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