Rotational flow pump

Abstract

The utility model belongs to the technical field of fluid machinery, and particularly relates to a vortex pump which comprises a pump body, an impeller, an inner pump cover, an auxiliary impeller, a sealing cavity, a mechanical seal and a bearing component. The pump body is fixedly connected with the bearing component; the inner pump cover, the auxiliary impeller, the sealing cavity and the mechanical sealing piece are arranged on the impeller in a sleeving mode. An inner pump cover is arranged at one end of the auxiliary impeller; a sealing cavity is formed in the other end of the auxiliary impeller; a mechanical seal is arranged at the end, away from the auxiliary impeller, of the sealing cavity. The mechanical seal is arranged in the bearing component; the two sides of the inner pump cover are fixedly connected with the bearing component; the two sides of the sealing cavity are fixedly connected with the bearing component. According to the vortex pump, media are not prone to crystallization, the sealing effect is high, the vortex pump is not prone to damage, the suction speed is reduced, the suction performance is improved, energy loss is reduced, the efficiency of the pump is greatly improved, and the problems of high noise and large vibration in the operation process are solved.

Description

Technical Field

[0001] This utility model belongs to the technical field of fluid machinery, specifically relating to a vortex pump. Background Technology

[0002] Cyclone pumps are widely used in chemical processes to transport materials with high particle content and long fibers, as well as to discharge wastewater. With the increasing application of cyclone pumps in chemical and petrochemical industries, the requirements for pump reliability, energy efficiency, and environmental friendliness are also increasing. Currently, some shortcomings in the performance of existing cyclone pumps limit their use, such as easy crystallization of the medium, easy damage to seals, high operating noise, and large vibration, which in turn cause energy loss and low hydraulic efficiency within the pump body. Utility Model Content

[0003] To address the shortcomings of the existing technology, this invention provides a cyclone pump that is less prone to crystallization of the medium, has a high sealing effect, and is less susceptible to damage. It reduces the suction speed, improves suction performance, and solves problems such as high operating noise and large vibration.

[0004] To solve the technical problem, the present invention adopts the following technical solution: a cyclone pump, comprising a pump body, an impeller, an inner pump cover, an auxiliary impeller, a sealing cavity, a mechanical seal, and a bearing assembly; the pump body and the bearing assembly are fixedly connected; the pump cover, the auxiliary impeller, the sealing cavity, and the mechanical seal are sleeved on the impeller; an inner pump cover is provided at one end of the auxiliary impeller; a sealing cavity is provided at the other end of the auxiliary impeller; a mechanical seal is provided at the end of the sealing cavity away from the auxiliary impeller; the mechanical seal is placed inside the bearing assembly; both sides of the inner pump cover are fixedly connected to the bearing assembly; both sides of the sealing cavity are fixedly connected to the bearing assembly.

[0005] Furthermore, the impeller includes a wheel body, a wheel shaft at the center of the wheel body, and blades on the side of the wheel body. The blades are composed of a front section, a middle section, and a rear section in sequence. The inlet angle of the front section is θ; the outlet angle of the rear section is φ; the middle section transitions from the front section to the rear section; the blade angle of the middle section conforms to the relative flow tilt angle of the liquid; the inlet angle θ of the front section is in the range of 20~35°; and the outlet angle φ of the rear section is 90°.

[0006] Furthermore, the blades are 8 or 12 in number; the rear section of the blades is a straight blade; the straight blades begin to tilt at approximately 1 / 4 of their total length at the blade exit end; the back of the blades is chamfered; the cross-section of the blades is pentagonal; the wheel body, the axle at the center of the wheel body, and the blades on the side of the wheel body rotate counterclockwise.

[0007] Furthermore, the diameter of the wheel body is greater than 315mm, and short blades are provided between the rear sections of the blades.

[0008] Furthermore, the short blade is located at the exit of the blade, and the short blade is a straight blade segment.

[0009] Furthermore, the inlet of the short blade is inclined towards the back of the blade.

[0010] Furthermore, the pump body includes a vortex diffuser section, a vortex inlet section, a baffle, and a vortex pressure chamber section, with a baffle between the vortex diffuser section and the vortex pressure chamber section; the radial diameter of the baffle is D0; the radial diameter of the outlet of the vortex pressure chamber section is D3; the ratio of D0 to D3 is within the range of 90%±3%; the pump body adopts a semi-vortex pressure chamber; the vortex pressure chamber section extends from the baffle to within 180°; the outlet of the vortex pressure chamber section to the vortex outlet diffuser section is a circular pressure chamber.

[0011] Furthermore, the vortex inlet section adopts an inner diffusion angle α and a large fillet R; the angle value of the inner diffusion angle α is 2°~8°; the value of the large fillet R is 50% of the pump body inlet diameter.

[0012] Compared with the prior art, this utility model has the following beneficial effects: the medium of this cyclone pump is not prone to crystallization, has a high sealing effect and is not easily damaged, reduces the suction speed, improves suction performance, reduces energy loss, greatly improves pump efficiency, solves the problems of high noise and large vibration during operation, increases pump head through impeller semi-open structure, reduces resistance loss during operation, and ultimately improves the internal flow of the cyclone pump, improves the flowability of the cyclone pump pressure chamber for liquids containing impurities and the hydraulic efficiency of the cyclone pump. Attached Figure Description

[0013] Figure 1 This is a schematic diagram of the structure of an embodiment of the present utility model;

[0014] Figure 2 This is a schematic diagram of the pump body according to an embodiment of the present invention;

[0015] Figure 3 This is a schematic diagram of the impeller structure according to an embodiment of the present invention;

[0016] Figure 4 for Figure 3 Sectional view of KK;

[0017] Figure 5 A schematic diagram of the impeller structure according to a preferred embodiment of the utility model;

[0018] Figure 6 for Figure 5 A sectional view;

[0019] In the diagram: 1. Wheel body, 2. Wheel shaft, 3. Front section of blade, 4. Middle section of blade, 5. Rear section of blade, 6. Chamfer, 7. Pump body, 8. Impeller, 9. Inner pump cover, 10. Auxiliary impeller, 11. Sealing cavity, 12. Mechanical seal, 13. Bearing components, 14. Vortex diffuser section, 15. Vortex inlet section, 16. Divider tongue, 17. Vortex pressure chamber section, 18. Short blade, 19. Blade. Detailed Implementation

[0020] The technical solution of this utility model will now be clearly and completely described with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this utility model. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this utility model.

[0021] Combined with appendix Figure 1-4 As shown, an embodiment of the present invention provides a cyclone pump, comprising a pump body 7, an impeller 8, an inner pump cover 9, an auxiliary impeller 10, a sealing cavity 11, a mechanical seal 12, and a bearing assembly 13. The pump body 7 and the bearing assembly 13 are fixedly connected. The inner pump cover 9, the auxiliary impeller 10, the sealing cavity 11, and the mechanical seal 12 are fitted onto the impeller 8. One end of the auxiliary impeller 108 is provided with the inner pump cover 9. The other end of the auxiliary impeller 108 is provided with the sealing cavity 11. The end of the sealing cavity 11 away from the auxiliary impeller 10 is provided with the mechanical seal 12. The mechanical seal 12 is placed inside the bearing assembly 13. Both sides of the inner pump cover 9 are fixedly connected to the bearing assembly 13. Both sides of the sealing cavity 11 are fixedly connected to the bearing assembly 13.

[0022] Further, the impeller 8 includes a wheel body 1, a wheel shaft 2 at the center of the wheel body, and blades 19 on the side of the wheel body. The blades 19 are composed of a front section 3, a middle section 4, and a rear section 5 in sequence. The inlet angle of the front section 3 is θ; the outlet angle of the rear section 5 is φ; the middle section 4 transitions from the front section 3 to the rear section 5; the blade angle of the middle section 4 conforms to the relative flow tilt angle of the liquid; the inlet angle θ of the front section 3 is in the range of 20~35°; and the outlet angle φ of the rear section 5 is 90°.

[0023] In one embodiment, there are 8 blades (12 blades when the impeller diameter is greater than 400); the rear section 5 of the blade is a straight blade; the straight blade begins to tilt at about 1 / 4 of its total length at the blade exit end; a chamfer 6 is provided on the back of the blade; the cross section of the blade is pentagonal; the wheel body 1, the wheel axle 2 at the center of the wheel body, and the blades on the side of the wheel body rotate counterclockwise.

[0024] It should be noted that the impeller 8 of this application adopts a semi-open structure and is placed on one side of the vortex chamber. The vortex casing flow channel of the pump body 7 in front of the impeller 8 is not blocked, and the conveying of media with impurities and particles is not blocked, and has good flowability. At the same time, the blade inlet placement angle of the impeller 8 is between 20 and 35°. This blade inlet placement angle is similar to the blade inlet angle of other centrifugal pumps, which reduces the hydraulic loss caused by the inlet flow and the impact of the blades.

[0025] In addition, the blade outlet angle is 90°, which makes the liquid generate a large circumferential velocity at the impeller outlet 8, thereby increasing the pump head. At the same time, the blade angle in the middle section of the blade is consistent with the relative flow direction of the liquid, so that the blade transitions smoothly from the inlet to the outlet, reducing resistance loss during operation, improving hydraulic efficiency, and also greatly reducing pump noise.

[0026] The rear section 5 of the blade in this application retains a straight blade of approximately 1 / 4 the blade length, ensuring good hydraulic performance even after the impeller 8 diameter is cut.

[0027] The blade of this application has a chamfered 6 structure on the back (see...). Figure 4 This reduces the resistance of the swirling liquid entering the impeller 8, increases the flow rate of the impeller 8, and allows more liquid to circulate and be pressurized through the impeller 8, thereby improving hydraulic efficiency.

[0028] In a preferred embodiment, the diameter of the wheel body 1 is greater than 315 mm, and a short blade 18 is provided between the rear section 5 of the blade.

[0029] In a preferred embodiment, the short blade 18 is located at the blade outlet, and the short blade 18 is a straight blade segment.

[0030] It should be noted that for impellers with a diameter greater than 315mm, without changing the inlet angle of the blades, short blades 18 are added to the straight blade segment at the blade outlet to reduce vortex losses between blades caused by the large distance between blades at the large diameter.

[0031] Furthermore, the inlet of the short blade 18 is inclined towards the back of the blade.

[0032] It should be noted that the inlet design of the short blade 18 is inclined towards the back of the blade, which effectively improves the reasonable distribution of flow and makes the outlet pressure of the blade more evenly distributed; the addition of the short blade 7 effectively increases the pump head and improves the pump efficiency.

[0033] In one embodiment, the pump body 7 includes a vortex diffuser section 14, a vortex inlet section 15, a baffle 16, and a vortex pressure chamber section 17. A baffle 16 is provided between the vortex diffuser section 14 and the vortex pressure chamber section 17. The radial diameter of the baffle 16 is D0. The radial diameter of the outlet of the vortex pressure chamber section 17 is D3. The ratio of D0 to D3 is within the range of 90% ± 3%. The pump body 7 adopts a semi-vortex pressure chamber. The vortex pressure chamber section 17 extends from the baffle 16 to within 180°. The vortex pressure chamber section 17 to the outlet of the vortex diffuser section 14 is a circular pressure chamber.

[0034] It should be noted that the design of the pump body 7 in this application is twofold: firstly, to address the problem that the "barrier tongue 16" at the outlet of the circular pressure chamber vortex chamber is not effective in separating and drawing out the liquid, and most of the liquid continues to circulate within the pump body 7, resulting in energy loss; and secondly, to solve the problem that the large diffusion angle of the vortex shell at the barrier tongue 16 in conventional pump bodies 7 leads to excessive changes in the circumferential dimensions of the vortex chamber, causing losses of the swirling liquid during circulation within the pump body 7.

[0035] In one embodiment, the volute inlet section 15 adopts an inner diffusion angle α and a large fillet R; the angle value of the inner diffusion angle α is 2°~8°, and a larger value is selected for large impeller diameter or large flow rate; the value of the large fillet R is 50% of the pump body inlet diameter.

[0036] It should be noted that the inlet section of the pump body 7 adopts an internal diffusion angle and a large fillet design, with the internal diffusion angle value between 2° and 8°; the fillet radius R is 50% of the inlet diameter of the pump body 7. With the same impeller 8 and pump body 7 matching design, the larger the inlet diffusion angle α and fillet radius R of the pump body 7, the higher the flow rate at the pump's optimal efficiency point. At the same flow rate, this application reduces the suction velocity, improves suction performance, and gives the pump better cavitation performance. However, further increases in α and R will result in a lower head. Therefore, the inlet DN design can be modified according to the required pump parameters.

[0037] The design principle of this application is as follows: The impeller 8 of the pump is mounted on the shaft. The impeller 8 is located on one side of the volute chamber of the pump body 7, with a large distance between it and the inlet side wall of the pump body 7, forming a flow channel. Driven by a motor, the impeller 8 accelerates the liquid into the volute flow channel. This portion of the liquid has a high velocity. Some of the liquid at the inlet of the impeller 8 that is not accelerated by the impeller 8 will enter the impeller 8, filling the space where the liquid flows towards the edge of the impeller 8 due to acceleration and centrifugal force, forming a local vortex. At the same time, the liquid forms an overall vortex around the circumference of the volute chamber of the pump body 7 as the impeller 8 rotates. The liquid gains energy during the continuous acceleration and circulation process. A portion of the liquid flows out from the pump outlet, while the portion continues to be accelerated in the form of a vortex within the volute chamber. Therefore, the liquid in a vortex pump is also subject to repeated acceleration.

[0038] Impeller 8 adopts a back blade design, which can automatically discharge heavy particles to the outer edge of impeller 8 during rotation, preventing the back of impeller 8 from being blocked due to the high solid content of the medium, and reducing the back pressure of impeller 8 and the pressure of the sealing cavity.

[0039] Furthermore, this pump employs a secondary impeller 10 dynamic seal, which further lowers the sealing cavity and acts as an isolation mechanism to prevent media containing fine particles from entering the sealing cavity 11, thus ensuring the service life of the mechanical seal 12.

[0040] In addition, the pump of this application adopts a horizontal installation and a pull-back structure, which facilitates the disassembly of rotor components for replacement and maintenance; the bearing component 13 adopts a common standard design to improve the standardization of the pump; and the standardization of the pump is improved through the design of common components and reasonable hydraulic planning.

[0041] Obviously, the above embodiments are merely illustrative examples for clear explanation and are not intended to limit the implementation. Those skilled in the art will recognize that other variations or modifications can be made based on the above description. It is neither necessary nor possible to exhaustively list all possible implementations here. However, obvious variations or modifications derived therefrom are still within the protection scope of this utility model.

Claims

1. A cyclone pump, characterized in that: The pump includes a pump body, impeller, inner pump cover, auxiliary impeller, sealing cavity, mechanical seal, and bearing assembly. The pump body and bearing assembly are fixedly connected. The inner pump cover, auxiliary impeller, sealing cavity, and mechanical seal are fitted onto the impeller. The inner pump cover is located at one end of the auxiliary impeller. The sealing cavity is located at the other end of the auxiliary impeller. The mechanical seal is located at the end of the sealing cavity away from the auxiliary impeller. The mechanical seal is placed inside the bearing assembly. The two sides of the inner pump cover are fixedly connected to the bearing assembly. The two sides of the sealing cavity are fixedly connected to the bearing assembly.

2. The cyclone pump according to claim 1, characterized in that: The impeller includes a wheel body, a wheel shaft at the center of the wheel body, and blades on the side of the wheel body. The blades are composed of a front section, a middle section, and a rear section in sequence. The inlet angle of the front section is θ. The outlet angle of the rear section is φ. The middle section transitions from the front section to the rear section. The blade angle of the middle section conforms to the relative flow tilt angle of the liquid. The inlet angle θ of the front section of the blade is in the range of 20~35°; the outlet angle φ of the rear section of the blade is 90°.

3. A cyclone pump according to claim 2, characterized in that: The blades are 8 or 12 in number; the rear section of the blades is a straight blade; the straight blades begin to tilt at about 1 / 4 of their total length at the blade exit end; the back of the blades is chamfered; the cross-section of the blades is pentagonal; the wheel body, the axle at the center of the wheel body, and the blades on the side of the wheel body rotate counterclockwise.

4. A cyclone pump according to claim 2, characterized in that: The diameter of the wheel body is greater than 315mm, and short blades are provided between the rear sections of the blades.

5. A cyclone pump according to claim 4, characterized in that: The short blade is located at the exit of the blade, and the short blade is a straight leaf segment.

6. A cyclone pump according to claim 4, characterized in that: The inlet of the short blade is inclined towards the back of the blade.

7. A cyclone pump according to claim 1, characterized in that: The pump body includes a vortex diffuser section, a vortex inlet section, a baffle, and a vortex pressure chamber section. A baffle is provided between the vortex diffuser section and the vortex pressure chamber section. The radial diameter of the baffle is D0. The radial diameter of the outlet of the vortex pressure chamber section is D3. The ratio of D0 to D3 is within the range of 90%±3%. The pump body adopts a semi-vortex pressure chamber. The vortex pressure chamber section extends from the baffle to within 180°. The vortex pressure chamber section to the outlet of the vortex diffuser section is a circular pressure chamber.

8. A cyclone pump according to claim 7, characterized in that: The volute inlet section adopts an inner diffusion angle α and a large fillet R; the angle value of the inner diffusion angle α is 2°~8°; the value of the large fillet R is 50% of the pump body inlet diameter.

Images