A new tooth profile shearing pump

Abstract

The utility model relates to the field of shearing pump discloses a novel tooth shape shearing pump, including the opposite setting stator and rotor, the stator is outwardly circumferentially provided with the stator shearing tooth of multiple circle interval settings from inside, the rotor is outwardly circumferentially provided with the rotor shearing tooth of multiple circle interval settings from inside, every circle stator shearing tooth and rotor shearing tooth all have multiple and evenly interval settings, and the axial section of stator shearing tooth and rotor shearing tooth on the stator and rotor all are trapezoidal. Effectively improve the efficiency, stability and applicability of shearing pump.

Description

Technical Field

[0001] This utility model relates to the field of shear pumps, and in particular to a novel toothed shear pump. Background Technology

[0002] The stator and rotor tooth profiles of a shear pump play a crucial role in fluid handling. They primarily generate powerful mechanical impact, kinetic, and shearing forces through the high-speed relative rotation of the rotor and stator within a very small gap, achieving the pulverization and homogenization of granular materials. The tooth profile design directly affects performance parameters such as shearing efficiency, flow stability, noise level, and load-bearing capacity.

[0003] Traditional toothed shear pumps suffer from the following main drawbacks: uneven radial force leads to uneven bearing load; large flow pulsations cause unstable flow and significant vibration; limited viscosity range makes it difficult to handle high-viscosity fluids; and insufficient suction capacity affects pumping performance. Spur gears have fewer meshing teeth, resulting in large flow pulsations; helical gears generate axial forces requiring reinforced bearing design; oil trapping causes oil heating, noise, and cavitation problems; limited load-bearing capacity makes them prone to "scouring" under high-pressure conditions; and concentrated shearing zones at the tooth root can cause localized overheating and degradation of heat-sensitive materials. These drawbacks collectively limit the efficiency, stability, and applicability of traditional toothed shear pumps. Utility Model Content

[0004] This invention provides a novel toothed shear pump that solves the technical problems of low efficiency, stability, and applicability of traditional toothed shear pumps.

[0005] The technical solution adopted by this utility model to solve its technical problem is: a novel toothed shear pump, comprising a stator and a rotor arranged opposite to each other. The stator has multiple rings of stator shear teeth arranged at intervals from the inside to the outside circumferentially, and the rotor has multiple rings of rotor shear teeth arranged at intervals from the inside to the outside circumferentially. Each ring of stator and rotor shear teeth has multiple teeth arranged at even intervals, and the axial cross-section of the stator and rotor shear teeth is trapezoidal. This effectively improves the efficiency, stability, and applicability of the shear pump.

[0006] Furthermore, the stator shear teeth are evenly distributed circumferentially in multiple rows, with corresponding inner and outer columns. The inner and outer edges of the stator shear teeth on the cross-section perpendicular to the stator axis are both on concentric circles centered at the axis. The left side wall of each row of stator shear teeth lies on a straight line passing through the stator axis, and the right side wall of each row of stator shear teeth also lies on a straight line passing through the stator axis. The axial arrangement of the stator shear teeth results in more uniform radial force distribution on the stator, and the structure is simple and practical.

[0007] Furthermore, the rotor shear teeth are evenly distributed circumferentially in multiple rows, with corresponding inner and outer columns. The inner and outer edges of the rotor shear teeth on the cross-section perpendicular to the rotor axis are both on concentric circles centered at the axis. The left side wall of each row of rotor shear teeth lies on a straight line passing through the rotor axis, and the right side wall of each row of rotor shear teeth also lies on a straight line passing through the rotor axis. The axial arrangement of the rotor shear teeth results in more uniform radial force distribution on the rotor, and the structure is simple and practical.

[0008] Furthermore, the number of stator shear teeth and rotor shear teeth is the same for each revolution. This ensures uniform force on the stator and rotor while increasing the number of stator and rotor shear teeth, thus increasing the number of meshing teeth and stabilizing flow pulsations.

[0009] Furthermore, the stator shearing teeth are arranged in three concentric circles, and the rotor shearing teeth are arranged in four concentric circles, with the three concentric circles of stator shearing teeth located between the four concentric circles of rotor shearing teeth. This spacing arrangement ensures a reasonable spatial arrangement.

[0010] Furthermore, the trapezoids formed by the three rings of stator shear teeth and the three rings of rotor shear teeth located on the inner side in the axial section are all isosceles trapezoids with the same lower base length and cross-sectional area. The axial section of the outermost ring of rotor shear teeth in the four rings is also an isosceles trapezoid. This ensures the strength of the shear teeth while effectively utilizing space.

[0011] Furthermore, a central shaft hole is provided at the center of the rotor, and an annular protruding fixing boss is provided on the outer side of the central shaft hole at one end of the rotor shear teeth on the rotor body. An inclined surface transitioning to the rotor body is provided on the outer side of the fixing boss. This effectively increases the thickness of the rotor body at the central shaft hole, improving robustness and thus extending service life. Attached Figure Description

[0012] Figure 1 This is a schematic diagram of the axial cross-section of the present invention;

[0013] Figure 2 This is a schematic diagram of the stator's front view;

[0014] Figure 3 This is a front view schematic diagram of the rotor.

[0015] The markings in the diagram are: stator 100, stator shearing tooth 110, rotor 200, central shaft hole 201, and rotor shearing tooth 210. Detailed Implementation

[0016] The present invention will be further described below with reference to the accompanying drawings and specific embodiments.

[0017] like Figure 1A novel toothed shear pump is shown, comprising a stator 100 and a rotor 200 arranged opposite to each other. The stator 100 has multiple rings of stator shear teeth 110 arranged at intervals from the inside out, and the rotor 200 has multiple rings of rotor shear teeth 210 arranged at intervals from the inside out. Each ring of stator shear teeth 110 and rotor shear teeth 210 has multiple teeth evenly spaced. The axial cross-section of the stator shear teeth 110 and rotor shear teeth 210 on both the stator 100 and rotor 200 is trapezoidal. The trapezoidal design of the stator shear teeth 110 and rotor shear teeth 210 results in high strength, a wider viscosity range that can be handled, less flow pulsation, lower noise, and significantly enhanced stability and practicality compared to straight teeth. The trapezoidal design effectively reduces oil trapping, which can lead to oil heating, noise, and cavitation problems. It also reduces the likelihood of "chamber scraping" under high-pressure conditions, and the concentration of the shearing zone at the tooth root is reduced, preventing localized overheating and degradation of heat-sensitive materials. This effectively improves the efficiency, stability, and applicability of the shear pump.

[0018] Based on the above, such as Figure 1 and Figure 2 As shown, multiple rings of stator shear teeth 110 are evenly distributed circumferentially in multiple rows with corresponding inner and outer columns. The inner and outer edges of the multiple rings of stator shear teeth 110 on the cross-section perpendicular to the stator 100 axis are on concentric circles centered at the axis. The left side wall of each row of stator shear teeth 110 lies on a straight line passing through the stator 100 axis, and the right side wall of each row of stator shear teeth 110 lies on a straight line passing through the stator 100 axis. The axial arrangement of the stator shear teeth 110 results in more uniform radial force distribution on the stator 100, avoiding the increased axial force caused by the oblique design of the shear teeth, which necessitates a more robust bearing design. The structure is simple and practical.

[0019] Based on the above, such as Figure 1 and Figure 3 As shown, multiple rings of rotor shear teeth 210 are evenly distributed circumferentially in multiple rows with corresponding inner and outer columns. The inner and outer edges of the multiple rings of rotor shear teeth 210 on the cross-section perpendicular to the rotor 200 axis are on concentric circles centered at the axis. The left side wall of each row of rotor shear teeth 210 lies on a straight line passing through the rotor 200 axis, and the right side wall of each row of rotor shear teeth 210 lies on a straight line passing through the rotor 200 axis. The axial arrangement of the rotor shear teeth 210 results in more uniform radial force on the rotor 200, avoiding the increased axial force caused by the oblique design of the shear teeth, which necessitates a more robust bearing design. The structure is simple and practical.

[0020] Based on the above, such as Figures 1 to 3As shown, the number of stator shear teeth 110 and rotor shear teeth 210 is the same in each revolution. While ensuring uniform force on the stator 100 and rotor 200, the number of stator shear teeth 110 and rotor shear teeth 210 is increased, increasing the number of meshing teeth and stabilizing flow pulsation.

[0021] Based on the above, such as Figures 1 to 3 As shown, the number of stator shear teeth 110 and rotor shear teeth 210 is the same in each revolution. While ensuring uniform force on the stator 100 and rotor 200, the number of stator shear teeth 110 and rotor shear teeth 210 is increased, increasing the number of meshing teeth and stabilizing flow pulsation.

[0022] Based on the above, such as Figures 1 to 3 As shown, the trapezoids formed by the three rings of stator shear teeth 110 and the three rings of rotor shear teeth 210 located on the inner side in the axial section are all isosceles trapezoids with the same lower base length and cross-sectional area. The axial section of the outermost ring of rotor shear teeth 210 is also an isosceles trapezoid. In a specific implementation, the outer wall of the outermost ring of rotor shear teeth 210 is located on the same annular surface as the rotor 200 and the outer wall of the rotor. The inclination angle of the inner wall of the outermost ring of rotor shear teeth 210 is the same as the inclination angle of the inner rings of rotor shear teeth 210, thus ensuring the strength of the shear teeth while effectively utilizing space.

[0023] Based on the above, such as Figure 1 and Figure 3 As shown, a central shaft hole 201 is provided at the center of the rotor 200. An annular protruding fixing boss is provided on the outer side of the central shaft hole 201 at one end of the rotor shearing tooth 210. An inclined surface transitioning to the rotor 200 body is provided on the outer side of the fixing boss. This effectively increases the thickness of the rotor 200 body at the central shaft hole 201, improving its robustness and thus extending its service life.

[0024] The specific embodiments described above further illustrate the purpose, technical solution, and beneficial effects of this utility model. It should be understood that the above descriptions are merely specific embodiments of this utility model and are not intended to limit this utility model. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A novel toothed shear pump, comprising a stator (100) and a rotor (200) arranged opposite to each other, wherein the stator (100) has multiple rings of stator shear teeth (110) arranged at intervals from the inside to the outside circumferentially, and the rotor (200) has multiple rings of rotor shear teeth (210) arranged at intervals from the inside to the outside circumferentially, wherein each ring of the stator shear teeth (110) and the rotor shear teeth (210) has multiple and evenly spaced teeth, characterized in that: The axial cross-sections of the stator shear teeth (110) and rotor shear teeth (210) on the stator (100) and rotor (200) are both trapezoidal.

2. The novel toothed shear pump according to claim 1, characterized in that: The stator shear teeth (110) are evenly distributed in multiple rings around the circumference, arranged in multiple rows corresponding to each other. The inner and outer edges of the stator shear teeth (110) in the cross section perpendicular to the axis of the stator (100) are on concentric circles with the center located at the axis. The left side wall of each row of stator shear teeth (110) is located on a straight line passing through the axis of the stator (100), and the right side wall of each row of stator shear teeth (110) is located on a straight line passing through the axis of the stator (100).

3. A novel toothed shear pump according to claim 2, characterized in that: The rotor shear teeth (210) are evenly distributed in multiple rings in the circumferential direction, arranged in multiple rows corresponding to each other. The inner and outer edges of the rotor shear teeth (210) in the cross section perpendicular to the axis of the rotor (200) are on concentric circles with the center located at the axis. The left side wall of each row of rotor shear teeth (210) is located on a straight line passing through the axis of the rotor (200), and the right side wall of each row of rotor shear teeth (210) is located on a straight line passing through the axis of the rotor (200).

4. A novel toothed shear pump according to claim 3, characterized in that: The number of stator shear teeth (110) and rotor shear teeth (210) per revolution is the same.

5. A novel toothed shear pump according to claim 4, characterized in that: The stator shear teeth (110) are arranged in three rings, and the rotor shear teeth (210) are arranged in four rings, with the three rings of stator shear teeth (110) located between the four rings of rotor shear teeth (210).

6. A novel toothed shear pump according to claim 5, characterized in that: The trapezoids formed by the three rings of stator shear teeth (110) and the three rings of rotor shear teeth (210) located on the inner side in the axial section are all isosceles trapezoids with the same lower base length and cross-sectional area. The axial section of the outermost ring of rotor shear teeth (210) in the four rings is an isosceles trapezoid.

7. A novel toothed shear pump according to claim 1, characterized in that: The rotor (200) has a central shaft hole (201) at its center. The rotor (200) body has an annular protruding fixed boss on the outer side of the central shaft hole (201) at one end of the rotor shearing tooth (210). The outer side of the fixed boss has an inclined surface that transitions to the rotor (200) body.

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