Wear-resistant low-pulsation traveling wave pump profile and traveling wave pump

Abstract

The invention discloses a wear-resistant low-pulsation traveling wave pump profile and a traveling wave pump, a 1 / 4 line segment of the profile is composed of a first transition curve AB, a correction cycloid segment BC, a high-order transition curve CD and a second transition curve DE, and the first transition curve AB is connected with the second transition curve DE through the correction cycloid segment BC and the high-order transition curve CD. According to the invention, the correction cycloid is adopted at the start and end of the correction cycloid segment BC, when the contact stress reaches the maximum and the rotor is at the maximum contact stress, and the correction cycloid acts as that the acceleration of the correction cycloid at the start and end of the stroke is zero, so that the soft impact is eliminated, and the jump is changed into a limited value; and finally, the dynamic characteristics which are extremely smooth, stable and very suitable for high-speed movement are obtained, the sealing effect between the pump body and the inner wall of the pump body is good under the high-pressure conveying working condition, it is guaranteed that the conveying pressure is durable and stable, pulsation is reduced, and working efficiency is improved.

Description

Technical Field

[0001] This invention relates to the field of traveling wave pump technology, and in particular to a wear-resistant, low-pulsation traveling wave pump profile and a traveling wave pump. Background Technology

[0002] In the field of microfluidics, applications such as precision drug delivery, lab-on-a-chip (Lab-on-a-Chip), biochemical analysis, and micro / nanoliter liquid handling utilize micropumps, which drive the fluid and are the core actuators for achieving their functions. These applications place extreme demands on the performance of micropumps: not only do they need to be tiny enough to fit into integrated systems, but more importantly, they must possess extremely low flow pulsation, ultra-high operational stability, and long-term reliability. Even minute flow fluctuations can directly interfere with the mixing ratio of reaction reagents, affect the precision of cell-level operations, and even lead to a deterioration in the signal-to-noise ratio of detection signals. Furthermore, wear on the moving parts inside the micropump can generate particulate contaminants and alter the sealing characteristics of the microchannels, which is fatal for channels with a scale of only micrometers, ultimately causing the entire microfluidic chip to malfunction.

[0003] Currently, the core moving parts (such as rotors and cams) of positive displacement micropumps (e.g., piezoelectric pumps, gear pumps) widely used in the microfluidics field are mostly designed based on traditional cycloidal, involute, or simple circular arc profiles. However, the inherent defects of these traditional profiles are drastically amplified at the microscale and under high-speed operating conditions. 1. Significant flow and pressure pulsations: Traditional profiles are prone to sudden acceleration changes during meshing or motion, triggering so-called "soft impacts" or "rigid impacts." This dynamic discontinuity translates into periodic pressure spikes and flow fluctuations in the fluid, severely disrupting the stable, laminar flow state sought by microfluidic systems and greatly limiting their application in precision analysis and transport.

[0004] 2. Intractable Wear Problems: In areas of highest contact stress (usually the start and end points of the profile), traditional profiles, due to design flaws, lead to stress concentration. Under the high-frequency, long-life operation requirements of micropumps, these areas become the hardest hit by wear. Wear not only shortens the service life of the micropump but also gradually increases internal leakage over time, leading to a decrease in output flow and pressure, making it impossible to guarantee the stability and consistency of long-term operation.

[0005] 3. Poor dynamic characteristics limit high-speed performance: Many traditional profiles exhibit discontinuous acceleration curves during motion, and may even have infinitely large jumps (derivatives of acceleration). These undesirable dynamic characteristics cause vibration and noise in the rotor during high-speed operation, limiting the increase in the operating speed of the micropump and thus restricting its application potential in small-volume, high-flow-rate microfluidic systems.

[0006] Traveling wave pumps are a type of micro pump. In existing technologies, the profile of traveling wave pumps has not been corrected, resulting in non-zero acceleration at the beginning and end of the stroke, leading to soft impacts. This makes it impossible to obtain smooth, stable dynamic characteristics that are well-suited for high-speed motion. At the same time, under large pressure differences, the speed difference is also large, resulting in significant friction and wear. When the rotor is under high pressure, the large speed difference will affect the rotor's lifespan. Furthermore, under high-pressure conveying conditions, the sealing effect between the pump and the inner wall of the pump body is poor and cannot be constant, leading to increased pulsation and low efficiency. Summary of the Invention

[0007] The purpose of this invention is to address the shortcomings of existing technologies by providing a wear-resistant, low-pulsation traveling wave pump profile and a technical solution for the traveling wave pump. The design of this traveling wave pump profile ensures maximum contact stress at the beginning and end of the corrected cycloidal segment BC. When the rotor experiences maximum contact stress, a corrected cycloidal section is employed. Because the corrected cycloidal section ensures zero acceleration at the start and end of its stroke, soft impacts are eliminated, and the abrupt change is reduced to a finite value. This results in extremely smooth, stable dynamic characteristics highly suitable for high-speed motion. Under high-pressure conveying conditions, the pump exhibits excellent sealing with the pump body wall, ensuring sustained and stable conveying pressure, reducing pulsation, and improving working efficiency.

[0008] To solve the above-mentioned technical problems, the present invention adopts the following technical solution: A wear-resistant, low-pulsation traveling wave pump profile is characterized in that: a quarter segment of the profile consists of a first transition curve AB, a modified cycloidal segment BC, a higher-order transition curve CD, and a second transition curve DE. The first transition curve AB connects to the second transition curve DE through the modified cycloidal segment BC and the higher-order transition curve CD. In this traveling wave pump profile design, the contact stress reaches its maximum at the beginning and end of the modified cycloidal segment BC. When the rotor is at the point of maximum contact stress, a modified cycloidal segment is used. Because the modified cycloidal segment ensures zero acceleration at the beginning and end of its stroke, soft impacts are eliminated, and the jump becomes a finite value. Ultimately, this results in extremely smooth, stable dynamic characteristics that are very suitable for high-speed motion. Under high-pressure conveying conditions, the sealing effect between the pump profile and the pump body wall is good, ensuring long-term stable conveying pressure, reducing pulsation, and improving working efficiency.

[0009] Furthermore, both the first transition curve AB and the second transition curve DE are straight line segments.

[0010] Furthermore, the equation of the first transition curve AB is: ; Where 0 < t < π / 24, R is the radius of the base circle, and R = 16.

[0011] Furthermore, the lift of the cycloidal segment BC is revised to h1, and the lift of the higher-order transition curve CD is revised to 10-h1.

[0012] Furthermore, the equation of the cycloidal segment BC is corrected as follows: ; Where π / 24 < t < 6*π / 24, R is the radius of the base circle, R = 16, and h1 is the lift of the corrected cycloidal segment BC.

[0013] Furthermore, the equation for the higher-order transition curve CD is: ; Where 5*π / 12<t<10*π / 12, R is the radius of the base circle, R=16; 0.9549 is the final velocity of the corrected cycloidal segment BC, 6*π / 24<t<11*π / 24, R is the radius of the base circle, a3, a4, and a5 are the coefficients of the fifth-order polynomial, a3 is -0.0087079143, a4 is 0.0004157723, and a5 is -0.000000000000000000007.

[0014] Furthermore, the equation for the second transition curve DE is: ; Where 11*π / 24<t<12*π / 24, R is the radius of the base circle, R=16.

[0015] Furthermore, the profile is an axisymmetric structure.

[0016] A traveling wave pump includes an integrally formed sleeve and a rotor body, the rotor body being distributed on the outer circumferential side of the sleeve, the sleeve having interconnected shaft holes and stepped holes, characterized in that: the edge of the rotor body adopts a wear-resistant, low-pulsation traveling wave pump profile as described above.

[0017] The present invention, by adopting the above-described technical solution, has the following beneficial effects: This invention achieves maximum contact stress at the beginning and end of the corrected cycloidal segment BC. When the rotor is at the point of maximum contact stress, a corrected cycloidal line is used. Since the corrected cycloidal line ensures zero acceleration at the beginning and end of its stroke, soft impacts are eliminated, and the jump is reduced to a finite value. Ultimately, extremely smooth and stable dynamic characteristics that are very suitable for high-speed motion are obtained. Under high-pressure conveying conditions, the sealing effect between the rotor and the pump body wall is good, ensuring long-term stable conveying pressure, reducing pulsation, and improving working efficiency. Attached Figure Description

[0018] The present invention will be further described below with reference to the accompanying drawings: Figure 1 This is a schematic diagram of a wear-resistant, low-pulsation traveling wave pump profile and a traveling wave pump midline according to the present invention; Figure 2 This is a schematic diagram of the rotor structure in this invention; Figure 3 This is a schematic diagram of the base circle radius of the rotor in this invention; Figure 4 This is a schematic diagram of the rotor design principle in MATLAB in this invention; Figure 5 This is a schematic diagram of the space curve of the rotor in this invention; Figure 6 This is a rendering of the rotor in this invention.

[0019] In the figure: 1-sleeve; 2-rotor body; 3-shaft hole; 4-stepped hole. Detailed Implementation

[0020] The present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0021] To enable those skilled in the art to better understand the present invention, the technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort should fall within the scope of protection of the present invention.

[0022] It should be noted that the terms "first," "second," etc., in the specification, claims, and accompanying drawings of this invention are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion.

[0023] like Figures 1 to 5 As shown, this is a wear-resistant, low-pulsation traveling wave pump profile of the present invention, which has an axisymmetric structure.

[0024] The quarter segment of the profile consists of a first transition curve AB, a modified cycloidal segment BC, a higher-order transition curve CD, and a second transition curve DE. The first transition curve AB connects to the second transition curve DE through the modified cycloidal segment BC and the higher-order transition curve CD. In this traveling wave pump profile design, the contact stress reaches its maximum at the beginning and end of the modified cycloidal segment BC. When the rotor is at the point of maximum contact stress, a modified cycloidal segment is used. Because the modified cycloidal segment ensures that the acceleration at the beginning and end of the stroke is zero, soft impacts are eliminated, and the jump is transformed into a finite value. Ultimately, extremely smooth and stable dynamic characteristics that are very suitable for high-speed motion are obtained. Under high-pressure conveying conditions, the sealing effect between the rotor and the pump body wall is good, ensuring long-term stable conveying pressure, reducing pulsation, and improving working efficiency.

[0025] The lift of the corrected cycloidal segment BC is h1, and the lift of the higher-order transition curve CD is 10-h1.

[0026] The first transition curve AB and the second transition curve DE are both straight line segments.

[0027] The equation of the first transition curve AB is: ; Where 0 < t < π / 24, R is the radius of the base circle, R = 16 mm.

[0028] The equation of the corrected cycloid segment BC is: ; Where π / 24 < t < 6*π / 24, R is the base circle radius, R = 16 mm, and h1 is the lift of the corrected cycloidal segment BC.

[0029] The equation for the higher-order transition curve CD is: ; Where 5*π / 12<t<10*π / 12, R is the radius of the base circle, R=16mm; 0.9549 is the final velocity of the corrected cycloidal segment BC, 6*π / 24<t<11*π / 24, R is the base circle radius, R=16mm, a3, a4, a5 are the coefficients of the fifth-order polynomial, a3 is -0.0087079143, a4 is 0.0004157723, a5 is -0.00000000000000000007.

[0030] The equation for the second transition curve DE is: ; Where 11*π / 24<t<12*π / 24, R is the radius of the base circle, R=16mm.

[0031] The following is a method for determining the profile of a wear-resistant, low-pulsation traveling wave pump: 1) First, set the rotor base circle radius R, R=16mm, and draw the straight line segment according to the following equation: The equation of the first transition curve AB is: ; Where 0 < t < π / 24; 2) Then, taking the total lift of segment BD as 10mm, determine the lift of the corrected cycloidal segment BC as h1. Because the corrected cycloidal segment can provide a smooth motion transition, curve BC is determined to be the corrected cycloidal segment, and its equation is: ; Where π / 24 < t < 6*π / 24, the effect of the corrected cycloid is to make its acceleration zero at the beginning and end of the stroke, thereby eliminating soft impact and turning the jump into a finite value.

[0032] 3) Next, draw the higher-order transition curve CD. The higher-order transition curve CD is a fifth-order polynomial curve with a lift of 10-h1. The initial velocity is the final velocity of the corrected cycloidal segment BC, and the final velocity is 0. The resulting fifth-order polynomial equation is: ; 0.9549 is the final velocity of the corrected cycloidal segment BC, 6*π / 24<t<11*π / 24, a3, a4, and a5 are the coefficients of the fifth-order polynomial, a3 is -0.0087079143, a4 is 0.0004157723, and a5 is -0.00000000000000000007. By setting the high-order transition curve CD, the initial velocity can be 0 when reaching the next straight segment without any sudden change in velocity, thus achieving a smoother transition to the next second transition curve DE.

[0033] 4) Draw the second transition curve DE connecting the segment to the fifth-degree polynomial curve, with an initial velocity of 0. Its equation is: ; Among them, 11*π / 24<t<12*π / 24.

[0034] like Figure 6 As shown, this invention discloses a traveling wave pump, comprising an integrally formed sleeve 1 and a rotor body 2. The rotor body 2 is distributed on the outer circumferential side of the sleeve 1. The sleeve 1 is provided with interconnected shaft holes 3 and stepped holes 4. The edge of the rotor body 2 adopts a wear-resistant, low-pulsation traveling wave pump profile as described above. The above are merely specific embodiments of the present invention, but the technical features of the present invention are not limited thereto. Any simple changes, equivalent substitutions, or modifications made based on the present invention to achieve substantially the same technical effect are all covered within the protection scope of the present invention.

Claims

1. A wear-resistant, low-pulsation traveling wave pump profile, characterized in that: The 1 / 4 segment of the profile is composed of a first transition curve AB, a modified cycloid segment BC, a higher-order transition curve CD, and a second transition curve DE. The first transition curve AB is connected to the second transition curve DE through the modified cycloid segment BC and the higher-order transition curve CD.

2. The wear-resistant, low-pulsation traveling wave pump profile according to claim 1, characterized in that: Both the first transition curve AB and the second transition curve DE are straight line segments.

3. The wear-resistant, low-pulsation traveling wave pump profile according to claim 1, characterized in that: The equation of the first transition curve AB is: ； Where 0 < t < π / 24, and R is the radius of the base circle.

4. The wear-resistant, low-pulsation traveling wave pump profile according to claim 1, characterized in that: The lift of the modified cycloidal segment BC is h1, and the lift of the higher-order transition curve CD is 10-h1.

5. The wear-resistant, low-pulsation traveling wave pump profile according to claim 4, characterized in that: The equation of the modified cycloid segment BC is: ； Where π / 24 < t < 6*π / 24, R is the base circle radius, and h1 is the lift of the corrected cycloidal segment BC.

6. The wear-resistant, low-pulsation traveling wave pump profile according to claim 1, characterized in that: The equation for the higher-order transition curve CD is: ； Where 5*π / 12<t<10*π / 12, and R is the radius of the base circle; 0.9549 is the final velocity of the modified cycloidal segment BC, 6*π / 24<t<11*π / 24, and R is the radius of the base circle.

7. The wear-resistant, low-pulsation traveling wave pump profile according to claim 1, characterized in that: The equation for the second transition curve DE is: ； Where 11*π / 24<t<12*π / 24, and R is the radius of the base circle.

8. The wear-resistant, low-pulsation traveling wave pump profile according to claim 1, characterized in that: The profile is an axisymmetric structure.

9. A traveling wave pump, comprising an integrally formed sleeve and a rotor body, the rotor body being distributed on the outer circumferential side of the sleeve, the sleeve having interconnected shaft holes and stepped holes, characterized in that: The edge of the rotor body adopts a wear-resistant, low-pulsation traveling wave pump profile as described in any one of claims 1 to 8.

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