Molded line design method of corrosion-resistant multi-cavity plum pump

Abstract

The invention discloses a molded line design method for a corrosion-resistant multi-cavity plum pump. The molded line design method comprises the following steps that S1, molded line parameters are designed; s2, designing an outer rotor; and S3, designing an inner rotor. The design method is simple in step, the molded lines of the inner rotor and the outer rotor can be accurately meshed in the whole running process, a suction cavity and a discharge cavity can be separated through meshing points, stable running and high efficiency of the pump are ensured, the inner rotor and the outer rotor rotate around the centers of the inner rotor and the outer rotor, a closed cavity is formed through molded line combination, and gas compression is achieved; meanwhile, the molded line overcomes the defects that a traditional circular rotor air cylinder molded line is simple, the area utilization rate is low, flow fluctuation is too large, and the defect that an asymmetric structure needs dynamic balance is overcome.

Description

Technical Field

[0001] This invention relates to the field of plum blossom pump profile design technology, and in particular to a profile design method for a corrosion-resistant multi-chamber plum blossom pump. Background Technology

[0002] Energy storage is the process of storing energy through a medium or device and releasing it when needed. A significant amount of heat is generated during energy storage, primarily from energy conversion and the physical or chemical changes in the storage materials. Furthermore, in practical applications, the electrochemical reactions during charging and discharging also generate heat. If this heat cannot be effectively dissipated from the energy storage system, it may lead to an increase in the internal temperature of the system, thereby affecting the performance and safety of the energy storage materials.

[0003] In the field of energy storage, refrigerant is typically used to remove heat from the system and lower its internal temperature. During refrigerant transport, a pump is needed to power the process, thereby removing heat from the system, lowering the temperature, extending the lifespan of the energy storage equipment, and improving safety and reliability. A swivel pump is generally used for refrigerant transport.

[0004] The rotor is an important component of the plum blossom pump. Traditional double circular rotors are limited by the single-chamber structure, resulting in inherent defects such as low gas transport efficiency and significant flow pulsation. At the same time, the rotor profile design is relatively complex. Summary of the Invention

[0005] The purpose of this invention is to provide a technical solution for the profile design method of a corrosion-resistant multi-chamber plum blossom pump, addressing the shortcomings of existing technologies. This design method is simple in steps and can not only ensure that the profiles of the inner and outer rotors are precisely meshed throughout the operation, with the meshing point separating the suction chamber and the discharge chamber to ensure stable operation and high efficiency of the pump, but also that the inner and outer rotors rotate around their respective centers, forming a closed chamber through the combination of profiles to achieve gas compression. At the same time, this profile overcomes the shortcomings of traditional circular rotor cylinder profiles, such as simple design, low area utilization, excessive flow fluctuations, and the need for dynamic balancing to overcome asymmetrical structures.

[0006] To solve the above-mentioned technical problems, the present invention adopts the following technical solution: A method for designing the profile of a corrosion-resistant multi-chamber plum blossom pump, characterized by the following steps: S1, Profile Parameter Design Determine the number of blades for the inner and outer rotors of the plum blossom pump, and design the profile design parameters for the inner and outer rotors. S2, External Rotor Design Based on the profile design parameters, the profile of the first worm claw of the outer rotor is designed. The profile of the first worm claw is composed of arc segments AB, BC, DE and EF connected in sequence. The equation of the circular arc AB is: ; Where a1 is the X coordinate of the center of the arc segment AB, b1 is the Y coordinate of the center of the arc segment AB, r1 is the radius of the arc segment AB, and θ1 is the angular parameter variable of the arc segment AB. The equation of the circular arc BC is: ; Where a2 is the X coordinate of the center of the arc segment BC, b2 is the Y coordinate of the center of the arc segment BC, r2 is the radius of the arc segment BC, and θ2 is the angular parameter variable of the arc segment BC. The equation of the circular arc DE is: ; Where a3 is the X coordinate of the center of the arc segment DE, b3 is the Y coordinate of the center of the arc segment DE, r3 is the radius of the arc segment DE, and θ3 is the angular parameter variable of the arc segment DE. The equation of the circular arc EF is: ; Where a4 is the X coordinate of the center of the arc segment EF, b4 is the Y coordinate of the center of the arc segment EF, r4 is the radius of the arc segment EF, and θ4 is the angular parameter variable of the arc segment EF. S3, Internal Rotor Design Based on the profile design parameters, the profile of the second worm claw of the inner rotor is designed. The second worm claw is composed of arc segments A'B', B'C', D'E' and E'F connected in sequence. The equation of the circular arc segment A'B' is: ; Where a1 is the X coordinate of the center of the arc segment AB, b1 is the Y coordinate of the center of the arc segment AB, r1 is the radius of the arc segment AB, θ1 is the angle parameter variable corresponding to the arc segment AB, E is the straight-line distance between the inner rotor rotation center O' and the outer rotor rotation center O, and Φ2 is the angle of rotation of the coordinate system X2O'Y2. The equation of the circular arc segment B'C' is: ; Where a2 is the X coordinate of the center of the arc segment BC, b2 is the Y coordinate of the center of the arc segment BC, r2 is the radius of the arc segment BC, θ2 is the angular parameter variable of the arc segment BC, E is the straight-line distance between the inner rotor rotation center O' and the outer rotor rotation center O, and Φ2 is the angle of rotation of the coordinate system X2O'Y2. The equation of the circular arc segment D'E' is: ; Where a3 is the X coordinate of the center of the arc segment DE, b3 is the Y coordinate of the center of the arc segment DE, r3 is the radius of the arc segment DE, θ3 is the angular parameter variable of the arc segment DE, E is the straight-line distance between the inner rotor rotation center O' and the outer rotor rotation center O, and Φ2 is the angle of rotation of the coordinate system X2O'Y2. The equation of the circular arc segment E'F' is: ; Where a4 is the X coordinate of the center of the arc segment EF, b4 is the Y coordinate of the center of the arc segment EF, r4 is the radius of the arc segment EF, θ4 is the angular parameter variable of the arc segment EF, E is the straight-line distance between the inner rotor rotation center O' and the outer rotor rotation center O, and Φ2 is the angle of rotation of the coordinate system X2O'Y2.

[0007] This design method is simple in steps and can not only ensure that the inner and outer rotor profiles are precisely meshed throughout the operation, but also separate the suction chamber and discharge chamber at the meshing point, ensuring the smooth operation and high efficiency of the pump. Furthermore, the inner and outer rotors rotate around their respective centers and form a closed chamber through the combination of profiles to achieve gas compression. At the same time, this profile makes up for the shortcomings of traditional circular rotor cylinder profiles, such as simple profiles, low area utilization, excessive flow fluctuations, and the need for dynamic balancing to overcome asymmetrical structures.

[0008] Furthermore, in step S2, the circular arc segment BC and the circular arc segment DE are connected by a straight line segment CD. The equation of the straight line segment CD is: ; Where n is the Y-coordinate of the center of the arc segment BC, and r2 is the radius of the arc segment BC.

[0009] Furthermore, in step S2, the range of the angle parameter variable θ1 for arc segment AB is -0.1526π < θ1 < -π / 2, the range of the angle parameter variable θ2 for arc segment BC is -0.3475π < θ2 < π / 2, the range of the angle parameter variable θ3 for arc segment DE is 0.4267π < θ3 < 1.5π, and the range of the angle parameter variable θ4 for arc segment EF is 0 ≤ θ4 < π / 2.

[0010] Furthermore, the profile of the second worm claw of the inner rotor is a conjugate curve obtained by transforming the profile of the first worm claw of the outer rotor using the meshing theorem.

[0011] Furthermore, in step S3, the circular arc segment B'C' and the circular arc segment D'E' are connected by a straight line segment C'D', the equation of which is: ; Where n is the Y-coordinate of the center of the arc segment BC, r2 is the radius of the arc segment BC, and E is the straight-line distance between the inner rotor rotation center O' and the outer rotor rotation center O.

[0012] Furthermore, in step S3, the range of the angle parameter variable θ1 corresponding to the arc segment AB is -π / 2 < θ1 < -0.1526π, the range of the angle parameter variable θ2 corresponding to the arc segment BC is -0.3475π < θ2 < π / 2, the range of the angle parameter variable θ3 corresponding to the arc segment DE is 0.4267π < θ3 < 1.5π, and the range of the angle parameter variable θ4 corresponding to the arc segment EF is 0 < θ4 < 0.3929π.

[0013] Furthermore, the profile is an axisymmetric structure, formed by the outer rotor being fixed and the inner rotor being formed by the eccentric rotation and meshing of the outer rotor.

[0014] The present invention, by adopting the above-described technical solution, has the following beneficial effects: The profile design method of this invention is simple in steps. It can not only ensure that the inner and outer rotor profiles are precisely meshed throughout the operation, and the meshing point can separate the suction chamber and the discharge chamber, ensuring the smooth operation and high efficiency of the pump, but also that the inner and outer rotors rotate around their respective centers and form a closed chamber through the combination of profiles to achieve gas compression. At the same time, this profile makes up for the shortcomings of traditional circular rotor cylinder profiles, such as simple profiles, low area utilization, excessive flow fluctuations, and the need for dynamic balancing to overcome asymmetrical structures. Attached Figure Description

[0015] The present invention will be further described below with reference to the accompanying drawings: Figure 1 A flowchart illustrating the profile design method of a corrosion-resistant multi-chamber plum blossom pump according to the present invention; Figure 2 This is a schematic diagram of the profile of the outer rotor in this invention; Figure 3 This is a schematic diagram of the profile of the outer rotor in this invention; Figure 4 This is a schematic diagram of the meshing profile of the first worm claw and the second worm claw in this invention; Figure 5These are schematic diagrams of the rotor profile at meshing point M before and after coordinate transformation (a and b). Figure 6 This is a schematic diagram of the structure of the inner and outer rotors of the present invention, which includes two sets of worm gear assemblies, three sets of worm gear assemblies, and four sets of worm gear assemblies (i.e., corresponding to two blades, three blades, and four blades).

[0016] In the figure: 1-Outer rotor; 101-First worm claw portion; 102-First worm claw groove; 2-Inner rotor; 201-Second worm claw part; 202-Second worm claw groove. Detailed Implementation

[0017] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0018] 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.

[0019] 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.

[0020] like Figures 1 to 5 As shown, this invention provides a profile design method for a corrosion-resistant multi-chamber plum blossom pump, comprising the following steps: S1, Profile Parameter Design Determine the number of blades for the inner and outer rotors of the plum blossom pump, and design the profile design parameters for the inner and outer rotors. S2, External Rotor Design Based on the profile design parameters, the profile of the first worm claw of the outer rotor is designed. The profile of the first worm claw is composed of arc segments AB, BC, DE and EF connected in sequence. The equation of the circular arc AB is: ; Where a1 is the X coordinate of the center of the arc segment AB, b1 is the Y coordinate of the center of the arc segment AB, r1 is the radius of the arc segment AB, and θ1 is the angle parameter variable of the arc segment AB. The range of the angle parameter variable θ1 of the arc segment AB is -0.1526π < θ1 < -π / 2.

[0021] The equation of the circular arc BC is: ; Where a2 is the X coordinate of the center of the arc segment BC, b2 is the Y coordinate of the center of the arc segment BC, r2 is the radius of the arc segment BC, and θ2 is the angle parameter variable of the arc segment BC. The value range of the angle parameter variable θ2 of the arc segment BC is -0.3475π<θ2<π / 2.

[0022] The circular arc segment BC and the circular arc segment DE are connected by the straight line segment CD. The equation of the straight line segment CD is: ; Where n is the Y-coordinate of the center of the arc segment BC, and r2 is the radius of the arc segment BC.

[0023] The equation of the circular arc DE is: ; Where a3 is the X coordinate of the center of the arc segment DE, b3 is the Y coordinate of the center of the arc segment DE, r3 is the radius of the arc segment DE, and θ3 is the angle parameter variable of the arc segment DE. The value range of the angle parameter variable θ3 of the arc segment DE is 0.4267π < θ3 < 1.5π.

[0024] The equation of the circular arc EF is: ; Where a4 is the X coordinate of the center of the arc segment EF, b4 is the Y coordinate of the center of the arc segment EF, r4 is the radius of the arc segment EF, and θ4 is the angle parameter variable of the arc segment EF. The value range of the angle parameter variable θ4 of the arc segment EF is 0≤θ4<π / 2.

[0025] S3, Internal Rotor Design The profile of the second worm claw of the inner rotor is a conjugate curve obtained by coordinate transformation of the profile of the first worm claw of the outer rotor and using the meshing theorem.

[0026] Based on the profile design parameters, the profile of the second worm claw of the inner rotor is designed. The second worm claw is composed of arc segments A'B', B'C', D'E' and E'F connected in sequence. The equation of the circular arc segment A'B' is: ; Where a1 is the X coordinate of the center of the circle corresponding to arc segment AB, b1 is the Y coordinate of the center of the circle corresponding to arc segment AB, r1 is the radius of arc segment AB, θ1 is the angle parameter variable corresponding to arc segment AB, and the value range of the angle parameter variable θ1 corresponding to arc segment AB is -π / 2 < θ1 < -0.1526π, E is the straight-line distance between the inner rotor rotation center O' and the outer rotor rotation center O, and Φ2 is the angle of rotation of coordinate system X2O'Y2; The equation of the circular arc segment B'C' is: ; Where a2 is the X coordinate of the center of the arc segment BC, b2 is the Y coordinate of the center of the arc segment BC, r2 is the radius of the arc segment BC, θ2 is the angle parameter variable of the arc segment BC, the value range of the angle parameter variable θ2 of the arc segment BC is -0.3475π<θ2<π / 2, E is the straight-line distance between the inner rotor rotation center O' and the outer rotor rotation center O, and Φ2 is the angle of rotation of the coordinate system X2O'Y2; The circular arc segments B'C' and D'E' are connected by a straight line segment C'D', the equation of which is: ; Where n is the Y-coordinate of the center of the arc segment BC, r2 is the radius of the arc segment BC, and E is the straight-line distance between the inner rotor rotation center O' and the outer rotor rotation center O.

[0027] The equation of the circular arc segment D'E' is: ; Where a3 is the X coordinate of the center of the arc segment DE, b3 is the Y coordinate of the center of the arc segment DE, r3 is the radius of the arc segment DE, θ3 is the angle parameter variable of the arc segment DE, and the value range of the angle parameter variable θ3 of the arc segment DE is 0.4267π<θ3<1.5π, E is the straight-line distance between the inner rotor rotation center O' and the outer rotor rotation center O, and Φ2 is the angle of rotation of the coordinate system X2O'Y2; The equation of the circular arc segment E'F' is: ; Where a4 is the X coordinate of the center of the arc segment EF, b4 is the Y coordinate of the center of the arc segment EF, r4 is the radius of the arc segment EF, θ4 is the angle parameter variable of the arc segment EF, and the value range of the angle parameter variable θ4 of the arc segment EF is 0 < θ4 < 0.3929π, E is the straight-line distance between the inner rotor rotation center O' and the outer rotor rotation center O, and Φ2 is the angle of rotation of the coordinate system X2O'Y2.

[0028] This design method is simple in steps and can not only ensure that the inner and outer rotor profiles are precisely meshed throughout the operation, but also separate the suction chamber and discharge chamber at the meshing point, ensuring the smooth operation and high efficiency of the pump. Furthermore, the inner and outer rotors rotate around their respective centers and form a closed chamber through the combination of profiles to achieve gas compression. At the same time, this profile makes up for the shortcomings of traditional circular rotor cylinder profiles, such as simple profiles, low area utilization, excessive flow fluctuations, and the need for dynamic balancing to overcome asymmetrical structures.

[0029] The profile is an axisymmetric structure, formed by the outer rotor being fixed and the inner rotor being formed by the eccentric rotation and meshing of the outer rotor.

[0030] Set the outer diameter of inner rotor 2 to 25mm, the outer diameter of outer rotor 1 to 26.5mm, and the eccentricity e between the rotors to 1mm. Draw the circular arc segments AB and BC.

[0031] The equations for the circular arc segments AB and BC of the outer rotor 1 are as follows: ; ; Where a1 is the X-coordinate of the center of the arc segment AB, b1 is the Y-coordinate of the center of the arc segment AB, r1 is the radius of the arc segment AB, θ1 is the angle parameter variable of the arc segment AB, a2 is the X-coordinate of the center of the arc segment BC, b2 is the Y-coordinate of the center of the arc segment BC, r2 is the radius of the arc segment BC, and θ2 is the angle parameter variable of the arc segment BC.

[0032] a1=0, r1=22.5, -0.1526π<θ1<-π / 2, b1=29.8, -0.3475π<θ2<π / 2, a2=9, b2=12.5, r2=3.

[0033] To increase the airtightness of the inlet and outlet and to increase their size, and to prevent excessive instantaneous pressure, a straight section CD is left at the inlet and outlet.

[0034] The equations for the straight segment CD and the circular arc segment DE of the outer rotor 1 are as follows: ; ; Where n is the Y-coordinate of the center of the arc segment BC, r2 is the radius of the arc segment BC, a3 is the X-coordinate of the center of the arc segment DE, b3 is the Y-coordinate of the center of the arc segment DE, r3 is the radius of the arc segment DE, and θ3 is the angular parameter variable of the arc segment DE.

[0035] Among them, a3=7.5, b3=20, 0.4267π<θ3<1.5π, n=12.5, r2=3, r3=3.

[0036] The equation of the circular arc segment EF of the outer rotor 1 is: ; Where a4 is the X coordinate of the center of the arc segment EF, b4 is the Y coordinate of the center of the arc segment EF, r4 is the radius of the arc segment EF, θ4 is the angular parameter variable of the arc segment EF, a4=0, b4=0, 0≤θ4<π / 2.

[0037] a4=0, r4=20, 0<θ4<0.3929π, b4=0.

[0038] The second worm gear section 201 of the inner rotor 2 is composed of sequentially connected arc segments A'B', arc segment B'C', straight segment C'D', arc segment D'E', and arc segment E'F'.

[0039] The second worm claw section 201 profile of the inner rotor 2 is a conjugate curve obtained by transforming the first worm claw section 101 profile of the outer rotor 1 using the meshing theorem.

[0040] Outer rotor 1 rotates around point O, and inner rotor 2 rotates around O'. Points O and O' are the instantaneous centers of inner rotor 2 and outer rotor 1, respectively. The angular velocity of outer rotor 1 is... The angular velocity of the inner rotor 2 is The distance between the centers of the inner rotor 2 and the outer rotor 1 is an eccentricity e, that is, the distance between points O and O' is e.

[0041] The equation of the circular arc segment A'B' of the inner rotor 2 is: ; Where a1 is the X coordinate of the center of the arc segment AB, b1 is the Y coordinate of the center of the arc segment AB, r1 is the radius of the arc segment AB, θ1 is the angle parameter variable corresponding to the arc segment AB, -π / 2<θ1<-0.1526π, E is the straight-line distance between the rotation center O' of the inner rotor 2 and the rotation center O of the outer rotor 1, and Φ2 is the angle of rotation of the coordinate system X2O'Y2.

[0042] a1=0, r1=22.5, -π / 2<θ1<-0.1526π, b1=29.8, E=1.5, Ф2=π / 6.

[0043] Arc segments DE and BC are located on opposite sides of the inlet and outlet. To ensure that both sides of the inlet and outlet have the same airtightness, arc segments DE and D'E', and arc segments BC and B'C' have the same meshing process. Therefore, arc segments DE and B'C', and arc segments BC and D'E' are drawn as arcs with the same radius. Line segments CD and C'D' are the endpoints of one meshing process.

[0044] The equation of the circular arc segment B'C' is: ; Where a2 is the X coordinate of the center of the arc segment BC, b2 is the Y coordinate of the center of the arc segment BC, r2 is the radius of the arc segment BC, θ2 is the angular parameter variable of the arc segment BC, -0.3475π<θ2<π / 2, E is the straight-line distance between the rotation center O' of the inner rotor 2 and the rotation center O of the outer rotor 1, and Φ2 is the angle of rotation of the coordinate system X2O'Y2.

[0045] -0.3475π<θ2<π / 2, a2=9, b2=12.5, r2=3, E=1.5, Ф2=π / 6.

[0046] A certain distance must be maintained between the arc segment B'C' and the arc segment E'F' to ensure the strength of the rotor; therefore, the straight segment C'D' is introduced.

[0047] The equation of the straight line segment C'D' of the inner rotor 2 is: ; Where n is the Y-coordinate of the center of the arc segment BC, r2 is the radius of the arc segment BC, and E is the straight-line distance between the rotation center O' of the inner rotor 2 and the rotation center O of the outer rotor 1. n=12.5, r2=3, E=1.5.

[0048] The equations of the circular arc segment D'E' are as follows: ; Where a3 is the X coordinate of the center of the arc segment DE, b3 is the Y coordinate of the center of the arc segment DE, r3 is the radius of the arc segment DE, θ3 is the angle parameter variable of the arc segment DE, 0.4267π<θ3<1.5π, E is the straight-line distance between the rotation center O' of the inner rotor 2 and the rotation center O of the outer rotor 1, and Φ2 is the angle of rotation of the coordinate system X2O'Y2, 0.4267π<θ3<1.5π.

[0049] a3=7.5, b3=20, 0.4267π<θ3<1.5π, Ф2=π / 6, E=1.5, r3=3.

[0050] The equation for the circular arc segment E'F' of the inner rotor 2 is: ; Where a4 is the X coordinate of the center of the arc segment EF, b4 is the Y coordinate of the center of the arc segment EF, r4 is the radius of the arc segment EF, θ4 is the angular parameter variable of the arc segment EF (0 < θ4 < 0.3929π), E is the straight-line distance between the rotation center O' of the inner rotor 2 and the rotation center O of the outer rotor 1, and Φ2 is the angle of rotation of the coordinate system X2O'Y2 (0 < θ4 < 0.3929π).

[0051] a4=0, r4=20, 0<θ4<0.3929π, b4=0, E=1.5, r3=3.

[0052] Through the above structural design, not only can the inner and outer rotor profiles be precisely meshed throughout the entire operation process, and the meshing point can separate the suction chamber and the discharge chamber, ensuring the smooth operation and high efficiency of the pump, but also the inner and outer rotors rotate around their respective centers, forming a closed chamber through the combination of profiles to achieve gas compression. At the same time, this profile makes up for the shortcomings of traditional circular rotor cylinder profiles, such as simple profiles, low area utilization, excessive flow fluctuations, and the need for dynamic balancing to overcome asymmetrical structures.

[0053] The present invention discloses a plum blossom pump, comprising an outer rotor 1 and an inner rotor 2. The outer rotor 1 includes at least two sets of first worm gear assemblies, each first worm gear assembly including two first worm gear portions 101 arranged in opposite directions. Adjacent first worm gear portions 101 and the outer rotor 1 cooperate to form a first worm gear groove 102. The inner rotor 2 includes at least two sets of second worm gear assemblies, each second worm gear assembly including two second worm gear portions 201 arranged in opposite directions. Adjacent second worm gear portions 201 and the inner rotor 2 cooperate to form a second worm gear groove 202. The outer rotor 1 is fixed, and the inner rotor rotates eccentrically along the outer rotor 1, meshing to form a tooth profile. The tooth profile adopts the corrosion-resistant multi-chamber plum blossom pump profile as described above.

[0054] like Figure 6 As shown in a, b, and c, these are schematic diagrams of the structure of the inner and outer rotors 1 with different numbers of blades according to the present invention.

[0055] 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 profile design method for a corrosion-resistant multi-chamber plum blossom pump, characterized in that... Includes the following steps: S1, Profile Parameter Design Determine the number of blades for the inner and outer rotors of the plum blossom pump, and design the profile design parameters for the inner and outer rotors. S2, External Rotor Design Based on the aforementioned profile design parameters, the profile of the first worm claw portion of the outer rotor is designed. The first worm claw portion profile is composed of sequentially connected arc segments AB, BC, DE, and EF. The equation of the circular arc segment AB is: ； Where a1 is the X coordinate of the center of the arc segment AB, b1 is the Y coordinate of the center of the arc segment AB, r1 is the radius of the arc segment AB, and θ1 is the angular parameter variable of the arc segment AB. The equation of the circular arc segment BC is: ； Where a2 is the X coordinate of the center of the arc segment BC, b2 is the Y coordinate of the center of the arc segment BC, r2 is the radius of the arc segment BC, and θ2 is the angular parameter variable of the arc segment BC. The equation of the circular arc segment DE is: ； Where a3 is the X coordinate of the center of the arc segment DE, b3 is the Y coordinate of the center of the arc segment DE, r3 is the radius of the arc segment DE, and θ3 is the angular parameter variable of the arc segment DE. The equation of the circular arc segment EF is: ； Where a4 is the X coordinate of the center of the arc segment EF, b4 is the Y coordinate of the center of the arc segment EF, r4 is the radius of the arc segment EF, and θ4 is the angular parameter variable of the arc segment EF. S3, Internal Rotor Design Based on the aforementioned profile design parameters, the profile of the second worm claw portion of the inner rotor is designed. The second worm claw portion is composed of sequentially connected arc segments A'B', B'C', D'E', and E'F. The equation of the circular arc segment A'B' is: ； Where a1 is the X coordinate of the center of the arc segment AB, b1 is the Y coordinate of the center of the arc segment AB, r1 is the radius of the arc segment AB, θ1 is the angle parameter variable corresponding to the arc segment AB, E is the straight-line distance between the inner rotor rotation center O' and the outer rotor rotation center O, and Φ2 is the angle of rotation of the coordinate system X2O'Y2. The equation of the circular arc segment B'C' is: ； Where a2 is the X coordinate of the center of the arc segment BC, b2 is the Y coordinate of the center of the arc segment BC, r2 is the radius of the arc segment BC, θ2 is the angular parameter variable of the arc segment BC, E is the straight-line distance between the inner rotor rotation center O' and the outer rotor rotation center O, and Φ2 is the angle of rotation of the coordinate system X2O'Y2. The equation of the circular arc segment D'E' is: ； Where a3 is the X coordinate of the center of the arc segment DE, b3 is the Y coordinate of the center of the arc segment DE, r3 is the radius of the arc segment DE, θ3 is the angular parameter variable of the arc segment DE, E is the straight-line distance between the inner rotor rotation center O' and the outer rotor rotation center O, and Φ2 is the angle of rotation of the coordinate system X2O'Y2. The equation of the circular arc segment E'F' is: ； Where a4 is the X coordinate of the center of the arc segment EF, b4 is the Y coordinate of the center of the arc segment EF, r4 is the radius of the arc segment EF, θ4 is the angular parameter variable of the arc segment EF, E is the straight-line distance between the inner rotor rotation center O' and the outer rotor rotation center O, and Φ2 is the angle of rotation of the coordinate system X2O'Y2.

2. The profile design method for a corrosion-resistant multi-chamber plum blossom pump according to claim 1, characterized in that: In step S2, the circular arc segment BC and the circular arc segment DE are connected by a straight line segment CD, the equation of which is: ； Where n is the Y-coordinate of the center of the arc segment BC, and r2 is the radius of the arc segment BC.

3. The profile design method for a corrosion-resistant multi-chamber plum blossom pump according to claim 1, characterized in that: In step S2, the range of the angle parameter variable θ1 of the arc segment AB is -0.1526π < θ1 < -π / 2, the range of the angle parameter variable θ2 of the arc segment BC is -0.3475π < θ2 < π / 2, the range of the angle parameter variable θ3 of the arc segment DE is 0.4267π < θ3 < 1.5π, and the range of the angle parameter variable θ4 of the arc segment EF is 0 ≤ θ4 < π / 2.

4. The profile design method for a corrosion-resistant multi-chamber plum blossom pump according to claim 1, characterized in that: The profile of the second worm claw of the inner rotor is a conjugate curve obtained by transforming the profile of the first worm claw of the outer rotor using the meshing theorem.

5. The profile design method for a corrosion-resistant multi-chamber plum blossom pump according to claim 1, characterized in that: In step S3, the circular arc segment B'C' and the circular arc segment D'E' are connected by a straight line segment C'D', the equation of which is: ； Where n is the Y-coordinate of the center of the arc segment BC, r2 is the radius of the arc segment BC, and E is the straight-line distance between the inner rotor rotation center O' and the outer rotor rotation center O.

6. The profile design method for a corrosion-resistant multi-chamber plum blossom pump according to claim 1, characterized in that: In step S3, the range of the angle parameter variable θ1 corresponding to the arc segment AB is -π / 2 < θ1 < -0.1526π, the range of the angle parameter variable θ2 corresponding to the arc segment BC is -0.3475π < θ2 < π / 2, the range of the angle parameter variable θ3 corresponding to the arc segment DE is 0.4267π < θ3 < 1.5π, and the range of the angle parameter variable θ4 corresponding to the arc segment EF is 0 < θ4 < 0.3929π.

7. The profile design method for a corrosion-resistant multi-chamber plum blossom pump according to claim 1, characterized in that: The profile is an axisymmetric structure, and the profile is formed by the outer rotor being fixed and the inner rotor being eccentrically rotated and meshed with the outer rotor.

Images