A push-pull composite magnetic transmission device and a method for determining an optimal load carrying working condition

Abstract

The present application belongs to the technical field of magnetic transmission, and discloses a push-torque composite magnetic transmission device and a method for determining the optimal load working condition. The push-torque composite magnetic transmission device generates repulsive force to bear axial thrust through the transmission-push magnetic group installed on the end surface of the inner and outer hubs, and generates attractive force to bear rotating torque through the transmission-torque magnetic group installed on the circumferential surface of the inner and outer hubs, so as to realize the composite output of axial thrust and rotating torque, and has the technical advantages of short axial length, compact structure, high load capacity and the like. In order to make the comprehensive performance of the push-torque composite magnetic transmission device in the optimal working interval, a method for determining the optimal load working condition is provided, which considers the weakening effect of the application of rotating torque on axial thrust, and determines the optimal load working condition by solving the maximum torque angle difference, thereby providing a theoretical basis for the development of composite magnetic transmission devices with high efficiency and high load capacity.

Description

Technical Field

[0001] This invention belongs to the field of magnetic transmission technology and relates to a push-torsion composite magnetic transmission device and a method for determining the optimal load-bearing conditions. Background Technology

[0002] Traditional underwater propulsion systems often employ a series structure of "thrust bearing + rotary drive coupling" to achieve a combined output of axial thrust and rotational torque. This results in a long axial length and bulky structure, limiting the miniaturization design of underwater equipment. Furthermore, underwater propellers may encounter unexpected situations such as entanglement or jamming during navigation. Traditional rigid transmission systems directly transmit the impact torque to the motor, potentially leading to motor stall and burnout or gearbox damage. Magnetic drive technology utilizes the magnetic force of interaction between magnetic fields to achieve non-contact transmission of force and torque. It is widely used in fields with extremely high sealing requirements, such as chemical, pharmaceutical, food, and underwater equipment. When the load exceeds the design value, "slippage" can provide overload protection for the drive system, effectively improving the survivability of underwater equipment in complex environments. Researching specific magnetic circuit designs and permanent magnet arrangements to achieve a combined load-bearing capacity of axial thrust and rotational torque is of great significance for further reducing the size of underwater equipment transmission systems and guiding miniaturization design.

[0003] To address the challenges of applying magnetic drive technology in underwater equipment transmission systems, He Tao, Ke Zhiwu, and Dai Lu proposed a magnetically supported flexible propulsion shaft system and ship in their patent "Magnetically Supported Flexible Propulsion Shaft System and Ship" (CN202210199802.4). This system utilizes a magnetic coupling to transmit rotational torque between the drive unit and the power unit, and a magnetic thrust bearing to withstand the axial thrust generated by the propeller. This achieves flexible support while reducing vibration transmitted from the shaft system to the hull. However, the axial thrust and rotational torque bearing of the proposed shaft system still rely on the magnetic thrust bearing and magnetic coupling, respectively. A simple combination cannot achieve simultaneous thrust and torque bearing, and the shaft system is excessively long and structurally complex.

[0004] In response to the development of magnetic composite transmission devices, Yang Qingsong, Gao Xikan, and Zhang Jichang proposed a composite magnetic transmission device in their patent "A Composite Magnetic Transmission Device" (CN202220193198.X). This device allows the inner rotor to drive the outer rotor in both axial linear motion and rotational motion. The device utilizes the axial push-pull force generated by the misalignment of the inner and outer axial magnets to achieve synchronous axial motion. However, the axial push-pull force generated by the misalignment of the inner and outer magnets is relatively small, only meeting the requirements for synchronous motion and not the axial load-bearing requirements of underwater equipment. Furthermore, the magnitude of the axial force generated by the device is related to the distance of the axial misalignment between the inner and outer rotors. Due to the reduction in the area of ​​the magnetic poles facing each other when misaligned, the actual torque bearing capacity decreases.

[0005] To address the aforementioned issues, this invention proposes a novel push-torsion composite magnetic transmission device that can achieve a composite output of axial thrust and rotational torque. Based on this, a method for determining its optimal load-bearing conditions is provided, enabling the overall performance of the transmission device to be within its optimal operating range. This provides a theoretical basis for the development of high-efficiency, high-load-bearing composite magnetic transmission devices. Summary of the Invention

[0006] To overcome the shortcomings of existing technologies, this invention provides a push-torsion composite magnetic transmission device. Its working principle utilizes the repulsive force generated by the inner and outer rotor push-torsion magnetic groups embedded in the end faces of the inner and outer hubs to withstand the axial thrust, and the tangential attractive force generated by the inner and outer rotor torsion magnetic groups embedded in the circumferential surfaces of the inner and outer hubs to withstand the rotational torque, thus achieving simultaneous bearing of axial thrust and rotational torque. Considering that the reduction in the area of ​​the magnetic poles facing each other during the axial movement of the inner rotor weakens the rotational torque, the axial width of the outer rotor torsion magnetic group is designed to be greater than that of the inner rotor torsion magnetic group to ensure that the effective working area remains unchanged, thereby ensuring that the axial movement of the inner rotor does not affect the magnitude of the rotational torque. Since the axial repulsive force generated by the inner and outer rotor push-torsion magnetic groups on the inner rotor is always present, aligning one end of the unequal-length inner and outer rotor torsion magnetic groups generates a reverse attractive force to balance the axial repulsive force, thus achieving force balance on the inner rotor in the axial direction. Furthermore, in order to ensure that the overall performance of the push-torsion composite magnetic transmission device of the present invention is within the optimal operating range, a method for determining the optimal load-bearing condition of the push-torsion composite magnetic transmission device is proposed. This method considers the weakening effect of the applied rotational torque on the axial thrust, and determines the optimal load-bearing condition range of the push-torsion composite magnetic transmission device of the present invention by solving for the optimal rotational torque value, thereby providing a theoretical basis for the development of a high-efficiency, high-load-bearing composite magnetic transmission device.

[0007] The technical solution of this invention: A push-torsion composite magnetic transmission device includes an outer hub 1, an outer rotor torsion-transmitting magnetic assembly 2, an outer rotor push-transmitting magnetic assembly 3, an inner rotor push-transmitting magnetic assembly 4, an inner rotor torsion-transmitting magnetic assembly 5, and an inner hub 6; wherein, the outer hub 1, the outer rotor torsion-transmitting magnetic assembly 2, and the outer rotor push-transmitting magnetic assembly 3 constitute the outer rotor, and the inner rotor push-transmitting magnetic assembly 4, the inner rotor torsion-transmitting magnetic assembly 5, and the inner hub 6 constitute the inner rotor; The outer rotor torsion transmission magnetic assembly 2, outer rotor thrust transmission magnetic assembly 3, inner rotor thrust transmission magnetic assembly 4, and inner rotor torsion transmission magnetic assembly 5 are divided at the same equal angle along the circumferential direction. During installation, the outer rotor torsion transmission magnetic assembly 2 and rotor thrust transmission magnetic assembly 3 on the outer rotor, and the inner rotor thrust transmission magnetic assembly 4 and inner rotor torsion transmission magnetic assembly 5 on the inner rotor, are strictly aligned according to the equal angle division results. The outer rotor torsion transmission magnetic assembly 2 and inner rotor torsion transmission magnetic assembly 5 are fixed in the annular grooves along the circumferential direction of the outer hub 1 and inner hub 6 respectively by embedding. The circumferential attraction between the outer rotor torsion transmission magnetic assembly 2 and inner rotor torsion transmission magnetic assembly 5 is used to bear the rotational torque. The axial width of the outer rotor torsion transmission magnetic assembly 2 is longer than that of the inner rotor torsion transmission magnetic assembly 5 to ensure that the effective working area and the rotational torque borne by the inner rotor torsion transmission magnetic assembly 5 remain unchanged during axial movement. One end of the outer rotor torsion transmission magnetic assembly 2 and inner rotor torsion transmission magnetic assembly 5 is in contact with the axial movement. The unequal and asymmetrical alignment of the outer rotor torsion magnetic assembly 2 and the inner rotor torsion magnetic assembly 5, with opposite directions of alignment, generates an attractive force on the inner rotor in the same direction as the axial movement. The outer rotor thrust magnetic assembly 3 and the inner rotor thrust magnetic assembly 4 are respectively surface-mounted to the shaft end mounting surfaces of the outer hub 1 and the inner hub 6. Both the outer rotor thrust magnetic assembly 3 and the inner rotor thrust magnetic assembly 4 are magnetized axially in opposite directions. The repulsive force between the outer rotor thrust magnetic assembly 3 and the inner rotor thrust magnetic assembly 4 is used to withstand the axial thrust and generate a repulsive force on the inner rotor in the opposite direction of the axial movement. By adjusting the initial axial air gap thickness between the outer rotor thrust magnetic assembly 3 and the inner rotor thrust magnetic assembly 4 and the axial width difference between the outer rotor torsion magnetic assembly 2 and the inner rotor torsion magnetic assembly 5, the repulsive and attractive forces on the inner rotor in the axial movement direction cancel each other out, achieving a balance in the initial force state.

[0008] A method for determining the optimal load-bearing conditions of a push-torsion composite magnetic transmission device, comprising the following steps: The first step is to determine the parameters of the push-torsion composite magnetic transmission device; The inner radius of the outer rotor torsion transmission magnetic assembly 2 is r 1. Axial width is l 1. Thickness is h The outer radius of the inner rotor torsion transmission magnetic assembly 5 is... r 2, axial width is l 2, thickness is h ,and l 1> l 2; The thickness of the outer rotor torsion magnetic assembly (2) is the same as the thickness of the inner rotor torsion magnetic assembly (5); The inner radii of the outer rotor thrust magnetic assembly 3 and the inner rotor thrust magnetic assembly 4 are both r 3, the outer radius is r 4. The axial width is l 3; The initial axial air gap thickness between the outer rotor drive magnetic assembly 3 and the inner rotor drive magnetic assembly 4 is d 0, the maximum displacement of the inner rotor along the axial direction of motion is d max The minimum axial air gap thickness is d min = d 0- d max The outer rotor torsion magnetic group 2, outer rotor thrust magnetic group 3, inner rotor thrust magnetic group 4, and inner rotor torsion magnetic group 5 are all divided at equal angles along the circumferential direction. i And the number of magnetic pole pairs N p =180 / i The residual magnetic flux density is B r The relative permeability is 1. m r Take here m r =1.05; the torsional angle difference between the inner and outer rotors under the action of rotational torque is α ; The second step is to establish the relationship between the rotational torque and the difference in torsion angle. First, the fundamental amplitude of the magnetic flux density in the air gap between the outer rotor torsion transmission magnetic group 2 and the inner rotor torsion transmission magnetic group 5 is determined using the equivalent magnetic circuit method. B g The calculation formula is as follows: (1) In the formula, α p The polar arc coefficient is taken here because both the outer rotor torsion transmission magnetic group 2 and the inner rotor torsion transmission magnetic group 5 are ideally arranged without gaps. α p =1; Then, because l 1≠ l 2. The effective axial overlap width between the outer rotor torsion transmission magnetic assembly 2 and the inner rotor torsion transmission magnetic assembly 5 l eq Limited by the shorter side, the calculation formula is as follows: (2) Finally, the relationship between rotational torque and torsional angle difference is established. T ( α The calculation formula is as follows: (3) In the formula, m 0 is the free permeability, and m 0 = 4 π ×10 -7 H / m; r mThe radius of the centerline of the air gap between the outer rotor torsion transmission magnetic assembly 2 and the inner rotor torsion transmission magnetic assembly 5 is given. r m It is calculated by the following formula: (4) The third step is to establish the relationship between axial thrust, torsional angle difference, and minimum axial air gap thickness. First, obtain the maximum theoretical repulsive force when the axial air gap thickness between the outer rotor push magnetic assembly 3 and the inner rotor push magnetic assembly 4 is zero and they are directly aligned. F 0, the calculation formula is as follows: (5) In the formula, A 0 represents the magnetic pole area of ​​a single outer rotor drive magnetic group 3 or inner rotor drive magnetic group 4, and A 0 is calculated using the following formula: (6) Then, the axial thrust attenuation coefficient caused by the change in the axial air gap thickness between the outer rotor thrust magnetic assembly 3 and the inner rotor thrust magnetic assembly 4 is obtained. K g The calculation formula is as follows: (7) In the formula, e It is a natural constant; t The distance between the magnetic poles is denoted as , and t It is calculated by the following formula: (8) Finally, the relationship between axial thrust, torsional angle difference, and minimum axial air gap thickness was established. F ( α , d min The calculation formula is as follows: (9) Step 4: Solve for the maximum value of the torsion angle difference; Since the application of rotational torque weakens the axial thrust, in order to ensure minimum axial thrust... F min For the maximum torsional angle difference α max As can be seen from step three, restrictions are imposed. α max The calculation formula is as follows: (10) Step 5: Determine the optimal load-bearing range; When the torsion angle difference α When =0, the maximum axial thrust is known from step three as follows:F max = F (0, d min )= K g F 0, from the second step we know the rotational torque is T (0) = 0; when the torsional angle difference α = α max At that time, from the third step, we know that the minimum axial thrust is F min From the second step, we know that the rotational torque is... T ( α max Therefore, the optimal load-bearing condition is: the axial thrust range is... F min ~ F max Rotational torque range is 0~ T ( α max The range of torsion angle difference is 0~ α max Thus, the optimal load-bearing conditions for the push-torsion composite magnetic transmission device have been determined.

[0009] The beneficial effects of this invention are that it proposes a push-torsion composite magnetic transmission device. The inner rotor push-torsion magnetic assembly and the outer rotor push-torsion magnetic assembly, mounted on the end faces of the inner and outer hubs, generate repulsive forces to withstand axial thrust. The inner rotor push-torsion magnetic assembly and the outer rotor push-torsion magnetic assembly, mounted on the circumferential surfaces of the inner and outer hubs, generate attractive forces to withstand rotational torque. This achieves a composite output of axial thrust and rotational torque, offering technical advantages such as short axial length, compact structure, and high load-bearing capacity. Furthermore, to ensure the overall performance of the push-torsion composite magnetic transmission device of this invention is within its optimal operating range, a method for determining its optimal load-bearing condition is proposed. This method considers the weakening effect of applied rotational torque on axial thrust and determines the optimal load-bearing condition by solving for the maximum torsional angle difference. This provides a theoretical basis for the development of high-efficiency, high-load-bearing composite magnetic transmission devices. Attached Figure Description

[0010] Figure 1 This is an assembly drawing of a push-torsion composite magnetic transmission device; Figure 2 This is an assembly drawing of the outer rotor of a push-torsion composite magnetic drive device; Figure 3 This is an assembly drawing of the rotor inside a push-torsion composite magnetic transmission device. Figure 4 for Figure 1 Middle xyz A sectional view of a plane; Figure 5 for Figure 1 Middle yz A sectional view of a plane; Figure 6 The curves show the variation of axial thrust and rotational torque with the difference in torsional angle. Figure 7 A flowchart of a method for determining the optimal load-bearing conditions of a push-torsion composite magnetic transmission device; In the diagram: 1-outer hub, 2-outer rotor torsion transmission magnetic assembly, 3-outer rotor thrust transmission magnetic assembly, 4-inner rotor thrust transmission magnetic assembly, 5-inner rotor torsion transmission magnetic assembly, 6-inner hub. Detailed Implementation

[0011] The specific embodiments of the present invention will be further described below with reference to the accompanying drawings and technical solutions.

[0012] Example A push-torque composite magnetic drive device with a minimum axial thrust of not less than 400 N and a maximum rotational torque of not less than 35 N·m is selected (see...). Figure 1 , Figure 2 and Figure 3 The optimal load-bearing conditions are determined through the following process: Figure 7 As shown, the steps are as follows: The first step is to determine the parameters of the push-torsion composite magnetic transmission device; like Figure 4 and Figure 5 The inner radius of the outer rotor torsion transmission magnetic group 2 r 1 = 0.034m, axial width l 1 = 0.038m, thickness h =0.006m; Outer radius of the inner rotor torsion transmission magnetic assembly 5 r 2 = 0.032m, axial width is l 2 = 0.03m, thickness h =0.006m; Inner radius of outer rotor transmission magnetic assembly 3 and inner rotor transmission magnetic assembly 4 r 3 = 0.018m, outer radius r 4 = 0.032m, axial width l 3 = 0.006m; Initial axial air gap thickness between the outer rotor drive magnetic assembly 3 and the inner rotor drive magnetic assembly 4. d 0 = 0.004m, the maximum displacement of the inner rotor along the axial direction of motion. d max =0.003m, minimum axial air gap thickness is d min = d 0- d max=0.001m; the outer rotor torsion magnetic group 2, the outer rotor thrust magnetic group 3, the inner rotor thrust magnetic group 4, and the inner rotor torsion magnetic group 5 are divided at equal angles along the circumferential direction. i =45deg, number of magnetic pole pairs N p = 180 / i =4, Residual magnetic flux density B r =1.41T, relative permeability m r =1.05; the torsional angle difference between the inner and outer rotors under the action of rotational torque is α ; The second step is to establish the relationship between the rotational torque and the difference in torsion angle. Substituting the known parameters into equations (1) to (4), we obtain: B g =1.04T l eg = l 2 = 0.03m r m =0.033m, the relationship between the rotational torque and the difference in torsional angle is: T ( α )=44.5482sin(4 α ); The third step is to establish the relationship between axial thrust, torsional angle difference, and minimum axial air gap thickness. Substituting the known parameters into equations (5) to (9), we obtain: A 0 = 2.7489 × 10 -4 m 2 , F 0 = 1739.5875 N t =0.0196m K g =0.4427, the relationship between axial thrust, torsional angle difference, and minimum axial air gap thickness. F ( α , d min )= F ( α ,0.001)=770.1074cos(4 α ); Step 4: Solve for the maximum value of the torsion angle difference; Take the minimum axial thrust F min =400N, substituting into equation (10) yields the maximum torsional angle difference. α max =14.7deg; Step 5: Determine the optimal load-bearing range; like Figure 6 As shown, from steps two through four, we can see that: α max =14.7deg F min =400N F max = F (0, 0.001) = 770.1 N T ( α max )= T (14.7) = 38.1 N·m; therefore, the optimal load conditions are: axial thrust range of 400~770.1 N, rotational torque range of 0~38.1 N·m, and torsional angle difference range of 0~14.7 deg; thus, the optimal load conditions of the push-torsion composite magnetic transmission device are determined.

Claims

1. A push-torsion composite magnetic transmission device, characterized in that, The push-torsion composite magnetic transmission device includes an outer hub (1), an outer rotor torsion magnetic group (2), an outer rotor push magnetic group (3), an inner rotor push magnetic group (4), an inner rotor torsion magnetic group (5), and an inner hub (6); wherein, the outer hub (1), the outer rotor torsion magnetic group (2), and the outer rotor push magnetic group (3) constitute the outer rotor, and the inner rotor push magnetic group (4), the inner rotor torsion magnetic group (5), and the inner hub (6) constitute the inner rotor; The outer rotor torsion magnetic group (2), the outer rotor thrust magnetic group (3), the inner rotor thrust magnetic group (4), and the inner rotor torsion magnetic group (5) are divided at the same angle along the circumferential direction. During installation, the outer rotor torsion magnetic group (2) and the rotor thrust magnetic group 3 on the outer rotor, as well as the inner rotor thrust magnetic group (4) and the inner rotor torsion magnetic group (5) on the inner rotor, are strictly aligned according to the equal angle division. The outer rotor torsion magnetic group (2) and the inner rotor torsion magnetic group (5) are respectively embedded. Fixed in the annular grooves along the circumferential direction of the outer hub (1) and the inner hub (6), the attraction force along the circumferential direction between the outer rotor torsion magnetic assembly (2) and the inner rotor torsion magnetic assembly (5) is used to bear the rotational torque; the axial width of the outer rotor torsion magnetic assembly (2) is longer than the axial width of the inner rotor torsion magnetic assembly (5) to ensure that the effective working area and the rotational torque borne by the inner rotor torsion magnetic assembly (5) remain unchanged during axial movement; the outer rotor torsion magnetic assembly (2) and the inner rotor torsion magnetic assembly (5) One end is aligned with the side opposite to the axial movement direction. The unequal length and asymmetrical alignment between the outer rotor torsion magnetic group (2) and the inner rotor torsion magnetic group (5) generate an attractive force on the inner rotor in the same direction as the axial movement direction. The outer rotor thrust magnetic group (3) and the inner rotor thrust magnetic group (4) are fixed on the shaft end mounting surfaces of the outer hub (1) and the inner hub (6), respectively. The outer rotor thrust magnetic group (3) and the inner rotor thrust magnetic group (4) are both magnetized along the axial direction and in opposite directions. The repulsive force between the outer rotor thrust magnetic group (3) and the inner rotor thrust magnetic group (4) is used to withstand the axial thrust and generate a repulsive force on the inner rotor in the opposite direction to the axial movement direction. By adjusting the initial axial air gap thickness between the outer rotor thrust magnetic group (3) and the inner rotor thrust magnetic group (4) and the axial width difference between the outer rotor torsion magnetic group (2) and the inner rotor torsion magnetic group (5), the repulsive force and attractive force on the inner rotor along the axial movement direction cancel each other out and achieve the balance of the initial force state.

2. A method for determining the optimal load-bearing conditions of a push-torsion composite magnetic transmission device, characterized in that, The steps are as follows: The first step is to determine the parameters of the push-torsion composite magnetic transmission device; The inner radius of the outer rotor torsion transmission magnetic assembly (2) is r 1. Axial width is l 1. Thickness is h The outer radius of the inner rotor torsion transmission magnetic assembly (5) is r 2. Axial width is l 2. Thickness is h ,and l 1> l 2; The thickness of the outer rotor torsion magnetic assembly (2) is the same as the thickness of the inner rotor torsion magnetic assembly (5); The inner radii of the outer rotor thrust magnetic assembly (3) and the inner rotor thrust magnetic assembly (4) are both r 3, the outer radius is r 4. The axial width is l 3; The initial axial air gap thickness between the outer rotor drive magnetic assembly (3) and the inner rotor drive magnetic assembly (4) is δ 0, the maximum displacement of the inner rotor along the axial direction of motion is δ max The minimum axial air gap thickness is δ min = δ 0- δ max The outer rotor torsion magnetic group (2), outer rotor thrust magnetic group (3), inner rotor thrust magnetic group (4), and inner rotor torsion magnetic group (5) are all divided at equal angles along the circumferential direction. θ And the number of magnetic pole pairs N p =180 / θ The residual magnetic flux density is B r The relative permeability is 1. μ r ,Pick μ r =1.05; the torsional angle difference between the inner and outer rotors under the action of rotational torque is α ; The second step is to establish the relationship between the rotational torque and the difference in torsion angle. The third step is to establish the relationship between axial thrust, torsional angle difference, and minimum axial air gap thickness. Step 4: Solve for the maximum value of the torsion angle difference; Step 5: Determine the optimal load-bearing range.

3. The method for determining the optimal load-bearing conditions of the push-torsion composite magnetic transmission device according to claim 2, characterized in that, The specific implementation process of the second step is as follows: First, the fundamental amplitude of the magnetic flux density in the air gap between the outer rotor torsion transmission magnetic group (2) and the inner rotor torsion transmission magnetic group (5) is determined using the equivalent magnetic circuit method. B g The calculation formula is as follows: In the formula, α p Let be the polar arc coefficient, and take . α p =1; Then, because l 1≠ l 2. The effective axial overlap width between the outer rotor torsion transmission magnetic assembly (2) and the inner rotor torsion transmission magnetic assembly (5) l eq Limited by the shorter side, the calculation formula is as follows: Finally, the relationship between rotational torque and torsional angle difference is established. T ( α The calculation formula is as follows: In the formula, μ 0 is the permeability of free space, and μ 0 = 4 π ×10 -7 H / m; r m The radius of the centerline of the air gap between the outer rotor torsion transmission magnetic assembly (2) and the inner rotor torsion transmission magnetic assembly (5) is given. r m It is calculated by the following formula: 。 4. The method for determining the optimal load-bearing conditions of the push-torsion composite magnetic transmission device according to claim 3, characterized in that, The specific implementation process of the third step is as follows: First, obtain the maximum theoretical repulsive force when the axial air gap thickness between the outer rotor push magnetic assembly (3) and the inner rotor push magnetic assembly (4) is zero and they are directly opposite each other. F 0, the calculation formula is as follows: In the formula, A 0 represents the magnetic pole area of ​​a single outer rotor push magnetic group (3) or inner rotor push magnetic group (4), and A 0 is calculated using the following formula: Then, the axial thrust attenuation coefficient caused by the change in the axial air gap thickness between the outer rotor thrust magnetic assembly (3) and the inner rotor thrust magnetic assembly (4) is obtained. K g The calculation formula is as follows: In the formula, e It is a natural constant; τ The distance between the magnetic poles is [the distance between the poles], and τ It is calculated by the following formula: Finally, the relationship between axial thrust, torsional angle difference, and minimum axial air gap thickness was established. F ( α , δ min The calculation formula is as follows: 。 5. The method for determining the optimal load-bearing condition of the push-torsion composite magnetic transmission device according to claim 4, characterized in that, The specific implementation process of the fourth step is as follows: Since the application of rotational torque weakens the axial thrust, in order to ensure minimum axial thrust... F min For the maximum torsional angle difference α max To impose restrictions, α max The calculation formula is as follows: 。 6. The method for determining the optimal load-bearing condition of the push-torsion composite magnetic transmission device according to claim 5, characterized in that, The specific implementation process of step five is as follows: When the torsion angle difference α When =0, the maximum axial thrust is known from step three as follows: F max = F (0, δ min )= K g F 0, from the second step we know the rotational torque is T (0) = 0; when the torsional angle difference α = α max At that time, from the third step, we know that the minimum axial thrust is F min From the second step, we know that the rotational torque is T ( α max ); Therefore, the optimal load-bearing condition is: the axial thrust range is F min ~ F max Rotational torque range is 0~ T ( α max The range of torsion angle difference is 0~ α max Thus, the optimal load-bearing conditions for the push-torsion composite magnetic transmission device have been determined.

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