International Journal of Aerospace Engineering
Volume 2021 (2021), Article ID 6624774, 18 pages
https://doi.org/10.1155/2021/6624774

Research Article

Analysis and Experimental Study on Dynamic Behavior of Stepper-Actuated Dual-Axis Data Transmission Antenna

Zhaomingyue Zheng,¹ Wei Cheng,¹ Ming Li,¹ Guangyuan Wang,² and Limeng Tan³

¹School of Aeronautic Science and Engineering, Beihang University, Beijing 100191, China
²China Academy of Space Technology, Beijing, China
³Beijing Institute of Spacecraft System Engineering, Beijing, China

Correspondence should be addressed to Ming Li; li_ming@buaa.edu.cn and Guangyuan Wang; zhuichilun@126.com

Received 17 December 2020; Revised 4 March 2021; Accepted 25 March 2021; Published 15 April 2021

Academic Editor: Mohammad Tawfik

Copyright © 2021 Zhaomingyue Zheng et al. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.

Abstract.

The satellite-borne data transmission antenna is the main disturbing source of low-frequency microvibration of spacecraft, which immensely affects the image quality of remote sensing satellite. In this paper, the dynamic characteristics of flexible load driven by stepping motor on flexible boundary are studied. The dynamic equation of the stepping motor driven by current subdivision is simplified by linearization method. The dynamic model of flexible load driven by stepping motors on flexible boundary is established by using the Dynamic Substructure Method, and the analytical expression of microvibration of the data transmission antenna is given. The coupling relationship between the stepping motors and the flexible structure is analyzed by modal coordinate transformation. The microvibration model is verified by simulation and experiment, and the main causes and coupling factors of microvibration are explained. The results show that the model can accurately predict the microvibration of the satellite antenna and can be applied to the microvibration prediction in orbit. The reasonable selection of the working velocity of the stepping motors can effectively reduce the microvibration, which provides the basis for the design of the antenna control system.

1. Introduction

In order to improve the imaging quality of high-resolution remote sensing satellite, the stability requirements of remote sensing satellite are constantly raised [1]. But there are control moment gyroscope, momentum wheel, solar array and solar array drive assembly, data transmission antenna, and other moving parts on the satellite [2–5]. When the satellite is in orbit, the moving parts will cause microvibration. This phenomenon not only affects the resolution and pointing accuracy of payloads such as cameras but also affects the attitude control of satellites [6]. The spaceborne data transmission antenna plays an important role in spacecraft data relay and intersatellite link tasks, but it is also the main source of low-frequency microvibration [7–9].

Hybrid two-phase stepping motor is widely used in low-speed rotation of spacecraft moving parts due to its simple structure, high positioning accuracy, and easy open-loop control circuit [10, 11]. At present, Subdivision Drive (SDD) is widely used, which can improve the resolution of the motor [12] and the stability of operation [13] by subdividing the current change into multiple microelectric pulses. The satellite-borne data transmission antenna is driven by two vertically arranged stepper motors to rotate the reflector [14]. The reflector is a flexible structure with large size, which is connected with the support arm through the driving mechanism. In order to improve the pointing range of the antenna and avoid the structural interference between the reflector and the satellite body, the support arm of the antenna is designed longer. This makes the support arm a flexible structure. When the antenna is working, the electric pulse signal of the stepping motor and the harmonic drive of the meshing teeth of the deceleration mechanism will cause microdisturbance [15, 16]. The vibration may be coupled with the flexible load reflector and the flexible boundary support arm, which will further amplify the vibration. This kind of microdisturbance may cause structural vibration of the flexible load reflector and the flexible boundary support arm, which will react on the stepping motors. Furthermore, the coupling vibration not only affects the performance of the payload but also affects the pointing accuracy of the antenna itself. Therefore, the microvibration phenomenon of the data transmission antenna can be summarized as the coupling vibration problem of the flexible load driven by stepping motors on the flexible boundary. The modeling and analysis of this problem is more complex.

Most researchers take the pointing accuracy of data transmission antenna as the design goal [9] and model from the stepping motor and the control method. Liu et al. analyzed the influencing factors of the pointing accuracy of the data transmission antenna from the aspects of pointing algorithm, pointing execution, ground station pointing, and atmospheric transmission [17]. Zhou et al. established the drive mechanism model of the data transmission tracking antenna by considering the nonlinearity of the harmonic gear and the dynamic characteristics of the driving circuit [18]. Although this kind of method can be used to analyze the pointing accuracy of the antenna, it cannot be used to predict the torque of the microvibration of the antenna. Some researchers have established the dynamic model of the data transmission antenna from the perspective of the flexible structure. Song established the dynamic model of the data transmission antenna through the Finite Element Method and calculated and analyzed the vibration characteristics [19]. Cao et al. established the flexible coupling dynamic equation of the data transmission antenna by using the loading mode synthesis hybrid coordinate method [20]. Their research does not consider the coupling effect between the stepping motors and the flexible structure and could not accurately explain the microvibration phenomenon of the antenna.

In the research of the coupling vibration between stepping motor and structure, Yang et al. verified the existence of electromagnetic stiffness of the stepping motor through experiments and simulation [21]. According to the principle of stepping motor, Liu simplified the load to rigidity and established the general analytical model and simplified model of microvibration of the data transmission antenna [22]. Chen et al. established the vibration equation of the stepping motor by simplifying and linearizing the electromagnetic torque of the stepping motor and carried out simulation analysis with a two degree of freedom flexible system [23]. According to the Lagrange Energy Method, Sattar et al. established the dynamic model of kinematics and microvibration coupling between the stepping motor and the rigid load [24]. Other researchers have studied the microvibration phenomenon of the antenna through experiments, but have not discussed the cause and coupling principle in depth. Wu et al. proposed a semiempirical and semianalytical microvibration model of the data transmission antenna by considering the stepping motor and the structure modes of antenna [15]. Hyun-Ung Oh et al. tested the microvibration of a data transmission antenna using a force measuring platform manufactured by KISTLER and designed a pseudoelastic shape memory alloy-compressed mesh washer isolator to suppress the microvibration. But they did not reveal the coupling relationship between the stepper motor and the antenna structure [16]. Therefore, it is necessary to study the coupling vibration of the flexible load driven by stepping motors on the flexible boundary by mathematical modeling, at the same time verify and analyze the mechanism and influencing factors of microvibration of data transmission antenna through experiments.

By establishing the mathematical model of the flexible load driven by stepping motors on the flexible boundary to analyze the microvibration of the antenna not only can the electromechanical coupling relationship be revealed in essence but also has strong application value. Firstly, the microvibration data obtained from experiment and simulation can be used as design reference index of the antenna. By optimizing the control law and parameters, the microvibration of the antenna can be reduced from the source. Secondly, the coupling relationship of the system is analyzed, which can provide theoretical basis for vibration reduction and isolation design. Finally, in addition to the data transmission antenna, there are many flexible structures and moving parts in the satellite. The methods used in this paper can also provide reference for solving the same kind of coupling vibration problems.

This paper studies the dynamic model of the flexible load driven by stepping motors on the flexible boundary. The dynamic equation of stepping motor is simplified by linearization method. The dynamic model of the flexible load driven by stepping motors on the flexible boundary is established by using the Dynamic Substructure Method, and the analytical expression of the microvibration of the data transmission antenna is given. The coupling relationship of the system is analyzed by the coordinate change method. Finally, the method is verified by simulation and experiment.

2. Microvibration Model of the Dual-Axis Data Transmission Antenna

2.1. Simplification of Dynamic Equation of Stepping Motor Driven by Current Subdivision

The driving model of two-phase hybrid stepping motor is:

in which is the flux vector, is the current vector, and is the inductance matrix. The inductance matrix is symmetrical and ignores the higher-order harmonic components of periodic magnetic derivative function. The inductance matrix can be expressed as:

in which is the number of teeth of the rotor. In order to make the stepper motor run smoothly, the driving current of the stepper motor is usually subdivided step by step, so the current vector can be expressed as:

in which and are two-phase winding current of and , is equivalent excitation current of permanent magnet, is magnitude of current subdivision of two-phase winding, is step angle of current subdivision, and is operation step.

The dynamic model of the two-phase hybrid stepping motor is:

in which is the rotor angle, and are the motor rotor inertia and the viscous damping coefficient inside the motor, and and are the electromagnetic torque and the load torque. According to Equations (1) to (3), the electromagnetic torque can be reduced to:

in which is the electromagnetic torque coefficient and is the positioning torque coefficient. Since the positioning torque coefficient is far less than the electromagnetic torque coefficient, the positioning torque is ignored. is the theoretical equilibrium position of the motor rotor after the occurrence of the th electrical pulse signal, and is the angular displacement of the motor rotor during this period. In order to avoid the stepping motor out of step, the difference between the actual angular displacement of the motor rotor and the theoretical balance position should be kept between a mechanical step angle, that is, the value range of the difference between the two is as follows:

in which represents the mechanical step angle of the stepper motor and and are the running beats and the subdivisions number of the stepper motor. The working state of the data transmission antenna is low-speed operation. In order to make the data transmission antenna have high pointing accuracy, the mechanical step angle of the stepper motor is a small value, so is also a smaller angle value. Equation (5) can be linearized, that is, ; the electromagnetic torque can be further simplified as follows:

Therefore, the dynamic equation of stepper motor driven by current subdivision can be converted into:

in which is the equivalent electromagnetic stiffness of the stepping motor. is the step excitation component of electromagnetic torque, which is independent of the rotor angular displacement. Therefore, the stepping motor driven by current subdivision can be equivalent to an electromagnetic spring-damping system, which provides a basis for further analysis of the coupling vibration between the stepping motors and the flexible load and the flexible support arm.

2.2. Dynamic Model of the Dual-Axis Data Transmission Antenna

The dual-axis data transmission antenna consists of a support arm, an -axis stepping motor, a -axis stepping motor, and a reflector, in which the support arm and the reflector are flexible structures. Figure 1 shows the structure of a two-axis data transmission antenna. When the Finite Element Method is used to model the flexible structure, the degree of freedom of the structure is high, the amount of iteration calculation is large, and the efficiency is low. Therefore, the Dynamic Substructure Method is used to condensate the dynamic model of flexible structure and convert the high-degree-of-freedom physical coordinates into low-degree-of-freedom mode coordinates, which improves the computational efficiency. The microvibration of the antenna is mainly concentrated in the low-frequency band, so ignoring the influence of higher modes has little influence on the calculation accuracy.

Figure 1: Structure diagram of dual-axis data transmission antenna.

Figure 2 shows the coordinate system of the dual-axis data transmission antenna. is defined as the inertial coordinate system, is the fixed coordinate system with the origin at point C, is the intermediate coordinate system, and is the reflector coordinate system. is defined as the rotation angular displacement of the -axis motor, and is the rotation angular displacement of the -axis motor. First, the -axis motor and the reflector rotate around the -axis to the intermediate coordinate system, and then, the reflector rotates around the -axis. The transformation relationship of coordinate system is as follows:

in which , , and are the unit vectors of the fixed coordinate system; , , and are the unit vectors of the intermediate coordinate system; , , and are the unit vectors of the coordinate system; and and are the coordinate transformation matrices.

Figure 2: Coordinate system of dual-axis data transmission antenna.

The data transmission antenna is divided into four substructures, which are the reflector, the -axis stepping motor, the -axis stepping motor, and the support arm in turn. According to the Dynamic Substructure Method, the degrees of freedom of the substructure are divided into internal degrees of freedom and interface degrees of freedom. The dynamic equation of substructure 1 in its local coordinate system is:

in which superscript represents substructure 1 in local coordinate system, subscript represents internal degrees of freedom, and subscript represents interface degrees of freedom of interface node A, and , , and are the mass matrix, damping matrix, and stiffness matrix of substructure 1 in its local coordinate system, respectively. With the Rayleigh damping model, the damping matrix is:

in which and are Rayleigh damping coefficients of substructure 1 and and are the displacement and force column vectors. According to formula (9), the transformation relationship between the displacement vectors of the reflector in the local coordinate system and the displacement vectors in the global coordinate system is obtained as follows:

According to the fixed interface mode synthesis method, the hypothetical mode set of substructure is composed of the main and constraint modes, and the solution of the main and constraint modes of substructure 1 is:

in which subscript represents the order of the main modes retained by substructure 1, and the first line of Equation (14) is expanded to obtain:

Therefore, the hypothetical modal set of substructure 1 in its local coordinate system is:

Substructures 2 and 3 are single-degree-of-freedom vibration systems in the free interface, and only one degree of torsional freedom exists. According to Equation (8), the dynamic equation of the stepping motors can be written as follows:

In which superscripts 2 and 3 represent substructures 2 and 3, respectively, and each physical quantity has the meaning of:

Based on Equations (13)–(15), the hypothetical mode sets of substructures 2 and 3 are obtained:

Substructure 4 is also a flexible structure and its dynamic equation is:

in which superscript 4 represents substructure 4 in general coordinate system, subscript represents internal degree of freedom, subscript represents interface degree of freedom of interface node C, and subscript represents interface degree of freedom of interface node D. According to the displacement boundary conditions , the dynamic equation of substructure 4 can be reduced to:

in which , , and are mass matrix, damping matrix, and stiffness matrix of substructure 4, respectively. When Rayleigh damping model is used, the damping matrix is:

in which and are Rayleigh damping coefficients of substructure 4 and and are displacement column vectors and excitation column vectors, respectively. The method is given according to Equations (13)–(15). Subscript is defined as the order of main modes retained by substructure 4, then the hypothetical mode set of substructure 4 is:

After obtaining the hypothetical modal sets of all substructures, the mass matrix, damping matrix, stiffness matrix, displacement column vector, excitation column vector, and mode matrix of the system can be defined as:

The modal coordinate corresponding to the modal matrix can be written as:

in which and are the modal coordinates of substructures 1 and 4, and the relationship between the modal coordinates and the physical coordinates is:

By the first coordinate transformation of the dynamic equation of the system, the physical coordinates with high degree of freedom of the coupled system can be reduced into mixed coordinates with low degree of freedom, i.e., the dynamic equation of the system is:

in which

Substituting coordinate transformation relation given by Equation (12) and interface displacement coordination condition:

However, the modal coordinates are not completely independent. By substituting transformation matrix , the nonindependent coordinates in are eliminated and the independent mode coordinates of the coupling system are obtained:

Then, the dynamic equation of the coupled system expressed in independent mode coordinates with lower degrees of freedom can be written as follows:

in which

Equation (31) has -order degrees of freedom; coordinates are independent of each other; and , , and have clear physical meanings. It is convenient to establish the electromechanical coupling model of the data transmission antenna by combining the control model. At the same time, the lower degree of freedom guarantees the efficiency of iteration calculation and the independent coordinates are convenient to analyze the coupling relationship. In order to facilitate the connection between the dynamic model and the control model, the subscript is used to represent the coupling structure, and Equation (31) is rewritten into the state space form:

in which

The state variable is composed of the independent modal coordinates and their derivatives. The system matrix is composed of transformed mass matrix, damping matrix, and stiffness matrix, which reflects the dynamic characteristics of the coupling structure. The input vector consists of the input force of two stepping motors, and the input transformation matrix reflects the position of the input force and mode shape information. The output variable is composed of the angular displacement of the stepping motors. As the feedback of the closed-loop control of the angular displacement of the motors, the output transformation matrix can extract the required output variables from the state variables. The order of the state space equation of the data transmission antenna is low, which improves the simulation efficiency. Moreover, the state space equation can be easily connected with the control model of the two-axis motors for cosimulation to optimize the control method and control parameters.

2.3. Microvibration Model and Coupling Relationship Analysis of the Antenna

When the stepper motor of the two-axle antenna is started, the driving system will input pulse current to the motor, which will cause vibration of the planetary gear during meshing. The fundamental frequency of vibration caused by current pulses is:

in which is the speed of the stepping motor, is the deceleration ratio, and is the mechanical step angle of the stepping motor. According to Equation (6), the mechanical step angle is related to the running beats, the subdivisions number, and the number of rotor teeth of the stepping motor. In addition, the planetary gear will generate multiple frequency doubling excitation along with the fundamental frequency.

The microvibration generated by the coupling system of the dual-axis data transmission antenna can be calculated by the reaction force generated by the coupling system on the fixed interface, i.e., the supporting reaction force at node D. The microvibration generated by the coupling system of two-axis digital transmission antenna can be calculated by the reaction force generated by the coupling system on the fixed interface, that is, the supporting reaction force at node D. In the third line of Equation (20) and substituting the displacement boundary conditions , the calculation formula of microvibration of coupled system can be obtained:

According to Equation (27), the specific expressions of mass matrix and stiffness matrix in the dynamic equation after polycondensation are as follows:

The stiffness matrix is diagonal matrix, which indicates that the dynamic equation of the system after polycondensation is decoupled on stiffness. and are diagonal matrices, representing the retained main modes frequency of the substructure 1 reflector and the substructure 4 support arm, respectively. The mass matrix is a symmetrical nondiagonal matrix, which indicates that the dynamic equation of the system is coupled on mass. reflects the coupling relationship between the modes of the flexible load and the physical coordinates of the system, and reflects the coupling relationship between the modes of the flexible boundary and the physical coordinates of the system.

3. Simulation Analysis of the System Using MATLAB/Simulink Toolbox

3.1. Simulation Model of the Dual-Axis Data Transmission Antenna

The dynamic behavior of the coupling structure of the data transmission antenna can be preliminarily analyzed through the simulation. Firstly, the mode of the data transmission antenna is obtained by modal experiment. The modal frequency and mode shape of the data transmission antenna are given in Table 1. According to the modal experiment results, the finite element model of the data transmission antenna is established. Then, the mass matrix and the stiffness matrix of the flexible structure reflector and support arm are extracted from the finite element model. The state space form of coupled system dynamics equation is obtained according to the method given in the second section. The simulation model of digital antenna is established by using the Simulink toolbox of commercial software MATLAB (as shown in Figure 3). Table 2 gives the parameters used in the simulation process.

Table 1: Modal frequency and mode shape of the data transmission antenna.

Order
Frequency/Hz
Mode shapes

1
7.924
The combination torsion around -axis

2
12.209
First-order bending of the support arm in plane

3
17.860
First-order bending of the support arm in plane

4
52.337
Tension of the combination along the -axis

5
89.975
Second-order bending of the support arm in plane

6
112.781
Second-order bending of the support arm in plane

7
118.847
Bending of the reflector

Figure 3: Simulation model of data transmission antenna.

Table 2: Simulation parameters.

Parameter symbol
Physical meaning
Value
Unit

Phase resistance
6.5

Phase inductance
30

Amplitude of two-phase current
0.6

The subdivisions number
8
—

Mechanical step angle
π/100

Rotor teeth
50
—

Motor rotor inertia
0.0001

Viscous damping factor of the motor
0.02

Electromagnetic moment coefficient
0.16

Deceleration ratio
100
—

—
Total quality of the antenna
25

—
Rotating inertia driven by x-axis motor
0.34

—
Rotating inertia driven by y-axis motor
0.0925

Rayleigh damping coefficient
0.001
—

Rayleigh damping coefficient
0.0005
—

3.2. Simulation Results and Analysis

The simulation program can output the time domain and frequency domain results of the microvibration caused by the coupled structure, but the frequency domain results of the microvibration are more concerned in practice. The simulation results of the microvibration caused by the -axis motor and -axis motor of the coupled structure are given in Figures 4 and 5. When the -axis motor rotates, natural frequencies of 7.7 Hz, 18 Hz, 112 Hz, and 117.9 Hz appear at different velocity conditions, corresponding to 7.9 Hz, 17.8 Hz, 112.7 Hz, and 118.8 Hz of the first, third, sixth, and seventh order mode frequencies of the structure, respectively, and the mode shapes of these modes all have components in the direction of -axis motor rotation. On the other hand, when the -axis motor rotates, natural frequencies of 7.7 Hz, 14 Hz, 87.3 Hz, and 117.9 Hz appear at different velocity conditions, corresponding to 7.9 Hz, 12.2 Hz, 89.9 Hz, and 118.8 Hz of the first, second, fifth, and seventh order modal frequencies of the structure, respectively, and the mode shapes of these modes all have components in the direction of -axis motor rotation.

(a)

(b)

Figure 4: Simulation results of microvibration frequency domain curve: (a) -axis motor; (b) -axis motor.

(a)

(b)

Figure 5: Simulation results of microvibration of the antenna at different velocity: (a) -axis motor; (b) -axis motor.

At the same time, the simulation results of microvibration of two motors at different velocity not only show the fundamental frequency caused by the current pulse satisfying Equation (35), such as 11.11 Hz, 22.22 Hz, 33.33 Hz, 44.44 Hz, 55.56 Hz, and 66.67 Hz, but also multiple frequency doubling accompanied by the fundamental frequency. According to the amplitude of each frequency, the amplitude of microvibration caused by fundamental frequency of current pulse is larger, while the amplitude of microvibration caused by frequency doubling shows a tendency to decrease with the increase of frequency as a whole. However, if the frequency doubling approaches the structural mode frequency, the coupling phenomenon of common amplification will occur.

4. Experimental Tests of the Antenna in Simulated Zero Gravity State

4.1. Experimental System

The experimental system consists of three parts: equipment to be tested, test equipment, and zero gravity state simulation equipment (as shown in Figure 6). The equipment to be tested are the data transmission antenna and the antenna control equipment. The test equipment includes the microvibration testing bed, unidirectional force sensor, acceleration sensor, and force hammer. The microvibration testing bed is a high rigidity piezoelectric force testing bed developed by Beihang University. Its testing principle and method are given in manuscript [25]. It is used to measure the microvibration of the coupling system. When the helium balloon is inflated, the unidirectional force sensor measures the tension of the lifting rope of the helium balloon. The acceleration sensor and the force hammer are used to test the antenna mode.

Figure 6: Microvibration experiment of the data transmission antenna.

In order to simulate the zero gravity state of the satellite-borne data transmission antenna in orbit, the helium balloon is used to balance the load gravity of the motor shaft, and the zero gravity state of the motor shaft is simulated. The simulation equipment also includes lifting rope, lifting ring installed in antenna reflector and protective rope. During the experiment, the helium balloon was suspended from the antenna reflector by the lifting rope. The laboratory is a confined space, and the air conditioner and other equipment that can cause air flow are closed during the experiment, so the influence of air flow on the experiment can be ignored. The suspended helium balloon can be equivalent to a pendulum model, and its suspension frequency is as follows:

in which is the rope tension, is the mass of the helium balloon when it is not inflated, and is the distance from the lifting point to the balloon centroid. The balloon mass and the length of the lifting rope are measured before the experiment, and the tension of the lifting rope is measured by a unidirectional force sensor during the experiment. The suspension frequency to simulate the zero gravity state of the -axis and -axis motors is calculated (as shown in Table 3). The suspension frequency is much lower than the first mode frequency of the coupling structure, so the influence of the helium balloon shaking on the experiment can be ignored.

Table 3: Suspension frequency of zero gravity simulator.

Object

-axis motor
79.56
0.53
2.96
0.658

-axis motor
60.20
0.53
2.96
0.573

4.2. Experimental Results and Coupling Analysis

Figure 7 shows the comparison of experimental results and simulation results of microvibration frequency domain curve. Tables 4 and 5 show the comparison of experimental results and simulation results of microvibration amplitude. Through comparison, the frequency of microvibration obtained by experiment and simulation is consistent, and the amplitude error of main frequency is less than 6%. Therefore, the microvibration model given in Section 2 can accurately predict the microvibration of the coupled system.

(a)

(b)

(c)

(d)

Figure 7: Simulation results of microvibration frequency domain curve: (a) -axis motor, (b) -axis motor and experimental results of microvibration frequency domain curve: (c) -axis motor, (d) -axis motor.

Table 4: Comparison of microvibration amplitude between experiment and simulation for -axis motor.

Simulation amplitude of microvibration of -axis motor/Nm
Experimental amplitude of microvibration of -axis motor/Nm

Frequency
0.01°/s
0.02°/s
0.03°/s
0.04°/s
0.05°/s
0.06°/s
Frequency
0.01°/s
0.02°/s
0.03°/s
0.04°/s
0.05°/s
0.06°/s

7.7
0.0999
0.0887
0.0728
0.0754
0.0947
0.1147
7.688
0.0982
0.0870
0.0710
0.0761
0.0988
0.1157

11.1
0.1268

11.125
0.1260

18.0
0.1376
0.1571
0.1575
0.1814
0.2398
0.2734
18.000
0.1451
0.1590
0.1635
0.1878
0.2453
0.2776

22.2
0.0473
0.0936

22.188
0.0491
0.0947

33.3
0.0235

0.0356

33.313
0.0240

0.0345

44.4
0.0145
0.0276

0.0306

44.375
0.0147
0.0294

0.0306

55.6
0.0113

0.0422

55.625
0.0114

0.0432

66.7
0.0109
0.0191
0.0286

0.0462
66.688
0.0100
0.0183
0.0298

0.0457

77.8
0.0104

77.813
0.0106

88.9
0.0096
0.0138

0.0184

88.875
0.0098
0.0147

0.0203

100.0
0.0087

0.0170

100.000
0.0072

0.0157

111.1
0.0267
0.0210

0.0541

111.125
0.0273
0.0208

0.0559

112.0
0.0420
0.0386
0.0248
0.0254
0.0860
0.0326
112.000
0.0423
0.0389
0.0251
0.0269
0.0894
0.0329

117.9
0.0284
0.0212
0.0208
0.0195
0.0348
0.0252
117.875
0.0280
0.0229
0.0202
0.0210
0.0344
0.0267

122.2
0.0106

122.188
0.0113

133.3
0.0054
0.0095
0.0142
0.0189

0.0117
133.313
0.0057
0.0083
0.0141
0.0190

0.0116

144.4
0.0043

144.375
0.0058

Table 5: Comparison of microvibration amplitude between experiment and simulation for -axis motor.

Simulation amplitude of microvibration of -axis motor/Nm
Experimental amplitude of microvibration of -axis motor/Nm

Frequency
0.01°/s
0.02°/s
0.03°/s
0.04°/s
0.05°/s
0.06°/s
Frequency
0.01°/s
0.02°/s
0.03°/s
0.04°/s
0.05°/s
0.06°/s

7.7
0.0525
0.0462
0.0592
0.0608
0.0820
0.1131
7.688
0.0511
0.0460
0.0607
0.0640
0.0796
0.1139

11.1
0.0936

11.125
0.0886

14.2
0.1062
0.0967
0.1269
0.1575
0.2032
0.2604
14.188
0.1102
0.0902
0.1319
0.1524
0.1987
0.2586

22.2
0.0448
0.0700

22.188
0.0445
0.0690

0.0050
0.0044

33.3
0.0235

0.0612

33.313
0.0216

0.0647

44.4
0.0144
0.0276

0.0571

44.375
0.0135
0.0273

0.0564

55.6
0.0114

0.0422

55.625
0.0106

0.0415

66.7
0.0110
0.0191
0.0286

0.0462
66.688
0.0112
0.0188
0.0289

0.0455

77.8
0.0155

77.813
0.0141

87.3
0.0357
0.0474
0.0314
0.0521
0.0423
0.0531
87.313
0.0344
0.0487
0.0326
0.0503
0.0404
0.0542

88.9
0.0317
0.0458

0.0486

88.875
0.0336
0.0443

0.0462

100.0
0.0088

0.0169

100.000
0.0088

0.0172

111.1
0.0107
0.0110

0.0241

111.125
0.0102
0.0119

0.0245

117.9
0.0181
0.0163
0.0184
0.0166
0.0250
0.0262
117.875
0.0178
0.0178
0.0187
0.0164
0.0245
0.0286

122.2
0.0126

0.0227
122.188
0.0135

0.0221

133.3
0.0054
0.0095
0.0142
0.0189

133.313
0.0058
0.0090
0.0143
0.0187

144.4
0.0043

144.375
0.0034

Taking the experimental results as reference, the simulation results have deviation. The possible reasons are the deviation caused by simplification and linearization of electromagnetic torque, the vibration and fluctuation of real current, the error caused by the instability of motor system, the test error of the microvibration testing bed, and the random interference of the experimental process.

According to the frequency domain curve of microvibration, the main causes of microvibration are as follows:

(1)The rotation of the stepping motor causes the coupling structure to generate microvibration at the modal frequency with the rotational direction component(2)Electromagnetic excitation generated by the pulse exciting current(3)In the meshing process of planetary gear, the frequency doubling excitation of pulse excitation is produced

Figure 8 shows the experimental results of microvibration of the antenna at different velocity. Combined with the simulation results, it can be seen that there is electromechanical coupling between the stepping motor and the flexible load or flexible boundary. The specific performance is that the electromagnetic stiffness of the stepping motor will affect the microvibration frequency of the coupling structure, which deviates from the original structure frequency.

(a)

(b)

Figure 8: Experimental results of microvibration of the antenna at different velocity: (a) -axis motor; (b) -axis motor.

When the velocity of stepper motor is low, the coupling structure has more resonance frequency in low-frequency band. If the fundamental frequency and frequency doubling of the microvibration caused by the pulse exciting current are close to the natural frequency of the coupling structure, the coupling phenomenon of amplifying the amplitude of the microvibration will occur. As the velocity of the stepper motor increases, the fundamental frequency and frequency multiplication of the microvibration caused by the pulsed excitation current increase, the resonance frequency in the low frequency band decreases, and the probability of coupling with the structure frequency decreases. However, when the velocity is high, the low-frequency microvibration amplitude of the coupling structure increases significantly.

Therefore, in order to reduce the microvibration caused by the coupling structure, the appropriate velocity should be selected as the working velocity. The working velocity should not only make the frequency of microvibration caused by pulse current avoid the structure frequency which may cause coupling but also avoid too fast velocity to cause large low-frequency vibration.

5. Conclusions

In this study, the microvibration phenomena of the stepper motors driving the flexible load on the flexible boundary are analyzed. A dynamic equation and a microvibration model of the dual-axis data transmission antenna oriented to the control system are given by simplifying the stepper motor electromagnetic moment and the Dynamic Substructure Method. The coupling relationship between the stepping motors and the flexible structure is analyzed through the transformation of modal coordinates. The simulation and experimental results show that the model can accurately predict the microvibration of the coupling structure, and the main causes of the microvibration are the electromechanical coupling of the stepper motors and the flexible structure, electromagnetic pulse excitation, and planetary gear meshing. The influence of velocity of the motors on the output microvibration of the coupling structure is studied. It is pointed out that the influence of the working velocity, excitation torque, load torque, mechanical step angle, and other parameters should be carefully considered in the antenna design to avoid coupling between microvibration and structure frequency.

This study can be used to predict the microvibration of remote sensing satellite in orbit and provide a research basis for the design of the antenna control system and the vibration suppression of remote sensing satellite in orbit.

Data Availability

The available data are given in the manuscript.

Conflicts of Interest

The authors declare that they have no conflicts of interest.

Acknowledgments

The research is funded by the China High Resolution Earth Observation Project.

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