Shock and Vibration
Volume 2018 (2018), Article ID 9821870, 16 pages
https://doi.org/10.1155/2018/9821870

Research Article

Nonlinear Resonance Responses of Electromechanical Integrated Magnetic Gear System

Xiu-hong Hao, Hong-qian Zhu, and Deng Pan

School of Mechanical Engineering, Yanshan University, Qinhuangdao, China

Correspondence should be addressed to Deng Pan; pandeng1896@sina.com

Received 28 September 2017; Revised 28 January 2018; Accepted 6 February 2018; Published 14 March 2018

Academic Editor: Tai Thai

Copyright © 2018 Xiu-hong Hao 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.

Nonlinear differential equations for an electromechanical integrated magnetic gear (EIMG) system are developed by considering the nonlinearity in the magnetic force of the system components. Expressions for the main resonances and superharmonic resonances are obtained for output wave frequencies close to the natural frequency and half the natural frequency of the derived EIMG system. The response laws are discussed in detail. The magnetic coupling stiffness among the components is found to exhibit distinct nonlinearity, leading to strong main resonances and superharmonic resonances. Smaller values of the magnetic coupling stiffness and damping result in larger response amplitudes and transient responses that slowly decay to zero. When the main resonances and superharmonic resonances occur, the dominant frequency of the response is the natural frequency of the derived EIMG system, and the amplitudes of different components of the resonance display large differences.

1. Introduction

Magnetic drives, and especially magnetic gear boxes, are extensively used in the medical, food, and chemical industries. These systems have the advantages of being contactless, wear-free, and lubrication-free, with low levels of vibration and noise, and built-in overload protection [1]. The field-modulated magnetic gear (FMMG) has a coaxial topology, which significantly improves the permanent magnet (PM) utilization rate and can generate much higher torque and torque density than traditional magnetic gears that use a parallel shaft topology [2]. Therefore, FMMGs are widely used in the vehicle, wind, marine, and aerospace fields [3–5]. Various high-performance FMMG-based systems have been proposed, such as axial-flux magnetic gears, linear magnetic gears, and intersecting axes magnetic gears [6–8]. Various direct current PM rotors and alternating current PM motors have been developed for use in electric vehicles and wind power systems [9, 10]. Together, these innovations have significantly promoted the development of magnetic gears.

Electrical and control techniques are widely used in mechanical engineering, resulting in the development of many cutting-edge composite drives such as the electromagnetic harmonic drive and electromechanical integrated toroidal drive. One of the authors has previously presented a drive system known as the electromechanical integrated magnetic gear (EIMG) [11]. This integrates power and control systems into FMMG. Thus, EIMG possesses the advantages of FMMG alongside a compact structure with torque and speed control. Compared with FMMG, EIMG can generate higher torque at lower speeds. EIMG can transmit torque by magnetic field coupling, unlike mechanical gears, which require direct contact to do so. The magnetic coupling stiffness of EIMG is much lower than the contact stiffness of mechanical gears [12, 13], and EIMG has different dynamic characteristics compared with mechanical gear systems. Because EIMG system has a lower magnetic coupling stiffness, its natural frequencies are much lower than those of mechanical gear systems. As a result, low-frequency resonance can easily occur. When such resonance occurs, the amplitudes of the EIMG system’s components slowly attenuate, degrading the dynamics of the system. To overcome this problem, Frank et al. added damper windings to synchronous generators to suppress the oscillations caused by transients [14]. Montague et al. used servo control in magnetic gears to overcome the disadvantages of low stiffness [15].

As EIMG is a relatively new type of magnetic gear, its dynamics should be thoroughly studied to control the behavior and improve the service performance of such a system. This study develops a dynamic model and differential equations for EIMG system by considering the nonlinearity of the magnetic coupling stiffness. The main resonances and superharmonic resonances produced by a torque wave are discussed, and these provide the foundation for the parameter optimization and performance improvement of the EIMG system.

2. Nonlinear Dynamic Model of EIMG

Figure 1 shows the inner rotor, inner and outer stator, and inner and outer ferromagnetic pole-pieces (FP) that comprise an EIMG system. All components are concentric, and the EIMG has four air gaps. Windings made of insulated wire are mounted in the dew-drop slot of the inner stator. PMs are positioned uniformly on the inner surface of the outer stator and the inner and outer surfaces of the inner rotor. The inner and outer FP comprise permeable and nonpermeable magnetic materials layered at regular intervals. FP modulate the magnetic fields in the two air gaps next to them, thus ensuring that the number of pole pairs of PMs on the inner rotor and outer stator agrees with the number of pole pairs of the space harmonic flux density of the air gaps.

Figure 1: Topology of electromechanical integrated magnetic gear.

A three-phase alternating current is supplied to the inner stator coils to generate a rotary magnetic field with a main harmonic of . After being modulated by the inner FP, the main harmonic of the magnetic field in the second air gap is consistent with the number of pole pairs of PMs on the inner surface of the inner rotor. Therefore, the inner rotor can be actuated, thereby realizing the first drive. When the inner rotor runs, a magnetic field with a main harmonic of in the third air gap is generated and modulated by the outer FP. As a result, the main harmonic of the magnetic field in the fourth air gap becomes equal to the number of pole pairs of PMs on the outer stator. Then, the second drive is achieved.

To realize equal pole coupling among the EIMG components, ,  ,  , and have the following constraint relations:

where is the number of pole pairs of the three-phase alternating current and ,  , and are the number of pole pairs of PMs on the stator and the inner and outer surfaces of the inner rotor, respectively.

The magnetic coupling torques among the components are calculated as follows:

where ,  , and are the torques on the inner stator, inner rotor, and outer stator, respectively; ,  , and are the maximum torques on the inner stator, inner rotor, and outer stator, respectively; and are the relative rotation angles between the inner stator and inner rotor and between the inner rotor and outer stator, respectively; and ,  ,  , and are the relative torsional displacements between the inner stator and inner FP, inner FP and inner rotor, inner rotor and outer FP, and outer FP and outer stator, respectively.

Figure 2 shows the dynamic model of the EIMG system. This model contains four subsystems: inner stator/inner FP subsystem, inner FP/inner rotor subsystem, inner rotor/outer FP subsystem, and outer FP/outer stator subsystem. Because the magnetic coupling stiffness is much lower than the supporting stiffness [12], only torsional displacements are considered, and transverse vibration displacements are assumed to be negligible.

(a) Inner stator/inner FP subsystem

(b) Inner FP/inner rotor subsystem

(c) Inner rotor/outer FP subsystem

(d) Outer FP/outer stator subsystem

Figure 2: Nonlinear dynamic model of electromechanical integrated magnetic gear.

The tangential magnetic coupling forces among the components are calculated as follows:

where ,  ,  , and are the tangential magnetic coupling forces between the inner stator and inner FP, inner FP and inner rotor, inner rotor and outer FP, and outer FP and outer stator, respectively; ,  , and are the equivalent radius of gyration of the inner stator, inner rotor, and outer stator, respectively; and () is the torsional angular displacement of the inner stator, inner FP, inner rotor, outer FP, and outer stator, respectively.

For convenience, the torsional angular displacements are all replaced by their corresponding torsional displacements as

where () is the torsional displacement of the inner stator, inner FP, inner rotor, outer FP, and outer stator, respectively, and .

The magnetic coupling forces among the components are functions of the relative torsional displacements. When , namely, , the magnetic coupling forces are expanded using the Taylor series as

where ,  ,  ,  ,  , and ;  ,  ,  ,  ,  , and ;  ,  ,  ,  ,  , and ; and ,  ,  ,  ,  , and  .

The magnetic coupling forces among the components are nonlinear functions of the relative torsional displacements. The constant components of the Taylor series expansions of the magnetic coupling forces will lead to relative static displacements rather than dynamic displacements. Therefore, is neglected. Based on Newton’s second law of motion, the nonlinear dynamic differential equations of an EIMG system can be expressed as follows:

where and are the masses of the inner stator and inner FP, respectively; () and () are the equivalent masses of the inner stator and inner FP along their torsional vibration direction, respectively; () and () are the mass moments of inertia of the inner stator and inner FP, respectively; and () are the mass and equivalent mass of the inner rotor, respectively; () is the mass moment of inertia of the inner rotor; and () are the mass and equivalent mass of the outer FP, respectively; () is the mass moment of inertia of the outer FP; and () are the mass and equivalent mass of the outer stator, respectively; is the mass moment of inertia of the outer stator; ,  , and are the torsional support stiffness values of the inner stator, inner FP, and outer stator, respectively; , , , , and are the damping coefficients of the inner stator, inner FP, inner rotor, outer FP, and outer stator, respectively (,  ,  ,  , and  , where ,  ,  ,  , and are the damping ratios of the inner stator, inner FP, inner rotor, outer FP, and outer stator, resp.).

Equation (6) can be rewritten in matrix form as

The mass matrix , displacement vector , damping matrix , stiffness matrix , load vector , and equivalent load vector have the following forms:

where is the amplitude of the torque fluctuation and is the excitation frequency of the torque wave.

Equation (7) can be normalized as

where ,  , and are the normal displacement vector, normal stiffness matrix, and normal equivalent load vector, respectively; these are expressed as follows:

where is the natural frequency of the linear system derived for the EIMG.

Because the damping matrix is diagonal, the elements on the primary diagonal of the normal damping matrix are much larger than the other elements. Therefore, the normal damping matrix in (9) is simplified into the following diagonal matrix:

3. Main Resonance

A multiscale method is used to solve (9). To balance the effects of the damping forces and nonlinear elements and express them in the same perturbation equation, the following assumptions are made:

When the wave frequency of the output torque is close to the natural frequency of the outer FP rotational mode, the following assumption is introduced:

By substituting (12) and (13) into (9) and setting the power coefficients of the small parameters on both sides of the equations to be equal, the following differential equations are obtained:

 Zero power

 First power

where

Under the normal coordinate system, the general solution of (14) is expressed as

Under the regular coordinate system, the solutions of (14) are

where ,  ,  ,  , and ;  ,  ,  ,  , and ;  ,  ,  ,  , and ;  ,  ,  ,  , and ; and ,  ,  ,  , and .

Here, denotes the element in the th row and th column of the normal modal matrix :

By substituting (18), (15) can be rewritten as

where is the complex conjugate of the right-hand-side expression in (20) and is a constant associated with ,  ,  , and that is expressed as follows:

There are multiple frequency components in the right-hand-side expressions of (20), such as ,  , and , where and . When there is no internal resonance, the secular terms can be eliminated to obtain

where , and 5.

Solutions of (22) are obtained as follows:

where and are constants related to the output torque, is a constant related to and , , and .

Under the normal coordinate system, the zero-order approximate analytical solution of the EIMG system is expressed as

After eliminating the secular terms, the first-order approximate solutions are obtained by substituting (23) and (24) into (20):

where

will approach zero with increasing time because of the damping among components. The stable responses of the first-order approximate analytic solution of the EIMG system can be obtained by substituting (24) and (25) into (12):

Based on (27), approximate analytic solutions of the EIMG system under the regular coordinate system are given by

When the torque wave frequency approaches a certain frequency of the derived EIMG system, resonance will occur. In this situation, stable responses of the EIMG system under the normal coordinate system are calculated as

where .

4. Superharmonic Resonance

When the wave frequency of the output torque is close to half of the natural frequency of the outer FP rotational mode, the following assumption is introduced:

By substituting (30) into (9) and setting the power coefficients of the small parameters on both sides of the equation to be equal, the following differential equations are obtained:

 Zero power

 First power

where

Under the normal coordinate system, the general solution of (31) is expressed as

where .

Under the regular coordinate system, solutions of (31) are calculated as

where , , , , and .

After substituting (35) into (32), there are multiple frequency components such as , , , and , where and . When there is no internal resonance, the secular terms can be eliminated from (32) to obtain

The solutions of (36) are written as

where is a constant related to and , , and .

Because of the damping in the EIMG system, the initial vibration displacements will decrease to zero. Under the normal coordinate system, the zero-order stable analytical solutions are given by

After eliminating the secular terms, the first-order approximate solutions are obtained by substituting (38) into (32):

where ,  ,  ,  ,  ,  , and ;  ,  ,  , and ; and ,  ,  , and .

Under the normal coordinate system, the approximate solutions are then calculated by substituting (38) and (39) into (29):

When the wave frequency of the torque wave is close to half of the natural frequency of the EIMG system, namely, , the approximate solutions of the EIMG system under the normal coordinate system are

The superharmonic resonance responses of the EIMG system under the regular coordinate system are calculated using (28).

The initial displacements are obtained from the static solution of the linear differential equations derived for the EIMG system. The linear differential equations in (7) are expressed as

where and , are the output torques on the inner and outer FP, respectively.

By setting the mass matrix in (42) equal to zero and only considering the static loads, the static displacement equations can be expressed under the assumption that the deformations of components caused by gravity and the stiffness waves are negligible. In this case, we have

where .

5. Resonance of Example EIMG System and Discussion

A finite element model (FEM) of the example EIMG system described in Table 1 can be built using Ansys; a diagram of the system is presented in Figure 3. In this model, the inner stator and the permeable magnetic of the inner and outer FP consist of silicon steel (23TW250) sheets. The back irons of the inner rotor and outer stator are also made of 23TW250. The nonpermeable magnets of the inner and outer FP are made of epikote, which has similar material characteristics to air. The remanence and coercivity of the PMs on the inner rotor and outer stator are coincident (see Table 1). In this study, we consider linear and unsaturated magnetic circuits. The air gaps have denser grids because these areas have greater magnetic reluctance and higher variation gradients of magnetic flux density than the PMs and back irons. The torque profiles calculated for all components are displayed in Figure 4.

Table 1: Parameters of example EIMG system.

Number of pole pairs on inner stator
2
Number of pole pairs on inner surface of inner rotor
5

Number of pole pairs on outer surface of inner rotor
4
Number of pole pairs on outer stator
17

Number of inner FP
7
Number of outer FP
21

Outer radius of inner stator/mm
98
Inner radius of inner FP/mm
100

Outer radius of inner FP/mm
130
Thickness of PMs on inner rotor/mm
10

Inner radius of inner rotor yoke/mm
152
Outer radius of inner rotor yoke/mm
182

Inner radius of outer FP/mm
204
Outer radius of outer FP/mm
234

Thickness of PMs on outer stator/mm
10
Inner radius of outer stator yoke/mm
256

Outer radius of outer stator yoke/mm
276
Axial length/mm
40

Remanence of PMs/T
1.3
Coercive force of PMs/KOe
11.6

Magnitude of currents on inner stator/A
20

Figure 3: FEM of the example EIMG system.

(a)

(b)

Figure 4: Torque profiles of the example EIMG system.

Figure 4 indicates that the torques on all components vary sinusoidally with respect to the phase angle. The wave period is determined by the number of pole pairs of the currents on the inner stator or the number of pole pairs of the PMs on the inner rotor and outer stator; that is, . The torque profiles can be expressed as , where is the relative torsional displacement between two adjacent components. When the outer torque on the outer FP is less than the maximum and takes a constant value, is also constant. As such, is a (nonlinear) sinusoidal function of the relative torsional displacements.

Table 2 shows the corresponding dynamic parameters of the example EIMG system.

Table 2: Characteristic parameters of example EIMG system.

(N/m)
(N/m)
(N/m)
(rad)
(rad)
(kg)
(kg)

8.6444 × 10⁵
3.1446 × 10⁵
4.5467 × 10⁵
5π/12
π/4
0.64
0.657

(kg)
(kg)
(kg)

5.4
3.0
3.85
0.057
0.0653
0.019
0.0173

(N⋅m)
(N⋅m)
(N⋅m)
(N⋅m)
(N⋅m)
Δ (N⋅m)

0.0793
22
77
55
288.75
233.75
1

By substituting the dynamic parameters of the example system into (25) and (28), the main resonance responses of the EIMG system can be determined. When the wave frequency is close to the natural frequency of the outer FP rotational mode, the transient responses of the components are shown in Figure 5.

(a)

(b)

(c)

Figure 5: Transient responses of EIMG system when .

Figure 5 indicates that the output torque causes larger initial static displacements among the components of the EIMG system. The system damping ensures that the transient responses will gradually transition to the steady state. This process takes approximately 6 s. When resonance occurs, there are multiple frequency components in the transient responses, and the steady-state responses have a particular frequency.

Because of the magnetic coupling among components in the EIMG system, the magnetic coupling stiffness is much smaller than the mechanical support stiffness. Moreover, because there is no contact among the components (namely, no frictional damping), the resonance amplitudes of the transient responses will be larger and will slowly decay to zero. This results in some deterioration in the dynamic characteristics.

Considering the effects of damping, the resonance will gradually be close to stabilization. When the wave frequency is close to the natural frequency and half of the corresponding frequency of the derived nonlinear EIMG system, the steady-state response curves are as shown in Figures 6 and 7.

(a)

(b)

(c)

(d)

(e)

Figure 6: Main resonance when .

(a)

(b)

(c)

(d)

(e)

Figure 7: Main resonance when .

Figures 6 and 7 show that strong resonance will occur when the wave frequency is close to the natural frequency or half of the natural frequency of the derived EIMG system. The dominant frequency in the superharmonic resonance is the natural frequency, rather than the wave frequency or half of the natural frequency. The resonance amplitudes are much larger when the wave frequency is close to the natural frequency of the inner rotor rotational mode and outer FP rotational mode than when the wave frequency is close to the natural frequency of the inner FP rotational mode and inner stator rotational mode.

When resonance occurs and the displacement of a certain degree of freedom reaches its maximum, the resonance amplitudes are very different. For instance, when the wave frequency is close to the natural frequency of the outer FP rotational mode, the torsional displacements of the outer FP attain their maximum. Furthermore, the displacements of the adjacent components, namely, the inner rotor and outer stator, will also be larger; however, the displacements of the interval components, namely, the inner FP and stator, will be much smaller.

Similarly, when the wave frequency is close to twice the natural frequency of the derived EIMG system, strong subharmonic resonance will occur because of the nonlinear magnetic coupling stiffness. The dynamic behavior is similar to the superharmonic response. When the outer stator outputs torque with a wave frequency close to the natural frequency of the derived EIMG system, strong resonance will occur. Furthermore, the amplitudes of the various components will be very different.

Because there is no contact among the components, the relative influences among adjacent (interval) components are larger (smaller) than those in a mechanical gear system. Because of the output torque on the outer FP waves, the equivalent load is greatest on the outer FP. Therefore, the largest resonance occurs when the wave frequency is close to the natural frequency of the outer FP rotational mode. Because the magnetic coupling stiffness is much smaller than the support stiffness, the natural frequencies of the inner rotor and outer FP rotational mode are much larger. When the current frequency is smaller, the EIMG can be used in applications that easily admit low frequencies, high torque, and low-frequency resonance. When the current frequency is larger, low-frequency main resonances may not occur; however, superharmonic resonances can easily occur.

6. Conclusion

EIMG systems output torque as a result of the magnetic coupling among components. The magnetic coupling stiffness is much smaller than the mesh stiffness of mechanical gear systems and exhibits distinct nonlinearity. Thus, there are quadratic nonlinearities in the EIMG dynamic system. When the wave frequency is close to the natural frequency or twice/half the natural frequency of the derived EIMG system, strong resonance will occur. The dominant frequency is the natural frequency, and the resonance amplitudes exhibit large differences when superharmonic resonance occurs. Because of the smaller magnetic coupling stiffness and damping, the transient responses slowly decay to zero. In order to accelerate the decay rate of the transient responses and avoid the resonances, the vibration control strategy of the EIMG system should be analyzed. These can provide the foundation for the parameter optimization and performance improvement of the EIMG system.

Conflicts of Interest

The authors declare that there are no conflicts of interest regarding the publication of this paper.

Acknowledgments

This project is supported by the National Natural Science Foundation of China (Grant no. 51675463) and the Natural Science Foundation of Hebei Province of China (E2017203098).

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