Diagnosis of the Misaligned Faults of the Vertical Test Instrument of High-Precision Industrial Robot Reducer

High-precision reducer is the core component of industrial robots. In order to achieve the comprehensive performance testing of precision reducers, an instrument with a vertical layout and a cylindrical structure is designed. As a rotating machine, the inevitable coupling misalignment of the instrument can lead to vibration faults which lead to errors in the test. So it is pretty necessary to diagnose and monitor the coupling misalignment while the instrument is working. ,e causes of the coupling misaligned fault of the instrument and the relationship between the misalignment fault and torque ripple are analyzed in this paper. A method of using the torque transducer in the measurement chain of the instrument to diagnose the coupling misalignment is proposed in this paper. Many experiments have been done to test the capability of detecting the coupling misalignment using this method. Experimental results show that the amplitude of torque ripple of the shaft is linearly related to the coupling misalignment and is quadratically related to the rotation speed of the shaft when the misalignment exists in the shaft.,e combination of components at the rotation frequency (fr) and the additional components can be used to diagnose faults due to coupling misalignment.


Introduction
As a core component of the actuators in robots, the robot reducer directly affects their performance factors, such as the kinematic accuracy, load capacity, and fatigue life [1]. erefore, the comprehensive performance test of precision reducers is required for developing high-precision industrial robots, and it has become the focus of attention of researchers [2]. Some progress has been achieved concerning the performance testing of precision reducers [3,4]. e reducer detector often shows vibration faults caused by shaft misalignment [5]. An instrument, designed by Dhaouadi and Ghorbel, is designed to be a vertical structure to ensure an excellent shaft misalignment [6][7][8]. However, the methods to reduce the shaft misalignment caused by the manufacturing tolerances incur high costs and require much effort [9]. Even if an accurate alignment is secured, it cannot be continued for a long duration due to many effects, such as thermal deformation and load imbalance [10,11]. Many studies [12][13][14] indicated that the misalignment would undoubtedly lead to deterioration of whole lubrication characteristics of bearing and even the failure of the system.
Flexible couplings are usually used to overcome slight misalignment of the rotating machinery [15][16][17]. However, as is described above, many factors can increase misaligned faults. erefore, a feasible method for misaligned fault diagnosis is required. Recently, many efforts have been made to diagnose misaligned faults of rotating machinery through the combination of signal acquisition, data processing, and fault classification [18][19][20][21][22]. Vibration analysis is the most common technique for monitoring and diagnosing mechanical systems [23][24][25]. e signal acquisition for certain mechanical faults is accomplished by installing an accelerometer or proximity probe [26,27]. However, due to the confusing spectral characteristics of vibration, vibrationbased misalignment detection led to less reliability [10]. Furthermore, especially for the vertical reducer detector with a torque sensor in the measuring chain, the additional sensors mounted on the mechanism can cause a series of problems such as signals acquired to vary according to the positioning of sensors [28,29], onefold information acquisition [30], and additional cost.
Some scholars and experts have made some progress on the research of detection and monitoring of coupling misalignment based on torque signal [31]. However, their work only shows the possibilities of torque measurements as a valuable technique for detecting misalignment, and more theoretical studies are needed to show the relationship between the coupling misalignment and the ripple of torque. In other works, techniques for estimating torque from the sensing of the electrical variables of the motors have been proposed and tested using the frequency spectrum of the current electrical motor for diagnosis [16]. However, the estimated torque, which includes the component due to either misalignment of stator and rotor or rotor eccentricity of the motor, cannot represent the torque transmitted by the shaft.
us, it cannot show the effect of coupling misalignment of the shaft clearly. Besides, the experiment is carried out on the horizontal instrument, which cannot represent the effect of the method on the vertical instrument.
In order to solve the problem of diagnosis coupling misalignment in the vertical robot reducer detector, a method of using the torque transducer to diagnose the coupling misaligned fault of performance testing instruments of precision reducers is proposed in this paper to overcome the shortcoming of diagnosis of misaligned fault using an accelerometer or proximity probe. e paper is mainly organized as follows: Firstly, the structure of a vertical performance testing instrument of precision reducers, including guide rail mechanism, measurement module on the input side (MMIS), tested assemblies (TA), measurement module on the output side (MMOS), and workbench, is introduced in Section 2 combined with analysis of the causes of the misaligned fault. Next, the relationships between the misaligned fault and the torque ripple are analyzed in Section 3. Moreover, the experiment's effects using the Fast Fourier Transform and power spectrum analysis of the torque signal to diagnose the misaligned fault are revealed in Section 4. Finally, some conclusions are given in the fifth section.

Structure of the Vertical Instrument and
Analysis of the Causes of the Misaligned Fault e vertical instrument is designed to measure the comprehensive performance of the reducer, as shown in Figure 1.
is instrument consists of four assistance modules, which are guide rail mechanism, tested assemblies (TA), power supply system, and workbench, and two measurement modules, namely, the measurement module at the input side of the reducer (MMIS) and that at the output side of the reducer (MMOS). Each measurement module is mainly composed of the five following subsystems: motor, torque transducer, test mode conversion part, angle encoder, and other connecting parts. e red component in Figure 1 represents the TA. e robot reducer was installed inside the TA, which is used to achieve a rapid installation of different reducer types. e connections with the measurement systems adopt a uniform and standard structure. e instrument is of vertical type in which functional components are sequentially connected in series in the vertical direction. MMIS, MMOS, and TA are the core components. e causes of the misaligned fault are as follows: (1) Although the disk supports inside the hollow cylinder are designed to ensure that the shafts are centered, the manufacturing tolerances and assembly error of the disk supports can still lead to shaft misalignment. (2) e flexible coupling is used in the connecting parts to overcome slight misalignment between the shafts. However, many factors can increase misaligned faults, and flexible coupling can never solve the problem caused by increasing misalignment. (3) Moreover, the test mode conversion components allow the input or output shaft of the tested reducer to be under unconstrained, driven, or locked conditions, thereby satisfying the functional requirements of different dynamic and static performance tests. However, there is no guarantee that the conversion components move along the axis. e changing of the test mode can increase the misaligned faults because of the motion of the conversion components.
Since all the three factors above can lead to the misaligned fault and the misalignment mainly between the shafts connected by the flexible coupling and spline coupling, a feasible method is required to realize the misaligned fault diagnosis. In this paper, the torque transducer is used to diagnose the misaligned fault of performance testing instruments of precision reducers through testing the torque ripple. e relationships between the misaligned fault and the torque ripple are analyzed in the next section.

Relationships between the Misaligned Fault and the Torque Ripple
ere are three common types of shaft misalignment (as shown in Figure 2): parallel misalignment (a), angle misalignment (b), and comprehensive misalignment (c). Due to the inevitable manufacturing tolerances and assembly error, the three kinds of misalignment faults shown in Figure 2 can exist in the flexible coupling and spline coupling at each of the two shafts of MMIS and MMOS. Especially for the rectangular spline sleeve, which connects two spline shafts at the same time, the misalignment fault can exist. Due to the excessive spline clearance, both spline shafts can be considered unconstrained at one end, and the other end is supported in the state of high-precision bearing. In the transmission process, it is likely that the misalignment between the two spline shafts and the spline sleeve changes with the rotation of the shaft. at is, the three states in Figure 2 may appear alternately. e rotating shaft of MMIS, which is the same as that of MMOS, is shown in Figure 3. When the parallel or angular offsets exist in the shaft, the mass center of the shaft does not coincide with the rotation center. e shaft will be affected by the electromagnetic torque of the motor and the eccentric torque. Under the effect of the cogging effect and misalignments, the electromagnetic torque of the motor and the eccentric torque change with the rotation of the shaft. e driving torque, which is defined as the sum of the electromagnetic torque of the motor and the eccentric torque, can be expressed as the sum of averaged torque and torque ripple [32].
where T and T n are the averaged torque and amplitude for the nth driving torque, respectively, n is the harmonic orders of the output shaft, and θ out and ∅ n are the position of the output shaft and phase offset for the nth driving torque, respectively. e ripple of the driving torque can cause the friction torque of the shaft to change with the shaft rotation. at is because the friction torque is caused by the friction generated in the bearing because of rotation. e ripple of the driving torque leads to the ripple of the acceleration of the shaft. e ripple of the acceleration of the shaft can cause the ripple of the rotation speed and finally leads to the ripple of the friction torque of bearings [33]. en, the friction torque can be expressed as follows: where T f and μ are the friction torque and friction coefficient, respectively, N is the supporting force of the bearing, r is the radius of the shaft, m is the eccentric mass of the shaft, Δr is the misalignment of the shaft, n is the harmonic orders  of the output shaft, ω n is the amplitude for the nth rotation speed of the shaft, and θ out and ∅ n are the position of the output shaft and phase offset for the nth driving torque, respectively. e driving torque and the friction torque, which are changing with the shaft rotation, eventually lead to the torque ripple of the shaft. As is analyzed above, the driving torque and the friction torque are affected by the misalignment. e torque ripple of the shaft is also affected by the misalignment. According to the analysis in the second section, the misalignment is mainly between the shafts connected by the flexible coupling and spline coupling. e impact of misalignment of various shaft parts on torque ripple, especially about the misalignment between the two spline shafts and the spline sleeve, is analyzed in detail in the following.

Torque Ripple Caused by the Misalignment of Flexible
Coupling. When the parallel misalignment Δx exists between the motor shaft and the transmission shaft, the flexible coupling connecting the two shafts will be deformed. According to Hooke's law, the deformed flexible coupling will produce reaction forces F 1 ′ and F 2 ′ on the shafts at both ends of the flexible coupling. Besides, the mass center of the shaft does not coincide with the rotation center. e shaft will be affected by the eccentric force. At this time, the transmission shaft is not only affected by the driving torque T transmitted by the flexible coupling but also affected by the reaction force and the eccentric force caused by the parallel misalignment. e reaction force and the eccentric force will eventually be balanced by the supporting forces F 1 and F 2 provided by the bearing. Finally, the friction torque T f1 will be brought due to the reaction force and the eccentric force acting on the bearing. erefore, the parallel misalignment Δx exists between the motor shaft and drive shaft producing friction torque, which affects the torque transmitted through the shaft. Because the driving torque is changing with the shaft rotation, it will cause the rotation speed to change with the shaft rotation. e ripple of the rotation speed will lead to the friction torque change with the shaft rotation. Figure 4 shows the force and friction torque caused by the parallel misalignment Δx between the motor shaft and the transmission shaft. e torque transmitted by the transmission shaft T 1 is the drive torque minus the friction torque. When the parallel misalignment Δx exists between the motor shaft and the transmission shaft, the torque transmitted by shaft T′ can be expressed as follows [34]: where T and T n are the averaged torque and amplitude for the nth driving torque, respectively, n is the harmonic orders of the output shaft, θ out and ∅ n are the position of the output shaft and phase offset for the nth driving torque, respectively, μ 1 is the friction coefficient of the transmission shaft, k 1 is the coefficient of elasticity of the transmission shaft, m 1 is the mass of the transmission shaft, r 1 is the radius of the transmission shaft, Δx is the parallel misalignment, and ω n is the amplitude for the nth rotation speed of the shaft. e misalignment errors comprise radial and angular displacements. When the angle misalignment Δθ exists between the motor shaft and the transmission shaft, the flexible coupling connecting the two shafts will be deformed. e deformed coupling will produce a reaction force on the shafts at both ends of the flexible coupling. According to Hooke's law, the reaction force on the transmission shaft caused by the angle misalignment can be expressed as follows: where L 1 is the length of the transmission shaft, Δθ is the angular misalignment, and k 1 is the coefficient of elasticity of the transmission shaft. Besides, when the angular offsets exist in the shaft, the mass center of the shaft does not coincide with the rotation center. e shaft will be affected by the eccentric force. e eccentric force on the shaft caused by the angle misalignment can be expressed as follows: where F e is the eccentric force, m 1 is the mass of the transmission shaft, L 1 is the length of the transmission shaft, Δθ is the angular misalignment, n is the harmonic orders of the output shaft, ω n is the amplitude for the nth rotation speed of the shaft, and θ out and ∅ n are the position of the output shaft and phase offset for the nth driving torque, respectively. At this time, the transmission shaft is not only affected by the driving torque T transmitted by the flexible coupling but also affected by the reaction force and the eccentric force caused by the angular misalignment. e reaction force and the eccentric force will eventually be balanced by the supporting force provided by the bearing. Finally, the friction torque T f1 ′ will be brought due to the reaction force and the eccentric force acting on the bearing. erefore, the angle misalignment Δθ exists between the motor shaft and drive shaft producing friction torque, which affects the torque transmitted through the shaft. Because the driving torque is changing with the shaft rotation, it will cause the rotation speed to change with the shaft rotation. e ripple of the rotation speed will lead to the friction torque change with the shaft rotation. Figure 5 shows the force and friction torque caused by the angle misalignment Δθ between the motor shaft and the transmission shaft.
When an angular misalignment error exists, the torque transmitted by shaft T 1 ′ is the drive torque minus the friction torque. When the angle misalignment Δθ exists between the motor shaft and the transmission shaft, the torque transmitted by shaft T 1 ′ can be expressed as follows [35]: where T and T n are the averaged torque and amplitude for the nth driving torque, respectively, L 1 is the length of the transmitted shaft, Δθ is the angular misalignment, k 1 is the coefficient of elasticity of the transmission shaft, μ 1 is the friction coefficient of the transmission shaft, m 1 is the mass of the transmission shaft, r 1 is the radius of the transmission shaft, n is the harmonic orders of the output shaft, ω n is the amplitude for the nth rotation speed of the shaft, and θ out and ∅ n are the position of the output shaft and phase offset for the nth driving torque, respectively.

Torque Ripple Caused by the Misalignment of Spline
Coupling. e spline coupling is a complex structure. e spline structure in our instrument is equivalent to two sets of spline coupling. One spline sleeve connects two spline shafts at the same time. In general, the torque is transmitted to the spline sleeve through the transmission shaft and then is transferred to the torque transducer shaft by the spline sleeve. Due to the excessive spline clearance, both spline shafts can be considered unconstrained at one end and supported by a high-precision bearing at the other end. In the transmission process, it is likely that the misalignment between the two spline shafts and the spline sleeve changes with the rotation of the shaft. Besides, as long as there is a misalignment between the spline shaft and spline sleeve, only 25%∼50% of the spline's teeth participate in meshing simultaneously in actual work. Besides, the meshing of the spline shaft and spline sleeve is uneven, some of the spline's teeth meshing is tight, and some of the spline's teeth meshing is loose. As a result, the engagement force of each spline's teeth is different, and a resultant force is generated at the teeth of the spline shaft offset. e resultant force produces sliding between the spline sleeve and the spline shaft. So the friction torque, which affects the torque transmitted through the shaft, is generated. e resultant force is balanced by the friction force and support force provided by the bearing. Due to misalignment, the spline sleeve point meshed with the spline shaft at the spline shaft offset is changed with the shaft rotation.
When the parallel misalignment Δx ′ exists between the transmission shaft and the torque transducer shaft, the meshing of the spline shaft and spline sleeve is uneven. e friction torque T f2 caused by the uneven meshing of the spline shaft and spline sleeve and the sliding between the spline sleeve and the spline shaft is generated. At this time, the torque transducer shaft is not only affected by the driving torque T transmitted by the transmission shaft but also Shock and Vibration 5 affected by the friction torque T f2 caused by the parallel misalignment. erefore, the parallel misalignment Δx ′ that exists between the two spline shafts produces friction torque, which affects the torque transmitted through the shaft. Because the driving torque is changing with the shaft rotation, it will cause the rotation speed to change with the shaft rotation. e ripple of the rotation speed will lead to the friction torque change with the shaft rotation. Figure 6 shows the force and friction torque T f2 caused by the parallel misalignment Δx ′ between the two spline shafts. e torque transmitted by the torque transducer shaft T 2 is the drive torque minus the friction torque. When the parallel misalignment Δx 1 exists between the transmission shaft and the torque transducer shaft, the torque transmitted by the torque transducer shaft T 2 can be expressed as follows [34]: where T and T n are the averaged torque and amplitude for the nth driving torque, respectively, n is the harmonic orders of the output shaft, θ out and ∅ n are the position of the output shaft and phase offset for the nth driving torque, respectively, μ 2 is the friction coefficient of the torque transducer shaft, m 2 is the mass of the torque transducer shaft, r 2 is the radius of the torque transducer shaft, k 2 is the coefficient of elasticity of the torque transducer shaft, Δx ′ is the parallel misalignment, L 0 is the equivalent meshing distance of each spline's teeth in good alignment condition, and ω n is the amplitude for the nth rotation speed of the shaft. When an angular misalignment Δθ ′ exists between the transmission shaft and the torque transducer shaft, the meshing of the spline shaft and spline sleeve is uneven. e friction torque T f2 ′ caused by the uneven meshing of the spline shaft and spline sleeve and the sliding between the spline sleeve and the spline shaft is generated. erefore, the angular misalignment Δθ ′ that exists between the two spline shafts produces friction torque, which affects the torque transmitted through the shaft. Because the driving torque is changed with the shaft rotation, it will cause the rotation speed to change with the shaft rotation. e ripple of the rotation speed will lead to the friction torque change with the shaft rotation. Figure 7 shows the force and friction torque T f2 ′ caused by the angular misalignment Δθ ′ between the two spline shafts. e torque transmitted by the torque transducer shaft T 2 ′ is the drive torque minus the friction torque. When the angular misalignment Δθ ′ exists between the transmission shaft and the torque transducer shaft, the torque transmitted by the torque transducer shaft T 2 ′ can be expressed as follows [35]: n L 0 − L 2 tan △θ ′ cos nθ out + ∅ n cos nθ out + ∅ n ,  where T and T n are the averaged torque and amplitude for the nth driving torque, respectively, n is the harmonic orders of the output shaft, θ out and ∅ n are the position of the output shaft and phase offset for the nth driving torque, respectively, μ 2 is the friction coefficient of the torque transducer shaft, m 2 is the eccentric mass of the torque transducer shaft, r 2 is the radius of the torque transducer shaft, k 2 is the coefficient of elasticity of the torque transducer shaft, Δθ ′ is the angular misalignment, L 0 is the equivalent meshing distance of each spline's teeth in good alignment condition, ω n is the amplitude for the nth rotation speed of the shaft, and L 2 is the length of the torque transducer shaft.

Experimental Results of Diagnosing the Misalignment Using the Fast Fourier Transform and Power Spectrum Analysis of the Torque Signal
According to the analysis proposed in the above section, it can be seen that the amplitude of torque ripple of the shaft is linearly related to the misalignment of the flexible coupling and the spline coupling and is quadratically related to the rotation speed of the shaft when the parallel or angular misalignment exists in the shaft. Moreover, the frequency of the torque ripple is the same as the frequency of the rotation speed. So, the amplitude and frequency of torque ripple can be used to diagnose the misalignment of the MMIS and MMOS. Experiments have been done to test the capability of detecting the misalignment of the flexible coupling and the spline coupling of the MMIS and MMOS using the measurement and analysis of torque ripple. e Fast Fourier Transform and power spectrum analysis of torque are used to obtain the amplitude and frequency of torque ripple. e singular value decomposition (SVD) filtering stage is included in the data processing to obtain the amplitude and frequency of torque ripple. SVD filtering algorithm is to decompose the signal into a series of pure signal subspace and noise subspace, which are corresponding to the singular matrix. In the singular matrix, the larger singular value corresponds to the pure signal, and the smaller singular value corresponds to the noise signal. erefore, after determining the reasonable effective rank of the singular matrix, the singular values with the same number of effective ranks are taken from the large to the small, and the remaining values are set to zero. en the matrix estimation of pure signal is obtained by inverse operation of SVD, and the final signal after singular value denoising is obtained by inverse reconstruction of phase space. In signal processing, SVD filtering stage, which has excellent invariance and stability, is mainly used for the extraction of periodic components and the denoising of signals. By using the maximum salient point of singular value difference spectrum to accurately judge the order of noise reduction, the interference of noise components in the signal can be effectively eliminated; and the main components of fault information can be retained. e structure of the MMIS and MMOS is introduced in the second section, as shown in Figure 1. In the experiment, the motor drives the transmission shaft coupled to the torque transducer shaft.
at means the test mode conversion components make the shaft of the MMIS or MMOS under driven conditions. e angular misalignment conditions and radial misalignment conditions are controlled by adjusting the radial and angular displacements of the conversion components and the transmission shaft when installing the shaft of MMIS or MMOS, as shown in Figure 8. e torque transducers in MMIS and MMOS are used to test the torque ripple. e diagrammatic sketch of the experimental device (MMIS) is shown in Figure 9.
As an example, the details of adjusting the radial misalignment in the experiment are shown as follows: (1) Put the hollow cylinder in the center of the turntable. (2) Put the disk support on the hollow cylinder. (3) Adjust the radial misalignment between the torque transducer shaft and the disk support using the dial gauge. (4) Adjust the radial misalignment between the disk supports and the hollow cylinder using the dial gauge and install the disk support on the hollow cylinder. (5) Adjust the radial misalignment between the transmission shaft and the hollow cylinder using the dial gauge and install the transmission shaft on the disk support. e torque transducers in the instrument are produced by the HBM company. e model of the torque transducer is T40B. e measuring range of the torque transducer in the MMIS is 0-50 Nm, and its measuring accuracy is 0.1% in full scale. e measuring range of the torque transducer in MMOS is 0-2000 Nm, and its measuring accuracy is 0.05% in full scale. As the best product of torque transducer of the world, the maximum allowable radial misalignment of T40B can reach about 2 mm. But, when the radial misalignments reach more than 100 μm, the radial misalignments will lead to torque oscillation. e servo motor and torque motor used in the MMIS and MMOS are made by the Modrol Electric Co., Ltd. e model of the servo motor is SMS15-42P2C, and the model of the torque motor is MDD310. e loading accuracies of the servo motor and torque motor are 0.1% in full scale. e load ranges of the servo motor and torque motor are 50 Nm and 2000 Nm, respectively. A PXIe acquisition system produced by the NI company is used to collect the torque transducer's signals. e accuracy of torque signal acquisition of the PXIe acquisition system is 0.1% in full scale. e torque signal data is collected using LabVIEW ™ software at a rate of 25 k samples per second.
First of all, experiments of diagnosing the misalignment fault of the shaft are carried out for alignment, a 0.5 mm radial misalignment, and a 1.0 mm radial misalignment. e experiments are carried out under no load. Using the MMIS as an example, the rotation speed is increased by 200 rpm every time from 0 rpm to 800 rpm. e torque transducer tests the transmitted torque of the MMIS under different rotation speeds. e ripple of the transmitted torque under different rotation speeds is analyzed using the Fast Fourier Transform and power spectrum analysis after SVD filtering.   Figure 10 shows the frequency spectrum of the transmitted torque under different rotation speeds for the case of shaft alignment. For such conditions, the rotational frequency, when the rotation speed is increased by 200 rpm every time from 0 rpm to 800 rpm, is increased by 3.33 Hz every time from 0 Hz to 13.33 Hz. e figure showing the absence of components at the rotation frequency (fr), which is shown in the third section, is able to detect fault misalignment.

Shock and Vibration
e additional components of twice the rotational frequency (2fr), fourth of the rotational frequency (4fr), and even eighth of the rotational frequency (8fr) are also observed in Figure 10. is component may be due to the cogging torque and electromagnetic torque ripple. Figure 11 shows the power spectrum of the transmitted torque under different rotation speeds for the case of shaft alignment. e powers of the additional components of twice the rotational frequency (2fr), fourth of the rotational frequency (4fr), and even eighth of the rotational frequency (8fr) are all the same. is phenomenon means that all the torque ripple causes, such as the cogging torque and electromagnetic torque ripple, have the same effect on the torque ripple. Figure 12 shows the frequency spectrum for 0.5 mm radial misalignment. Figure 13 shows the frequency spectrum for 1.0 mm radial misalignment. In this particular case, a component at the rotation frequency (fr) of greater amplitude can be observed. ese components clearly show misalignment between the transmission shaft and the torque transducer shaft. Furthermore, it can be observed that the components of twice the rotational frequency (2fr), fourth of the rotational frequency (4fr), and eighth of the rotational frequency (8fr) are higher than those for aligned shafts. Figure 14 shows the power spectrum of the transmitted torque under different rotation speeds for 0.5 mm radial misalignment. Figure 15 shows the power spectrum of the transmitted torque under different rotation speeds for 1.0 mm radial misalignment. e powers of the additional components of the rotational frequency (fr), twice the rotational frequency (2fr), fourth of the rotational frequency (4fr), and even eighth of the rotational frequency (8fr) are  decreased with the increase of frequency. is phenomenon can be explained by the friction torque due to misalignment on shaft extension. Such torque increases the eccentricity which appears in the components at fr. After comparison, we can come to the conclusion that the component fr and the power of the additional components both allow diagnosing faults due to misalignment. From Figures 10-15, it can be seen that the robustness and effects of the SVD filtering are so good that those unuseful signals of high frequency and low amplitudes have been filtered.
at means only the main components of torque ripple, which can be used to diagnose the misalignment fault, left after SVD filtering.
In order to verify the diagnostic accuracy and robustness of the proposed method and the SVD filtering method, comparison experiments of diagnosing the misalignment fault of the shaft are carried out for alignment, a 0.125 mm radial misalignment, a 0.25 mm radial misalignment, a 0.375 mm radial misalignment, a 0.5 mm radial misalignment, a 0.625 mm radial misalignment, a 0.75 mm radial misalignment, a 0.875 mm radial misalignment, and a 1.0 mm radial misalignment. Figure 16 shows the amplitude of the components of torque ripple at fr, 2fr, and 4fr for alignment, 0.125 mm radial misalignment, 0.25 mm radial misalignment, 0.375 mm radial misalignment, 0.5 mm radial misalignment, 0.625 mm radial misalignment, 0.75 mm radial misalignment, 0.875 mm radial misalignment, and 1.0 mm radial misalignment under the same rotation speeds. Figure 17 shows the amplitude of torque ripple at fr under different rotation speeds for alignment, 0.5 mm radial misalignment, and 1.0 mm radial misalignment, respectively. From the two figures, we can see that the amplitude of torque ripple of the shaft is linearly related to the radius misalignment and is quadratically related to the rotation speed of the shaft. en, comparison experiments of diagnosing the misalignment fault of the shaft are carried out for alignment, a 0.125°angular misalignment, a 0.25°angular misalignment, a 0.375°angular misalignment, a 0.5°angular misalignment, a 0.625°angular misalignment, a 0.75°0    Figure 18 shows the amplitudes of the component of torque ripple at fr, 2fr, and 4fr for alignment, 0.125°a ngular misalignment, 0.25°angular misalignment, 0.375°angular misalignment, 0.5°angular misalignment, 0.625°angular misalignment, 0.75°angular misalignment, 0.875°angular misalignment, and 1°angular misalignment under the same rotation speeds. Figure 19 shows the amplitude of torque ripple at fr under different rotation speeds for alignment, 0.5°angular misalignment, and 1°angular misalignment, respectively. From the two figures, we can see that the amplitude of torque ripple of the shaft is linearly related to the angular misalignment and is quadratically related to the rotation speed of the shaft.

Conclusions
A method of using the torque transducer to diagnose the coupling misaligned fault of performance testing instruments of precision reducers is proposed in this paper. e causes of the coupling misaligned fault of the instrument and the relationship between the misalignment fault and torque ripple are analyzed. Experiments have been done to test the capability of detecting the coupling misalignment of the instrument using the measurement and analysis of torque ripple. From the analysis and experimental results presented in the third and fourth sections, we can see that the amplitude of torque ripple of the shaft is linearly related to the misalignment of the flexible coupling and the spline coupling and is quadratically related to the rotation speed of the shaft when the parallel or angular misalignment exists in the shaft. e amplitude and frequency of torque ripple can be used to diagnose the misalignment of the MMIS and MMOS. e frequency components of the torque ripple test by the torque transducer in the MMIS and MMOS allow identifying radial and angular misalignment when the increasing misalignment exists in the shaft connected by the flexible coupling and spline coupling.
Such a characteristic can be demonstrated with small levels of angular and radial misalignment faults. e components of the torque at fr and 2fr frequencies are suitable for detecting misalignment. erefore, it is considered a more suitable fault indicator than that of the component at fr frequency. Moreover, the powers of the additional components of the rotational frequency (fr), twice the rotational frequency (2fr), fourth of the rotational frequency (4fr), and even eighth of the rotational frequency (8fr) are decreased with the increase of frequency. is phenomenon can be explained by the friction torque due to misalignment on shaft extension. Such torque increases the eccentricity which appears in the components at fr. After comparison, we can come to the conclusion that the combination of components at the rotation frequency (fr) and the additional components can be used to diagnose faults due to coupling misalignment. e method proposed in this paper is mainly about the diagnosis of static misalignment, caused by installation and the manufacturing tolerances. ose misaligned faults can lead to continuing periodical torque ripple. e frequency and the amplitude of torque ripple can be used to diagnose the misaligned fault. But when talking about the torque oscillation caused by the joint flexibility or backlash at joints, on one side, it is not periodical signal, and, on the other side, the amplitude of the torque oscillation will change with the rotation of shaft. So, the torque oscillation caused by the joint flexibility or backlash at joints will not influence the effect of the method proposed in this paper. e diagnosis of the joint flexibility or backlash at joints will be our research work in the future.
Data Availability e data that support the findings of this study are available from the corresponding author upon reasonable request.

Conflicts of Interest
e authors declare that they have no conflicts of interest.