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The Relationship Between TE and Gear Elemental Deviations
Release Time：29 Aug,2025
<p style="text-align: center;"><img src="/ueditor/php/upload/image/20250829/1756473319289388.png" title="1756473319289388.png" alt="2.png"/></p><p style="text-align: justify;"><span style="font-family: arial, helvetica, sans-serif; font-size: 12px;">TE refers to the difference between the actual position of the output and the ideal position that the output shaft of a drive would occupy if the drive were perfect (Ref. 15). Further, TE has three basic forms: tangential composite deviation of a gear, TE of a gear pair, and TE of a gear transmission chain.</span></p><p style="text-align: justify;"><span style="font-family: arial, helvetica, sans-serif; font-size: 12px;">The tangential composite deviation of a gear is equivalent to the TE of a tested gear mated with a master gear (Ref. 16). The TE of a gear pair represents the difference between the actual position of the driven gear and its theoretical position based on the position of the driving gear. The mathematical expression for the TE of a gear pair can be represented by Equation 1. Among them, θ1(t) and θ2(t) respectively represent the angular displacement of the input and output gears, and z1 and z2 respectively represent the number of teeth of the input and output gears. (1) A gear transmission chain refers to a system consisting of multiple gear pairs. In such a chain, TE is defined as the difference between the actual position of the output end gear and its theoretical position based on the input end gear. The mathematical expression for TE of a gear transmission chain is provided in Equation 2 (Refs. 17–19). Among them, TEn is the TE of the nth level transmission, and in-1 is the total transmission ratio of the transmission chain of n pairs of gears. (2) The Relationship Between TE and Gear Elemental Deviations Gears exist in pairs, and TE is a comprehensive representation of the elemental deviations of both the driving and driven gears. However, it is not possible to derive the elemental deviations of the driving and driven gears from the TE of a gear pair. Figure 4 reflects the combination of tooth profile deviations (Ref. 16). In 1969, R.G. Munro (Ref. 20) conducted theoretical and experimental research on single-flank and double-flank testing of gears. Munro also provided composite error curves for single and double testing that correspond to the combination of various tooth profile deviation shapes of involute gears. Figure 4—Profile deviations combination. It is difficult to separate the elemental deviations of gears from the TE curve alone, which means it is impossible to analyze the main factors affecting gear transmission or to clarify the process of TE generation. The GIE measurement technique proposed by Huang Tongnian has solved the above problems. A typical GIE curve is shown in Figure 5, where the TE curve is the outer envelope of the GIE curve. By examining the GIE curve, one can clearly observe the change-over process from 2-pair-teeth contact to 1-pair-teeth contact, distinguish between the 1-pair-teeth contact zone and 2-pair-teeth contact zone, and isolate the elemental deviations, which cannot be achieved through the TE curve alone. Figure 5—Comparison between GIE and TE. Classification of TE In this study, TE is divided into three main types: static transmission error, quasi-static transmission error, and dynamic transmission error. Static TE (STE) STE exclusively considers the impact of geometric errors, such as manufacturing and assembly errors, without considering the influences of loading deformation, vibration, and tooth-pair disengagement. It needs to be measured at low speed and without load, which can be represented by equation (3), where u represents the geometric error of the gear.</span></p><p style="text-align: justify;"><span style="font-family: arial, helvetica, sans-serif; font-size: 12px;">Quasi-Static TE (QSTE) The STE varies when the gear is loaded, and this variation depends on the gear’s rotational speed and loading deformation. When the gear bears a load and runs at low speed, the difference between the actual position of the driven gear and its ideal position is referred to as the QSTE. The QSTE considers the effects of manufacturing errors, assembly errors, and loading deformations but does not consider factors such as tooth-pair disengagement. It needs to be measured under low-speed loading and can be represented by formula (4), where L denotes the gear dynamic error. (4) Dynamic TE (DTE) QSTE is measured at low speeds and under load, without considering the impact of acceleration and deceleration on TE during high-speed operation of gears. As the rotational speed increases, the transmission error caused by acceleration and deceleration becomes more apparent and may even lead to the tooth-pair disengagement of the driving and driven gears, resulting in a clash due to disengagement. Disengagement is divided into hard and soft disengagement. Hard disengagement refers to the situation where the driven gear is suddenly accelerated during tooth shifting, causing the tooth profiles of the driving and driven gears to disengage. Soft disengagement occurs when the driven gear attempts to maintain its original speed due to inertia during deceleration, leading to the disengagement of the tooth profiles. Hard disengagement generally occurs at the point of tooth alternation, while soft disengagement typically occurs during deceleration. As shown in Figure 6, the solid line represents the TE curve, and the dashed line represents the TE curve after disengagement. Soft disengagement is generally easier to occur, while hard disengagement can only happen under certain conditions. Typically, as the gear rotation speed increases, the likelihood of disengagement also increases. As the load increases, the likelihood of disengagement decreases. Due to the impact of disengagement, the continuity of gear transmission is lost. Figure 6—Detachment impact (Ref. 21). DTE takes into account the combined effects of geometric error, kinematic error, and dynamic error. It is essential to measure DTE at high speeds in order to obtain a comprehensive understanding of the transmission system’s behavior. It can be represented by formula (5), where η represents gear kinematic error. (5) Composition of TE Sources of TE TE can arise from various sources, primarily categorized into five aspects: Manufacturing Errors: These arise from various inaccuracies in the manufacturing process system, including tools, machine tools, workpiece fixtures and so on. Assembly Errors: Gears are mounted on shafts within a housing, supported and fixed by bearings. Assembly errors primarily reflect eccentric mounting and parallelism issues with the axis. Elastic Deformation: Under load, gears undergo elastic deformation, causing one gear to rotate slightly relative to another, leading to transient changes in the meshing position during transmission. Thermal Deformation: As gears operate, temperature rise occurs, resulting in thermal deformation that disrupts the original involute tooth profile. This causes instability in the direction of force transmission and variability in the gear ratio, affecting motion smoothness. Gear Disengagement: Due to gear deviations, there can be instances where the tooth profiles lose contact, leading to impacts from disengagement. Contact Point Motion Gear Pair Without Errors Gear transmission operates by utilizing the interaction between the teeth of the driving gear and the teeth of the driven gear. This process entails the sequential engagement of the conjugate tooth surfaces. Figure 7 illustrates the meshing process of involute cylindrical gears, where two involute gears (labeled as o1 and o2) rotate around their respective fixed axes. o1 represents the driving gear and o2 represents the driven gear, and the base circle radii are rb1 and rb2, respectively. P is the pitch point. As gear o1 drives gear o2, the path of moving of contact point of the conjugate tooth surfaces is the line of action B1 – B2. The driving gear transfers motion and force to the driven gear by their interaction, along the direction of the line of action (Refs. 22–23). Figure 7—The meshing process of involute gears. During the transmission cycle of a pair of teeth, the contact point starts from the point G1, and the meshing sequence is G1B1, , and B2G2. The G1B1 segment represents the entry stage, which is the edge contact section of the driven gear, where the contact point moves from the tooth mid to the tooth root on the tooth surface of the driving gear. The B2G2 segment is the exit stage, which is the edge contact section of the driving gear, with the contact point moving from the tooth root to the tooth mid on the driven gear’s tooth surface. For involute spur gears, the GIE curve during the edge contact segment is parabolic. The segment illustrates the normal involute contact process, corresponding to the middle smooth section on the GIE curve, where the contact point moves from the tooth root along the involute to the tooth tip on the driving gear’s tooth surface, and from the tooth tip along the involute to the tooth root on the driven gear’s tooth surface. Gear Pair with Errors Figure 8 illustrates the meshing phase of a pair of gears. The driving gear is perfect, while the driven gear exhibits a positive base pitch deviation Δfpb, with the driving gear rotating at a constant speed. In this case, the driving and driven gears cannot directly enter the involute meshing segment, resulting in the meshing process EA2 shown in Figure 8. In the EA2 segment, the contact point first appears at point E, and then moves from point E to point A2 on the tooth surface of the driving gear. Starting from point A2, it enters the involute contact section, where the contact point gradually moves from the tooth root to the tooth top on the driving gear tooth surface. As depicted in Figure 8, for the driving gear, the radius of point E exceeds the radius of point A2. This procedure signifies a transition from the tooth apex to the tooth root direction, constituting the meshing process of the upper edge of the driven gear. Figure 8—Gear meshing process with positive base pitch deviation. The process mentioned above corresponds to the TE curve shown in Figure 9. By taking the first and second derivatives of the TE curve, we can obtain the velocity error curve and acceleration error curve, respectively. The entry impact point marked λ plays a significant role in these calculations. At that point, the driven gear experiences the greatest change in rotational speed, with a jump occurring at this point. Theoretically, the acceleration is infinitely large at this moment; however, due to damping and elastic deformation, a pulse is formed. Figure 9—TE curve of gear with positive base pitch deviation. Gear Pair Under Load Figure 10 displays the GIE curve of a perfect gear pair. During light load transmission, there is no error, as indicated by the non-fluctuating portion of the TE curve in the figure. However, when the gear pair bears the load, the teeth of the gears bend, causing the TE curve to sink as a whole. This leads to the driving gear moving backward and the driven gear moving forward, as depicted by the red curve in the figure. Under the action of load, the dynamic performance of a perfect gear pair deteriorates. On one hand, the driven gear tooth tip enters into contact with the driving gear tooth root ahead of time in the meshing process, causing meshing-in impact; on the other hand, after the ideal meshing is interrupted, the driving gear tooth tip still contacts the driven gear tooth root, causing meshing-out impact when they separate. Due to the meshing in and out impacts, the gear speed loses continuity and fluctuates, resulting in degraded performance of the ideal gear. Figure 10—TE curve of a perfect gear pair under load. Gear Pair with Modified Flank The case of an ideal gear is shown in Figure 11, where the corresponding GIE curve is smooth and straight, without any meshing-in and -out impact. When the gear is under load, tooth deformation disrupts smooth transmission, causing meshing-in and -out impacts. To achieve good transmission performance, gear modification is often employed to avoid meshing-in and -out impacts. Typically, the tooth surface is modified to a crowning shape, as shown in Figure 12. The key issue in gear modification is the control of the modification curve and the amount of modification. When the gear is loaded and if the amount of modification is less than the amount of deformation, meshing-in and -out impacts still occur, as shown in Figure 13. Figure 11—The smooth process of ideal gears. Figure 12—The smooth change-over process of the crowning profile. Figure 13—The nonstationary change-over of the crowning profile. Functions and Limitations Functions Guidance Design In gear design, TE curves are commonly employed as a reference for design guidance, particularly in the modification and utilization of high-order polynomial functions of transmission error (H-TE) (Refs. 24–27). The concept of H-TE was originally developed for spiral bevel gears, where the transmission function ideally exhibits linearity. However, due to assembly errors, the transmission function becomes piecewise linear, resulting in a larger amplitude of geometric transmission error at the tooth pair transition point. This adversely affects the dynamic performance of the gear and can lead to meshing apart in severe cases, as depicted in Figure 14. Figure 14—Piecewise linear function of TE. Litvin et al. (Ref. 9) addressed the linear transmission error resulting from assembly errors by introducing a TE parabolic function, as depicted in Figure 15. With this approach, the angular velocity jump at the tooth pair transition is reduced, thereby mitigating the impact. Compared to second-order transmission error functions, higher-order transmission error functions exhibit a lower steepness at the transition point of the meshing cycle, as evident from the mathematical expression of the curve. Consequently, the amplitude at the transition point is minimized, which helps to diminish the impact. From a strength perspective, less material is removed from the tooth surface, alleviating the reduction in tooth strength. In the past, achieving the tooth surface of H-TE through traditional machining methods posed challenges. However, with the increasing maturity of intelligent control technology in CNC machine tools and greater flexibility, numerous scholars are exploring machining methods for H-TE. Figure 15—Parabolic transmission function. Process Error Analysis Gear machining errors can stem from various factors (Refs. 28–30), and based on their manifestation, they can be classified as follows, as illustrated in Figure 16. Figure 16—Gear machining errors and their causes. TE has found extensive application in the analysis of process errors. A single flank testing is used to obtain the TE curve of the tested gear, which is then subjected to order analysis using Fourier transform FFT (or finite Fourier transform DFT). Several researchers have made significant contributions to understanding the causes of the TE spectrum and its various spectral components. Figure 17 presents the TE curve of a gear exhibiting radial runout due to eccentricity in the machine tool. The order analysis revealed the presence of eccentricity, with a larger amplitude observed in the first order and the appearance of side frequencies near other prominent orders. These findings suggest the existence of errors on the gear teeth as a likely cause. Figure 17—TE curve with radial runout and order analysis. Figure 18—TE curve with pitch deviation and order analysis. The spectrum diagram also reveals the presence of ghost frequencies, which are orders that are not multiples of the number of gear teeth. These ghost frequencies arise from various machining errors, making it challenging to pinpoint their main source. Figure 18 illustrates the TE curve of a gear with Z teeth, displaying prominent orders such as Z, 2Z, 3Z, 4Z, 5Z, and 6Z. However, numerous ghost frequencies are observed between these orders. Practical applications of TE analysis often involve the examination of eccentricity, which represents long-period errors. However, it is challenging to separate elemental errors, which correspond to short-period errors, due to the presence of kinematic errors in TE. Accuracy Characterization of Transmission Chains TE is a robust indicator encapsulating the comprehensive attributes of a transmission system, making it the optimal parameter for characterizing the accuracy of the transmission chain. The TE in a machine tool’s transmission chain is a holistic precision index receiving extensive attention from academic circles both nationally and internationally over numerous years. Beginning in the 1950s, notable scholars, including K. Stepanks (Refs. 17–19), Qin et al. (Ref. 31), and Peng et al. (Ref. 32), have invested considerable effort in exploring the detection principles, methodologies, and equipment for assessing TE in machine tool transmission chains. The gear hobbing process is broadly utilized in gear manufacturing, with a typical gear hobbing machine tool depicted in Figure 19. The generative motion correlation between the hob and the workpiece is ensured by the machine tool’s transmission chain. In this context, errors in the transmission chain directly implicate the machining accuracy of the gear hobbing tool, culminating in workpiece gear issues like tooth pitch error and tooth shape error. This can even instigate vibrations during the hobbing process (Refs. 33–34). Figure 19—Gear hobbing machine tool structure. Figure 20 demonstrates the measurement principle for TE within the hob machine tool’s transmission chain. Both the hob shaft and the end of the workbench are fitted with circular gratings B and C, respectively. As the workbench and hob shaft rotate, the two circular gratings produce sinusoidal signals. An interpolator, also known as a subdivision box, processes and subdivides these two signals. The digital signal acquisition card then detects the falling edge of the two signals. Subsequently, a calculation program reads the count values and computes the rotation angles of both the hob shaft and the workbench. This ultimately allows for the determination of the transmission chain’s TE. Beyond just machine tools, accurate TE measurement is also imperative for precision transmission machinery like observatories, radars, weapon systems, and printing machinery. This is necessary to ensure the transmission chain’s quality and precision. Once the TE of the transmission chain is obtained, it becomes necessary to trace and compensate for any identified error. Figure 20—Measurement principle of TE for transmission chain of hobbing machine tools. Performance Prediction With the advancing electrification of the automotive industry, electric vehicles demand higher standards for noise, vibration, and harshness (NVH) in their transmission systems. In traditional internal combustion engine vehicles, the engine noise eclipses that of the gearbox, thereby reducing the need for stringent control of gearbox noise. However, in electric vehicles, the gearbox becomes the primary source of noise. This noise becomes even more critical as motor speeds in newer electric vehicles reach or exceed 30,000 rpm, necessitating effective control over gearbox noise and setting standards for individual gear noise levels. TE stands as a crucial metric for quantifying gear noise levels. By charting the TE curve of a singular gear and carrying out order analysis, the noise level of the gear can be assessed (Refs. 35–36). Gear transmission noise originates from two key sources: firstly, the noise generated by impacts during the alternate meshing transmission of crossing teeth, which predominantly contributes to high gear noise, and secondly, resonances caused by gear rotation due to eccentricities and other long-term errors. An inspection of the TE curve alone does not allow for the identification of the single and double meshing zones. Therefore, when employing the TE curve to predict gear transmission noise, only resonance-generated noise can be analyzed, while impact noise remains unpredictable. Currently, the state-of-the-art technique for predicting gear noise both domestically and globally involves assessing gear noise levels by analyzing gear surface waviness, which fundamentally employs TE (Refs. 37–38). The red curve in Figure 21 is derived by aligning the tooth profile deviation of each tooth on the gear with the rotation angle and tooth pitch. The blue line is produced by the gear’s radial runout, and the ripples on the tooth surface are clearly visible in the figure. This ripple is precisely what gives rise to the gear’s noise characteristics. An order analysis and separation are then performed on the curve shown in Figure 21. Figure 21—TE from profile deviations and Fourier analysis. Limitation Five primary constraints and shortcomings associated with TE can be delineated as follows: TE is composed of geometric errors, kinematic errors, and dynamic errors. The low-frequency components are mainly due to geometric and assembly errors, while high-frequency components encompass all three types of errors. Therefore, it is not feasible to infer the geometric error components of gears from the measurement results. The TE measurement outcomes are not full and fail to completely encapsulate the transmission attributes of gears. When the gear is being tested with a master gear, only a part of the tooth profile (where the contact ratio is less than 1) is inspected. Meanwhile, the unexamined segments often emerge in actual transmission operations under specific gear pair error amalgamations. The TE curve represents aggregate data that does not distinguish which gear teeth are meshing and cannot differentiate between single and double contact zones. This results in a knowledge gap concerning the influence of meshing impacts on transmission and a lack of further comprehension of TE. Merely observing the TE curve makes it impossible to discern the change-over form of tooth-pair during gear transmission; identical TE curves can produce completely different effects. The existing dynamic equations for gear transmission superimposed with transmission errors cannot reflect the differences between double and single contact zones. Overcoming TE Defects: Gear Pair Integrated Error (GPIE) In contrast to transmission error, the gear integrated error inherent in a gear pair carries more comprehensive error data. Not only can it evaluate the transmission quality of the gear pair, but it can also scrutinize which tooth surface or surfaces are the source of the error. It allows for an exploration of how the errors from two pairs of teeth engaged in meshing reciprocally affect the transmission quality in the double meshing zone. This enhances the control over the transmission quality of the gear pair and lays a foundation for adjustments in gear technology and enhancements in gear design. The integrated error of a gear pair consolidates the collective errors of the primary and driven gears. This not only exhibits the outcome of the interaction between the primary and driven gear errors during the meshing process but, more significantly, reflects the nature and progression of this interaction. It especially illuminates the alternating process of the meshing teeth. The integrated error of a gear pair intimately merges the geometric error of the driving and driven gears with the kinematic error of the gear pair. It can unveil the actual contact process of gears with errors and the influence of gear geometric error on transmission quality. By employing the overall error of gear pairs, the direction of error changes post gear loading can be investigated. Coupled with dynamics, it enables the study of gear impact, subsequently predicting dynamic gear characteristics such as vibration and noise. Conclusion Research on TE has a history of nearly a hundred years. TE is widely used in characterizing the quality of gear transmission, analyzing the dynamic characteristics of gears (vibration, noise, etc.), gear pairing, and guiding the design of high-performance gears. Although TE seems simple, it encompasses a plethora of intricate manufacturing operations, elastic deformations, energy conversions, energy transfers, and issues related to motion control. This paper provides a summary of the mechanisms, features, functions, and measurement methods of TE and, importantly, elucidates its limitations and drawbacks. The article suggests that the path to circumvent the drawbacks of TE is through the integrated error of the gear pair. This integrated error of gear pair represents a further evolution of TE. By investigating other gear-related issues, a series of results that were previously challenging to attain can be acquired, thereby offering a novel pathway for the future evolution of TE.</span></p><p><br/></p>
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