JP5820177B2 - Measuring method of meshing vibration force - Google Patents

Description

  The present invention relates to a method for measuring a meshing excitation force generated in a gear unit.

  In recent years, in order to further improve the quietness of the interior of a vehicle in an automobile, there is an increasing demand for reduction of gear noise of various gear units used in a power transmission system. In order to take measures to reduce gear noise, it is necessary to elucidate and evaluate the cause of the occurrence of gear noise more accurately and in detail than before.

  As a technique related to the gear noise evaluation method, for example, there is a gear meshing inspection method disclosed in Patent Document 1 below. This is to detect the vibration generated by meshing and rotating the drive gear and the driven gear by the vibration sensor, and to perform the pass / fail judgment of the gear by further performing arithmetic processing such as FFT on the detection result. It is.

  By the way, the gear plays a role such as power transmission by intermittently engaging the teeth at a certain position. However, the tooth surface position of the gear that causes the engagement is actually a dimensional error of the gear or assembly. Due to errors or elastic deformation of the gear itself, it is often present at a position different from the position where it should be. As a result, constant speed motion is not transmitted between the gears, and the driven gear (driven gear) causes some advance or delay of the rotational phase with respect to the drive gear. This advance or delay of the rotational phase (also referred to as meshing transmission error) is a cause of vibration that occurs when the gear unit meshes and rotates. Therefore, if gear noise is accurately evaluated, it is considered important to accurately evaluate not the amount of vibration but the vibration force (also referred to as meshing force) generated by the meshing of the gear that causes the generation.

  The inspection method described in Patent Document 1 below detects vibrations generated at the time of meshing of gears, and it is difficult to say that the meshing vibration force that is the cause of occurrence is properly evaluated. In addition, this method also detects vibrations other than vibrations caused by the meshing behavior at the same time, so there is a problem that the detection result is not reliable and accurate.

  Here, the following non-patent documents 1 to 4 propose theoretical formulas related to gear meshing vibrations. This is the vibration equation derived by replacing the relative torsional vibration with the linear motion on the meshing action line in the gear pair meshing with each other. By solving this vibration equation, the vibration force due to the spring stiffness change and the tooth surface It is theoretically possible to derive the meshing excitation force as the sum of the excitation forces due to errors.

JP-A-9-61300

Kuzo Aizo and Umezawa Kiyohiko, “Study on Load Transmission Characteristics of Cylindrical Gears with Errors (1st Report, Basic Considerations)”, Transactions of the Japan Society of Mechanical Engineers (Part 3), 1997, Vol. 43, 371, p. 2771-2783 Junichi Ogawa, Shigeki Matsumura, Haruo Kitajo, Taichi Sato, Kiyohiko Umezawa, “Analysis of rotational vibration behavior of spur gears considering tooth direction error”, Transactions of the Japan Society of Mechanical Engineers (C), 1999, Volume 65 634, p. 2486-2493 Umezawa Kiyohiko, Sato Taichi, Ishikawa Jiro, “Simulation of Spur Gear Rotational Vibration”, Transactions of the Japan Society of Mechanical Engineers (C), 1983, 49, 411, p. 794-802 Shigeki Matsumura, Kiyohiko Umezawa, Haruo Kitajo, “Rotational vibration analysis of helical gears under light load considering errors (3rd report, tooth trace direction error and vibration performance curve)”, Transactions of the Japan Society of Mechanical Engineers (C) ), 1996, 62, 603, p. 4315-4323

  Thus, if the theoretical formulas described in Non-Patent Documents 1 to 4 are used, the meshing excitation force can be obtained by calculation using a computer or the like, but the values obtained by this method are theoretical values only. It is not calculated considering environmental factors and other factors. In addition, since the above factors are also uncertain factors that change from time to time, even if these factors are taken into account and the theoretical values are calculated, the values are calculated with the uncertain factors taken into account. Lack.

  For the reasons described above, it is considered most desirable to directly measure the meshing vibration force in order to accurately evaluate the meshing vibration force. However, since this kind of vibration force is generated between gear pairs that cause meshing rotation, it is very difficult to directly measure the vibration force. For example, the vibration component in the rotation direction can be measured by using a vibration pickup or a laser Doppler, and the displacement amount in the rotation direction can also be measured by using an encoder. It is only indirectly evaluated.

  In view of the above circumstances, in this specification, it is a technical problem to be solved by the present invention to accurately evaluate the meshing excitation force generated when the gears are meshed.

The solution to the above-described problem is achieved by the method for measuring the meshing excitation force according to the present invention. That is, this measurement method is a method for measuring a meshing excitation force generated in a gear unit having a drive gear, a driven gear that rotates by meshing with the drive gear, and a fixed gear that meshes with the driven gear. A load measuring means for measuring the load acting on the fixed gear is disposed on the side of the fixed gear, and when the meshing vibration is generated by the meshing rotation of the drive gear and the driven gear, it acts on the fixed gear via the driven gear. A load measuring process that measures the load to be measured by a load measuring means, a load function defining process that models the meshing behavior of the driven gear as a linearly rotating motion, and defining the meshing excitation force as a function of the load, and a load function defining process using a function defined by the load, provided with a mesh excitation force calculation step for calculating a vibratory force engagement from the load measured by the load measuring step, the weighting function defined step The function of the load is at least one of the equation of motion related to the linear motion of the driven gear obtained by modeling the meshing behavior, the equation of motion related to the rotational motion of the driven gear, and the relational equation between the acceleration and angular acceleration of the driven gear. Characterized with points defined based on one .

  The present inventors have established a new measurement method capable of accurately measuring the meshing vibration generated by the meshing rotation of the gear. That is, the present inventors, for example, represented by a planetary gear unit, in a gear unit in which a grounded fixed gear exists, should be referred to as a reaction force of the excitation force simultaneously with the generation of the meshing excitation force. Paying attention to the point that the force is transmitted to the fixed gear without being attenuated via the driven gear, a load measuring means is disposed on the fixed gear side, and the driven gear is engaged when the drive gear and the driven gear are engaged. By measuring the load acting on the fixed gear, it has come to be understood that even a load generated in the movable part such as the meshing vibration force can be measured stably and with high accuracy.

  The present invention has been made based on the above knowledge, and when a meshing vibration is generated by meshing rotation of a drive gear and a driven gear, a load acting on the fixed gear via the driven gear is applied to the fixed gear. It is characterized in that the meshing vibration force is calculated from the measured load using the relationship between the meshing vibration force and the load, which is measured by a load measuring means provided on the side of the blade and acquired in advance. As described above, by measuring the load acting on the fixed gear as the meshing vibration force is generated, a measurement result that accurately reflects the magnitude of the meshing vibration force actually generated can be obtained. In addition, it is possible to obtain a measurement result with higher reliability as compared with the case where other physical events (displacement, acceleration, etc.) are measured and the meshing vibration force is indirectly evaluated. In addition, in the present invention, since the load is directly measured by the load measuring means provided on the fixed gear side, the occurrence of measurement error due to attenuation or the like is avoided, and highly accurate measurement is stably performed. Can be done.

  The method for measuring the meshing excitation force according to the present invention further includes a load function defining step of modeling the meshing behavior of the driven gear as a linearly rotating motion and defining the meshing excitation force as a function of the load. In this case, in the meshing excitation force calculation step, the meshing excitation force may be calculated from the load measured in the load measurement step using the function defined in the load function defining step.

  Here, an example of the motion model will be described with reference to the drawings. FIG. 4B is a motion model for measuring the meshing excitation force, in which the meshing behavior of the driven gear 22 in the planetary gear unit shown in FIG. 4A is replaced with a simple linear rotational motion model. . Here, the load acting on the shaft of the driven gear 22 is N, the mass of the driven gear 22 is M, the pitch circle radius is r, the meshing force with the drive gear 21, that is, the meshing vibration force is F, the meshing vibration force F The equation of motion when f is the resistance force that the driven gear 22 receives from the fixed gear 24 (in this case, the internal gear) in accordance with the occurrence of the In addition, in the case of this type of linear movement of the gear, the relationship shown in Formula 3 is generally established.

  Here, when Equation 3 is substituted into Equation 2, Equation 4 below is obtained, and when Equation 4 is substituted into Equation 1, Equation 5 below is obtained.

  Here, when the rotation speed of the drive gear 21 is constant (the speeds are constant), the acceleration is zero. Also, when the acceleration is zero, Expression 2 is derived from Expression 2.

  Therefore, from these formulas 6 and 7, the meshing excitation force F can be defined by a function (here, F = f) of the resistance force f received by the driven gear from the fixed gear. Here, since the reaction force of the resistance force f can be regarded as a force (load) acting on the fixed gear 24, the meshing vibration force F results in the generation of the meshing vibration force F. Accordingly, it can be defined by a function of a load f ′ (see FIG. 1 described later) acting on the fixed gear 24.

  By replacing the meshing behavior of the driven gear with a simple motion model and defining the meshing excitation force as a function of the load acting on the fixed gear, the relationship between the meshing excitation force and the load is clarified and It can be simplified. Therefore, the load measured as described above can be converted into a meshing vibration force by a simple and reliable method, and thereby the meshing vibration force can be measured with higher accuracy.

  Further, in the method for measuring the excitation force according to the present invention, the driving gear and the driven gear are each provided with vibration amount measuring means for measuring the vibration component in the rotational direction of the driving gear and the driven gear, and measured by the vibration amount measuring means. The meshing vibration force between the drive gear, the driven gear, and the fixed gear may be evaluated based on the rotational direction vibration component and the meshing vibration force obtained in the meshing vibration force calculation step.

  Since the value of the meshing vibration force obtained in the meshing vibration force calculation step is the sum of the meshing vibration forces generated by the meshing of all gears, as described above, based on the measurement result of the rotational vibration component of each gear. Thus, by extracting and identifying the meshing excitation force of each gear from the calculated value of the meshing excitation force, it becomes possible to appropriately evaluate the individual meshing behavior including the meshing excitation force of each gear. .

  As described above, according to the method for measuring the meshing vibration force according to the present invention, the meshing vibration force generated when the gears are meshed can be accurately evaluated.

It is a front view of the measuring apparatus of the meshing excitation force which concerns on one Embodiment of this invention. It is an example of the graph which shows the time fluctuation of the meshing excitation force obtained with the measuring method which concerns on this invention. It is another example of the graph which shows the time fluctuation of the meshing excitation force obtained with the measuring method which concerns on this invention. The specific example of the process which prescribes | engages meshing excitation force as a function of the load which acts on a fixed gear, (a) is the gear unit used as a measuring object, (b) is the driven in the gear unit shown to (a). It is a principal part enlarged front view which shows the movement model at the time of replacing the meshing | engagement behavior of a gear with a rectilinear rotational movement. It is a front view which shows the other example of the gear unit which can measure a meshing excitation force with the measuring method which concerns on this invention.

  Hereinafter, an embodiment of a method for measuring a meshing excitation force according to the present invention will be described with reference to the drawings. In this embodiment, when the sun gear of the planetary gear unit is a drive gear, the pinion gear is a driven gear, and the internal gear is a fixed gear, an example of measuring the meshing excitation force generated by the meshing of the drive gear and the driven gear is described. Will be described below.

  FIG. 1: has shown the front view of the measuring apparatus 10 of the meshing excitation force which concerns on one Embodiment of this invention. This measuring apparatus 10 is constructed by incorporating a gear unit 20 to be measured, and includes a load measuring means 12 attached to a ground side member 11 for fixing a fixed gear 24 to be described later to the ground side, and this load measurement. And a calculation device 13 that performs a series of calculation processes from the load f ′ measured by the means 12 to the calculation of the meshing vibration force F. The gear unit 20 to be measured in this embodiment is a so-called planetary planetary gear unit, and is a drive gear 21 and one or more driven gears that mesh with the drive gear 21 and rotate (rotate or revolve). It has a gear 22, a carrier 23 that supports the driven gear 22 so as to rotate freely and guides the revolution, and a fixed gear 24 that meshes with the driven gear 22 and guides the revolution of the driven gear 22 together with the carrier 23. In this illustrated example, three driven gears 22 are configured to mesh with the drive gear 21 and the fixed gear 24 so as to be rotatable.

As shown in FIG. 1, the load measuring means 12 is attached to the ground side member 11 for fixing the fixed gear 24 to the ground side, or directly attached to the fixed gear 24. Various load measuring means 12 can be used. For example, a load measuring means suitable for detection at a high vibration level (for example, on the order of 10 ² to 10 ⁴ Hz) such as a dynamic load related to meshing of gears. Dynamic load measuring means) is preferably used. Here, as an example of a suitable dynamic load measuring means, a piezoelectric load cell (particularly a quartz piezoelectric type) can be cited. When the load measuring means 12 is a type capable of measuring a load in one axis direction, the load measuring means 12 is set so that the load measuring direction is oriented along the circumferential speed direction of the fixed gear 24 having an annular shape. It is good to attach to the ground side member 11. The term “dynamic load” as used herein refers to a load whose magnitude and direction of force acting on an object change with time, such as an impact load, and a load whose magnitude rapidly changes in an extremely short time. Including.

  The arithmetic device 13 is electrically connected to the load measuring means 12 and performs a series of arithmetic processing until the meshing excitation force F is calculated from the value of the load f ′ measured by the load measuring means 12. That is, the arithmetic device 13 stores the relationship between the meshing vibration force F acquired in advance and the load f ′ acting on the fixed gear 24 when the meshing vibration force F is generated. A program for calculating the meshing vibration force F from the load f ′ measured by the load measuring means 12 using the relationship can be executed. Here, as the relationship between the meshing vibration force F to be memorized and the load f ′ acting on the fixed gear 24 when it is generated, the meshing vibration force F is applied to the load f using, for example, a motion model shown in FIG. In the case of defining as a function of ', the arithmetic unit 13 has a program for defining this function, and a function of the load f' according to the driving conditions (rotation speed, load torque to the carrier 23, etc.) at the time of meshing Can be defined. For example, when the rotational speed of the drive gear 21 is constant, the magnitude of the meshing excitation force F can be handled as being equal to the magnitude of the load f ′ acting on the fixed gear 24 as described above. This is because, as described above, since the meshing behavior occurs intermittently in a very short period under actual driving conditions, the acceleration can be regarded as substantially zero (constant rotational speed) in this span. by.

  In this embodiment, the driving gear 21 and each driven gear 22 are provided with vibration amount measuring means 14 capable of measuring a vibration component in the rotational direction. The rotational direction vibration components of the gears 21 and 22 measured by the vibration amount measuring means 14 are sent to the arithmetic unit 13 and compared with the meshing excitation force F calculated from the measured load f ′. From the calculated time fluctuation component of the meshing vibration force F, the time fluctuation components of the gears 21 and 22 are overlapped with the time fluctuation component of the meshing vibration force F by making the time axes coincide. The meshing excitation force component between the gears (drive gear 21 and first driven gear 22, drive gear 21 and second driven gear 22, driven gear 22 and fixed gear 24, etc.) can be found individually. Yes. Various types of vibration amount measuring means 14 (for example, one that detects displacement, velocity, or acceleration, one that is used in contact with the object to be measured, or one that is used without contact) are used. In consideration of measurement superiority under actual use conditions, for example, an acceleration pickup is preferably used.

  Hereinafter, an example of a method for measuring the meshing vibration force F of the gear unit 20 using the meshing vibration force measuring device 10 having the above-described configuration will be described.

  First, prior to the measurement of the meshing vibration force F, the relationship between the meshing vibration force F and the load f ′ acting on the fixed gear 24 when the vibration force F is generated is acquired. Specifically, the meshing vibration force F acting on the driven gear 22 is defined as a function of the load f ′ using the motion model illustrated in FIG. Step), the function of the specified load f ′ is stored in the arithmetic unit 13.

  Thereafter, a motor (not shown) connected to the shaft of the drive gear 21 is driven to rotate the drive gear 21. As a result, the driven gear 22 meshes with the drive gear 21 with one or two teeth, and starts rotating (spinning, revolving). At this time, the meshing excitation force F is generated between the drive gear 21 and the driven gear 22. This force (meshing excitation force F) is transmitted via the driven gear 22 to the fixed gear 24 that meshes with the driven gear 22, so that the above-described vibration measurement is performed by the load measuring means 12 provided on the fixed gear 24 side. A load f ′ acting on the fixed gear 24 as the force F is generated is measured (load measurement step).

  Then, a program for calculating the meshing vibration force F from the load f ′ measured by the load measuring means 12 is executed using a function of the load f ′ stored in the arithmetic device 13 in advance, and the meshing vibration force F is calculated. Is calculated (meshing excitation force calculation step).

  Simultaneously with the measurement of the meshing excitation force F (load f ′), the vibration component in the rotational direction of the drive gear 21 and the driven gear 22 (here, the acceleration component in the direction along the rotational direction) is measured by the vibration amount measuring means 14. Measure (vibration measurement process). The measured vibration components (acceleration components) of the gears 21 and 22 are sent to the arithmetic unit 13 and compared with the time fluctuation component of the meshing vibration force F calculated as described above, thereby causing the meshing between the gears. The vibration component is extracted individually.

  FIG. 2 is a graph showing an example of a temporal variation component of the meshing excitation force F obtained as a result of carrying out the measurement method according to the present invention in the gear unit 20 shown in FIG. From this graph, the meshing excitation force components (1) to (6) corresponding to all the meshing of the driven gear 22 are included in the unit meshing cycle 1 / fz [s] (fz: meshing frequency [Hz]). You can see it. In other words, in this case, the gear unit 20 to be measured has one drive gear 21, three driven gears 22, and one fixed gear 24, so that each driven gear 22 is driven. Since there are meshing with the gear 21 and meshing with the fixed gear 24, and there are as many as the number (three) of the driven gears 22, it can be seen that there are a total of six components. Therefore, by superimposing this result and the rotational direction vibration component (time variation component thereof) of each of the gears 21 and 22 measured by the vibration amount measuring means 14 in a state where the time axes coincide with each other, for example, (1) to It can be determined which of the meshing vibration force components of (6) is the meshing vibration force component of the drive gear 21 and the one driven gear 22. Moreover, the gear noise level can be individually evaluated by extracting each meshing excitation force component and evaluating the magnitude thereof.

  As described above, in the present invention, the actual engagement is generated by setting the load f ′ acting on the fixed gear 24 with the generation of the meshing excitation force F between the drive gear 21 and the driven gear 22 as a measurement object. A measurement result that accurately reflects the magnitude of the excitation force F can be obtained. In addition, it is possible to obtain a measurement result with higher reliability as compared with the case where other physical events (displacement, acceleration, etc.) are measured and the meshing vibration force is indirectly evaluated. In addition, in the present invention, since the load f ′ is directly measured by the load measuring means 12 provided on the fixed gear 24 side, the occurrence of measurement error due to attenuation or the like can be avoided and high accuracy can be achieved. Measurement can be performed stably.

  Further, by measuring the meshing excitation force F using a load measuring means (dynamic load measuring means) 12 capable of dealing with a high vibration level such as a piezoelectric load cell, the meshing excitation under a condition in accordance with the actual use conditions. Since the force F can be measured, a measurement result having a high correlation with the unit noise level is obtained at a stage before the gear unit 20 is incorporated in a unit assembly such as a reduction gear or a power split mechanism, that is, in the state of the gear unit 20 alone. Can be obtained. Therefore, the final noise level estimation accuracy can be improved. As a result, the design speed of the gear unit 20 is improved and the meshing behavior state of the gear unit 20 including the meshing vibration force F can be appropriately evaluated, which leads to an improvement in the design level.

  Moreover, the measurement method according to the present invention is particularly effective when the gear unit 20 is a planetary gear unit in which the gear unit 20 has a triaxial meshing structure (sun gear and pinion, pinion and ring gear). That is, when the existence of a problem related to gear noise is recognized, it is difficult to identify which gear is the direct cause of the gear noise unless the gear change test is performed. On the other hand, as in the present invention, the measurement of the rotational direction vibration component and the measurement result of the meshing excitation force F are compared in synchronization, in other words, the time axis is matched to By comparing the portion where the fluctuation is remarkable and the meshing vibration force component corresponding thereto, for example, a gear having a very large meshing vibration force component can be easily specified as a generation source of gear noise. Therefore, it is possible to greatly reduce the time required for elucidating the cause when a problem occurs in gear noise and for subsequent design change.

  In the above embodiment, when the function of the load f ′ indicating the meshing vibration force F is defined using the motion model of the driven gear 22 shown in FIG. The function of the load f ′ is defined with the number being constant, but of course, the function of the meshing vibration force F by the load f ′ under other driving conditions is also possible. For example, when the rotational speed is increased at a predetermined acceleration, depending on the driving conditions, the acceleration is substituted into Formula 2 and Formula 5 as a predetermined value, and the meshing excitation force F and the load f are solved by solving the substituted formula. A relationship with “(function of load f)” may be obtained.

  In the above embodiment, the planetary type planetary gear unit having three driven gears has been described as a measurement target. However, the present invention can be applied to other types of planetary gear units. is there. For example, the present invention can be applied not only to three driven gears 22 but also to one, two, or four or more types. Similarly, the present invention can be applied to a planetary gear unit of a type other than the planetary type (for example, a type in which the drive gear 21 and the fixed gear 24 shown in FIG. 1 are interchanged).

  In the above embodiment, the planetary gear unit is exemplified as the gear unit 20 having the drive gear 21, the driven gear 22, and the fixed gear 24. However, the present invention can be applied to other types of gear units 20. Is possible. FIG. 5 shows an example thereof, and the gear unit 20 shown in FIG. 5 may have a rack formed by cutting the surface of a flat plate member as the fixed gear 24. In this case, the driven gear 22 and the fixed gear 24 form a so-called rack and pinion mechanism, and the drive gear 21 is meshed with the driven gear 22 as a pinion gear, so that the parallel gear is engaged with the fixed gear 24 (rack). The driven gear 22 is configured to linearly rotate on the tooth surface. Therefore, also in this case, the load measuring means 12 is attached to the rack (the direction along the longitudinal direction) as the fixed gear 24, and the fixed gear is connected via the driven gear 22 as the meshing vibration force F is generated. By measuring the load f ′ acting on 24, the meshing vibration force F can be accurately measured.

  In order to confirm the usefulness of the measurement method of the meshing excitation force according to the present invention, the following measurement test was performed. That is, the meshing vibration force F in a planetary planetary gear unit having two driven gears was measured using the meshing vibration force measuring device having the structure shown in FIG.

  Here, the gear unit used as a measurement object is made of S45C as a material for all of the driving gear, driven gear, and fixed gear, the module is 1, the number of teeth of the driving gear is 12, the number of teeth of the driven gear is 24, The number of teeth was 60. Each tooth width was 10 mm. A quartz piezoelectric load cell was used as the dynamic load measuring means. Then, the load acting on the fixed gear with the generation of the meshing vibration force was measured by setting the input rotation speed to 1200 rpm and the load to the carrier to 0.4 Nm.

  The measurement results are shown in FIG. As shown in the figure, the meshing excitation force component corresponding to the meshing cycle 1 / fz (≈5 [ms]) can be confirmed, and the meshing cycle 4 × 1 / fz (≈20 [ ms]) and the meshing excitation force component can be confirmed. In addition, the magnitude of these meshing excitation force components can be confirmed. Therefore, as described above, the measurement of the vibration component in the rotational direction of each gear is performed simultaneously with the measurement of the meshing excitation force, and by comparing each result (time variation component), there are a plurality (four in this case). It is possible to discriminate which of the meshing vibration force components is the meshing vibration force component between the drive gear and the driven gear (and which driven gear) and to evaluate them individually.

DESCRIPTION OF SYMBOLS 10 Measuring device of meshing vibration force 11 Grounding side member 12 Dynamic load measuring means 13 Arithmetic device 14 Vibration amount measuring means 20 Gear unit 21 Driving gear 22 Driven gear 23 Carrier 24 Fixed gear F Meshing vibration force f Meshing vibration force Resistance force f ′ received by the driven gear from the fixed gear as a result of generation The load acting on the fixed gear as a result of meshing vibration generation

Claims (2)

A method for measuring a meshing excitation force generated in a gear unit having a drive gear, a driven gear that rotates by meshing with the drive gear, and a fixed gear that meshes with the driven gear,
A load measuring means capable of measuring a load acting on the fixed gear is arranged on the fixed gear side,
A load measuring step of measuring the load acting on the fixed gear via the driven gear by the load measuring means when the meshing vibration is generated by the meshing rotation of the drive gear and the driven gear;
A load function defining step of modeling the meshing behavior of the driven gear into a linearly rotating motion and defining the meshing excitation force as a function of the load;
Using the function of the load defined in the load function defining step, and a meshing excitation force calculating step of calculating the meshing excitation force from the load measured in the load measuring step ,
In the load function defining step, the function of the load is an equation of motion related to the linear motion of the driven gear obtained by modeling the meshing behavior, an equation of motion related to the rotational motion of the driven gear, and the driven gear. A method for measuring a meshing vibration force defined based on at least one of relational expressions between acceleration and angular acceleration . The driving gear and the driven gear are each provided with vibration amount measuring means for measuring the rotational vibration component of the driving gear and the driven gear,
Based on the rotational direction vibration component measured by the vibration amount measuring means and the meshing vibration force obtained in the meshing vibration force calculation step, each of the drive gear, the driven gear, and the fixed gear is connected to each other. The method for measuring a meshing vibration force according to claim 1 , wherein the meshing vibration force is evaluated.

Images