JP2007003507A - Gear inspection device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a gear inspection device capable of inspecting a gear easily in a short time. <P>SOLUTION: The gear inspection device 10 for inspecting an inspected gear 30 comprises a reference gear 20 rotatably engaging with the inspected gear, a driving means 53 for driving one of the reference gear and the inspected gear, a vibration acceleration detecting means 51 for detecting a vibration acceleration generated by the reference gear and the inspected gear during rotation of the reference gear and the inspected gear, a rotation trigger signal detecting means 54 for detecting a rotation trigger signal of each rotation shaft of the reference gear and the inspected gear, and an inspection means 40 for inspecting the inspected gear based on the vibration acceleration detected by the vibration acceleration detecting means and the rotation trigger signal detected by the rotation trigger signal detecting means. The number of teeth of the reference gear and that of the inspected gear are mutually prime, and the greatest common divisor of them is significantly small. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a gear inspection device for inspecting a manufactured gear.

  An inspection apparatus for inspecting a gear in the prior art is a kind of coordinate measuring device that confirms whether or not the shape of the gear is manufactured as designed (see, for example, Patent Document 1 and Patent Document 2). For example, with respect to involute gears, the outer shape of gears is inspected based on the relationship between the rotation angle of the gear shaft and the linear motion of a stylus (measurement element) in contact with the tooth surface.

In standards such as ISO (International Organization for Standardization), three teeth of a plurality of tooth parts of a gear are measured, or three or four tooth forms in one tooth part of a plurality of tooth parts are used. It is recommended to measure.
Japanese Patent Laid-Open No. 08-029157 Japanese Patent Laid-Open No. 08-029156

  However, since the shape of the tooth surface varies for each tooth portion of the gear, when the gear is inspected by the inspection device disclosed in Patent Literature 1 and Patent Literature 2, some of the plurality of tooth portions are used. Even if the shape of the tooth part is appropriate, it cannot be determined whether or not the other tooth part is appropriate.

  In recent years, it has been required to drive gears with low vibration. Some of the shape characteristics of the teeth, for example, surface waviness, may cause vibration when the gear is driven. For example, even if the surface waviness is about 0.1 micrometer, depending on the frequency, vibration can be generated when the gear is driven. In order to determine whether the gear can be driven with low vibration, it is necessary to confirm that all the teeth are appropriate. In such a case, the inspection work becomes complicated and the inspection time is also delayed. There was a problem.

  This invention is made | formed in view of such a situation, and it aims at providing the gear inspection apparatus which can perform a gear inspection simply and in a short time.

  In order to achieve the above-described object, according to a first invention, a gear inspection device for inspecting an inspection gear includes a reference gear rotatably engaged with the inspection gear, the number of teeth of the reference gear and the number of teeth The number of teeth of the inspection gear is relatively prime, and further, driving means for applying a load to the other of the reference gear and the inspection gear while driving one of the reference gear and the inspection gear; Vibration acceleration detecting means for detecting vibration acceleration formed by the reference gear and the inspection gear when the reference gear and the inspection gear are rotated, and rotation trigger signals of the respective rotation shafts of the reference gear and the inspection gear; Rotation trigger signal detection means for detecting, the vibration acceleration detected by the vibration acceleration detection means, and the rotation detected by the rotation trigger signal detection means Based on the trigger signal, the gear inspection apparatus is provided comprising an inspection means for inspecting the test gear.

  That is, in the first invention, since the inspection gear is inspected based on the vibration acceleration and the rotation trigger signal, the inspection gear can be inspected more easily and in a shorter time than the conventional inspection device using the measuring element. Can be done.

  According to a second aspect of the present invention, in the gear inspection apparatus for inspecting the inspection gear, the inspection gear includes a reference gear that is rotatably engaged with the inspection gear, and the interval between the number of teeth of the reference gear and the number of teeth of the inspection gear. The greatest common divisor of the motor is significantly smaller than the number of teeth, and further, the drive that applies a load to the other of the reference gear and the inspection gear while driving one of the reference gear and the inspection gear. Means, vibration acceleration detecting means for detecting vibration acceleration formed by the reference gear and the inspection gear when the reference gear and the inspection gear are rotated, and rotation of the respective rotation shafts of the reference gear and the inspection gear Rotation trigger signal detection means for detecting a trigger signal, the vibration acceleration detected by the vibration acceleration detection means, and the detection before the rotation trigger signal detection means Based on the rotational trigger signal, gear inspection apparatus comprising an inspection means for inspecting the test gear is provided.

  That is, in the second invention, since the inspection gear is inspected based on the vibration acceleration and the rotation trigger signal, the inspection gear can be inspected more easily and in a shorter time than the conventional inspection device using the measuring element. Can be done. In a preferred embodiment, the greatest common divisor is 2, 3 or 5.

According to a third aspect, in the first or second aspect, the inspection means synchronously averages the vibration acceleration with the rotation trigger signal, thereby obtaining a vibration characteristic of the inspection gear and a vibration characteristic of the reference gear. Separating means for separating, frequency response function calculating means for calculating and quantifying a frequency response function relating to the reference gear and the inspection gear, vibration characteristics of the inspection gear separated by the separation means, and the frequency Tooth surface shape calculating means for determining the tooth surface shape of the inspection gear from the quantified frequency response function calculated by the response function calculating means.
That is, in the third aspect of the invention, the number of teeth of the reference gear and the inspection gear are relatively prime or the greatest common divisor is considerably small. It meshes with almost all the teeth distributed around the circumference. Therefore, by performing the synchronous averaging by the separating means, the reference gear can be regarded as engaging with the inspection gear having a substantially average tooth surface shape. Further, since the frequency response function calculating means is used, even a vibration with a slight amplitude can be easily detected when the frequency is high.

According to a fourth invention, in the third invention, the inspection means is further calculated by a storage means for storing a plurality of tooth surface shape patterns for the inspection gear and the tooth surface shape calculation means. Comparing means for comparing the tooth surface shape of the inspection gear with the tooth surface shape pattern stored in the storage means.
That is, in the fourth invention, based on the comparison result regarding the tooth surface shape, the problem specific to the gear manufacturing apparatus that manufactured the inspection gear is clarified, and the combination of the inspection gear that can be driven with low vibration is appropriately selected. It is also possible to select.

According to a fifth aspect, in the fourth aspect, the inspection means further includes a waveform calculation means for calculating a vibration waveform of the inspection gear based on a vibration characteristic of the inspection gear separated by the separation means. Storage means for storing a plurality of vibration waveform patterns for the inspection gear; and comparison means for comparing the vibration waveform of the inspection gear calculated by the waveform calculation means with the vibration waveform pattern stored in the storage means It comprises.
That is, in the fifth invention, based on the comparison result regarding the vibration waveform, the problems unique to the gear manufacturing apparatus that manufactured the inspection gear are clarified, and the combination of the inspection gear that can be driven with low vibration is appropriately selected. It is also possible to select.

According to a seventh invention, in the first or second invention, the inspection means synchronously averages the vibration acceleration with the rotation trigger signal, whereby the vibration characteristics of the inspection gear and the vibration characteristics of the reference gear are obtained. Separating means for separating the gears, meshing vibration component extracting means for extracting meshing vibration components from the vibration characteristics of the inspection gear separated by the separating means, and frequency for calculating and quantifying a frequency response function relating to the inspection gear Using the response function calculation means, the meshing vibration component of the inspection gear extracted by the meshing vibration component extraction means, and the frequency response function related to the inspection gear calculated by the frequency response function calculation means, Excitation force calculating means for calculating an excitation force corresponding to the tooth surface shape.
That is, in the seventh invention, the calculated excitation force does not include the influence of the rotation speed of the gear and the influence of the characteristics as the vibration system of the gear inspection device. Therefore, in the seventh aspect, by using the excitation force, it is possible to universally show the geometric characteristics represented by the tooth surface shape of the inspection gear. Therefore, the inspection gear can be inspected by comparing this excitation force with another excitation force obtained in advance.

According to an eighth aspect, in the seventh aspect, the meshing vibration component extracting means calculates the mesh frequency and the amplitude and phase spectra of the harmonic components extracted from the vibration characteristics of the inspection gear in a complex plane. The meshing vibration component is acquired by expressing above.
That is, in the eighth aspect, the amplitude and phase of the meshing vibration component can be shown on the same complex plane, so that the tooth surface shape can be accurately determined.

According to the ninth aspect, in the eighth aspect, the phase of the meshing primary component is made zero in the complex plane.
That is, in the ninth aspect, the phase of the meshing primary component is made zero, so that the meshing primary component functions as a reference time axis, thereby drawing the same pattern on the complex plane in the case of the same waveform. Can do.

According to a tenth invention, in any of the seventh to ninth inventions, the frequency response function calculating means calculates the meshing frequency extracted from the vibration characteristic of the inspection gear and the amplitude of each of its harmonic components. The frequency response function is obtained by concatenating the spectrum and concatenating the spectrum of each phase of the meshing frequency and its harmonic component.
That is, in the tenth invention, the frequency response function can be obtained by an experimental method. Note that the vibration characteristics of the inspection gear used in the tenth invention can be obtained by performing a synchronous averaging process while changing the rotational speed while keeping the torque constant.

According to an eleventh aspect, in any one of the seventh to tenth aspects, the inspection means further includes storage means for storing a plurality of tooth surface information for the inspection gear, and the excitation force calculation means. Comparing means for comparing the excitation force of the inspection gear calculated by the above and the tooth surface information stored in the storage means on a complex plane.
That is, in the eleventh aspect, the tooth surface shape of the inspection gear can be grasped by comparison on the complex plane, and feedback to the manufacture of the gear is facilitated.

According to a twelfth aspect, in the eleventh aspect, the tooth surface information is a plurality of excitation forces determined in advance for a plurality of other gears.
That is, in the twelfth aspect, the tooth surface shapes of the inspection gear can be accurately compared by a relatively simple method.

Embodiments of the present invention will be described below with reference to the accompanying drawings. In the following drawings, the same members are denoted by the same reference numerals. In order to facilitate understanding, the scales of these drawings are appropriately changed.
FIG. 1 is a schematic view of a gear inspection apparatus according to the present invention. The gear inspection device 10 includes a reference gear 20 included in a gear box 11. As shown in the drawing, the rotating shaft portion 21 of the reference gear 20 is rotatably supported by the gear box 11 via bearings 25a and 25b. The reference gear 20 is provided in the gear inspection device 10 from the beginning in order to inspect the inspection gear 30 described later. For this reason, the reference gear 20 is preferably a high-precision involute gear, but the reference gear 20 may be an ordinary typical gear. In any case, it is assumed that all the tooth surfaces of the reference gear 20 are measured by a known gear measuring device or the like, and the characteristics, particularly the geometric shape, of the reference gear 20 are clear. In a typical representative gear, that is, a representative gear selected from gears used in mesh with an inspection gear, the geometric shape may not be measured. In this case, it is desirable to have a known inspection gear.

  On the other hand, the inspection gear 30 to be inspected by the gear inspection device 10 is mounted on the gear inspection device 10 at the time of inspection. In FIG. 1, the inspection gear 30 in which the rotating shaft portion 31 of the inspection gear 30 is rotatably supported by the gear box 11 via bearings 35 a and 35 b is engaged with the reference gear 20.

  The rotating shaft 31 of the inspection gear 30 is connected to the motor 53 via a V belt or the like (not shown). The motor 53 is driven to rotate the inspection gear 30 according to a command from the inspection means 40 described later. The motor 53 also plays a role of applying a load to the reference gear 20. Note that the motor 53 may be connected to the rotation shaft portion 21 of the reference gear 20 and the reference gear 20 may be rotationally driven by the motor 53.

  In one embodiment of the present invention, the number of teeth of the inspection gear 30 and the number of teeth of the reference gear 20 are in a “prime” relationship. In order to be able to inspect the inspection gear 30 having different numbers of teeth, the number of teeth of the reference gear 20 is preferably a relatively large prime number. In an embodiment, the number of teeth of the reference gear 20 is “53”, and the number of teeth of the inspection gear 30 is “30”. When the number of teeth of the inspection gear 30 is different, the diameter of the inspection gear 30 may be different. Therefore, the inspection gear 30 is changed to the reference gear 20 by changing the positions of the bearings 35a, 35b and the like along the gear box 11. It shall be possible to arrange so that it can be engaged.

  Incidentally, as shown in FIG. 1, two acceleration pickups 29 are provided on one end face of the reference gear 20 so as to face each other in the diametrical direction. These acceleration pickups 29 detect vibrations in the rotation direction of the reference gear 20 and the inspection gear 30. The vibration closely related to the rotation direction of the gear is input to the inspection means 40 through a slip ring or a telemeter 51 (hereinafter abbreviated as “telemeter 51”). Instead of the acceleration pickup 29 provided on the end face of the reference gear 20, the vibration in the rotational direction may be obtained by an acceleration pickup 29 'provided in the gear box 11. Further, the acceleration pickup 29 may be attached to the bearings 35a and 35b to obtain vibrations closely related to the rotation direction of the gear. In this case, it is not necessary to use the telemeter 51.

  Further, a dynamometer 52 that detects the shaft output of the rotary shaft portion 21 of the reference gear 20 is also connected to the inspection means 40. When driving the reference gear 20, the dynamometer 52 is connected to the rotary shaft portion 31. Further, as shown in the drawing, rotation detectors 54 and 54 ′ provided in the rotary shaft portion 21 and the rotary shaft portion 31 respectively make one rotation per rotation of the rotary shaft portion 21 and the rotary shaft portion 31. A rotation trigger signal is also input to the inspection means 40.

  FIG. 2 is a functional block diagram showing the inspection means 40 of the gear inspection apparatus shown in FIG. The inspection means 40 is generally composed of a digital computer. The inspection unit 40 performs a synchronous averaging of the vibration acceleration with the rotation trigger signal, thereby separating the vibration characteristic of the inspection gear 30 and the vibration characteristic of the reference gear 20, and the frequency response regarding the reference gear 20 and the inspection gear 30. From the frequency response function calculation means 42 for calculating and quantifying the function, the vibration characteristics of the inspection gear 30 separated by the separation means 41, and the quantified frequency response function calculated by the frequency response function calculation means 42 Tooth surface shape calculating means 43 for determining the tooth surface shape of the inspection gear 30 is included. Further, the inspection means 40 is stored in the database 50 that stores a plurality of tooth surface shape patterns for the inspection gear 30 and the tooth surface shape of the inspection gear 30 calculated by the tooth surface shape calculation means 43. Comparing means 45 for comparing the tooth surface shape pattern is included. As shown in the figure, the comparison result obtained by the comparison means 45 and the tooth surface shape obtained by the tooth surface shape calculation means 43 are output as an inspection result of the inspection gear 30 by the output means 60 of the gear inspection device 10, for example, a monitor. Can be output to a printer or the like.

  Further, the inspection means 40 includes waveform calculation means 44 that calculates a vibration waveform of the inspection gear 30 based on the vibration characteristics of the inspection gear 30 separated by the separation means 41, and the database 50 includes a plurality of inspection gears 30. The vibration waveform pattern is also stored. Then, the comparison unit 45 can also compare the vibration waveform of the inspection gear 30 calculated by the waveform calculation unit 44 with the vibration waveform pattern stored in the database 50. The comparison result obtained by the comparison means 45 and the vibration waveform obtained by the waveform calculation means 44 are output to the output means 60 in the same manner. The waveform calculating means 44 calculates the vibration waveform of the inspection gear based on the vibration characteristics of the inspection gear 30 separated by the separating means 41 and the tooth surface shape obtained by the tooth surface shape calculating means. May be.

  Hereinafter, the inspection method of the inspection gear 30 by the gear inspection device 10 will be specifically described. In addition, the following method shall be performed in the inspection means 40 of the gear inspection apparatus 10.

  As shown in FIG. 1, after the inspection gear 30 is attached so as to be engaged with the reference gear 20, the motor 53 is energized by a command from the inspection means 40, and the inspection gear 30 is rotated at a predetermined rotational speed and torque. . In one embodiment, the number of rotations of the inspection gear 30 is about 1800 rpm. The torque applied to the reference gear 20 when the inspection gear 30 is driven is about 245 Nm.

  As the inspection gear 30 rotates, the reference gear 20 rotates in the opposite direction, and the rotation direction vibration of the reference gear 20 at the time of rotation is detected by the acceleration pickup 29 and input to the inspection means 40 through the telemeter 51. This rotational vibration is a superposition of the gear characteristics of the reference gear 20 and the inspection gear 30, that is, vibration characteristics based on the tooth surface shape. Therefore, the separating means 41 of the inspection means 40 separates the vibration characteristics of the reference gear 20 and the inspection gear 30.

  As shown in FIG. 2, rotational vibration from the telemeter 51 is input to the separating unit 41. Further, each rotation trigger signal per rotation of the rotary shaft portions 21 and 31 is input to the separation means 41 of the inspection means 40 through the rotation detectors 54 and 54 ′.

  In the separation means 41, synchronization with the rotation shaft portion 21 of the reference gear 20 and the rotation shaft portion 31 of the inspection gear 30 is performed by performing a synchronous averaging process on the vibration waveform of the rotation direction vibration using a rotation trigger signal. Only vibration components are extracted. Since the vibration measurement result may vary depending on the error for each tooth surface or an assembly error, it is possible to obtain a highly reliable waveform by performing the synchronous averaging process.

  Although the specific method of the synchronous average is already known and will not be described in detail, the specific method of the synchronous average is described in Ratanasumong C.I. Houjoh H .; , Matsumura S .; , Saitoh M. et al. , And Ueda Y. et al. , "Utilization of synchronous averaging of visualization for diagnosis of gear system to estimate to error. Proc. Of DETC'03, ChicAus.

  In the present invention, since the number of teeth of the reference gear 20 and the number of teeth of the inspection gear 30 are relatively prime to each other, one tooth portion of the inspection gear 30 meshes with all the tooth portions of the reference gear 20. And since the vibration regarding each tooth | gear part is averaged by a synchronous average, while the reference | standard gear 20 is regarded as engaging with the test | inspection gear 30 with an average tooth surface shape, the test | inspection gear 30 is average tooth surface. It can be regarded as engaging the reference gear 20 having a shape.

  Furthermore, in the present invention, a relatively small number of synchronization averages is sufficient. For example, when the number of teeth of the reference gear 20 is “53” and the number of teeth of the inspection gear 30 is “30”, if the reference gear 20 rotates 30 times (corresponding to the number of teeth of the inspection gear 30), Data regarding all the tooth portions of the inspection gear 30 is obtained. That is, the specific tooth portion of the inspection gear 30 that has been engaged with the reference gear 20 at the start of rotation is re-engaged with the reference gear 20 when the reference gear 20 rotates 30 times.

  However, in order to completely separate the vibration characteristics of the reference gear 20 and the vibration characteristics of the inspection gear 30, the average number of synchronous averages is preferably sufficiently large. In an embodiment, the average number of synchronous averages is 256 times or more.

  FIG. 3A is a diagram illustrating a waveform of the inspection gear 30 calculated based on the rotation trigger signal of the rotating shaft portion 31. In FIG. 3A, the horizontal axis indicates time, and the length of the horizontal axis matches the rotation cycle of the rotary shaft portion 31. In addition, the vertical axis | shaft in Fig.3 (a) shows vibration acceleration.

  Since the signal after synchronous averaging as shown in FIG. 3 (a) has a period of exactly one rotation, if DFT (Discrete Fourier Transform) processing is performed with the rotation period as the window width, weighting by the Hanning window is unnecessary. Become. As shown in FIG. 3B, a line spectrum whose primary frequency is the rotation primary is obtained by the DFT processing. In FIG. 3B, reference numeral fz indicates the fundamental frequency of the meshing of the inspection gear 30 with respect to the reference gear 20, and reference numerals 2fz and 3fz corresponding to integral multiples thereof indicate harmonic components of the fundamental frequency fz. The fundamental frequency fz and the harmonic components 2fz and 3fz are collectively referred to as “meshing components” as appropriate.

  When the signal is processed in this way, the vibration characteristics of the inspection gear 30 can be obtained without duplication or omission.

  Note that the DFT processing may be performed with an arbitrary data length. FIG. 3C is a view similar to FIG. 3B obtained for a window width longer than the rotation period of the rotating shaft portion 31. In this case, it is generally necessary to use a Hanning window due to frequency leakage. In FIG. 3 (c), it can be seen that the level is lower than the line spectrum shown in FIG. 3 (b), and the spectrum is broadened. This means that a part of the vibration characteristic is discarded.

  On the other hand, FIG. 4A is a view similar to FIG. 3A showing the waveform of the reference gear 20 calculated based on the rotation trigger signal of the rotating shaft portion 21. Similarly, FIGS. 4B and 4C are views similar to FIGS. 3B and 3C obtained for the reference gear 20, respectively.

  In particular, as can be seen by comparing FIG. 3B and FIG. 4B, the respective meshing components fz, 2fz, and 3fz in these drawings are equal to each other. The non-integer order components fa, fb, etc. in FIG. 3B are different from the non-integer order components at the same position of the reference gear 20 (see FIG. 4B).

  That is, even when the same rotation direction vibration input from the telemeter 51 is used, the result of the synchronous averaging process differs depending on the rotation trigger signal used, and the characteristics of the inspection gear 30 and the reference gear 20 are different. It was possible to separate. Further, the non-integer order components fa and fb represent characteristics based on the tooth surface shape of the inspection gear 30. Of the non-integer order components fa and fb, the non-integer order component fa is a sideband generated on both sides of the meshing components fz, 2fz, and 3fz, and a slight deviation from the average shape of the tooth portion is present for each tooth portion. Is present. Such deviation is related to variations in pitch error and / or pressure angle error. Further, the non-integer order component fb is a component of slight undulation that is transferred to the tooth surface by the wrinkles and / or individuality that the gear manufacturing machine individually has when the inspection gear is manufactured.

  FIG. 5 shows a cascade diagram in which the spectrum of vibration acceleration of the gear pair including the reference gear 20 and the inspection gear 30 is arranged in the order of the rotation speed. FIG. 5 shows a list of spectra that are not subjected to synchronous averaging. In FIG. 5, there are a plurality of natural frequencies indicated by triangles, and the influence of the natural frequencies around 3600 Hz and 4000 Hz is between the harmonic components 2fz and 3fz in FIGS. 3 (b) and 4 (b). Appear. This means that the spectra in FIGS. 3B and 4B do not directly represent the size of the tooth surface irregularities. In order to detect the tooth surface unevenness, the relationship between the tooth surface unevenness and the observed non-integer order components fa and fb is required.

The meshing non-integer order components fa, fb, etc. are expressed by the equation (1) as the product of the displacement excitation of the system due to the tooth surface shape and the response function of the system, and the magnitude of vibration changes due to resonance or the like.
A (ω) = H (ω) × E (ω) (1)

  In equation (1), A (ω) represents the meshing non-integer order vibration component, H (ω) represents the frequency response function of the system, and E (ω) represents the tooth surface irregularity information. Therefore, by knowing the frequency response function H (ω) of the vibration system, the tooth surface unevenness information E (ω) can be obtained from the vibration measurement result (A (ω)).

  The tooth surface unevenness information E (ω) is estimated by the frequency response function calculation means 42 of the inspection means 40 in the following procedure.

(1) Estimation of frequency response function shape Since the tooth surface unevenness acts as displacement excitation, the amplitude of the excited non-integer order component is not affected by torque. For this reason, the shape of the frequency response function of the system including the reference gear 20 and the inspection gear 30 can be obtained from the response of the meshing non-integer order component. FIG. 6A is a diagram in which a plurality of remarkable rotational order responses are obtained by rotational order analysis. When these are averaged, it can be regarded as the shape of the frequency response function of the gear pair composed of the reference gear 20 and the inspection gear 30 as shown in FIG.

(2) Quantification of frequency response function In FIG. 6B, only the shape of the frequency response function is obtained. In the present invention, since the tooth surface shape of the tooth surface of the reference gear 20, that is, the amplitude of the unevenness is known, this can be used to quantify the frequency response function. In order to perform calibration accurately, it is preferable that both the amplitude of the vibration of the order of reference and the size of the unevenness are large. For example, it is preferable to use a 26th-order component in FIG.

(3) Inverse estimation of tooth surface shape Since the characteristics of the inspection gear 30 are independent of the characteristics of the reference gear 20, the tooth surface information of the inspection gear 30 can be calculated backward from a single frequency response function. When the vibration acceleration synchronously averaged with this frequency response function is applied to the equation (1), information on the tooth surface shape of the inspection gear 30 can be obtained. It is known that the meshing components fz, 2fz, 3fz and rotational primary sidebands are generated from vibration sources other than the tooth surface irregularities, and are not handled.

  FIG. 7A shows the characteristics of the tooth surface shape of the inspection gear 30 obtained from the gear inspection device 10 of the present invention by the above method. On the other hand, FIG. 7B is a diagram showing the characteristics of the tooth surface shape of the inspection gear obtained by the conventional technique, that is, the tooth surface measurement using the measuring element. As can be seen from these drawings, the tooth surface shape of the inspection gear 30 obtained from the gear inspection device 10 of the present invention is substantially equal to the tooth surface shape obtained by the conventional technique, and the gear inspection device of the present invention. 10 indicates that it is possible to accurately detect irregularities of about 0.1 micrometers. As is well known, since acceleration is proportional to the square of frequency, the frequency response function calculating means 42 as in the present invention can be used to easily detect even slight amplitude vibration when the frequency is high. It is possible.

  7A is considered to be obtained by averaging the tooth forms in the contact line direction in each tooth portion of the inspection gear 30 and connecting them for one rotation. Further, it is considered that the unevenness of the tooth surface synchronized with the direction of the tooth trace does not affect the vibration, and is ignored by averaging in the above method. In the prior art, the detection of the amount of such unevenness is extremely time-consuming, but the gear inspection device 10 of the present invention can be used with the above technique without the need for the prior art. Shape can be obtained.

  In the gear inspection device 10 of the present invention, a plurality of tooth surface shapes for the inspection gear 30 obtained by experiments or the like are incorporated in the database 50 in advance as a tooth surface shape pattern for comparison as shown in FIG. ing. Then, the tooth surface shape calculated by the tooth surface shape calculating unit 43 is compared with the tooth surface shape pattern in the database 50 by the comparing unit 45, and the tooth surface shape of the inspection gear 30 is evaluated based on the comparison result. Next, the evaluation result is output from the output means 60 as the inspection result of the inspection gear 30 (see FIG. 2). The tooth surface shape of the inspection gear 30 obtained by the frequency response function calculating unit 42 is also output to the output unit 60.

  Thus, in the present invention, since the tooth surface shape of the inspection gear 30 is inspected based on the measured vibrations of the reference gear 20 and the inspection gear 30, it is simpler and shorter than the conventional inspection device. The inspection gear 30 can be inspected in time. For example, when the number of teeth of the reference gear 20 is 53, the number of teeth of the inspection gear 30 is 30, and the inspection gear 30 rotates at 1800 rpm, data acquisition for the inspection gear 30 is completed in about 1 second. In addition, the inspection gear 30 can be inspected in an extremely short time compared to the case of the prior art. Thus, in the present invention, it is possible to inspect all the tooth portions of the inspection gear 30.

  When a plurality of inspection gears 30 manufactured under the same conditions are inspected by the gear inspection device 10, problems in manufacturing the inspection gear 30 are obtained by examining the comparison results of the tooth surface shape and / or the vibration waveform. That is, it becomes possible to clarify the problems unique to the gear manufacturing apparatus. Further, in the present invention, a combination of the inspection gears 30 that can be driven with low vibration is appropriately selected based on the comparison result of the tooth surface shape and / or the vibration waveform for each of the plurality of inspection gears 30. You can also. This further improves the drive at low vibration in the case of a highly accurate gear pair, and drives at low vibration under limited conditions when the accuracy of the gear is relatively limited. Can be realized as much as possible.

  Further, in the gear inspection device 10 of the present invention, the waveform calculation means 44 may obtain the vibration waveform of the inspection gear 30, specifically, the waveform of the meshing vibration component. The meshing components fz, 2fz, and 3fz of the line spectrum (see FIG. 3B) obtained in the separating means 41 are extracted, and the waveforms of the meshing vibration components relating to the inspection gear 30 are obtained by inversely transforming these meshing components. Can be calculated. In FIG. 9, the waveform of the meshing vibration component relating to the inspection gear 30 is shown.

  Further, in the database 50 of the inspection means 40, a plurality of waveforms for the inspection gear 30 obtained by experiments or the like are stored in the database 50 as vibration waveform patterns for comparison or as feature information thereof as shown in FIG. Pre-installed. The vibration waveform calculated by the waveform calculation means 44 is compared with the vibration waveform pattern or feature information in the database 50 by the comparison means 45, and the vibration waveform of the inspection gear 30 is evaluated based on the comparison result. Next, as in the case described above, this evaluation result is output from the output means 60 as the inspection result of the inspection gear 30 (see FIG. 2). In such a case, it is obvious that the same effect as described above can be obtained. Note that this waveform may be output from the output means 60 as in the case of the tooth surface shape of the inspection gear 30.

  In the embodiment described with reference to the drawings, the case where the number of teeth of the reference gear 20 and the number of teeth of the inspection gear 30 are relatively prime has been described, but the number of teeth of the reference gear 20 and the number of teeth of the inspection gear 30 are The gear inspection apparatus 10 of the present invention can be applied even when the greatest common divisor between the two is significantly smaller than the number of teeth, for example, even when the greatest common divisor is 2 or 3.

  When the greatest common divisor is 2, every tooth portion of the inspection gear 30 is engaged with every other tooth portion of the reference gear 20 when the inspection gear 30 rotates. That is, one tooth portion of the inspection gear 30 does not engage with all the tooth portions of the reference gear 20. However, since the characteristics of the inspection gear 30 are considered to be substantially uniform over the entire inspection gear 30, it is possible to derive the characteristics of the inspection gear 30 almost accurately even when all the teeth are not engaged. . It is apparent that the same effect can be obtained when the greatest common divisor between the number of teeth of the reference gear 20 and the number of teeth of the inspection gear 30 is 3 or 5.

  FIG. 11 is a functional block diagram showing inspection means of a gear inspection device according to another embodiment of the present invention. In FIG. 11, the inspection unit 40 further includes a meshing vibration component extraction unit 62 that extracts a meshing vibration component from the vibration characteristics of the inspection gear 30 separated by the separation unit 41. The excitation force calculation means 63 of the inspection means 40 uses the meshing vibration component of the inspection gear extracted by the meshing vibration component extraction means 62 and the frequency response function related to the inspection gear 30 calculated by the frequency response function calculation means 42. Thus, the excitation force corresponding to the tooth surface shape of the inspection gear 30 is calculated.

  Here, the meshing vibration component extracting means 62 obtains the meshing vibration component by expressing the meshing frequency extracted from the vibration characteristics of the inspection gear 30 and the spectrum of the amplitude and phase of each of its harmonic components on a complex plane. .

  Further, the frequency response function calculating means 42 connects the mesh frequency extracted from the vibration characteristic of the inspection gear 30 and the spectrum of the amplitude of each of its harmonic components, and also the phase of each of the mesh frequency and its harmonic components. The frequency response function is obtained by concatenating the spectra.

  Further, as shown in the figure, the inspection unit 40 includes a comparison unit 64 that compares the excitation force of the inspection gear 30 calculated by the excitation force calculation unit 63 with the tooth surface information stored in the database 50 on a complex plane. Contains. In the present embodiment, the tooth surface information stored in the database 50 includes a plurality of excitation forces obtained in advance for a plurality of gears other than the inspection gear 30.

Hereinafter, a method for calculating a plurality of excitation forces stored in the database 50 will be described.
First, as shown in FIG. 12, a plurality of gears having different tooth surface shapes are prepared. Although nine types of gears are shown in FIG. 12 as an example, many types of gears having various shapes may be prepared.

  In the column of FIG. 12, “crn” means lead crowning, that is, roundness of the tooth trace, and is appropriately referred to as “crowning”. “Cvx” in the horizontal column means a convex profile, that is, roundness of the tooth profile, and is appropriately referred to as “convex”.

  “Pp” in the horizontal column means pressure angle error plus, that is, a pressure angle error in the positive direction. Further, “pm” in the horizontal column means a pressure angle error minus, that is, a pressure angle error in the minus direction. The unit of the numerical values shown in FIG. 12 is micrometers, and for example, “crn5” means that the crowning is 5 micrometers.

  These gears shown in FIG. 12 are attached to the gear inspection device 10 instead of the inspection gear 30. Next, while changing the torque at the rotation speed of 1800 rpm, the vibration acceleration and the trigger signal are measured for each gear, and the same synchronous averaging process as described above is performed.

  FIGS. 13 to 16 are diagrams showing the results of the synchronous averaging process, and (a) to (c) in FIGS. 13 to 16 show the relationship between the amplitude and the torque, and (d) to (f) ) Indicates the relationship between phase and torque. Further, (a) and (d) in each of FIGS. 13 to 16 show the case of the meshing frequency (meshing primary component) fz, and (b) and (e) are harmonics twice the meshing frequency fz. The case of the component (interlocking secondary component) 2 fz is shown, and (c) and (f) show the case of a harmonic component (meshing tertiary component) 3 fz that is three times the meshing frequency fz.

  Further, FIGS. 13 and 14 show cases where the convex is changed while the crowning is kept constant at 5 micrometers and 13 micrometers, respectively. FIG. 15 shows a case where the crowning is changed while the convex is maintained at 6 micrometers. FIG. 16 shows a case where the pressure angle error is changed while maintaining the convex and the crowning.

  Focusing on “crn5cvx3” in (a) and (d) in FIG. 13, the vibration is the smallest when the torque is around 73.5 Nm. In FIGS. 13B and 13D, the optimum torque values are different, and the optimum torque in FIGS. 13B and 13E is 147 Nm. As can be seen from FIG. 13E, the phase changes by 180 ° at the optimum torque. Further, as can be seen from FIG. 13, this optimum torque also changes depending on the amount of convex.

  Although not described in detail, it will be understood that a similar optimum torque exists in FIG. 15 and that this optimum torque varies with the amount of crowning. Also in FIG. 16, a similar optimum torque exists. However, in FIG. 16, even if the pressure angle error changes, the optimum torque hardly changes.

  In FIGS. 13 to 16, the amplitude ((a) to (c)) and the phase ((d) to (f)) are separately shown. However, since both the amplitude and phase for each meshing component are the main elements constituting the vibration waveform, the amplitude ((a) to (c)) and the phase ((d) to (f)) are compared with each other. It is inconvenient to determine the surface shape. For this reason, it is desirable to determine the tooth surface shape by comprehensively expressing the amplitude and phase.

FIG. 17A to FIG. 17C are diagrams for explaining a method for comprehensively expressing the amplitude and the phase. _First , as shown in FIG. 17A, the amplitude (A ₁ , A ₂ , A ₃ ) and phase (θ ₁ , θ ₂ , θ ₃ ) of the meshing vibration component are collected. In FIG. 17A, the horizontal axis represents frequency and the vertical axis represents time. In FIG. 17A, these meshing vibration components are represented by the following formulas (2) to (4).

Next, these meshing vibration components are connected on the complex plane. As can be seen from FIG. 17B, the end point of the primary component corresponds to the start point of the secondary component, and the end point of the secondary component corresponds to the start point of the tertiary component. Hereinafter, in the present specification, the amplitude and phase shown on the complex plane in this way are referred to as “Polar Plot”. On the polar plot, the amplitude (A ₁ , A ₂ , A ₃ ) is the length of the line segment, and the phase (θ ₁ , θ ₂ , θ ₃ ) is the x-axis and the line as shown in FIG. Expressed in angle between minutes.

  In the polar plot shown in FIG. 17B, the relationship between the meshing vibration components at a specific time is shown. For this reason, when the reference times are different as shown by time t1 and time t2 in FIG. 17B, the polar plot pattern changes (rotates) even if the waveform is the same.

In order to solve such a problem, in the present invention, the meshing primary component is shifted so that the phase of the meshing primary component becomes zero (see Equation (5)). As a result, the meshing primary component functions to determine the reference time axis, and the secondary component and the tertiary component are shifted by twice and three times the phase of the primary component, respectively (Equation (6) and Equation (7)). See). When shifted in this way, the same waveform can be drawn on the complex plane as the same pattern.

Furthermore, in order to enable comparison under different conditions, the amplitudes of all the components are normalized by the amplitudes of the primary components (see equations (8) to (10)). A polar plot after normalization is shown in FIG. Thereby, the comparison in various driving | running conditions can be performed on the same polar plot.

  Such a polar plot is created by the meshing vibration component extraction means 62 of the inspection means 40. 18 to 20 are diagrams showing polar plots when the gear shown in FIG. 12 is used at a rotational speed of 1800 rpm. Since these polar plots are represented in a complex plane, the horizontal axis in FIGS. 18 to 20 represents a real number (real number, real), and the vertical axis represents an imaginary number (imaginary number, Img.). A line segment between the origin in the polar plot and a point where (real number, imaginary number) = (1, 0) corresponds to the primary component of the meshing frequency (see FIG. 17C). The same applies to other polar plots described later.

  18 (a) to 18 (c) and FIG. 19 (a) to FIG. 19 (c) show the cases where the convex is changed with the crowning kept constant at 5 micrometers and 13 micrometers, respectively. Show. As can be seen from FIGS. 18 and 19, except for “crn5cvx3” and “crn13cvx6”, the phases of the meshing secondary components tend to be approximately equal. In particular, in these drawings, when the torque is (optimum torque) 147 Nm or less, the phase of the meshing secondary component is substantially equal. It can be seen that when the optimum torque is exceeded, the phase changes significantly.

  Furthermore, FIG. 20A to FIG. 20C show a case where the pressure angle error is changed while maintaining the convex and the crowning. As shown in the figure, when there is a pressure angle error (the positive side in FIG. 20A and the negative side in FIG. 20C), the phase of the meshing secondary component rotates as the torque increases. I understand.

  For the case where the crowning is changed while maintaining the convex, for example, with the convex maintained at 6 micrometers, it is sufficient to refer to FIGS. 18B, 19B and 20B. In this case, a tendency similar to that in the case where the crowning as shown in FIGS. 18A to 18C is maintained is shown.

  Incidentally, the polar plots shown in FIGS. 18 to 20 include the influence of the rotational speed of the gear and the influence of the dynamic characteristics of the gear inspection apparatus 10 as the vibration system. For this reason, it is desired to extract the characteristics of the tooth surface shape of the gear while eliminating the influence of the dynamic characteristics of the gear inspection device 10 as the vibration system.

  Hereinafter, a method for acquiring only the dynamic characteristics as the vibration system of the gear inspection apparatus 10 will be described. The method described below is performed by the frequency response function calculating unit 42 of the inspection unit 40. FIG. 21 is a cascade diagram showing the relationship between the amplitude of the appearing frequency component and the rotation speed. The cascade diagram of FIG. 21 is obtained by performing the above-described synchronous averaging process while slightly changing the rotational speed at a torque of 245 Nm. It is assumed that the illustrated rotation speed interval is necessary and sufficient to express a frequency response characteristic described later. FIG. 21 obtained in this way shows lines of three meshing frequency components, that is, a primary component fz, a secondary component 2fz, and a tertiary component 3fz.

  As can be seen from FIG. 21, the line of the primary component fz covers only the frequency range from about 0.5 kHz to about 2 kHz, and the line of the secondary component 2fz only has a frequency range of about 1 kHz to about 4 kHz. The line of the third order component 3fz covers only the frequency range from about 1.5 kHz to about 5 kHz. That is, these three lines alone cannot cover the entire frequency range on the horizontal axis.

Therefore, a schematic diagram as shown in FIG. 22 is used to cover all frequency ranges to be noticed. At this time, it is assumed that the relationship of Expression (11) and Expression (12) described with reference to FIG. 23 which is a model diagram of the gear inspection device based on the present invention is satisfied.

That is, as shown in FIG. 23, when the reference gear 20 and the inspection gear 30 are engaged, a damper having a damping coefficient C and a spring having a spring constant K act between these gears. As can be seen from FIG. 23, M is the equivalent inertial mass, x is the relative displacement, and Δx is the amount of delay caused by the deflection of the gear pair. Symbols J ₁ and J ₂ used to represent the equivalent inertia mass M and relative displacement x are the inertia moments of the inspection gear 30 and the reference gear 20, respectively, and symbols r _b1 and r _b2 are the inspection gear 30 and the reference gear 20, respectively. The reference radius and the symbols θ ₁ and θ ₂ indicate the rotation angles of the inspection gear 30 and the reference gear 20, respectively. Further, symbol e ₁ is a gear pair meshing error, and ΔK is a change amount of the spring constant K.

  Referring again to FIG. 22, a schematic diagram corresponding to FIG. 21 is shown in the upper part of FIG. 22. The amplitude (Amplitude) and phase (Phase) for each of the primary component fz to the tertiary component 3 fz at each rotation speed are shown. Is extracted from the upper diagram of FIG. The result is shown in the lower part of FIG. 22, and lines relating to the primary component fz to the tertiary component 3fz are shown for each of the amplitude and the phase. It will be appreciated that these lines can partially overlap almost completely.

  These lines are then translated and joined so that they overlap each other, resulting in lines for each of amplitude and phase as shown at the bottom of FIG. These are collectively referred to as a frequency response function G (ω). The amplitude is shown in a decibel scale. In addition, in FIG. 22, when there is a portion where the lines do not overlap when the lines are connected, the average value of both lines is appropriately adopted.

  FIG. 24 is a diagram showing the frequency response function G (ω) (amplitude / phase) thus obtained. The frequency response function G (ω) shown in FIG. 24 is a vibration system of the gear inspection device 10. Represents the dynamic characteristics of The frequency response function obtained by such an operation can cover the entire frequency range, and its accuracy is also increased. Normally, the frequency response function G (ω) is obtained by performing an impact test on the gear, but in the present invention, the gear inspection device 10 is used for the inspection gear 30 without performing the impact test. The shape of the frequency response function G (ω) can be obtained.

Here, when V (ω) is each of the meshing vibration components, the excitation force X (ω) of the corresponding meshing component, that is, the Fourier transform of the right side of the formula (11) is expressed by the following formula (13).
X (ω) = V (ω) / G (ω) (13)

  Here, the meshing vibration component V (ω) has already been represented on the polar plots shown in FIGS. On the other hand, the frequency response function G (ω) obtained in FIG. 24 represents the dynamic characteristics of the gear inspection apparatus 10 as a vibration system. Therefore, by dividing this meshing vibration component V (ω) by the frequency response function G (ω), the amplitude and phase of each component normalized by the meshing frequency component are in the form of the excitation force X (ω) of the meshing component. Calculated. Therefore, the excitation force X (ω) calculated in this way does not include dynamic characteristics as the vibration system of the gear inspection device 10. In other words, the excitation force X (ω) universally represents only the geometric shape typified by the tooth surface shape of the inspection gear 30 and may be measured at the aforementioned rotational speed of 1800 rpm. means.

  25 to 27 are diagrams illustrating polar plots depicting the excitation force X (ω) calculated in this way. Further, (a) to (c) of FIG. 25 show a case where the convex is changed in a state where the crowning is kept constant at 5 micrometers. (A)-(c) of FIG. 26 has shown the case where convex and crowning are changed suitably. FIGS. 27A and 27B show a case where the pressure angle error is changed while maintaining the convex and the crowning.

  In the case of “crn5cvx3” shown in FIG. 25A, the phase angle of the secondary component is concentrated in the range of 100 ° to 120 °. When the torque increases, the secondary component amplitude also increases.

  In addition, as can be seen from FIGS. 25B, 25C, and 26A to 26C, in all cases other than “crn5cvx3”, the phase angle of the secondary component is −25 ° to − It is concentrated in the range of 35 ° and hardly changes with torque. However, the amplitude in FIG. 26B decreases when the torque increases.

  FIG. 28 is a plot of only the secondary components of all the excitation forces X (ω) shown in FIGS. 25 to 27. For this reason, in FIG. 28, there are a plurality of plots corresponding to the types of gears. The square plot in FIG. 28 shows the gear of “crn5cvx3”, the round plot shows the gear of “crn5cvx6”, the diamond plot shows the gear of “crn5cvx9”, and the upward triangle plot is “crn9cvx6” ”, The downward triangle plot indicates the gear“ crn13cvx3 ”, the cross-shaped plot indicates the gear“ crn13cvx9 ”, and the upward pentagonal plot indicates the gear“ crn9cvx6pp6 ” In addition, the downward pentagonal plot shows a gear of “crn9cvx6pm6”.

  The numbers attached to these plots indicate the torque amount. Specifically, numerical value 1 indicates torque 147 Nm, numerical value 2 indicates torque 196 Nm, numerical value 3 indicates torque 220.5 Nm, and numerical value 4 indicates torque 245 Nm.

  In FIG. 28, the distance between the plot position and the origin indicates the amplitude, and the angle formed by the line segment connecting the plot position and the origin and the X axis indicates the phase. Note that the shape of the plot used in FIG. 28 to indicate the type of gear does not necessarily match the shape of the plot used in FIGS.

  As shown in the drawing, the plurality of plots shown in FIG. 28 can be mainly classified into four regions Z1 to Z4. In the region Z1, a large number of plots having different crowning and / or convex are included. As shown in the figure, the slope of the straight line L formed by the plot of the region Z1 is about minus 45 °. An intersection point of the straight line L with the x axis is called an intersection point L0. For example, when the amount of crowning and / or convex increases, the plot position is seen to shift away from the intersection L0 on the straight line L.

  Region Z2 also includes a plot when both crowning and convex are the smallest. In the region Z2, since the direction of excitation is rotated by about 180 °, the region Z2 is substantially included in the second quadrant.

  Further, the region Z3 includes a plot in which the pressure angle error is positive, and the region Z4 includes a plot in which the pressure angle error is negative. These regions Z3 and Z4 are located at locations quite different from the region Z1.

  On the other hand, regarding the torque, it can be seen that in the region Z1, as the load torque increases, the plot position shifts on the straight line L toward the intersection L0. Further, as can be seen from the regions Z3 and Z4, the plot position shifts so as to approach the straight line L as the torque increases.

  Thus, the excitation force in FIG. 28 generally corresponds to the tooth surface information of the gear. Accordingly, a plurality of excitation force plot information shown in FIG. 28 can be used as the database 50 of the present invention.

  That is, the inspection gear 30 for which the tooth surface shape is desired is prepared, and the excitation force X (ω) of the meshing component of the inspection gear 30 is calculated as described above using the gear inspection device 10 of the present invention. Next, the calculated excitation force X (ω) is compared with a database 50 as shown in FIG. Specifically, it is sufficient to plot the excitation force X (ω) of the inspection gear 30 on FIG. 28 and compare it with other plots. At this time, the output unit 60 may output FIG. 28 in which the excitation force X (ω) of the inspection gear 30 is plotted. In the present invention, the inspection gear 30 can be inspected through the tooth surface information of the inspection gear 30 obtained from such comparison.

  For example, when the calculated excitation force X (ω) of the inspection gear 30 is included in the region Z3, it can be seen that the pressure angle error of the inspection gear 30 is on the plus side. Then, if the result is fed back to the manufacture of the inspection gear 30, the inspection gear 30 can be manufactured more appropriately. It will be clear that in order to increase the inspection accuracy, the excitation force of more types of gears may be obtained and stored in the database 50.

  While the invention has been described in terms of exemplary embodiments, those skilled in the art will make the above described changes and various other changes, omissions, additions without departing from the scope and spirit of the invention. You will understand that you can.

It is the schematic of the gear inspection apparatus based on this invention. It is a functional block diagram which shows the test | inspection means of the gear test | inspection apparatus shown by FIG. (A) It is a figure which shows the waveform of the test | inspection gear calculated based on the rotation trigger signal of a rotating shaft part. (B) It is a figure which shows the line spectrum of an inspection gear. (C) It is a figure similar to FIG.3 (b) in case data length differs. (A) It is a figure similar to Fig.3 (a) which shows the waveform of the reference | standard gear calculated based on the rotation trigger signal of a rotating shaft part. (B) It is a figure which shows the line spectrum of a reference | standard gearwheel. (C) It is a figure similar to FIG.4 (b) in case data length differs. It is a cascade diagram of a gear pair. (A) It is the figure which calculated | required the response of the several remarkable rotation order by the rotation order analysis, (b) It is the figure which averaged Fig.6 (a). (A) It is a figure which shows the characteristic of the tooth surface shape of the test | inspection gear obtained from the gear test | inspection apparatus of this invention. (B) It is a figure which shows the characteristic of the tooth surface shape of the test | inspection gear obtained from the tooth profile test | inspection of the prior art. It is a figure which shows the several tooth surface shape pattern in a database. It is a figure which shows the waveform of a meshing vibration component. It is a figure which shows the some vibration waveform pattern in a database. It is a functional block diagram which shows the inspection means of the gear inspection apparatus based on other embodiment of this invention. It is a figure which shows the several gearwheel from which a tooth-surface shape mutually differs. (A)-(c) It is a figure which shows the relationship between the amplitude and torque for confirming the influence of a convex. (D)-(f) It is a figure which shows the relationship between the phase and torque for confirming the influence of a convex. (A)-(c) It is another figure which shows the relationship between the amplitude and torque for confirming the influence of a convex. (D)-(f) It is another figure which shows the relationship between the phase and torque for confirming the influence of a convex. (A)-(c) It is a figure which shows the relationship between the amplitude and torque for confirming the influence of crowning. (D)-(f) It is a figure which shows the relationship between the phase and torque for confirming the influence of crowning. (A)-(c) It is a figure which shows the relationship between the amplitude and torque for confirming the influence of a pressure angle error. (D)-(f) It is a figure which shows the relationship between the phase and torque for confirming the influence of a pressure angle error. (A)-(c) It is a figure for demonstrating the method of expressing an amplitude and a phase comprehensively. (A)-(c) It is a figure which shows a polar plot at the time of changing a convex. (A)-(c) It is another figure which shows a polar plot at the time of changing a convex. (A)-(c) It is a figure which shows the polar plot at the time of changing a pressure angle error. It is a cascade diagram which shows the relationship between the amplitude of the frequency component which appears, and rotation speed. It is a schematic diagram explaining acquiring the frequency response characteristic about an amplitude and a phase. It is a model figure of the gear inspection apparatus based on this invention. It is a figure which shows a frequency response function. (A)-(c) It is a figure which shows the polar plot of the excitation force at the time of changing a convex. (A)-(c) It is a figure which shows the polar plot of the excitation force at the time of changing crowning. (A)-(c) It is a figure which shows the polar plot of the excitation force at the time of changing a pressure angle error. It is the figure which plotted the secondary component of the meshing frequency in the polar plot of FIGS.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Gear inspection apparatus 11 Gear box 20 Reference gear 21, 31 Rotating shaft part 25a, 25b Bearing 29, 29 'Acceleration pick-up 30 Inspection gear 35a, 35b Bearing 40 Inspection means 41 Separation means 42 Frequency response function calculation means 43 Tooth surface shape calculation Means 44 Waveform calculation means 45 Comparison means 50 Database 51 Slip ring or telemeter 52 Dynamometer 53 Motor 54, 54 'Rotation detector 60 Output means 62 Meshing vibration component extraction means 63 Excitation force calculation means 64 Comparison means fa, fb Non-integer order Component fz, 2fz, 3fz Meshing component

Claims (12)

In the gear inspection device that inspects the inspection gear,
Comprising a reference gear rotatably engaged with the inspection gear;
The number of teeth of the reference gear and the number of teeth of the inspection gear are relatively prime,
further,
Driving means for applying a load to the other of the reference gear and the inspection gear while driving one of the reference gear and the inspection gear;
Vibration acceleration detecting means for detecting vibration acceleration formed by the reference gear and the inspection gear during rotation of the reference gear and the inspection gear;
A rotation trigger signal detecting means for detecting a rotation trigger signal of the respective rotation shafts of the reference gear and the inspection gear;
A gear inspection apparatus comprising: inspection means for inspecting the inspection gear based on the vibration acceleration detected by the vibration acceleration detection means and the rotation trigger signal detected by the rotation trigger signal detection means. In the gear inspection device that inspects the inspection gear,
Comprising a reference gear rotatably engaged with the inspection gear;
The greatest common divisor between the number of teeth of the reference gear and the number of teeth of the inspection gear is significantly smaller than the number of teeth;
further,
Driving means for applying a load to the other of the reference gear and the inspection gear while driving one of the reference gear and the inspection gear;
Vibration acceleration detecting means for detecting vibration acceleration formed by the reference gear and the inspection gear during rotation of the reference gear and the inspection gear;
A rotation trigger signal detecting means for detecting a rotation trigger signal of the respective rotation shafts of the reference gear and the inspection gear;
A gear inspection apparatus comprising: inspection means for inspecting the inspection gear based on the vibration acceleration detected by the vibration acceleration detection means and the rotation trigger signal detected by the rotation trigger signal detection means. The inspection means includes
Separating means for separating the vibration characteristic of the inspection gear and the vibration characteristic of the reference gear by synchronously averaging the vibration acceleration with the rotation trigger signal;
A frequency response function calculating means for calculating and quantifying a frequency response function related to the reference gear and the inspection gear;
Tooth surface shape calculation means for determining the tooth surface shape of the inspection gear from the vibration characteristics of the inspection gear separated by the separation means and the quantified frequency response function calculated by the frequency response function calculation means. The gear inspection device according to claim 1 or 2 including. The inspection means further includes
Storage means for storing a plurality of tooth surface shape patterns for the inspection gear;
The gear inspection apparatus according to claim 3, further comprising a comparison unit that compares the tooth surface shape of the inspection gear calculated by the tooth surface shape calculation unit with the tooth surface shape pattern stored in the storage unit. The inspection means further includes
Waveform calculating means for calculating a vibration waveform of the inspection gear based on vibration characteristics of the inspection gear separated by the separation means;
Storage means for storing a plurality of vibration waveform patterns for the inspection gear;
The gear inspection device according to claim 4, further comprising a comparison unit that compares the vibration waveform of the inspection gear calculated by the waveform calculation unit with the vibration waveform pattern stored in the storage unit.   The gear inspection apparatus according to any one of claims 2 to 5, wherein the greatest common divisor is 2, 3 or 5. The inspection means includes
Separating means for separating the vibration characteristic of the inspection gear and the vibration characteristic of the reference gear by synchronously averaging the vibration acceleration with the rotation trigger signal;
Meshing vibration component extracting means for extracting meshing vibration components from the vibration characteristics of the inspection gear separated by the separating means;
A frequency response function calculating means for calculating and quantifying a frequency response function related to the inspection gear;
Using the meshing vibration component of the inspection gear extracted by the meshing vibration component extraction means and the frequency response function related to the inspection gear calculated by the frequency response function calculation means, the tooth surface shape of the inspection gear was supported. The gear inspection device according to claim 1, further comprising: an excitation force calculating unit that calculates an excitation force. The meshing vibration component extracting means includes
8. The meshing vibration component is obtained by representing on the complex plane the amplitude and phase spectra of the meshing frequency extracted from the vibration characteristics of the inspection gear and its harmonic components. Gear inspection device.   The gear inspection device according to claim 8, wherein the phase of the meshing primary component is made zero in the complex plane. The frequency response function calculating means includes
The frequency response is obtained by concatenating the spectrum of the meshing frequency extracted from the vibration characteristics of the inspection gear and the amplitude of each of its harmonic components, and by concatenating the spectrum of each meshing frequency and each of the harmonic components thereof. The gear inspection device according to any one of claims 7 to 9, wherein a function is acquired. The inspection means further includes
Storage means for storing a plurality of tooth surface information for the inspection gear;
The comparison means for comparing the excitation force of the inspection gear calculated by the excitation force calculation means with the tooth surface information stored in the storage means on a complex plane. The gear inspection device according to item.   The gear inspection apparatus according to claim 11, wherein the tooth surface information is a plurality of excitation forces obtained in advance for a plurality of other gears.

Images