JP4019052B2 - Gear meshing vibration estimation method and apparatus - Google Patents

Description

The present invention relates to a method and apparatus for estimating the meshing vibratory force of the tooth wheel.

Conventionally, it is an unchanging problem to prevent the generation of gear noise when manufacturing gears. In particular, in recent years, with the improvement of user needs for quietness in the interior of a vehicle such as an automobile, there is an increasing demand for reduction of gear noise that is relatively pure and easily audible in gears used in power transmission systems of automobiles and the like. . In general, in order to reduce gear noise, it is often the case that the tooth surface finish is added after heat treatment, or the tooth surface accuracy management is strengthened. Tooth surface accuracy control is mostly carried out with a gear measuring machine in the case of helical gears, but especially with bevel gears and hypoid gears, the gear measuring machine is expensive and takes time to measure. In many cases, the conventional tooth contact evaluation method is substituted. The conventional tooth contact evaluation method using Komyotan is to apply Komyotan to the tooth surface and visually check where the Komyotan peeled off by meshing, or shoot with a camera Then, it has been performed by comparing and evaluating the location where the light attenuation has been peeled off by meshing and the tooth contact of a gear pair with good gear noise characteristics (for example, Patent Document 1).
JP 60-82905 A

  However, in the conventional tooth contact evaluation method using Komyotan as described above, even if the part does not hit the tooth, the part of the part will not be touched by the thickness of Komyotan. There is a problem that it is peeled off and accurate tooth contact cannot be evaluated, and there is a problem that the level of contact pressure cannot be determined, and it is difficult to evaluate the tooth contact with sufficient accuracy.

Furthermore, in order to reduce gear noise, it is considered effective to grasp the meshing excitation force of the gears and reduce the meshing excitation force. Since the hit evaluation method has the above-described problems, it is difficult to evaluate the meshing vibration generating force of the gear.
The present invention has been made in view of such a problem, by allowing measure the precise action area and surface pressure, the gear to be able to estimate the meshing vibratory force of the tooth wheel with high precision It is an object of the present invention to provide a meshing vibration force estimation method and apparatus.

For this reason , the gear tooth contact evaluation method as a related art of the present invention includes a lubricant application step of applying a lubricant to the tooth surfaces of at least one gear of a pair of gears meshing with each other, and the above-mentioned after the lubricant application step. Tooth surface temperature rise detection step for detecting the temperature rise distribution of the tooth surface of the one gear caused by the rotation of a pair of gears, and the distribution of the tooth surface temperature rise detected in the tooth surface temperature rise detection step And a tooth contact evaluation step for evaluating a region where the tooth surface temperature rise is relatively high as a meshing region and evaluating that the surface pressure is higher as the tooth surface temperature rise is relatively higher. It is characterized by.

In addition, the tooth surface temperature rise detection step includes a gear rotation step for rotating the pair of gears after the lubricating oil application step, and a tooth surface temperature distribution of the one gear after the gear rotation step. In the tooth contact evaluation step, the tooth surface temperature distribution as the distribution of the tooth surface temperature rise measured in the post-rotation tooth surface temperature measurement step is measured. based on, according with the tooth surface temperature is evaluated as meshing area a relatively high area, it is not preferable according tooth surface temperature is evaluated as relatively higher surface pressure is high. In this case, as a premise, the temperature in at least each portion of the tooth surface of the one gear is the same before the gear rotation step.

In addition, the tooth surface temperature rise detection step includes a rotation front tooth surface temperature measurement step for measuring a tooth surface temperature distribution of the one gear after the lubricant application step, and a pair of gears after the rotation front tooth surface temperature measurement step. A rotation process of the gear, a post-rotation tooth surface temperature measurement process that measures the distribution of the tooth surface temperature of the one gear after the gear rotation process, and the rotation before the rotation measured in the pre-rotation tooth surface temperature measurement process. The distribution of the tooth surface temperature, which is the difference between the distribution of the tooth surface temperature and the distribution of the tooth surface temperature after the rotation measured in the post-rotation tooth surface temperature measurement step, is calculated as the distribution of the tooth surface temperature increase. A tooth surface temperature difference calculating step, and in the tooth contact evaluation step, the tooth surface temperature difference is calculated based on the tooth surface temperature difference distribution as the distribution of the tooth surface temperature increase calculated in the tooth surface temperature difference calculating step. Biting areas with relatively high surface temperature differences With assessing the fit region, it is not preferable according tooth surface temperature difference is evaluated as a relatively higher surface pressure is high.

According to the first aspect of the present invention, there is provided a method for estimating the meshing excitation force of a gear according to the present invention, wherein a lubricant is applied to the tooth surfaces of at least one gear of a pair of gears engaged with each other; A tooth surface temperature rise detecting step for detecting a temperature rise distribution of the tooth surface of the one gear caused by the rotation of the pair of gears later, and the tooth surface temperature rise detected in the tooth surface temperature rise detecting step The meshing number area dividing step of dividing the distribution of each of the meshes into the number of simultaneous meshing sheets, and the temperature difference between the adjacent meshing numbers in the tooth surface temperature distribution divided in the meshing number area dividing step is calculated. Meshing for estimating the meshing excitation force based on the temperature difference between the regions for each adjacent simultaneous meshing number calculated in the interregional temperature difference calculating step. It is characterized in that a force estimating step.

The tooth surface temperature rise detection step includes a gear rotation step for rotating the pair of gears after the lubricating oil application step, and a tooth surface temperature distribution of the one gear after the gear rotation step. A post-rotation tooth surface temperature measurement step for measuring the distribution of the tooth surface temperature, and in the meshing number region dividing step, the tooth surface temperature as a distribution of the increase in the tooth surface temperature measured in the post-rotation tooth surface temperature measurement step. The distribution is divided into regions for each simultaneous meshing number, and in the inter-region temperature difference calculating step, the tooth surface temperature distribution as the distribution of the tooth surface temperature rise divided in the meshing number region dividing step is adjacent. It is preferable to calculate the temperature difference in the region for each simultaneous meshing number (Claim 2 ). In this case, as a premise, the temperature in at least each portion of the tooth surface of the one gear is the same before the gear rotation step.

In addition, the tooth surface temperature rise detection step includes a rotation front tooth surface temperature measurement step for measuring a tooth surface temperature distribution of the one gear after the lubricant application step, and a pair of gears after the rotation front tooth surface temperature measurement step. A rotation process of the gear, a post-rotation tooth surface temperature measurement process that measures the distribution of the tooth surface temperature of the one gear after the gear rotation process, and the rotation before the rotation measured in the pre-rotation tooth surface temperature measurement process. The distribution of the tooth surface temperature, which is the difference between the distribution of the tooth surface temperature and the distribution of the tooth surface temperature after the rotation measured in the post-rotation tooth surface temperature measurement step, is calculated as the distribution of the tooth surface temperature increase. A tooth surface temperature difference calculating step, and in the meshing number region dividing step, the tooth surface temperature difference distribution as the distribution of the tooth surface temperature increase calculated in the tooth surface temperature difference calculating step is calculated for each simultaneous meshing number. When divided into areas In addition, in the inter-region temperature difference calculation step, the temperature difference between the adjacent simultaneous meshing numbers in the tooth surface temperature difference distribution as the distribution of the tooth surface temperature difference divided in the meshing number region dividing step is calculated. It is preferable to calculate (Claim 3 ).

Further , a gear tooth contact evaluation device as a related art of the present invention includes a gear rotating means for rotating a pair of gears meshed with each other and having a lubricating oil applied to at least one gear tooth surface, and the gear rotating means. Tooth surface temperature rise detecting means for detecting a distribution of temperature rise of the tooth surface of the one gear caused by the rotation of the pair of gears, and for the tooth surface temperature rise detected by the tooth surface temperature rise detecting means. Based on the distribution, a region where the tooth surface temperature rise is relatively high is evaluated as a meshing region, and a tooth contact evaluation means for evaluating that the surface pressure is higher as the tooth surface temperature rise is relatively higher is provided. It is characterized by that.

The tooth surface temperature rise detecting means includes tooth surface temperature measuring means for measuring a tooth surface temperature distribution of the one gear as the tooth surface temperature rise distribution after the pair of gears is rotated by the gear rotating means. The tooth contact evaluation means engages an area where the tooth surface temperature is relatively high based on the tooth surface temperature distribution as the distribution of the tooth surface temperature rise measured by the tooth surface temperature measuring means. and with evaluating, it is not preferable according tooth surface temperature is evaluated as relatively higher surface pressure is high. In this case, as a premise, the temperature in at least each portion of the tooth surface of the one gear is the same before the pair of gears rotate.

Further, the tooth surface temperature rise detecting means is measured by the tooth surface temperature measuring means for measuring the temperature of the tooth surface of the one gear and the tooth surface temperature measuring means before the pair of gears are rotated by the gear rotating means. The difference between the distribution of the tooth surface temperature of the one gear and the distribution of the tooth surface temperature of the one gear measured by the tooth surface temperature measurement unit after the pair of gears is rotated by the gear rotation unit. A tooth surface temperature difference calculating means for calculating a tooth surface temperature difference distribution as the tooth surface temperature increase distribution, wherein the tooth contact evaluation means calculates the tooth surface temperature increase calculated by the tooth surface temperature difference calculating means. Based on the distribution of the tooth surface temperature difference as the distribution of the tooth surface, the region where the tooth surface temperature difference is relatively high is evaluated as the meshing region, and the surface pressure is higher as the tooth surface temperature difference is relatively higher. evaluation, it is not preferable to be.

The gear meshing excitation force estimating apparatus according to the present invention according to claim 8 is a gear rotating means for rotating a pair of gears meshed with each other, in which lubricating oil is applied to the tooth surfaces of at least one gear, and the gears. Tooth surface temperature rise detecting means for detecting the temperature rise distribution of the tooth surface of the one gear caused by the rotation of the pair of gears by the rotating means, and the tooth surface detected by the tooth surface temperature rise detecting means The temperature difference between the meshing number area dividing means for dividing the temperature rise distribution into areas for each simultaneous meshing number, and the area for each adjacent simultaneous meshing number in the tooth surface temperature rise distribution divided by the meshing number area dividing means The meshing excitation force is estimated based on the temperature difference between the regions calculated for the adjacent simultaneous meshing number calculated by the interregional temperature difference calculating unit and the interregional temperature difference calculating unit. It is characterized in that engagement and a vibratory force estimating means that.

The tooth surface temperature rise detecting means includes tooth surface temperature measuring means for measuring a tooth surface temperature distribution of the one gear as the tooth surface temperature rise distribution after the pair of gears is rotated by the gear rotating means. The meshing number region dividing means divides the tooth surface temperature distribution as the distribution of the tooth surface temperature measured by the tooth surface temperature measuring means into regions for each simultaneous meshing number, and the inter-region temperature. It is preferable that the difference calculating means calculates a temperature difference between adjacent tooth numbers in the tooth surface temperature distribution as the distribution of the tooth surface temperature divided by the mesh number area dividing means. Item 9 ). In this case, as a premise, the temperature in at least each portion of the tooth surface of the one gear is the same before the pair of gears rotate.

Further, the tooth surface temperature rise detecting means is measured by the tooth surface temperature measuring means for measuring the temperature of the tooth surface of the one gear and the tooth surface temperature measuring means before the pair of gears are rotated by the gear rotating means. The difference between the distribution of the tooth surface temperature of the one gear and the distribution of the tooth surface temperature of the one gear measured by the tooth surface temperature measurement unit after the pair of gears is rotated by the gear rotation unit. A tooth surface temperature difference calculating means for calculating a tooth surface temperature difference distribution as a distribution of the tooth surface temperature rise, and the meshing number region dividing means is the tooth surface temperature calculated by the tooth surface temperature difference calculating means. The distribution of the tooth surface temperature difference as the increase distribution is divided into regions for each simultaneous mesh number, and the inter-region temperature difference calculation means is the distribution of the tooth surface temperature increase divided by the mesh number region division means. age It is preferred to calculated the temperature difference between the area for each simultaneous meshing number adjacent in the distribution of the tooth surface temperature difference (claim 10).

The measurement of the tooth surface temperature distribution is preferably performed without contact with the tooth surface (claims 4, 11) .
Furthermore, it is preferable to measure the distribution of the tooth surface temperature using thermography (claims 5 and 12) .
The temperature of the lubricating oil, the tooth surface temperature rise detection step before preferably be kept at room temperature and isothermal (claim 6).
The temperature of the pair of gears, the tooth surface temperature rise detection step before preferably be kept at room temperature and isothermal (claim 7).
Furthermore, the temperature of the lubricating oil, before the pair of gears are rotated to be kept at room temperature and isothermal preferred by the gear rotation means (claim 13).
The temperature of the pair of gears, before the pair of gears are rotated to be kept at room temperature and isothermal preferred by the gear rotation means (claim 14).

Therefore, according to the gear tooth contact evaluation method and apparatus as the related art of the present invention, a pair of gears meshing with each other is rotated and a load is applied to the tooth surfaces of the pair of gears. The above-described tooth surface temperature is detected by detecting the distribution of the temperature increase of the tooth surface by utilizing the fact that the temperature of the tooth surface to which the lubricating oil is sheared and as a result the temperature of the tooth surface to which the lubricant oil is sheared is increased. It is possible to evaluate a region where the increase distribution is relatively large as a meshing region, and it can be evaluated that the surface pressure is higher as the distribution of the tooth surface temperature increase is relatively large. Therefore, it is possible to prevent erroneous determination of a portion where the tooth surfaces are not in contact with each other as the meshing region, and further, it is possible to determine the strength of the surface pressure within the meshing region, thereby improving the tooth contact evaluation of the gear. Ru can be done to accuracy.

Further, according to the method and apparatus for estimating the meshing excitation force of the gear according to the present invention, the pair of gears meshed with each other rotates, and a load is applied to the tooth surfaces of the pair of gears. The lubricating oil is sheared, and as a result, the temperature of the tooth surface where the lubricating oil is sheared rises, and the number of simultaneous meshing of the pair of gears changes, whereby the shear resistance of the lubricating oil applied on the tooth surface By utilizing the fact that fluctuation occurs in the tooth surface and causes a temperature difference on the tooth surface (distribution of tooth surface temperature increase), the distribution of the tooth surface temperature increase is divided into regions for each number of simultaneous meshes. The temperature difference between the regions for each simultaneous meshing number is calculated, and the meshing excitation force can be estimated with high accuracy based on this temperature difference (claims 1 to 3 , 8 to 10 ).

Further, according to the gear tooth contact evaluation method and apparatus and the gear meshing excitation force estimation method and apparatus according to the present invention as the related art of the present invention, the distribution of the tooth surface temperature of the tooth using the thermography camera is obtained. Since measurement is performed in a non-contact manner, measurement can be performed in a short measurement time (claims 4, 5, 11, 12 ) .

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[First Embodiment]
The first embodiment of the present invention (related technology of the present invention) will be described. FIGS. 1 and 2 show a gear tooth contact evaluation method and apparatus as a first embodiment of the present invention, and FIG. FIG. 2 is a flowchart showing a gear tooth contact evaluation method.

First, a gear tooth contact evaluation method and apparatus according to this embodiment will be described.
As shown in FIG. 1, the gear tooth contact evaluation apparatus according to the present embodiment includes a drive motor (gear rotating means) 20, a torque applying motor 21, a thermography camera (tooth surface temperature measuring means) 30, and a photo sensor 31. And a camera control unit 32 and an arithmetic unit 40.

  Here, of the pair of gears 10 and 11 to be evaluated for tooth contact, the gear 10 has a shaft 12 connected to the drive motor 20, and the gear 10 is configured as a drive gear that is rotationally driven by the drive motor 20. Has been. On the other hand, the gear 11 is configured as a driven gear that rotates following the rotation of the gear 10. The shaft 11 of the gear 11 is connected to a torque application motor 21, and the torque application motor 21 rotates the rotation speed of the gear 11 slower than the rotation of the gear 11 driven by the gear 10, that is, Rotational torque (torque corresponding to power transmission load) is applied to the pair of gears 10 and 11 by being controlled to rotate at a rotational speed slower than the rotational speed of the gear 10.

In addition, protrusions 14 are provided at predetermined intervals (every predetermined central angle) in the detection region of the photosensor 31 on the peripheral surface of the shaft 12 of the gear 10, and the plurality of protrusions 14 and the photosensor 31 are provided. The rotary encoder which detects the rotation angle of the gear 10 is comprised from these.
The photosensor 31 includes a light transmitting unit that transmits light and a light receiving unit that receives light transmitted from the light transmitting unit, and the protrusion 14 has passed between the light transmitting unit and the light receiving unit. By detecting this, the rotation angle of the gear 10 is detected. Thereby, the rotation position of a specific tooth (here, tooth 10a) in the gear 10 can be detected. Of course, the specific tooth whose rotational position is to be detected in this case can be arbitrarily selected.

The thermography camera 30 measures the temperature of an object in a non-contact manner. Here, in order to measure the temperature distribution of the tooth surface of the gear 10 immediately after passing through the meshing portion with the gear 11, the meshing of the gears 10 and 11 is performed. It is installed downstream of the section.
In this embodiment, in order to measure the distribution of the tooth surface temperature of the specific tooth 10a in the gear 10, the photo sensor 31 is connected to the camera control unit 32 that controls the activation of the thermographic camera 30, and the monitoring information by the photo sensor 31 is measured. The camera control unit 32 controls the thermographic camera 30 based on (that is, the rotational position information of the specific tooth 10a).

The camera control unit 32 includes emissivity calibration means (not shown) that constitutes the emissivity of the thermographic camera 30, and distribution data of the tooth surface temperature of the tooth 10a of the gear 10 measured by the thermographic camera 30 will be described later. To the arithmetic unit 40.
The arithmetic unit 40 evaluates the tooth contact of the gears 10 and 11 by evaluating the meshing area and the surface pressure based on the distribution data of the tooth surface temperature of the tooth 10a of the gear 10 received from the camera control unit 32. The tooth surface temperature difference calculating means 41 and the tooth contact evaluation means 42 are provided.

Here, the teeth 10a of the gear 10 generated by the rotation of the gears 10, 11 by the drive motor (gear rotating means) 20 by the thermographic camera (tooth surface temperature measuring means) 30 and the tooth surface temperature calculating means 41 are described. Tooth surface temperature rise detecting means for detecting the distribution of the temperature rise of the tooth surface is configured.
The tooth surface temperature difference calculating means 41 is a gear measured in each of the pre-rotation tooth surface temperature measurement step S20 and the post-rotation tooth surface temperature measurement step S40 in the gear tooth contact evaluation method of the present embodiment described later with reference to FIG. The temperature difference (the distribution of the tooth surface temperature difference; the distribution of the tooth surface temperature rise) at the same location of the tooth surface temperature distribution of the ten teeth 10a is calculated. The tooth surface temperature distribution of the tooth 10a measured in the pre-rotation tooth surface temperature measurement step S20 is subtracted from the tooth surface temperature distribution of the tooth 10a measured in the post-rotation tooth surface temperature measurement step S40. The distribution of the tooth surface temperature difference is calculated.

Further, the tooth contact evaluation means 42 is based on the distribution of the tooth surface temperature difference of the tooth 10 a of the gear 10 calculated by the tooth surface temperature difference calculation means 41, and the tooth surface temperature difference in the tooth 10 a of the gear 10 is relative. Thus, the tooth contact evaluation of the gears 10 and 11 is performed by evaluating the higher region as the meshing region and evaluating that the higher the tooth surface temperature difference is, the higher the surface pressure is.
Next, the tooth contact evaluation method of this embodiment will be described with reference to FIG.

  First, in the lubricating oil application step S10, lubricating oil is applied to the tooth surfaces of at least one gear (here, the gear 10) of the pair of gears 10 and 11 meshing with each other. Next, in the pre-rotation tooth surface temperature measurement step S <b> 20, the distribution of the tooth surface temperature of the specific tooth 10 a arbitrarily selected from the teeth of the gear 10 that is the drive gear is measured by the thermography camera 30. The measured tooth surface temperature distribution data is transmitted to the arithmetic unit 40 via the camera control unit 32.

  Next, in the gear rotation step S30, the pair of gears 10 and 11 are rotationally driven by the drive motor 20. Here, the rotation of the gears 10 and 11 in the gear rotation step S30 is performed at a predetermined number of rotations when the number of teeth of the gear 10 and the number of teeth of the gear 11 are the same and the teeth meshing every rotation are the same. Further, when the number of teeth of the gear 10 is the same as or different from the number of teeth of the gear 11 and the teeth of the gear 11 engaged each time the gear 10 makes one revolution, the teeth of the gear 11 engaged with the specific tooth 10a are different. Rotate until everything is engaged. At this time, a predetermined torque is constantly applied between the gears 10 and 11 by the torque applying motor 21.

  Then, immediately after the completion of the rotation in the gear rotation step S30, that is, as soon as the tooth 10a of the gear 10 passes through the meshing portion with the tooth of the gear 11, the tooth surface temperature of the tooth 10a is measured in the post-rotation tooth surface temperature measurement step S40. The distribution is measured with the thermographic camera 30. That is, the gears 10 and 11 are rotated at a predetermined number of rotations while meshing with each other, and a load is applied to the tooth surfaces of the gears 10 and 11, so that the tooth surfaces (here, the tooth surfaces of the teeth 10a) are applied in the lubricating oil application step S10. The increase in temperature is caused by the thermography camera 30 by utilizing the fact that the temperature of the tooth surface (ie, the tooth surface to which the load is applied) is increased. taking measurement. The measured tooth surface temperature distribution data is transmitted to the arithmetic unit 40 via the camera control unit 32.

Next, in the tooth surface temperature difference calculating step S50, the tooth surface temperature distribution data of the tooth 10a before rotation measured in the tooth surface temperature difference calculating unit 41 of the arithmetic unit 40 in the tooth surface temperature measuring step S20 before rotation and the after rotation. The distribution of the tooth surface temperature difference, which is the difference from the tooth surface temperature distribution data of the tooth 10a after rotation measured in the tooth surface temperature measuring step S40, is calculated.
Then, in the tooth contact evaluation step S60, based on the distribution of the tooth surface temperature difference of the tooth 10a of the gear 10 calculated in the tooth surface temperature difference calculation step S50 in the tooth contact evaluation means 42 of the arithmetic unit 40, the tooth surface temperature difference. Is evaluated as a meshing region, and the tooth contact evaluation of the gears 10 and 11 is performed by evaluating that the surface pressure is higher as the tooth surface temperature difference is relatively higher.

  Here, the rotation is caused by the rotation of the gears 10 and 11 by the tooth surface temperature measurement step S20 before rotation, the gear rotation step S30, the tooth surface temperature measurement step S40 after rotation, and the tooth surface temperature difference calculation step S50. A tooth surface temperature increase detecting step for detecting a tooth surface temperature increase distribution of the tooth 10a of the gear 10 is configured, and the above tooth surface temperature difference distribution calculated in the tooth surface temperature difference calculating step S50 is the tooth surface temperature increase distribution. Corresponds to the distribution.

In the tooth contact evaluation method of the present embodiment, since the lubricating oil is applied to the tooth surfaces of the gears 10 and 11 in the lubricating oil application step S10, before the rotation front tooth surface temperature measuring step S20 after the lubricating oil application step S10, An emissivity calibration step S11 for calibrating the emissivity of the thermographic camera 30 is provided by emissivity calibration means (not shown) of the camera control unit 32.
The lubricating oil applied to the tooth surface of the gear 10 in the lubricating oil application step S10 is the one used when the gears 10 and 11 are actually used as power transmission gears. However, in order to see the temperature rise of the tooth surface, a special lubricating oil different from that actually used may be used.

In addition, the temperature of the lubricating oil is basically determined in order to accurately measure the distribution of the tooth surface temperature difference of the tooth 10a of the gear 10 calculated in the tooth surface temperature difference calculating step S50 (execution of the pre-rotation tooth surface temperature measuring step S20). Previously, the temperature is kept isothermal with room temperature. Furthermore, for the same reason, the gears 10 and 11 themselves are basically kept isothermal with room temperature.
Here, in order to confirm the effectiveness of the gear tooth contact evaluation method and device of the present embodiment, the tooth surface temperature measurement result in the gear tooth contact evaluation method and device of the present embodiment and the above-described conventional method. A test conducted by comparing the tooth surface state in the tooth contact evaluation method using Komyotan and the test results will be described.

  In this test, Gleason type gradient tooth bevel gears were used as the pair of gears 10 and 11. The gears 10 and 11 are made of chromium molybdenum steel and subjected to induction hardening after gear cutting, and have a module of 4.0 m, a pressure angle of 20 °, a shaft angle of 90 °, a tooth width of 27 mm, and a twist angle of 35 °. The gears 10 and 11 have 20 teeth and the gear 11 has 40 teeth. The measurement wavelength of the thermographic camera 30 was about 3 to 4 μm.

  In this test, first, the tooth surface temperature difference distribution of the tooth 10a of the gear 10 obtained in the tooth surface temperature difference calculating step S50 by the gear tooth contact evaluation method and apparatus of the present embodiment and the above-described conventional method. The usefulness of measuring the tooth surface temperature difference distribution of the gears was confirmed by comparing the tooth surface condition in the tooth contact evaluation method using Komyotan. The results are shown in FIGS. 3 (a1), (a2), (b1), (b2), (c1), and (c2).

  3 (a1), (a2), (b1), (b2), (c1), and (c2), the left figure (that is, the figure with the reference number 1) is the above-described conventional light The right side figure (namely, figure with number 2) shows the state of the tooth surface in the tooth contact evaluation method and device of this embodiment ( Hereinafter, it is simply referred to as a tooth surface temperature difference distribution).

Further, in FIG. 3 and FIGS. 4, 6, 7, and 10 described later, the left side of the tooth surface is the inner end X of the gear 10 in FIG. 1, and the right side of the tooth surface is the outer end of the gear 10 in FIG. Since it is Y, hereinafter, the left side of the tooth surface is referred to as the inner end, and the right side of the tooth surface is referred to as the outer end.
In addition, the state of the tooth surface in the conventional tooth contact evaluation method using Komyotan in FIG. 3 and FIGS. 4, 6, 7, and 10, which will be described later, indicates the part where the smudged part remains. The white part surrounded by the shaded part shows the part where the light alum is peeled off.

In addition, the distribution of the tooth surface temperature difference in FIG. 3 and FIGS. 4, 6, 7, and 10 described later is represented by an isothermal line of 0.1 ° C., and the white tooth surface indicates the lowest temperature difference. The portion where the tooth surface is indicated by diagonal lines indicates the portion where the temperature difference is increasing, and the portion where the tooth surface is black indicates the portion where the temperature difference is most increased.
As shown in FIG. 3, in the state of the tooth surface in the conventional tooth contact evaluation method using Komyotan, the tooth contact position on the tooth surface of the tooth 10a moves from the inner end to the outer end, and the temperature rises. It can be seen that the area is moving as well. However, it is difficult to evaluate the variation in the tooth contact area (meshing area) in the state of the tooth surface in the conventional tooth contact evaluation method using Komyotan. On the other hand, according to the distribution of the tooth surface temperature difference, it can be confirmed from the temperature distribution that there is considerable variation in the contact portion even in the tooth contact region (engagement region).

Thus, the tooth contact can be confirmed by measuring the distribution of the tooth surface temperature difference by the tooth contact evaluation method and apparatus of the gear according to the present embodiment, and the contact portion in the tooth contact region (meshing region) can be confirmed. It becomes possible to check the variation.
In addition, the movement of the tooth contact position shown in FIG. 3 from the inner end to the outer end is such that the gear 10 is a beveled bevel gear and the tooth rigidity is greater on the outer end side than on the inner end side. It occurs because it is expensive.

  By the way, since the gears 10 and 11 used in this test are gradient teeth, considering the strength and gear noise in a high torque region, the tooth contact is in the shape of a tooth profile that tends to approach the inner end. Therefore, the shaft angle error is intentionally given to these gears 10 and 11, and the distribution of the tooth surface temperature difference when the tooth contact is changed at the outer end and the above-mentioned conventional light alumina are used. The tooth surface condition in the tooth contact evaluation method was compared. The results are shown in FIGS. 4 (a) and 4 (b). FIG. 4 (a) shows the state of the tooth surface in the conventional tooth contact evaluation method using the above-mentioned Komyotan, and the line A in the figure is measured by the thermographic camera 30 in the area where the Komyotan is peeled off. The meshing contact line estimated from the distribution data of the tooth surface temperature. FIG. 4B shows the distribution of the tooth surface temperature difference.

  Further, FIG. 5 shows tooth root stress values at respective portions (5 mm, 13 mm, and 20 mm from the inner end) in the tooth line direction of the tooth 10 a of the gear 10. The root stress value is a value measured by attaching a strain gauge to the root fillet of the tooth 10a of the gear 10 (located in Hofer's 30 ° tangent method). If the amount of root strain obtained from a certain strain gauge is large, the load applied to the location located on the tooth surface in the tooth profile direction where the strain gauge is attached will be large, and as a result, the surface pressure at that location will also be Get higher. That is, the higher the tooth root stress value obtained from a certain strain gauge, the higher the surface pressure, and the lower the tooth root stress value, the lower the surface pressure.

  As shown in FIGS. 4 (a) and 4 (b), in the state of the tooth surface in the conventional tooth contact evaluation method using Komichitan, the meshing region depends on the outer end of the tooth surface, but the tooth surface temperature difference In the distribution, the meshing area is slightly outside the center. As shown to Fig.4 (a), in the state of the tooth surface in the conventional tooth-contact evaluation method using Komichitan, it is the meshing start that the meshing area has approached the outer end and the tooth tip.

However, as shown in FIG. 5, the tooth root stress value at the outer end at the beginning of meshing is almost zero, and the tooth root stress value at the inner end is high. Therefore, in practice, it can be seen that the load applied to the tooth surface of the tooth 10a at this time is distributed in the center of the tooth surface, and the load at the outer end is extremely small.
In this way, in the state of the tooth surface in the conventional tooth contact evaluation method using Komyotan, the part of the tooth tip at the outer end has been peeled off due to the thickness of Komyotan, or the tooth surface is in contact. However, almost no load is considered.

On the other hand, as shown in FIG. 4B, according to the tooth surface temperature measurement result (distribution of tooth surface temperature difference) in the gear tooth contact evaluation method and apparatus according to this embodiment, it can be evaluated as a meshing region. Since the region where the temperature is rising is present in the central portion of the tooth surface and the temperature at the outer end is hardly increased, it can be evaluated that the surface pressure is extremely small at the outer end.
Thus, the tooth contact temperature measurement result (distribution of tooth surface temperature difference) in the tooth contact evaluation method and apparatus of the gear according to the present embodiment evaluates the tooth contact that matches the result of the tooth root stress value shown in FIG. Thus, the meshing area and the surface pressure of the gear can be accurately grasped.

  Next, we compared the distribution of the tooth surface temperature difference when the torque of the pair of gears 10 and 11 is changed with the state of the tooth surface in the above-described conventional tooth contact evaluation method using Komyotan. . The results are shown in FIGS. 6 (a1), (a2), (b1), (b2), (c1), and (c2). 6 (a1), (a2), (b1), (b2), (c1), and (c2), the left figure (that is, the figure with the reference number 1) is the above-mentioned conventional light-colored light. The state of the tooth surface in the tooth contact evaluation method using No. 1 is shown, and the diagram on the right side (that is, the figure with the number 2) shows the distribution of the tooth surface temperature difference. 6 (a1) and (a2) show when the torque is 98 Nm, FIGS. 6 (b1) and (b2) show when the torque is 68.8 Nm, and FIGS. 6 (c1) and (c2) show the torque. Indicates 49 Nm. These torque fluctuations were performed by controlling the rotational speed of the gear 11 by the torque application motor 21 so that the rotational speed of the gear 11 is slower than the rotational speed of the gear 11 driven by the gear 10.

  As shown in FIG. 6, the meshing area (meshing area) increases with an increase in torque both in the distribution of the tooth surface temperature difference and in the state of the tooth surface in the conventional tooth contact evaluation method using Komichitan. In particular, in the distribution of the tooth surface temperature difference, it can be clearly seen that the meshing area increases as the torque increases. Compared with this, there is not much change in the tooth surface state in the conventional tooth contact evaluation method using Komyotan. This is considered that the light agitation was peeled off during the period from the start of the gears 10 and 11 to the torque stable range (here, about 30 seconds), and no change due to torque was observed.

As described above, the tooth surface temperature measurement result (distribution of tooth surface temperature difference) in the gear tooth contact evaluation method and apparatus according to this embodiment is also effective when evaluating changes in tooth contact due to torque fluctuations.
Furthermore, in order to confirm that the surface pressure can be evaluated based on the distribution of the tooth surface temperature of the gear, in the tooth root stress value of the gears 10 and 11 and the tooth contact evaluation method and apparatus of the gear according to the present embodiment. The tooth surface temperature measurement results (tooth surface temperature difference distribution) were compared and examined focusing on the number of simultaneously meshed gears 10 and 11. FIG. 7A is a diagram showing the root stress value in the central portion of the tooth 10a of the gear 10 at the time of meshing, and FIG. 7B is a diagram showing the distribution of the tooth surface temperature difference of the tooth 10a at this time. is there.

  Since the actual meshing rate of the pair of gears 10 and 11 is about 1.4, the number of meshing state (the number of simultaneous meshing) between the teeth of the gear 10 and the teeth of the gear 11 is as shown in FIG. The meshing number state (simultaneous meshing number) includes a case of one sheet and a case of two sheets. Further, as shown in FIG. 7B, this meshing number state is on the distribution of the tooth surface temperature difference as meshing contact lines A1 to A4 estimated from the tooth surface temperature distribution data measured by the thermography camera 30. Can show. That is, the region sandwiched between the meshing contact lines A1 and A2 and the region sandwiched between the meshing contact lines A3 and A4 on the distribution of the tooth surface temperature difference indicate regions where the number of meshing states is one meshing state, A region sandwiched between the meshing contact lines A2 and A3 indicates a region where the number of meshed states is a meshed state. A method for determining the meshing number state will be described later as an explanation of the meshing number region dividing means 52 of the second embodiment described below.

  Here, comparing FIGS. 7 (a) and 7 (b), when the tooth root stress value in FIG. 7 (a) is seen, a high tooth root stress value is shown in one meshing region, and FIG. 7 (b). Also in the distribution of the tooth surface temperature difference, a high temperature is shown in the area where one piece is engaged. On the contrary, in the meshing area of the two sheets, the root stress value shows a low value, and the distribution of the tooth surface temperature difference shows a low temperature. This is considered to be because the load of the single-mesh area is shared by one tooth and the surface pressure is double that of the double-mesh condition.

From the above results, in the region where the tooth root stress value is high, that is, the region where the surface pressure is high, the tooth surface temperature difference is also high, and it is possible to grasp the strength of the surface pressure by checking the temperature distribution. it can.
As described above, according to the gear tooth contact evaluation method and apparatus of the present embodiment, the gears 10 and 11 rotate while meshing with each other, and a load is applied to the tooth surfaces of the gears 10 and 11, thereby applying the tooth surfaces. The tooth surface temperature is relatively increased based on the distribution of the tooth surface temperature difference before and after the rotation, utilizing the fact that the temperature of the tooth surface to which the lubricating oil is sheared increases. The area where the contact is made is evaluated as the meshing area, and the higher the tooth surface temperature is, the higher the surface pressure is evaluated. For this reason, it is possible to reliably prevent a portion where the tooth surfaces are not originally in contact with each other from being erroneously determined as the meshing region, and further to determine the strength of the surface pressure within the meshing region. Evaluation can be performed with high accuracy.

  In the gear tooth contact evaluation method and apparatus according to the present embodiment, the distribution of the tooth surface temperature of the tooth 10a is measured in a non-contact manner using the thermography camera 30, so that the measurement can be performed in a short measurement time. Further, since the emissivity of the thermographic camera 30 is calibrated in the emissivity calibration step S11, the influence of the tooth surface properties of the teeth 10a or the application of the lubricating oil can be surely removed, and a gear with higher accuracy can be obtained. Tooth contact evaluation and meshing excitation force estimation can be performed.

In addition, since the lubricating oil is applied to the pair of gears 10 and 11, it is possible to prevent the tooth surfaces of the gears 10 and 11 from being damaged when the gears 10 and 11 mesh with each other in the tooth contact evaluation method and apparatus of this gear. it can.
Further, since the distribution of the tooth surface temperature of the tooth 10a is measured by the thermography camera 30, the influence of the reflected light must be taken into account. In this embodiment, the pre-rotation measured in the pre-rotation tooth surface temperature measurement step S20. Tooth contact evaluation and meshing excitation force based on the difference between the tooth surface temperature distribution of the tooth 10a and the tooth surface temperature distribution of the tooth 10a after the predetermined rotation speed measured in the post-rotation tooth surface temperature measurement step S40 Therefore, the influence of the reflected light from the tooth surface of the tooth 10a on the thermographic camera 30 can be completely removed, and the gear tooth contact evaluation and the gear meshing vibration force estimation can be performed with higher accuracy. Can do.

[Second Embodiment]
Next, a second embodiment of the present invention will be described. FIGS. 8 and 9 show a gear meshing vibration estimation method and apparatus as a second embodiment of the present invention, and FIG. FIG. 9 is a flowchart showing a method for estimating the meshing vibration generating force of the gear.
First, the gear meshing excitation force estimation method and apparatus according to this embodiment will be described.

  As shown in FIG. 8, the gear meshing vibration generating device of the present embodiment is different from the gear tooth contact evaluation device of the first embodiment described above with reference to FIG. 20, the torque applying motor 21, the thermographic camera (tooth surface temperature measuring means) 30, the photo sensor 31, and the camera control unit 32 are configured with the same components, and only the configuration of the arithmetic unit 50 is different. Therefore, detailed description of the common parts is omitted here. In FIG. 8, the same reference numerals as those in FIG.

The arithmetic unit 50 of the gear meshing vibration generating device of this embodiment includes a tooth surface temperature difference calculating unit 51, a meshing number region dividing unit 52, an inter-region temperature difference calculating unit 53, and a meshing vibration force estimating unit 54. And a display means 57.
Here, the distribution of the increase in the tooth surface temperature of the tooth 10a of the gear 10 caused by the rotation of the gears 10, 11 by the thermography camera (tooth surface temperature measuring means) 30 and the tooth surface temperature difference calculating means 51 is shown. Tooth surface temperature rise detecting means for detecting is configured.

  The tooth surface temperature difference calculating means 51 is the same as the tooth surface temperature difference calculating means 41 in the gear tooth contact evaluation apparatus of the first embodiment shown in FIG. That is, the tooth surface of the tooth 10a of the gear 10 measured in the pre-rotation tooth surface temperature measurement step S20 and the post-rotation tooth surface temperature measurement step S40 in the gear tooth contact evaluation method of the present embodiment described later with reference to FIG. The distribution of the temperature difference (the distribution of the tooth surface temperature rise) is calculated.

  The meshing number area dividing unit 52 divides the distribution of the tooth surface temperature difference calculated by the tooth surface temperature difference calculating unit 51 for each simultaneous meshing number (meshing number state) of the teeth 10a of the gear 10 with the teeth of the gear 11. To do. The division for each simultaneous meshing number is obtained in advance by attaching a strain gauge to the tooth base (tooth root fillet portion) of the tooth 10a of the gear 10 and measuring the strain gauge while rotating in a state of engaging with the gear 11. The meshing rate calculated from the obtained tooth root stress value, the ratio of the time for each meshing number calculated based on this meshing rate, and the meshing estimated from the tooth surface temperature distribution data measured by the thermography camera 30 This is done by determining the point at which the number of simultaneous meshes changes from the relationship with the contact line.

The meshing rate is defined as a time from the start of meshing corresponding to the stress rising start point represented by the root stress value to the meshing end corresponding to the stress falling end point, and a pitch movement time of the tooth 10a being b. , A is divided by b.
In addition, if the value of the meshing rate is 1 or more and 2 or less, it indicates that the number of simultaneous meshing is one region and two regions, and the region (time) in which the meshing number is two is: The following formula (1) is used, and the region (time) in which the number of meshed one piece is one is calculated by the following formula (2).

Two-sheet meshing area (time) = (a / b−1) × a (1)
One-sheet meshing area (time) = [1− (a / b−1)] × a (2)
The inter-region temperature difference calculation unit 53 calculates the temperature difference between adjacent regions in the distribution of tooth surface temperature differences divided into regions for each simultaneous meshing number.
The meshing excitation force estimating means 54 calculates the temperature difference between the regions for each adjacent simultaneous meshing number in the distribution of the tooth surface temperature difference divided into the regions for each simultaneous meshing number calculated by the interregional temperature difference calculating unit 53. On the basis of this, the meshing vibration force is estimated. The meshing vibration force estimation means 54 includes a meshing vibration force storage unit 55 and a meshing vibration force estimation unit 56.

The meshing excitation force storage unit 55 displays a correspondence map (not shown) between the temperature difference between the regions for each adjacent simultaneous meshing number and the meshing excitation force (not shown) for each tooth surface region where the temperature difference has occurred, here. These are held for each of the three regions of the inner end portion of the tooth surface, the central portion of the tooth surface, and the outer end portion of the tooth surface.
Note that the values of the above three correspondence maps held in the meshing excitation force storage unit 55 are the values of the meshing excitation force according to the temperature difference between the regions for each adjacent simultaneous meshing number obtained empirically. A value calculated based on meshing transmission error (MTE) which is one index is adopted. The relationship between the temperature difference between the regions for each adjacent simultaneous meshing number and the meshing transmission error will be described later with reference to FIG.

The meshing vibration force estimation unit 56 calculates the temperature difference between adjacent regions calculated by the inter-region temperature difference calculation unit 53 and the tooth surface of the temperature difference held in the meshing vibration force storage unit 55. The meshing excitation force is estimated based on the corresponding map corresponding to the upper region (that is, the region of the tooth surface of the inner end portion, the central portion, or the outer end portion).
The display means 57 is for displaying the meshing vibration force estimated by the meshing vibration force estimation means 54.

  Next, the gear meshing excitation force estimation method of this embodiment will be described. As shown in FIG. 9, the gear meshing excitation force estimation method according to the present embodiment includes the gear tooth contact evaluation method according to the first embodiment described above with reference to FIG. The temperature difference calculation step S50 is the same, and the meshing number region dividing step S61, the inter-region temperature difference calculation step S70, and the meshing excitation force estimation step S80 are different. Therefore, the detailed description of the lubricant application step S10 to the tooth surface temperature difference calculation step S50 is omitted. In FIG. 9, the same reference numerals as those in FIG.

  That is, in the gear meshing excitation force estimation method of the present embodiment, the meshing number area dividing step 52 of the arithmetic unit 50 causes the tooth surface of the arithmetic unit 50 in the tooth surface temperature difference calculating step S50 by the meshing number area dividing means 52 of the arithmetic unit 50. The distribution of the tooth surface temperature difference of the teeth 10a of the gear 10 calculated by the temperature difference calculating means 51 is divided for each number of simultaneous meshes with the teeth of the gear 11 of the teeth 10a of the gear 10.

Next, in the inter-region temperature difference calculating step S70, the inter-region temperature difference calculating unit 53 uses the inter-region temperature difference calculating unit 53 to calculate the difference between the adjacent regions in the tooth surface temperature difference distribution divided into regions for each simultaneous mesh number. Calculate the temperature difference.
Then, in the meshing vibration force estimation step S80, the meshing vibration force estimation unit 56 of the meshing vibration force estimation means 54 calculates the temperature difference between adjacent regions calculated in the interregion temperature difference calculation step S70, and the meshing. The meshing vibration force is estimated based on the correspondence map in the vibration force storage unit 55.

  Here, the rotation is caused by the rotation of the gears 10 and 11 by the tooth surface temperature measurement step S20 before rotation, the gear rotation step S30, the tooth surface temperature measurement step S40 after rotation, and the tooth surface temperature difference calculation step S50. A tooth surface temperature increase detecting step for detecting a tooth surface temperature increase distribution of the tooth 10a of the gear 10 is configured, and the above tooth surface temperature difference distribution calculated in the tooth surface temperature difference calculating step S50 is the tooth surface temperature increase distribution. Corresponds to the distribution.

  Here, the estimation basis in the meshing vibration force estimation step S72 of the gear meshing vibration force estimation method according to the present embodiment is confirmed, that is, the meshing vibration force storage unit 55 of the gear meshing vibration force estimation device. A test conducted to confirm the basis of the correspondence between the temperature difference between the regions for each adjacent simultaneous meshing number and the meshing excitation force in the correspondence map for each meshing region held in the above will be described.

This test verifies the relationship between the mesh transmission error (MTE) as one index of the meshing excitation force and the temperature difference between the regions for each adjacent simultaneous meshing number based on FIG. 7B described above. The results are shown in FIG.
Incidentally, as described above, the meshing transmission error (MTE) is highly correlated with the meshing vibration force as one index of the meshing vibration force. Further, it is known that the meshing transmission error (MTE) generally varies depending on the torque variation and the position of the meshing region on the tooth surface. It is known that the primary component of the meshing transmission error (MTE) increases when the amount of change in the load applied to the tooth surface when the two sheets are meshed is large.

  Therefore, in this test, the temperature difference between the one-meshing area and the two-meshing area, and each area on the tooth surface of the tooth 10a where the temperature difference has occurred (here, the inner end area and the outer end area). The relationship with the meshing transmission error in each region) was verified. Note that the variation in the meshing transmission error (MTE) in FIG. 10 is due to the variation in torque, and as the torque increases, the meshing transmission error (MTE) also increases.

  As shown in FIG. 10, the change in meshing transmission error (MTE) due to torque is larger in the inner end region than in the outer end region. This is because the gears 10 and 11 used in this test are beveled bevel gears as described above, and therefore, the bending rigidity of the teeth is higher as the outer end portion is increased. As a result, the meshing transmission error (MTE) is increased at the outer end portion. ) Is considered to have decreased. Further, in both the inner end portion and the outer end portion, the temperature difference increases as the meshing transmission error (MTE) increases. However, even with the same meshing transmission error (MTE) of about 40 seconds, the temperature difference is larger at the outer end portion than at the inner end portion. From this, it can be considered that the effect of the meshing transmission error (MTE) is that the shift of the position of the meshing region on the tooth surface is larger than the fluctuation of the load applied to the tooth surface.

  From the above results, in the distribution of the tooth surface temperature difference divided into regions for each number of simultaneous meshes, if the region (meshing region) on the tooth surface of the tooth 10a where the temperature difference occurs is the same position (region). By obtaining a correspondence relationship between the temperature difference between adjacent regions and the mesh transmission error (MTE) in advance, the mesh transmission error (MTE) can be grasped from the temperature difference. Therefore, the meshing excitation force that can be obtained based on the meshing transmission error (MTE) can also be estimated for each region on the tooth surface of the tooth 10a where the temperature difference has occurred.

  As described above, according to the gear meshing excitation force estimation method and apparatus of this embodiment, the load applied to the tooth surfaces of the gears 10 and 11 causes the lubricating oil applied to the tooth surfaces to be sheared. As a result, the temperature of the tooth surface where the lubricating oil is sheared rises and the number of simultaneous meshes changes, resulting in a change in the shear resistance of the lubricating oil applied to the tooth surface, and the temperature on the tooth surface. Utilizing the fact that a difference (distribution of increase in tooth surface temperature) is caused, the distribution of the tooth surface temperature difference of the teeth 10a before and after the rotation of the gears 10 and 11 is divided into regions for each simultaneous meshing number, and divided adjacent The temperature difference between the regions for each simultaneous meshing number is calculated, and the correspondence map of the meshing excitation force storage unit 55 is calculated based on the temperature difference and the region on the tooth surface of the tooth 10a where the temperature difference has occurred. Gear 10 and 11 meshing It is possible to estimate the vibratory force with high precision.

  Furthermore, according to the gear meshing excitation force estimation method and apparatus of the present embodiment, the first configuration described above has the same configuration (common part) as the gear tooth contact evaluation method and apparatus according to the first embodiment described above. In the embodiment, it is possible to obtain the same function and effect as those obtained by the same configuration.

[Third Embodiment]
Next, a third embodiment of the present invention will be described. FIG. 11 and FIG. 12 show a gear meshing excitation force estimating method and apparatus as a third embodiment of the present invention, and FIG. FIG. 12 is a flowchart showing a method for estimating the meshing vibration generating force of the gear.

  The gear meshing vibration estimation device of the present embodiment estimates a meshing transmission error (MTE), which is one index of the meshing vibrational force, and based on this meshing transmission error (MTE), As shown in FIG. 11, only the configuration of the meshing vibration estimation means 54a of the arithmetic unit 50a is the same as that of the gear meshing vibration estimation apparatus of the second embodiment described above. Is different. As for the meshing excitation force estimation method of the present embodiment, as shown in FIG. 12, only the meshing transmission error estimation step S81 and the meshing excitation force estimation step S82 are performed as described above. It is different from the method for estimating the vibration force. Therefore, the detailed description of common parts with the second embodiment described above is omitted here. 11, the same reference numerals as those in FIG. 8 indicate the same elements, and in FIG. 12, the same reference numerals as those in FIG. 9 indicate the same elements.

As shown in FIG. 11, the meshing vibration estimation device of this embodiment is similar to the second embodiment described above in that the drive motor 20, the torque application motor 21, the thermography camera 30, the photo sensor 31, and the camera A control unit 32 is provided, and an arithmetic unit 50a is further provided.
The arithmetic unit 50a includes a tooth surface temperature difference calculating means 51, a meshing number area dividing means 52, an inter-area temperature difference calculating section 53, a meshing vibration force estimating means 54a, and a display means 57. Yes. Here, the tooth surface temperature difference calculating means 51, the meshing number area dividing means 52, the inter-area temperature difference calculating section 53, and the display means 57 are the same as those in the second embodiment described above, and therefore will be described in detail. Is omitted.

  The meshing vibration force estimation means 54a includes a meshing transmission error storage unit 58, a meshing transmission error estimation unit 59, and a meshing vibration force estimation unit 56a. The meshing transmission error storage unit 58 is adjacent to the meshing transmission error storage unit 58. A correspondence map (not shown) between the temperature difference between the regions for each simultaneous meshing number and the meshing transmission error (MTE) is shown for each tooth surface region where the temperature difference occurs, here, the inner end portion of the tooth surface, It is held for each of the three regions of the central portion of the tooth surface and the outer end portion of the tooth surface. Note that the above three correspondence maps held in the meshing transmission error storage unit 58 are obtained empirically.

Then, the meshing transmission error estimation unit 59 calculates the temperature difference between adjacent regions calculated by the inter-region temperature difference calculation unit 53 and the tooth difference of the temperature difference held in the meshing transmission error storage unit 58. The meshing transmission error (MTE) is estimated based on the correspondence map corresponding to the region (that is, the region of the tooth surface of the inner end portion, the central portion, or the outer end portion).
The meshing excitation force estimation unit 56a estimates the meshing excitation force according to the value of the meshing transmission error (MTE) estimated by the meshing transmission error estimation unit 59. That is, if the meshing transmission error (MTE) is large according to the numerical value of the meshing transmission error (MTE) estimated on the basis of the correspondence map, the meshing vibration estimation unit 56a has a large meshing vibration force and meshing transmission. If the error (MTE) is small, it is estimated that the meshing vibration force is also small.

Next, the gear meshing excitation force estimation method of this embodiment will be described.
As shown in FIG. 12, the gear meshing excitation force estimation method of the present embodiment is the same as the gear meshing excitation force estimation method of the second embodiment shown in FIG. The calculation is the same up to the calculation step S70, and only the meshing transmission error estimation step S71 and the meshing excitation force estimation step S82 are different. Accordingly, detailed description of the lubricant application step S10 to the inter-region temperature difference calculation step S70 is omitted here.

That is, in the gear meshing excitation force estimation method of the present embodiment, in the meshing transmission error estimation step S81, the meshing transmission error estimation unit 59 of the meshing vibration force estimation means 54a calculates in the inter-region temperature difference calculation step S70. Further, the mesh transmission error (MTE) is estimated based on the temperature difference between adjacent regions and the corresponding map in the mesh transmission error storage unit 58.
Then, in the meshing vibration force estimation step S82, the meshing vibration force estimation unit 56a of the meshing vibration force estimation means 54a performs the meshing based on the mesh transmission error (MTE) estimated in the meshing transmission error estimation step S81. If the transmission error (MTE) is large, the meshing vibration force is large. If the meshing transmission error (MTE) is small, it is estimated that the meshing vibration force is small.

  Thus, according to the gear meshing excitation force estimation method and apparatus of the present embodiment, based on the temperature difference between adjacent regions in the distribution of tooth surface temperature differences divided into regions for each simultaneous meshing number, In order to estimate the meshing transmission error (MTE), which is one index of the meshing excitation force of the gears 10 and 11, and estimate the magnitude of the meshing excitation force based on this meshing transmission error, the second embodiment described above is used. It is possible to obtain the same operation and effect as the gear meshing excitation force estimation method and apparatus.

[Fourth Embodiment]
Next, a fourth embodiment of the present invention (related technology of the present invention) will be described. FIGS. 13 and 14 show a gear tooth contact evaluation method and apparatus according to a fourth embodiment of the present invention. 13 is a schematic diagram showing the functional configuration, and FIG. 14 is a flowchart showing a gear tooth contact evaluation method. In FIG. 13, the same reference numerals as those in FIG. 1 indicate the same elements, and in FIG. 14, the same reference numerals as those in FIG. 2 indicate the same elements.

  The gear tooth contact evaluation method and apparatus according to the present embodiment is based on the distribution of the tooth surface temperature difference of the tooth 10a before and after the rotation, like the gear tooth contact evaluation method and apparatus according to the first embodiment described above. Rather than evaluating the tooth contact of 10 and 11, only the tooth surface temperature distribution of the tooth 10a after rotation is measured, and the tooth contact of the gears 10 and 11 is evaluated based on the tooth surface temperature distribution after rotation. To do.

  Therefore, as shown in FIG. 13, the gear tooth contact evaluation device of this embodiment is similar to the gear tooth contact evaluation device of the first embodiment shown in FIG. A thermography camera 30, a photo sensor 31, and a camera control unit 32 are provided. Detailed descriptions of these common parts are omitted.

Here, the thermographic camera (tooth surface temperature measuring means) 30 is configured as a tooth surface temperature rise detecting means for detecting the distribution of the tooth surface temperature rise of the tooth 10a of the gear 10 caused by the rotation of the gears 10 and 11. Is done.
And the arithmetic unit 40a concerning the gear tooth-contact evaluation apparatus of this embodiment is comprised only with the tooth-contact evaluation means 42a.

  This tooth contact evaluation means 42a is measured by the thermographic camera 30 and received from the camera control unit 32 in the post-rotation tooth surface temperature measurement step S31 in the gear tooth contact evaluation method of the present embodiment described later with reference to FIG. The tooth contact evaluation of the gears 10 and 11 is performed based on the tooth surface temperature distribution (tooth surface temperature increase distribution) of the rotated tooth 10a. That is, the tooth contact evaluation means 42a evaluates a region having a relatively high tooth surface temperature as a meshing region based on the tooth surface temperature distribution in the tooth 10a after rotation, and the tooth surface temperature is relatively high. The tooth contact evaluation of the gears 10 and 11 is performed by evaluating that the higher the surface pressure is, the higher.

  Next, the gear tooth contact evaluation method of this embodiment will be described. As described above, in the gear tooth contact evaluation method of the present embodiment, unlike the first embodiment described above, the measurement of the tooth surface temperature of the tooth 10a before the rotation (the rotation front tooth surface temperature measurement step S20 of FIG. 1). Therefore, without calculating the distribution of the tooth surface temperature difference before and after rotation (tooth surface temperature difference calculating step S50 in FIG. 1), only the distribution of the tooth surface temperature of the tooth 10a after rotation is measured. Thus, the tooth contact evaluation is performed based on the tooth surface temperature distribution.

  Therefore, as shown in FIG. 14, in the gear tooth contact evaluation method of the present embodiment, in the lubricating oil application step S10, the tooth surface of at least one gear (here, gear 10) of the pair of gears 10 and 11 meshing with each other. Lubricating oil is applied to the film, and then the emissivity of the thermographic camera 30 is calibrated in an emissivity calibration step S11. Note that the lubricant application step S10 and the emissivity calibration step S11 are the same as the lubricant application step S10 and the emissivity calibration step S11 according to the first embodiment described above, and thus detailed description thereof is omitted here.

Then, after the emissivity calibration step S11 after the lubricant application step S10, the gears 10, 11 are rotated by a predetermined number of revolutions in the gear rotation step S21. This gear rotation step S21 is a step corresponding to the gear rotation step S30 according to the first embodiment described above with reference to FIG.
Next, in the post-rotation tooth surface temperature measurement step S31, the distribution of the tooth surface temperature of the tooth 10a of the gear 10 is measured. This post-rotation tooth surface temperature measurement step S31 is a step corresponding to the post-rotation tooth surface temperature measurement step S40 according to the first embodiment described above with reference to FIG. Here, the tooth surface temperature for detecting the distribution of the tooth surface temperature rise of the tooth 10a of the gear 10 caused by the rotation of the gears 10, 11 by the gear rotation step S21 and the post-rotation tooth surface temperature measurement step S31. A rise detection step is configured.

Then, in the tooth contact evaluation step S41, the tooth surface temperature distribution after the rotation of the tooth 10a measured in the post rotation tooth surface temperature measurement step S31 by the tooth contact evaluation means 42a of the arithmetic unit 40a (the distribution of the tooth surface temperature rise). ), The region having a relatively high tooth surface temperature is evaluated as the meshing region, and the surface pressure is evaluated to be higher as the tooth surface temperature is relatively higher.
As described above, according to the gear tooth contact evaluation method and apparatus of the present embodiment, it is possible to obtain the same effects as those of the first embodiment described above.

However, in the gear tooth contact evaluation method and apparatus of the present embodiment, since the tooth contact evaluation is not performed based on the distribution of the tooth surface temperature difference before and after the rotation, the tooth contact of the tooth 10a of the gear 10 with respect to the thermography camera 30 is determined. The effect of reflected light cannot be completely removed.
However, if the gears 10 and 11 that are the object of the gear tooth contact evaluation method and apparatus of the present embodiment are gears that do not have a torsion angle of a gear such as a spur gear, for example, the tooth surface of the tooth 10a with respect to the thermography camera 30 There is almost no influence of the reflected light from the gears, and the gear tooth contact evaluation and the meshing excitation force estimation can be performed with high accuracy. Of course, even when the torsion angles of the target gears 10 and 11 are small, the gear tooth contact evaluation can be performed with a certain degree of accuracy.

  Therefore, when the torsion angle of the target gears 10 and 11 is not large or small, according to the gear tooth contact evaluation method and apparatus of the present embodiment, the rotation of the teeth 10a in the first embodiment is performed. The step of measuring the tooth surface temperature distribution (refer to the tooth surface temperature measurement step S20 before rotation in FIG. 1) and the step of calculating the distribution of the tooth surface temperature difference before and after rotation (see the tooth surface temperature difference calculation step S50 in FIG. 1). Therefore, the tooth contact evaluation of the gear can be performed more efficiently than in the first embodiment.

[Fifth Embodiment]
Next, a fifth embodiment of the present invention will be described. FIG. 15 and FIG. 16 show a gear meshing vibration estimation method and apparatus as a fifth embodiment of the present invention, and FIG. FIG. 16 is a flowchart showing a method for estimating the meshing vibration generating force of the gear. 15, the same reference numerals as those in FIG. 8 indicate the same elements, and in FIG. 16, the same reference numerals as those in FIG. 9 indicate the same elements.

  The gear meshing excitation force estimation method and apparatus according to the present embodiment is similar to the gear tooth contact evaluation method and apparatus according to the fourth embodiment described above, and the gear meshing excitation force estimation according to the second embodiment described above. Unlike the method and apparatus, the meshing vibration force of the gears 10 and 11 is not estimated based on the distribution of the tooth surface temperature difference between the teeth 10a before and after the rotation, but only the tooth surface temperature distribution of the teeth 10a after the rotation. , And the meshing excitation force of the gears 10 and 11 is estimated based on the tooth surface temperature distribution after the rotation. Here, the thermographic camera (tooth surface temperature measuring means) 30 is configured as a tooth surface temperature rise detecting means for detecting the distribution of the tooth surface temperature rise of the tooth 10a of the gear 10 caused by the rotation of the gears 10 and 11. Is done.

Therefore, as shown in FIG. 15, in the calculation unit 50b in the gear meshing excitation force estimation device of the present embodiment, the rotation measured by the thermography camera 30 and received from the camera control unit 32 by the meshing number region dividing means 52b. The tooth surface temperature distribution of the subsequent tooth 10a (the tooth surface temperature rise distribution) is divided into regions for each simultaneous meshing number. Then, the inter-region temperature difference calculation means 53 calculates the temperature difference between the regions for each adjacent mesh number based on the distribution of the tooth surface temperature of the tooth 10a after rotation divided by the mesh number region dividing means 52b. The meshing vibration force estimation means 54 estimates the meshing vibration force.
In addition, since the structure of the meshing vibration force estimation means 54 in the meshing vibration force estimation apparatus of this embodiment is the same as that of 2nd Embodiment mentioned above, the detailed description is abbreviate | omitted here.

Next, the gear meshing excitation force estimation method of this embodiment will be described.
As shown in FIG. 16, the gear meshing excitation force estimation method according to the present embodiment performs the tooth contact evaluation of the gear according to the fourth embodiment described above from the lubricating oil application step S <b> 10 to the post-rotation tooth surface temperature measurement step S <b> 31. Since it is similar to the method, its detailed description is omitted. Here, the tooth surface that detects the distribution of the tooth surface temperature increase of the tooth 10a of the gear 10 caused by the rotation of the gears 10, 11 by the gear rotation step S21 and the post-rotation tooth surface temperature measurement step S31. A temperature rise detection step is configured.

In the gear meshing excitation force estimation method of this embodiment, the tooth surface temperature distribution (tooth surface) of the tooth 10a after rotation measured in the tooth surface temperature measurement step S31 after rotation in the meshing number region dividing step S42. The temperature rise distribution) is divided into regions for each simultaneous meshing number.
Next, in the inter-region temperature difference calculating step S51, the temperature difference between the adjacent simultaneous meshing numbers in the tooth surface temperature distribution after rotation divided in the meshing number region dividing step S42 is calculated to estimate meshing excitation force. In step S62, the meshing excitation force is estimated based on the temperature difference. The inter-region temperature difference calculating step S51 corresponds to the inter-region temperature difference calculating step S70 in the second embodiment shown in FIG. 9, and the meshing excitation force estimating step S62 is the same as that shown in FIG. This corresponds to the meshing excitation force estimation step S80 in the second embodiment.

Thus, according to the gear meshing excitation force estimation method and apparatus of the present embodiment, the same operational effects as those of the second embodiment described above can be obtained.
However, in the gear meshing vibration estimation method and apparatus according to the present embodiment, the tooth contact evaluation and the meshing vibration estimation are not performed based on the distribution of the tooth surface temperature difference before and after the rotation. The influence of the reflected light from the tooth surface of the tooth 10a cannot be completely removed.

  However, if the gears 10 and 11 that are targets of the gear meshing excitation force estimation method and apparatus according to the present embodiment are gears that do not have a twist angle of a gear such as a spur gear, for example, the teeth 10a of the thermography camera 30 There is almost no influence of reflected light from the tooth surface, and the gear tooth contact evaluation and meshing vibration force estimation can be performed with high accuracy. Of course, even when the torsion angles of the gears 10 and 11 are small, the gear tooth contact evaluation and the meshing excitation force estimation can be performed with a certain degree of accuracy.

  Therefore, when the torsion angle of the gears 10 and 11 as a target is not large or small, according to the gear meshing excitation force estimating method and device of the present embodiment, the tooth 10a in the second embodiment described above is used. Step of measuring tooth surface temperature distribution before rotation (refer to tooth surface temperature measurement step S20 before rotation in FIG. 9) and step of calculating distribution of tooth surface temperature difference before and after rotation (tooth surface temperature difference calculation step S50 in FIG. 9) Therefore, the tooth contact evaluation and the meshing excitation force estimation can be performed more efficiently with a shorter time compared to the second embodiment described above.

[Others]
The gear tooth contact evaluation method and apparatus and the gear meshing vibration estimation method and apparatus according to the present invention have been described above as related techniques of the present invention, but the present invention is not limited to such embodiments. However, various modifications can be made without departing from the spirit of the present invention.
For example, in the above-described embodiment, when estimating the meshing vibration force, the meshing vibration force or meshing transmission error, and the temperature difference between adjacent meshing regions in the tooth surface temperature distribution divided for each simultaneous meshing number The meshing excitation force or meshing transmission error is estimated using the corresponding map, but the present invention is not limited to this. For example, when the meshing vibration force estimation means does not have such a correspondence map and the meshing vibration force estimation means estimates the meshing vibration force, the adjacent tooth surface temperature distribution divided by the number of simultaneous meshing is adjacent. If the temperature difference between the meshing regions is large, the meshing vibration force may be large, and if the temperature difference is small, it may be estimated that the meshing vibration force is small.

Further, the tooth surface temperature rise detection means in the gear tooth contact evaluation method and apparatus and the gear meshing vibration estimation method and apparatus according to the present invention are limited to the above-described embodiments. In particular, the tooth surface temperature rise distribution is not measured by the tooth surface temperature difference before and after the rotation as in the tooth surface temperature rise detection means of the first and second embodiments described above. If the detection device capable of directly detecting the distribution of the temperature increase of the tooth surface of the gear 10 (the temperature change of the tooth surface) caused by the rotation of the gears 10 and 11 can be used as the tooth surface temperature increase detection means, such detection is possible. You may comprise by an apparatus.

It is a schematic diagram which shows the function structure of the gear tooth-contact evaluation apparatus as 1st Embodiment of this invention. It is a flowchart which shows the tooth-contact evaluation method of the gear as 1st Embodiment of this invention. It is a figure which shows the temperature measurement result of the tooth surface in the gear tooth contact evaluation method and apparatus as a related technology of the present invention, and the state of the tooth surface in the conventional tooth contact evaluation method using Komyotan, FIG. (A1), (a2) is a diagram when the meshing region is generated at the inner end portion of the tooth surface, and FIGS. 3 (b1), (b2) are diagrams when the meshing region is generated at the central portion of the tooth surface, FIG. 3 (c1) and (c2) are diagrams when the meshing region is generated at the outer end portion of the tooth surface. It is a figure which shows the temperature measurement result of the tooth surface in the tooth contact evaluation method and apparatus as a related technology of the present invention, and the state of the tooth surface in the conventional tooth contact evaluation method using Komyotan, FIG. (A) is a figure which shows the state of the tooth surface in the tooth-contact evaluation method using the conventional Mitsumetan when changing a tooth-contact to the outer end of a tooth surface, FIG.4 (b) is a figure of a tooth surface. It is a figure which shows the temperature measurement result of the tooth surface in the gear tooth-contact evaluation method and apparatus as a related technology of this invention when changing a tooth-contact to an outer end. It is a figure which shows the tooth root stress value for every area | region of a tooth surface when changing a tooth | gear contact at the outer end of the tooth surface in FIG. It is a figure which shows the temperature measurement result of the tooth surface in the gear tooth contact evaluation method and apparatus as a related art of the present invention, and the state of the tooth surface in the conventional tooth contact evaluation method using Kokaridan, and FIG. (A1) and (a2) show the results when the torque between the gears is 98 Nm, and FIGS. 6 (b1) and (b2) show the results when the torque between the gears is 68.8 Nm, and FIG. ) And (c2) are those when the torque between the gears is 49 Nm. FIG. 6 is a diagram showing a gear tooth root stress value for each simultaneous meshing number of gears at the time of gear meshing, and a tooth surface temperature measurement result in a gear tooth contact evaluation method and apparatus as a related technique of the present invention. 7 (a) is a diagram showing a tooth root stress value of the gear for each simultaneous meshing number, and FIG. 7 (b) is a gear tooth contact evaluation method as a related technique of the present invention at the time of meshing shown in FIG. 7 (a). It is a figure which shows the temperature measurement result of the tooth surface in an apparatus. It is a schematic diagram which shows the function structure of the gear meshing excitation force estimation apparatus as 2nd Embodiment of this invention. It is a flowchart which shows the meshing meshing vibration force estimation method as 2nd Embodiment of this invention. The figure which shows the correspondence of a meshing transmission error (MTE) and the temperature difference between the area | regions for every adjacent simultaneous meshing | engagement number of the tooth-contact evaluation method of a gear as a related technique of this invention, and the temperature measurement result of a tooth surface. It is. It is a schematic diagram which shows the function structure of the gear meshing excitation force estimation apparatus as 3rd Embodiment of this invention. It is a flowchart which shows the meshing | meshing excitation force estimation method of the gear as 3rd Embodiment of this invention. It is a schematic diagram which shows the function structure of the gear tooth-contact evaluation apparatus as 4th Embodiment of this invention. It is a flowchart which shows the tooth-contact evaluation method of the gear as 4th Embodiment of this invention. It is a schematic diagram which shows the function structure of the gear meshing excitation force estimation apparatus as 5th Embodiment of this invention. It is a flowchart which shows the meshing | meshing excitation force estimation method of the gearwheel as 5th Embodiment of this invention.

Explanation of symbols

10, 11 Gear 10a Tooth surface 12, 13 Shaft 14 Projection 20 Drive motor (gear rotating means)
21 Torque imparting motor 30 Thermographic camera (tooth surface temperature measuring means)
31 Photo sensor 32 Camera control unit 40, 40a, 50, 50a, 50b Arithmetic unit 41 Tooth surface temperature difference calculating means 42, 42a Tooth contact temperature evaluating means 51 Tooth surface temperature difference calculating means 52, 52b Engagement number area dividing means 53 Between areas Temperature difference calculating means 54, 54a Meshing vibration force estimation means 55 Meshing vibration force storage section 56, 56a Meshing vibration force estimation section 57 Display means 58 Meshing transmission error storage section 59 Meshing transmission error estimation section S10 Lubricating oil application step S11 Emissivity calibration step S20 Pre-rotation tooth surface temperature measurement step S21, S30 Gear rotation step S31, S40 Post-rotation tooth surface temperature measurement step S41, S60 Tooth contact evaluation step S42, S61 Engagement number area division step S50 Tooth surface temperature difference calculation step S51 , S70 Temperature difference calculation process between regions S62 , S80, S82 Meshing vibration force estimating step S81 Meshing transmission error estimating step

Claims (14)

A lubricating oil application step of applying lubricating oil to the tooth surfaces of at least one gear of a pair of gears meshing with each other;
A tooth surface temperature rise detection step of detecting a temperature rise distribution of the tooth surface of the one gear generated by the rotation of the pair of gears after the lubricant application step;
A meshing number region dividing step of dividing the tooth surface temperature increase distribution detected in the tooth surface temperature rising detection step into regions for each simultaneous meshing number;
An inter-region temperature difference calculating step of calculating a temperature difference between adjacent adjacent meshing numbers in the distribution of the tooth surface temperature rise divided in the meshing number region dividing step;
A gear comprising: a meshing excitation force estimation step for estimating a meshing excitation force based on a temperature difference between adjacent adjacent meshing numbers calculated in the interregional temperature difference calculation step. Meshing excitation force estimation method. The tooth surface temperature rise detection step
A gear rotation step of rotating the pair of gears after the lubricant application step;
A post-rotation tooth surface temperature measurement step for measuring the tooth surface temperature distribution of the one gear as the distribution of the tooth surface temperature rise after the gear rotation step;
In the meshing number region dividing step, the tooth surface temperature distribution as the distribution of the tooth surface temperature rise measured in the post-rotation tooth surface temperature measuring step is divided into regions for each simultaneous meshing number, and between the regions In the temperature difference calculating step, the temperature difference of the region for each adjacent simultaneous meshing number in the tooth surface temperature distribution as the distribution of the tooth surface temperature rise divided in the meshing number region dividing step is calculated. The gear meshing excitation force estimation method according to claim 1 . The tooth surface temperature rise detection step
A pre-rotation tooth surface temperature measuring step of measuring the tooth surface temperature distribution of the one gear after the lubricating oil application step;
A gear rotation step of rotating the pair of gears after the rotation front tooth surface temperature measurement step;
A post-rotation tooth surface temperature measurement step of measuring the tooth surface temperature distribution of the one gear after the gear rotation step;
Tooth surface that is the difference between the tooth surface temperature distribution before rotation measured in the pre-rotation tooth surface temperature measurement step and the distribution of tooth surface temperature after rotation measured in the post-rotation tooth surface temperature measurement step A tooth surface temperature difference calculating step for calculating a temperature difference distribution as the above tooth surface temperature rise distribution,
In the meshing number region dividing step, the distribution of the tooth surface temperature difference as the distribution of the tooth surface temperature calculated in the tooth surface temperature difference calculating step is divided into regions for each simultaneous meshing number, and between the regions In the temperature difference calculating step, the temperature difference between the adjacent simultaneous meshing numbers in the tooth surface temperature difference distribution as the distribution of the tooth surface temperature rise divided in the meshing number region dividing step is calculated. The gear meshing excitation force estimation method according to claim 1 . The measurement of the distribution of the tooth surface temperature, and performing a non-contact with respect to the tooth surface, meshing excitation force estimating method according to claim 2 or 3, wherein the gear. 5. The gear meshing excitation force estimation method according to claim 4 , wherein the measurement of the tooth surface temperature distribution is performed using thermography. The gear meshing excitation force estimation method according to any one of claims 1 to 5 , wherein the temperature of the lubricating oil is kept isothermal with room temperature before the tooth surface temperature increase detection step. . The gear meshing excitation force estimation according to any one of claims 1 to 6 , wherein the temperature of the pair of gears is maintained at a temperature equal to room temperature before the tooth surface temperature increase detection step. Method. Gear rotating means for rotating a pair of gears meshed with each other, wherein lubricating oil is applied to the tooth surface of at least one gear;
Tooth surface temperature rise detection means for detecting the temperature rise distribution of the tooth surface of the one gear generated by the pair of gears rotated by the gear rotation means;
Meshing number area dividing means for dividing the distribution of the tooth surface temperature rise detected by the tooth surface temperature rise detecting means into areas for each simultaneous meshing number;
An inter-region temperature difference calculating means for calculating a temperature difference between adjacent meshes in the tooth surface temperature increase distribution divided by the meshing number region dividing unit;
A gear comprising: a meshing excitation force estimating means for estimating a meshing excitation force based on a temperature difference between adjacent adjacent meshing numbers calculated by the inter-region temperature difference calculating means. Meshing vibration estimation device. The tooth surface temperature rise detecting means is
A tooth surface temperature measuring means for measuring the tooth surface temperature distribution of the one gear as the distribution of the tooth surface temperature rise after the pair of gears are rotated by the gear rotating means;
The meshing number region dividing unit divides the tooth surface temperature distribution as the distribution of the tooth surface temperature measured by the tooth surface temperature measuring unit into regions for each simultaneous meshing number, and the temperature difference between the regions. The calculating means calculates a temperature difference between the adjacent simultaneous meshing numbers in the tooth surface temperature distribution as the distribution of the tooth surface temperature rise divided by the meshing number area dividing means. The gear meshing excitation force estimation apparatus according to claim 8 . The tooth surface temperature rise detecting means is
Tooth surface temperature measuring means for measuring the temperature of the tooth surface of the one gear,
The tooth surface temperature distribution measured by the tooth surface temperature measuring means before the pair of gears rotated by the gear rotating means, and the tooth surface temperature measurement after the pair of gears rotated by the gear rotating means. A tooth surface temperature difference calculating means for calculating a tooth surface temperature difference distribution, which is a difference from the tooth surface temperature distribution of the one gear measured by the means, as the tooth surface temperature rise distribution;
The meshing number area dividing means divides the tooth surface temperature difference distribution as the distribution of the tooth surface temperature rise calculated by the tooth surface temperature difference calculating means into areas for each simultaneous meshing number, and between the areas. The temperature difference calculating means calculates the temperature difference between the adjacent simultaneous meshing numbers in the tooth surface temperature difference distribution as the distribution of the tooth surface temperature rise divided by the meshing number area dividing means. The gear meshing excitation force estimation device according to claim 8 . 11. The gear meshing excitation force estimation device according to claim 9 or 10 , wherein the tooth surface temperature measuring means measures the temperature of the tooth surface in a non-contact manner. 12. The gear meshing vibration estimation device according to claim 11 , wherein the tooth surface temperature measuring means is constituted by thermography. Temperature of the lubricating oil before the said pair of gears is rotated by said gear rotating means, characterized in that it is kept at room temperature and isothermal gear according to any one of claims 8-12 Meshing vibration estimation device. Temperature of the pair of gears, before the pair of gears are rotated by the gear rotating means, characterized in that it is kept at room temperature and isothermal, the gear according to any one of claims 8 to 13 Meshing vibration estimation device.

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