Worm gear inspection device and worm gear inspection method

Abstract

To provide a worm gear inspection device capable of inspecting meshing noises on a worm gear alone, and a worm gear inspection method.SOLUTION: A disclosed worm gear inspection device determines whether the worm meshing noise is acceptable or not based on the absolute value of acceleration A that is obtained by second-order differentiation in the displacement amount X in the distance between the rotation shaft of the worm relative to the rotation angle of the mating gear and the rotating shaft of the mating gear, or based on the difference Dx between the maximum value Ap1 and the minimum value Ap2 of acceleration A. With this, the meshing noise of the worm can be inspected before assembling the worm to a product; i.e., at the worm manufacturing stage (manufacturer).SELECTED DRAWING: Figure 7

Description

Technical Field

[0001] The present invention relates to an inspection device for a worm gear and an inspection method for a worm gear.

Background Art

[0002] For example, as a conventional quality inspection of a worm gear described in Patent Document 1 below, conventionally, the meshing noise of the worm gear has been inspected in a state where the worm gear is assembled to a product to which the worm gear is applied.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] However, the conventional inspection method for a worm gear could not inspect the meshing noise of the worm gear unless the worm gear was assembled to a product to which the worm gear was applied. For this reason, there was a disadvantage that the meshing noise could not be inspected at the manufacturing stage (manufacturer) of the worm gear, and there was room for improvement.

[0005] The present invention has been devised in view of such technical problems, and an object thereof is to provide an inspection device for a worm gear and an inspection method for a worm gear that can inspect the meshing noise of the worm gear with the worm gear alone.

Means for Solving the Problems

[0006] In one aspect of the present invention, the quality of the meshing noise of the worm gear is determined by using the absolute value of the acceleration obtained by second-order differentiating the displacement of the axial distance between the rotation axis of the worm and the rotation axis of the mating gear with respect to the rotation angle of the mating gear, or the difference between the maximum value and the minimum value of the acceleration. [Effects of the Invention]

[0007] According to the present invention, the meshing noise of a worm gear can be inspected using the worm gear alone. [Brief explanation of the drawing]

[0008] [Figure 1] This is a plan view of a flow control valve to which the present invention is applied, showing the state with the second housing removed. [Figure 2] This is a cross-sectional view along line AA in Figure 1. [Figure 3] This is a schematic diagram of a worm gear inspection device. [Figure 4] Figure 3 is a magnified perspective view showing the main components of the worm gear inspection device. [Figure 5] Figure 4 is a cross-sectional view along line BB. [Figure 6] Figure 5 is a cross-sectional view along the CC line. [Figure 7] The graphs show the waveforms of each measured value, with (a) the waveform of the displacement of the distance between the rotation axis of the worm and the rotation axis of the mating gear with respect to the rotation angle of the mating gear, (b) the waveform of the velocity obtained by taking the first derivative of the displacement shown in Figure (a), and (c) the waveform of the acceleration obtained by taking the second derivative of the displacement shown in Figure (a). [Modes for carrying out the invention]

[0009] Hereinafter, embodiments of the worm gear inspection device and worm gear inspection method according to the present invention will be described with reference to the drawings. In the embodiments described below, the worm gear to be inspected according to the present invention will be applied to a conventional automobile coolant flow control valve as an example.

[0010] (Worm gear configuration) Figure 1 shows a plan view of the flow control valve CV with the second housing removed and the reduction mechanism 4 exposed. Figure 2 shows a cross-sectional view of the flow control valve CV cut along line AA in Figure 1.

[0011] As shown in Figures 1 and 2, the flow control valve CV to which the worm gear according to this embodiment is applied comprises a valve body 2 housed inside a housing 1, an electric motor 3 that drives the valve body 2, and a reduction mechanism 4 that reduces the rotational force of the electric motor 3 and transmits it to the valve body 2. In other words, the rotational position of the valve body 2 is controlled based on the operating state of an engine (not shown), thereby distributing the cooling water guided to the flow control valve CV to, for example, a heater, oil cooler, radiator, etc. (not shown).

[0012] Housing 1 comprises a first housing 11 that houses a valve body 2 and an electric motor 3, and a second housing (not shown) connected to the first housing 11 that houses a reduction mechanism 4. The first housing 11 has a cylindrical valve body housing portion 111 capable of housing the valve body 2, and a motor housing portion 112 provided in parallel with the valve body housing portion 111 and capable of housing the electric motor 3. The second housing (not shown) is attached to one end of the first housing 11 in the axial direction (the rotation axis direction of the valve body 2 and the electric motor 3) and defines a reduction mechanism housing portion 121 capable of housing the reduction mechanism 4 inside.

[0013] The electric motor 3 is housed in the motor housing 112 with its output shaft 32 facing the second housing (not shown). The electric motor 3 is fixed to the opening edge of the motor housing 112 by a plurality of screws 34 via a flange portion 33 that extends radially outward (in the direction perpendicular to the rotation axis of the electric motor 3) at the end of the motor body 31 on the output shaft 32 side. The electric motor 3 is controlled by an on-board electronic controller (not shown) and rotates the valve body 2 according to the operating state of the vehicle.

[0014] The speed reduction mechanism 4 is composed of a first worm gear 41 and a second worm gear 42, which are two sets of meshing gears. The first worm gear 41 is provided coaxially with the output shaft 32 of the electric motor 3, and includes a first worm 411 that rotates integrally with the output shaft 32, and a first helical gear 412 that is rotatably supported by a first support shaft 43 arranged perpendicular to the output shaft 32 of the electric motor 3 and meshes with the first worm 411. The second worm gear 42 is rotatably supported by a second support shaft 44, and includes a second worm 421 that rotates integrally with the first helical gear 412, and a second helical gear 422 that is fixedly and rotatably integrated with the rotation shaft 20 of the valve body 2 and meshes with the second worm 421.

[0015] Here, the first helical gear 412 and the second helical gear 422 are a composite gear member 40 in which the two gears 412 and 422 are arranged in series and integrally formed. The composite gear member 40 is rotatably supported by a pair of bearing portions 113, 113 of the first housing 11 via the first support shaft 43 and the second support shaft 44 inserted into both axial ends of the composite gear member 40. Thereby, the rotational driving force output from the output shaft 32 of the electric motor 3 is decelerated via the first worm gear 41 and the second worm gear 42 and transmitted to the valve body 2. In this embodiment, the first worm 411 corresponds to the worm according to the present invention, and the first helical gear 412 corresponds to the mating gear according to the present invention.

[0016] FIG. 3 shows a schematic diagram of an inspection device 5 for a worm gear according to this embodiment.

[0017] The inspection device 5 for a worm gear according to this embodiment, as shown in FIG. 3 for example, includes a support base 50 formed in a trapezoidal shape, a fixed support 51 fixed to the support base 50 and rotatably supporting a first worm 411, which is a worm, on a first rotation axis Z1, and a movable support 52 provided so as to be relatively movable with respect to the support base 50 and rotatably supporting a first helical gear 412, which is a mating gear, on a second rotation axis Z2 perpendicular to the first rotation axis Z1.

[0018] The fixed support 51 has a base 511 fixed to the support base 50 and a fixed support portion 512 extending laterally from the base 511 and rotatably supporting the first worm 411. The fixed support portion 512 rotatably supports the first worm 411 on the first rotation axis Z1 via a first support shaft 513 rotatably supported by the fixed support portion 512. A well-known stepping motor 53 provided on the support base 50 is connected to the first support shaft 513 supported by the fixed support portion 512 via a predetermined transmission mechanism (e.g., pulley and belt). As a result, the first worm 411 rotates around the first rotation axis Z1 by the driving force output from the stepping motor 53.

[0019] Furthermore, the stepping motor 53 incorporates a rotation sensor 54 capable of measuring the rotation angle θx1 of the first worm 411. The rotation sensor 54 measures the rotation angle θx1 of the first worm 411 using a pulse signal. Although this embodiment illustrates a configuration in which the rotation sensor 54 capable of measuring the rotation angle θx1 of the first worm 411 is incorporated into the stepping motor 53 that rotates the first worm 411, the rotation sensor 54 is not limited to being incorporated into the stepping motor 53 and may, for example, be provided outside the stepping motor 53.

[0020] The movable support 52 corresponds to the support according to the present invention, and includes a movable base 521 supported by a support base 50, and a movable support portion 522 disposed in a floating state on the movable base 521 and rotatably supporting the first helical gear 412. The movable base 521 is configured to be able to adjust the axial distance L between the first rotation axis Z1 and the second rotation axis Z2 via an actuator 524 and a speed reduction mechanism 525 linked to the movable base 521. The movable support portion 522 holds, via a second support shaft 523, a composite gear member 40 formed by integrally forming the first helical gear 412 and the second helical gear 422 rotatably around a second rotation axis Z2 orthogonal to the first rotation axis Z1. Further, the movable support portion 522 is provided so as to be relatively movable with respect to the fixed support 51 in the radial direction D of the first worm 411 orthogonal to the first rotation axis Z1, and is constantly biased toward the first worm 411 side via a biasing mechanism 526.

[0021] With the above configuration, in the inspection device 5, the first helical gear 412 rotatably supported by the movable support 52 meshes with the first worm 411 rotatably supported by the fixed support 51, and rotates following the first worm 411 rotationally driven by the stepping motor 53. Then, in the movable support 52, since the movable support portion 522 that rotatably supports the first helical gear 412 is constantly biased toward the first worm 411 side, according to the meshing between the first worm 411 and the first helical gear 412, the movable support portion 522 that supports the first helical gear 412 moves (displaces) along the radial direction D of the first worm 411 so that the first helical gear 412 approaches or separates from the first worm 411.

[0022] Further, the movable support 52 has a displacement sensor 55 capable of measuring the axial distance L between the first rotation axis Z1 and the second rotation axis Z2 and the movement distance (displacement) of the movable support 52 in the radial direction D of the first worm 411. For example, an optical linear scale is used for the displacement sensor 55. Note that the displacement sensor 55 can be arbitrarily changed according to the specifications of the inspection device 5 or the like as long as it is a sensor capable of measuring the displacement amount of the movable support 52.

[0023] Figure 4 shows a perspective view of the inspection device 5, enlarged to show the main parts of the inspection device 5 shown in Figure 3. Figure 5 shows a cross-sectional view of the inspection device 5 cut along line BB in Figure 4. Figure 6 shows a cross-sectional view of the inspection device 5 cut along line CC in Figure 5. For convenience of illustration, the base 511 and fixed support portion 512 of the fixed support 51 are omitted in Figures 4 and 5, respectively, and the movable base 521 of the movable support 52 is omitted. In Figure 6, the movable base 521 of the movable support 52 is also omitted.

[0024] As shown in Figures 4 to 6, the inspection device 5 includes a support base 50 formed in the shape of a platform, a fixed support 51 fixed to the support base 50 and rotatably supporting the first worm 411 on the first rotation axis Z1, and a movable support 52 provided so as to be movable relative to the support base 50 and rotatably supporting the first helical gear 412 on the second rotation axis Z2 which is perpendicular to the first rotation axis Z1.

[0025] The fixed support 51, as shown in Figures 4 and 5, for example, has a base 511 fixed to a support base 50, and a fixed support portion 512 provided on the side of the base 511 opposite the movable support 52, which rotatably supports the first worm 411 via a first support shaft 513. The fixed support portion 512 has a pair of first support shafts 515 that rotatably support both axial ends of a shaft member 514 that passes through a worm through-hole 411a formed in an axial direction (along the first rotation axis Z1) inside the first worm 411.

[0026] The movable support 52, as shown in Figures 4 and 6, for example, includes a movable base 521 supported by a support base 50, and a movable support portion 522 that is floating on the movable base 521 and rotatably supports the first helical gear 412. The movable support portion 522 is formed in a U-shape that rotatably supports the composite gear member 40 via a pair of second support shafts 523, 523 inserted at both ends in the axial direction (along the second rotation axis Z2), and is integrally formed from a predetermined metal material. Specifically, the movable support portion 522 has a pair of support arm portions 522a, 522b that extend generally parallel to the radial direction D of the first worm 411, and a linear connecting portion 522c that connects the support arm portions 522a, 522b. The first helical gear 412 is rotatably supported about the second rotation axis Z2 by a pair of second support shafts 523, 523 that are rotatably supported by the pair of support arm portions 522a, 522b.

[0027] (Inspection method for worm gears) Figure 7(a) shows a graph representing the waveform of the displacement X of the distance L between the rotation axis Z1 of the first worm 411 and the rotation axis Z2 of the first helical gear 412, with respect to the rotation angle θx2 of the first helical gear 412. Figure 7(b) shows a graph representing the waveform of the velocity V obtained by taking the first derivative of the displacement X of the distance L shown in Figure 7(a). Figure 7(c) shows a graph representing the waveform of the acceleration A obtained by taking the second derivative of the displacement X of the distance L shown in Figure 7(a).

[0028] To inspect the meshing noise of the first worm gear 41, which is formed by meshing a first worm 411 and a first helical gear 412, first, a set of first worm gears 41 that are intended to be used in actual meshing when mounted on a product is set in the inspection device 5 (see, for example, Figure 4). Next, the stepping motor 53 is rotated to drive the first worm 411 and the first helical gear 412, which constitute the first worm gear 41, to mesh. Then, the rotation sensor 54 and displacement sensor 55 measure the displacement (displacement amount X) of the distance L between the rotation axis Z1 of the first worm 411 and the rotation axis Z2 of the first helical gear 412 with respect to the rotation angle θx2 of the first helical gear 412. At the same time, the velocity V is measured by first differentiating the displacement amount X of the distance L, and the acceleration A is measured by second differentiating the displacement amount X of the distance L. The rotation angle θx2 of the first helical gear 412 is calculated based on the rotation angle θx1 of the stepping motor 53 that rotates the first worm 411.

[0029] Then, waveform data of the displacement X for the interaxial distance L, as shown in Figure 7(a), waveform data of the velocity V, as shown in Figure 7(b), and waveform data of the acceleration A, as shown in Figure 7(c), are obtained. Focusing on the waveform data of acceleration A shown in Figure 7(c), we find that in this waveform data, the absolute value of acceleration A is greater than a predetermined threshold P at angles θ1, θ2, θ3, θ4, and θ5. Furthermore, the difference Dx between the maximum value Ap1 of acceleration A recorded at angle θ2 and the minimum value Ap2 of acceleration A recorded at angle θ4 is greater than a predetermined threshold Q.

[0030] The phenomenon of a significant increase in acceleration A occurs at angles θ1, θ2, θ3, θ4, and θ5, when minute irregularities (catch) are overcome between the two tooth surfaces of the first worm 411 and the first helical gear 412. In other words, since acceleration A is the change in velocity V, the state of overcoming the aforementioned irregularities (catch) appears in the waveform data of acceleration A as an excessive acceleration A, which is a steep change in velocity V.

[0031] In this embodiment, the state of overcoming the above-mentioned irregularities (snagging) is reflected as a minute change F in the waveform data of the displacement X of the inter-axis distance L. However, depending on the degree of the irregularities (snagging), the displacement X of the inter-axis distance L may be minute, and there is a risk that the meshing noise of the first worm 411 and the first helical gear 412 cannot be properly confirmed. Furthermore, even if the evaluation using the above-mentioned acceleration A is judged to be defective, depending on the degree of the irregularities (snagging), it may fall within the JIS standard for meshing error. Therefore, it was difficult to properly inspect the meshing noise of the first worm 411 and the first helical gear 412 according to the JIS standard for meshing error.

[0032] Therefore, in the worm gear inspection method according to this embodiment, the meshing noise of the first worm 411 and the first helical gear 412 is inspected (measured) using the acceleration A obtained by taking the second derivative of the displacement X of the inter-axis distance L. If a defect in the meshing noise is confirmed based on this acceleration A obtained by taking the second derivative of the displacement X of the inter-axis distance L, the first worm 411 and the first helical gear 412 that have been determined to be defective are excluded as defective products. Furthermore, it is possible to determine whether the cause of the defect lies in the first worm 411 or the first helical gear 412 using the master gears of the first worm 411 and the first helical gear 412.

[0033] Furthermore, minute irregularities (catch) between the two tooth surfaces of the first worm 411 and the first helical gear 412 can be caused primarily by the lifespan of the rolling die that forms the first worm 411. Therefore, it is desirable to suppress the problem of a large number of first worms 411 being manufactured with meshing noise exceeding the specified value by appropriately managing the lifespan of the rolling die. In addition, in this embodiment, meshing noise caused by minute irregularities (catch) between the two tooth surfaces of the first worm 411 and the first helical gear 412, which may occur due to sudden or accidental factors other than the lifespan of the rolling die, can be appropriately inspected (sorted) by the inspection device 5, thereby suppressing quality defects of the first worm 411 and the first helical gear 412.

[0034] (Effects of this embodiment) The conventional inspection method for worm gears described above could not inspect the meshing noise of the worm gear unless the worm gear was assembled into a product that incorporates it. Therefore, there was a drawback in that the meshing noise could not be inspected during the manufacturing stage (by the manufacturer) of the worm gear, leaving room for improvement.

[0035] Furthermore, as described in Japanese Patent Publication No. 7-76681, it is known that an acceleration sensor is mounted on an inspection device, and this acceleration sensor is used to inspect the tooth surface of the worm. However, mounting an acceleration sensor on an inspection device increases equipment costs, and the device becomes an inspection device dedicated to a specific worm gear, which could increase the manufacturing cost of the worm gear. In addition, high precision is required for the installation of the acceleration sensor, making its management complicated, which could lead to a decrease in the productivity of the worm gear and an increase in manufacturing costs.

[0036] In contrast, the worm gear inspection device and inspection method according to this embodiment can solve the problems of the conventional worm gear inspection device by achieving the following effects.

[0037] In other words, the worm gear inspection device 5 according to this embodiment is a worm gear inspection device for inspecting the meshing noise of a worm gear (first worm gear 41) consisting of a worm (first worm 411) and a mating gear (first helical gear 412), and includes a support (movable support 52) ​​that rotatably holds the mating gear (first helical gear 412) and is provided to be movable in the radial direction by meshing the mating gear (first helical gear 412) with the worm (first worm 411) from the radial direction with respect to the rotation axis (first rotation axis Z1) of the worm (first worm 411), and the rotation angle θx2 of the mating gear (first helical gear 412), and the worm ( The system includes sensors (rotation sensor 54 and displacement sensor 55) capable of measuring the distance L between the axis of rotation of the first worm gear (first rotation axis Z1) and the axis of rotation of the mating gear (first helical gear 412) (second rotation axis Z2). The system rotates the worm gear (first worm gear 411) and determines the quality of the meshing noise of the worm gear (first worm gear 41) by taking the absolute value of the acceleration A obtained by taking the second derivative of the displacement (amount of displacement X) of the distance L between the axes with respect to the rotation angle θx2 of the mating gear (first helical gear 412) measured by the sensors (rotation sensor 54 and displacement sensor 55), or by the difference Dx between the maximum value Ap1 and the minimum value Ap2 of the acceleration A.

[0038] In other words, the worm gear inspection method according to this embodiment is a worm gear inspection method for inspecting the meshing noise of a worm gear (first worm gear 41) consisting of a worm (first worm 411) and a mating gear (first helical gear 412), and determines the quality of the meshing noise of the worm gear (first worm gear 41) by taking the absolute value of the acceleration A obtained by taking the second derivative of the displacement (amount of displacement X) of the distance L between the rotation axis (first rotation axis Z1) of the worm (first worm 411) and the rotation axis (second rotation axis Z2) of the mating gear (first helical gear 412) with respect to the rotation angle θx2 of the mating gear (first helical gear 412), or by the difference Dx between the maximum value Ap1 and the minimum value Ap2 of the acceleration A.

[0039] In this embodiment, the quality of the meshing noise of the first worm gear 41 is determined by the absolute value of the acceleration A obtained by taking the second derivative of the displacement X of the distance L between the rotation axis L of the first worm 411 (first rotation axis Z1) and the rotation axis of the first helical gear 412 (second rotation axis Z2) with respect to the rotation angle θx2 of the mating gear, the first helical gear 412, or by the difference Dx between the maximum value Ap1 and the minimum value Ap2 of the acceleration A. This makes it possible to inspect the meshing noise of the first worm gear 41 (composite gear member 40) before assembling it into a product, that is, at the manufacturing stage (manufacturer) of the first worm gear 41 (composite gear member 40).

[0040] Furthermore, in this embodiment, instead of directly detecting the acceleration A of the first helical gear 412 using an acceleration sensor or the like, the acceleration A is obtained by taking the second derivative of the displacement X of the distance L between the rotation axis L of the first worm 411 (first rotation axis Z1) and the rotation axis Z2 of the first helical gear 412. Therefore, compared to the conventional inspection method in which an acceleration sensor is placed on the support of the inspection device (corresponding to the movable support 52 in this embodiment) to detect the acceleration of the worm wheel (corresponding to the first helical gear 412 in this embodiment) and inspect the tooth surface of the worm, the complicated management of the acceleration sensor is eliminated, and the productivity of the worm gear can be improved.

[0041] In addition, since this embodiment does not use the acceleration sensor as in the conventional inspection method, there is no need to significantly change the configuration of the existing inspection device, nor is it necessary to make the inspection device a dedicated inspection device for a specific worm gear. Therefore, there is no risk of increasing the equipment costs required for the inspection device or increasing the manufacturing costs of the worm gear.

[0042] Furthermore, if one of the gears constituting the first worm gear 41 (the first worm 411 or the first helical gear 412) is configured as an inspection gear (master gear), even if the meshing noise is judged to be good in the inspection, there is a risk that the meshing noise of the first worm gear 41 may become poor after it is mounted on the actual product (flow control valve CV). In contrast, in this embodiment, the meshing noise of the first worm gear 41 is inspected based on the first worm 411 and the first helical gear 412 that actually mesh, so the quality of the product (flow control valve CV) on which the first worm gear 41 is mounted can be more accurately guaranteed.

[0043] Furthermore, by inspecting the meshing noise of the first worm gear 41 based on acceleration A, it is possible to appropriately inspect and determine whether the meshing noise is good or bad, even if the defect cannot be detected by the displacement X of the distance L between the rotation axis L of the first worm 411 (first rotation axis Z1) and the rotation axis L of the first helical gear 412 (second rotation axis Z2).

[0044] Furthermore, in this embodiment, the mating gear is a helical gear (first helical gear 412), and the support (movable support 52) ​​holds the mating gear (first helical gear 412) such that the direction of the rotation axis (second rotation axis Z2) of the helical gear (first helical gear 412) is perpendicular to the rotation axis (first rotation axis Z1) of the worm (first worm 411).

[0045] Thus, in this embodiment, the mating gear of the first worm 411 is configured as a first helical gear 412, which is a helical gear. Therefore, compared to the case where the mating gear of the first worm 411 is configured as a spur gear, the power transmission efficiency from the first worm 411 to the mating gear (first helical gear 412) is improved, and the meshing noise between the first worm 411 and the mating gear (first helical gear 412) can also be reduced.

[0046] The worm gear inspection device 5 and worm gear inspection method according to the present invention are not limited to the configuration exemplified in the above embodiment, and can be freely modified according to the specifications of the worm gear to be inspected, as long as they can achieve the effects of the present invention.

[0047] In particular, in the above embodiment, the first worm gear 41 was given as an example of a worm gear that is the target of inspection by the worm gear inspection device 5 and the inspection method using the same, but it goes without saying that the second worm gear 42 can also be inspected in the same manner.

[0048] Furthermore, as mentioned above, the mating gears of the first worm 411 and the second worm 421 are preferably composed of helical gears (first helical gear 412 and second helical gear 422) as exemplified in this embodiment, from the viewpoint of power transmission efficiency and meshing noise. However, they can also be changed to spur gears depending on the specifications of the worm gear, such as manufacturing costs. [Explanation of symbols]

[0049] 41...First worm gear (worm gear), 411...First worm (worm), 412...First helical gear (mating gear), 5...Inspection device, 52...Movable support (support), 54...Rotation sensor (sensor), 55...Displacement sensor (sensor), Z1...First rotation axis, Z2...Second rotation axis, L...Distance between axes, θx2...Rotation angle, X...Displacement amount (displacement), A...Acceleration, Ap1...Maximum value, Ap2...Minimum value, Dx...Difference,

Claims

1. A worm gear inspection device for inspecting the meshing noise of a worm gear consisting of a worm and a mating gear, A support is provided that rotatably holds the mating gear and is movable in the radial direction by engaging the mating gear with the worm from the radial direction with respect to the rotation axis of the worm, A sensor capable of measuring the rotation angle of the mating gear and the distance between the rotation axis of the worm and the rotation axis of the mating gear, It has, The worm is rotated, and the absolute value of the acceleration obtained by taking the second derivative of the displacement of the interaxial distance with respect to the rotation angle of the mating gear measured by the sensor, or the difference between the maximum and minimum values ​​of the acceleration, is used to determine the quality of the meshing noise of the worm gear. A worm gear inspection device characterized by the following.

2. A worm gear inspection device according to claim 1, The displacement of the interaxial distance is the radial displacement of the support. A worm gear inspection device characterized by the following.

3. A worm gear inspection device according to claim 2, The mating gear is an inclined gear, The support holds the mating gear such that the direction of the rotation axis of the helical gear is perpendicular to the rotation axis of the worm. A worm gear inspection device characterized by the following.

4. A method for inspecting a worm gear, which consists of a worm and a mating gear, for inspecting the meshing noise of the worm gear, The mating gear is held by a support that rotatably holds the mating gear, the mating gear is meshed with the worm from the radial direction with respect to the rotation axis of the worm, and with the support provided to be movable in the radial direction, the displacement of the distance between the rotation axis of the worm and the rotation axis of the mating gear with respect to the rotation angle of the mating gear is measured. The quality of the meshing noise of the worm gear is determined by the absolute value of the acceleration obtained by taking the second derivative of the displacement, or by the difference between the maximum and minimum values ​​of the acceleration. A method for inspecting a worm gear, characterized by the following:

Images