JP2007205866A - Gear evaluating apparatus - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a gear evaluating apparatus which can be made compact and low-cost by reducing spatial constraints, and can measure and evaluate a vibration compelling force of a gear effectively and precisely over a wide range of continuous rotational region, by detecting an rotational error or the like of the gear which rotates while gearing without being affected by vibration and resonance of the apparatus. <P>SOLUTION: The gear evaluating apparatus comprises: pulleys 15, 16 which are mounted on rotation shafts 13, 14 of gears 11, 12 being objects to be evaluated and rotate in synchronization with respective gears; a drive motor 18 for rotating the gears 11, 12 through a belt 17 engaging to these pulleys; a torsion mechanism 19 which is disposed between the gear and the pulley associated with one of the rotation shafts 13, 14, and applies a load torque to the gears 11, 12 through the associated rotation axis; rotary encoders 21, 22 for detecting rotations of the gears 11, 12; and an analyzing device 30 for analyzing a detection value detected by these rotary encoders. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a gear evaluation device for evaluating and measuring a vibration forcing force of a gear by detecting a rotation error of a gear used in, for example, an automobile transmission.

  For example, in a gear pair that rotates in mesh with each other used in an automobile transmission or the like, a rotation error including a mesh transmission error or the like occurs due to a tooth surface shape error or a tooth deflection. Such a rotation error may affect the power transmission performance or cause vibration. Therefore, Patent Document 1 discloses an apparatus for detecting a rotation error in a gear pair.

In Patent Document 1, the following configuration is shown as a conventionally proposed apparatus for detecting the rotation error as described above.
That is, one gear (drive gear) is rotated by a drive motor through a reduction gear, a torque meter, and a low-rigidity joint, and the other gear (driven gear) is low-rigidity. The driving motor is connected to a driven motor via a joint and a reduction gear, and a predetermined load torque (meshing load) is applied by the driven motor. In such a configuration, while the load torque is measured by the torque meter, the rotation angle of each gear is measured by a rotary encoder coupled in the vicinity of each gear, and the rotation error is detected as a rotation error (relative rotation speed fluctuation). ) Is detected.
The low-rigidity joint has low rigidity so that vibration caused by fluctuations in the rotation of the motor and vibrations of the reduction gear are transmitted to the gear pair to be detected and the load torque does not fluctuate. In addition, since the rotation of the motor is stabilized, a rotation error is detected using a high rotation range that is not easily affected by motor ripple (minute rotation fluctuation, torque fluctuation).

And in patent document 1, in a device in which a low-rigidity joint is used as described above and a high rotation range of a motor is used, the vibration frequency due to meshing in the gear pair becomes larger than the resonance frequency of the device. In view of the problem that the rotation error that is originally required to be measured as a static value cannot be accurately detected due to the influence of the vibration characteristics of the device, the weight is suspended by a structure in which a weight is suspended from a disk-shaped rotating body via a string or the like. In particular, an apparatus has been proposed in which load torque is applied and rotation error is detected in an extremely low rotation range.
JP-A-7-120353

The conventional apparatus has the following problems.
In other words, with respect to devices in which measures are taken to prevent transmission of vibration to the gear pair by using a low-rigidity joint and a high rotation range of the motor, the resonance system, motor, It is difficult to avoid fluctuations in the meshing load of the gear pair to be detected due to rotational fluctuations of the reduction gear. In other words, since a reduction gear or the like is interposed between the motor and the gear pair, only the rotation error due to the meshing in the gear pair is detected due to the resonance frequency of the device and the vibration of the motor and the reduction gear. Difficult to do.

In addition, with regard to devices configured with weights suspended from rotating bodies, it is true that load torque is statically applied and detection is performed in an extremely low rotation range, so that it is highly accurate without being affected by vibration. It is thought that rotation error can be detected at
However, due to the structure in which a weight is suspended from the rotating body and load torque is applied, if the gear diameter (number of teeth) in the gear pair is significantly different, the rotation range of the gear is limited and the entire circumference of the gear is It is thought that it is impossible to detect over.
Also, for structural reasons, there is a spatial restriction due to the length of the string for suspending the weight, etc., so it is considered that detection under continuous rotation is practically difficult. Therefore, under continuous rotation, phenomena unique to the dynamic gear pair, such as resonance caused by the natural vibration of the gear itself, occur from the gear shape, etc., but it is difficult to detect such phenomena. Become.

In the conventional apparatus, as described above, detection is performed in a high rotation range for stabilizing the rotation of the motor, and detection is performed in a very low rotation range for applying static load torque. Under such a limited rotation range condition, it is not possible to perform detection while reproducing a continuous rotation range such as a stop state to a high rotation range.
For this reason, for example, when detection is performed on a gear pair used in an automobile transmission or the like, it is desirable that a continuous rotation range such as a process of accelerating from a stopped state of the automobile is reproduced. However, the rotation range cannot be reproduced, and the behavior of the gear pair in the actual transmission, including phenomena specific to the dynamic gear pair, such as resonance caused by the natural vibration and rigidity of the gear, It is difficult to perform the detection corresponding to the entire rotation region.

  Therefore, the object of the present invention is to reduce the space constraints and reduce the size and cost, and in the continuous rotation region over a wide range without being affected by the resonance and vibration of the device, An object of the present invention is to provide a gear evaluation device capable of efficiently and accurately evaluating and measuring the vibration forcing force of a gear by detecting a rotation error of the gear rotating in mesh.

  The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described.

  That is, in Claim 1, it is a gear evaluation apparatus which makes the object of evaluation the some gear rotating meshingly, Comprising: The rotary body attached to the rotating shaft of each gear, and synchronizing with the said gear, and the said rotary body A drive source that rotates the gear via a transmission member that engages with the gear, and a load torque that is provided between the gear and the rotating body of any one of the rotary shafts and that is applied to the gear via the rotary shaft. Torque applying means for applying the rotation, rotation detecting means for detecting the rotation of the gear, and analyzing means for analyzing the detection value detected by the rotation detecting means.

  According to a second aspect of the present invention, torque detecting means for detecting the load torque applied by the torque applying means is provided.

  According to a third aspect of the present invention, there is provided acceleration detecting means for detecting acceleration of vibration of the gear, and the analyzing means analyzes the fluctuation of the rotation angle of the gear based on the detection value detected by the rotation detecting means. An angular fluctuation analyzing means; and a rotational order analyzing means for analyzing the rotational order of the gear based on the detection values detected by the rotation detecting means, the torque detecting means, the acceleration detecting means and the rotational angle fluctuation analyzing means; It is what has.

  According to a fourth aspect of the present invention, there is provided a gear evaluation device for evaluating a plurality of meshing gears, the rotating body being attached to the rotating shaft of each gear and rotating in synchronization with the gear, and the rotating body A drive source that rotates the gear via a transmission member to be coupled, and a load torque that is provided between the gear and the rotating body of any one of the rotary shafts and applies a load torque to the gear via the rotary shaft Torque applying means, rotation detecting means for detecting rotation of one of the gears, torque detecting means for detecting load torque applied by the torque applying means, and detection detected by the rotation detecting means Analyzing means for analyzing the value and the load torque value detected by the torque detecting means.

  According to a fifth aspect of the present invention, the apparatus includes an acceleration detection unit that detects an acceleration of vibration of the gear, and a rotation detection unit that detects a rotation of another gear among the gears, and the analysis unit includes the rotation detection unit. Rotation angle fluctuation analysis means for analyzing fluctuations in the rotation angle of the gear based on the detected value detected, and detected by the rotation detection means, the torque detection means, the acceleration detection means, and the rotation angle fluctuation analysis means. And a rotational order analyzing means for analyzing the rotational order of the gear based on the detected value.

  As effects of the present invention, the following effects can be obtained.

  According to the first aspect of the present invention, it is possible to reduce the space restriction and reduce the size and cost, and in the continuous rotation region over a wide range, the meshing without being affected by the resonance and vibration of the device. By detecting a rotation error or the like of the rotating gear, it is possible to efficiently evaluate and measure the vibration forcing force of the gear with high accuracy.

  In claim 2, since it is possible to accurately reproduce a torque state in which a predetermined load torque is applied to a gear that rotates in mesh, it is possible to perform an evaluation in accordance with the actual behavior of the gear, and Therefore, it is possible to acquire the vibration forcing force in the rotating gear more efficiently and with high accuracy.

  In claim 3, dynamic characteristics such as resonance caused by natural vibration and rigidity including interaction with an element having a frequency characteristic of a gear are included in an engagement transmission error which is a static characteristic of the gear pair. It is possible to evaluate and measure only the rotational angle fluctuation component, the torque fluctuation component, and the vibration component with high accuracy without being affected by the resonance and vibration of the apparatus.

  According to the fourth aspect of the present invention, it is possible to reduce the size and cost by reducing the spatial constraints, and in the continuous rotation region over a wide range, the meshing can be performed without being affected by the resonance and vibration of the device. By detecting a rotation error or the like of the rotating gear, it is possible to efficiently evaluate and measure the vibration forcing force of the gear with high accuracy.

  In claim 5, dynamic characteristics such as resonance due to natural vibration and rigidity including interaction with an element having a frequency characteristic of the gear are included in an engagement transmission error which is a static characteristic of the gear pair. It is possible to evaluate and measure only the rotational angle fluctuation component, the torque fluctuation component, and the vibration component with high accuracy without being affected by the resonance and vibration of the apparatus.

Next, embodiments of the invention will be described.
The gear evaluation apparatus according to the present invention evaluates a plurality of gears that mesh with each other, and specifically, a pair of gears (hereinafter referred to as “gear pairs”) that mainly mesh with each other. By rotating, by detecting a rotation error or the like in the gear pair, the vibration forcing force of the gear is evaluated and measured.

1st Embodiment of the gear evaluation apparatus which concerns on this invention is described using FIGS. 1-3.
The gear evaluation device according to the present embodiment is for evaluating a gear pair 10 composed of a first gear 11 and a second gear 12 that mesh with each other, and is attached to the rotary shafts 13 and 14 of the gears 11 and 12. The first gear 11 and the second gear 12 are connected via pulleys 15 and 16 as rotating bodies rotating in synchronization with the gears 11 and 12 in the pair 10 and a belt 17 as a transmission member engaged with the pulleys 15 and 16. A drive motor 18 as a drive source for rotating the shaft and a load torque (meshing load) applied to the gear pair 10 via the rotation shaft provided between the gear and the pulley on any one of the rotation shafts 13 and 14. A torsion mechanism 19 as torque applying means for applying torque, rotary encoders 21 and 22 as rotation detecting means for detecting the rotation of the gears 11 and 12, and these rotary engines And a analysis device 30 as an analysis means for analyzing the detected value detected by the over Da 21 - 22.

As shown in FIG. 1, the first gear 11 of the gear pair 10 is attached to and supported by a rotating shaft 13 (hereinafter referred to as “first rotating shaft 13”), and is integrated with the first rotating shaft 13. Rotate to. The first rotary shaft 13 is rotatably supported by a plurality of bearings 23a and work chucks 23b that are provided at appropriate intervals in the axial direction.
The second gear 12 of the gear pair 10 is attached to and supported by the rotary shaft 14 (hereinafter referred to as “second rotary shaft 14”), and rotates integrally with the second rotary shaft 14. The second rotary shaft 14 is provided in parallel with the first rotary shaft 13 and is rotatably supported by a plurality of bearings 24a and a work chuck 24b, like the first rotary shaft 13.

A pulley 15 (hereinafter referred to as “first pulley 15”) is attached to and supported by one end of the first rotating shaft 13, and the first pulley 15 rotates integrally with the first rotating shaft 13. To do. A pulley 16 (hereinafter referred to as “second pulley 16”) is attached to and supported by one end of the second rotating shaft 14, and the second pulley 16 is integrated with the second rotating shaft 14. Rotate to.
The first pulley 15 and the second pulley 16 are provided in the same position in the axial direction (left-right direction in FIG. 1) of the respective rotation shafts, and receive power from the drive motor 18 via the belt 17. .

The first pulley 15 and the second pulley 16 rotate in synchronization with the first gear 11 and the second gear 12 in the gear pair 10.
That is, in the configuration in which the first gear 11 and the first pulley 15 are pivotally supported on the first rotating shaft 13, and the second gear 12 and the second pulley 16 are pivotally supported on the second rotating shaft 14, the belt 17 is The rotation ratio of the first rotation shaft 13 and the second rotation shaft 14 due to the rotation of the first pulley 15 and the second pulley 16 through the rotation ratio of the first gear 11 and the second gear 12 is the same. The first pulley 15 and the second pulley 16 are synchronously rotated with respect to the first gear 11 and the second gear 12 that are engaged with each other and rotated.
In other words, the first gear 11 and the first pulley 15 rotate at the same speed through the first rotating shaft 13, and therefore the second gear 12 and the second pulley 16 rotate at the second rotation. Since the rotation is performed integrally through the shaft 14, the rotation speed is the same, and the rotation ratio of the first gear 11 and the second gear 12 in the gear pair 10 and the rotation ratio of the first pulley 15 and the second pulley 16 are It is the same.
Accordingly, the rotary shafts 13 and 14 are configured such that no torque is generated by the gear 11 (12) and the pulley 15 (16) rotating with each other.

The drive motor 18 is provided such that the motor drive shaft 18 a is parallel to the first rotary shaft 13 and the second rotary shaft 14. The power of the drive motor 18 is transmitted to the first pulley 15 and the second pulley 16 via a pulley 28 (hereinafter referred to as “motor pulley 28”) attached to and supported by the motor drive shaft 18a and the belt 17. .
That is, as shown in FIG. 2, the belt 17 is wound around the motor pulley 28 and the second pulley 16, and the first pulley 15 is engaged with the belt 17 from the outside between the motor pulley 28 and the second pulley 16. Arranged to match. As a result, the power of the motor drive shaft 18a that is rotationally driven by the drive motor 18 is transmitted to the first pulley 15 and the second pulley 16 via the motor pulley 28 and the belt 17, and the first pulley 15 and 16 rotate to rotate the first pulley 15. As the rotary shaft 13 and the second rotary shaft 14 are rotated, the first gear 11 and the second gear 12 are rotated.
The motor drive shaft 18 a is rotatably supported by the work chuck 25 on both sides of the motor pulley 28.
Hereinafter, the first pulley 15 pivotally supported by the first rotary shaft 13, the second pulley 16 pivotally supported by the second rotary shaft 14, the motor pulley 28 pivotally supported by the motor drive shaft 18a, and these pulleys are arranged. The power transmission mechanism including the belt 17 that transmits the power is referred to as a “pulley mechanism 20”.

In the pulley mechanism 20, a configuration is used in which slip elements are removed so that slip between the pulleys 15, 16, and 28 and the belt 17 does not occur.
As a configuration in which the sliding element in the pulley mechanism 20 is eliminated, for example, in the arrangement configuration of the pulleys 15, 16, and 28 and the belt 17 shown in FIG. A configuration using a pulley and using a toothed belt having teeth on both sides (inner and outer peripheral surfaces) as the belt 17 is conceivable. It is also conceivable to provide a mechanism for applying tension to the belt 17 in order to prevent slippage due to the slack of the belt 17.

The arrangement configuration of the pulleys 15, 16, 28 and the belt 17 in the pulley mechanism 20 is not limited to the case of the present embodiment shown in FIG. That is, as described above, the arrangement of the pulleys and the like in the pulley mechanism 20 is such that the rotation of the motor drive shaft 18a does not occur between the pulleys 15, 16, 28 and the belt 17 and the first pulley 15 and the second pulley. As long as the first pulley 15 and the second pulley 16 are configured to rotate in synchronization with the first gear 11 and the second gear 12 in the gear pair 10, various modes are conceivable.
For example, the rotation of the motor drive shaft 18a can be performed at a predetermined rotation by using a plurality of belts by adding pulleys, winding the belt between pulleys, using an idle pulley, or combining them. Various arrangements are conceivable which are transmitted in the direction to the first pulley 15 and the second pulley 16. However, from the viewpoint of reducing the power supplied by the drive motor 18 by reducing the resistance of each part in the pulley mechanism 20, it is preferable that the number of pulleys and belts is small.

As described above, in the power transmission system in which power is transmitted from the drive motor 18 to the gear pair 10 via the pulley mechanism 20, the power of the drive motor 18 is supported by the first rotating shaft 13 and the second rotating shaft 14. Are used only for the rotation of the first gear 11 and the second gear 12 in the gear pair 10, except for the resistance in the gear mechanism 10, the resistance of each part in the pulley mechanism 20, and the friction loss of the gear in the gear pair 10.
That is, the drive motor 18 is substantially used only for rotating the first gear 11 and the second gear 12, and the load torque for the gear pair 10 is applied only by the torsion mechanism 19 described below. Become.

The torsion mechanism 19 applies (acts) a load torque to the gear pair 10 via any one of the first rotating shaft 13 and the second rotating shaft 14 as described above. Is provided between the second gear 12 and the second pulley 16 on the second rotating shaft 14 and applies load torque to the gear pair 10 via the second rotating shaft 14.
That is, the second rotating shaft 14 includes a portion on the second gear 12 side (hereinafter referred to as “gear side shaft portion 14 a”) and a portion on the second pulley 16 side (hereinafter referred to as “pulley side”) via the torsion mechanism 19. The shaft portion is referred to as “shaft portion 14b”), and the torsion mechanism 19 shifts the rotation phase of the gear-side shaft portion 14a and the pulley-side shaft portion 14b to apply load torque. Thereby, the load torque is applied in any rotation direction in the gear pair 10 (direction in which the load torque is to be applied to the meshing of the gears). That is, in the second rotating shaft 14, the state where the load torque is applied to the gear pair 10 by the torsion mechanism 19 is maintained, and the torsion mechanism 19, the gear side shaft portion 14a, and the pulley side shaft portion 14b are integrally formed. Rotate.

As the torsion mechanism 19, for example, one having the following configuration is used. An example of a specific configuration of the twisting mechanism 19 will be described with reference to FIG.
As shown in FIG. 3, the torsion mechanism 19 in this example includes a worm wheel 31 provided integrally on the gear side shaft portion 14a side, a case body 32 provided integrally on the pulley side shaft portion 14b, and the case A worm 33 is rotatably supported with respect to the body 32 via a support shaft 34 and meshes with the worm wheel 31.

The worm wheel 31 is provided on the gear side shaft portion 14a side of the second rotation shaft 14, and rotates integrally with the gear side shaft portion 14a. In this example, the worm wheel 31 is provided via a base portion 31a provided integrally with the gear side shaft portion 14a.
The case body 32 is formed in a disc shape as a whole and is provided on the pulley-side shaft portion 14b side of the second rotating shaft 14, covers the worm wheel 31 and rotates integrally with the pulley-side shaft portion 14b.
The worm 33 is formed integrally with the support shaft 34 provided at one end of the case body 32 so as to be rotatable with the direction perpendicular to the radial direction of the case body 32 as an axial direction. Here, one end side (the right side in FIG. 3B) of the support shaft 34 has a protrusion 34 a that protrudes from a notch 32 a formed in the case body 32.

Further, in the torsion mechanism 19, as shown in FIG. 3B, the gear side shaft portion 14a and the pulley side shaft portion 14b are fitted so as to be relatively rotatable on a coaxial center by using a fitting method using an inlay or the like. Combined.
That is, in the torsion mechanism 19 configured on the second rotating shaft 14, the gear side shaft portion 14 a to which the worm wheel 31 is fixed and the pulley side shaft portion 14 b to which the worm 33 is fixed via the case body 32 are provided. The worm wheel 31 and the worm 33 are coaxially engaged with each other.

With the torsion mechanism 19 configured as described above, the application and adjustment of the load torque to the gear pair 10 are performed as follows.
First, the worm 33 is rotated by using the protruding portion 34a of the support shaft 34, whereby the worm wheel 31 meshing with the worm 33 is rotated. The rotation direction here is a direction in which a load torque is to be applied to the gear pair 10 by the torsion mechanism 19, and the load torque can be applied in different directions in order to reproduce the acceleration state or the deceleration state in the gear pair 10.
As the worm wheel 31 rotates, the worm wheel 31 rotates, whereby the gear side shaft portion 14a is rotated relative to the pulley side shaft portion 14b. Thereby, a torsion is applied between the gear side shaft portion 14a and the pulley side shaft portion 14b, and a load torque is applied from the second gear 12 to the gear pair 10 by this torsion.
That is, in the pulley mechanism 20, since the slip elements between the pulleys 15, 16, 28 and the belt 17 are eliminated as described above, the pulley side shaft portion 14b of the second rotating shaft 14 is provided with the motor drive shaft 18a. The gear side shaft portion 14a and the pulley side are rotated by rotating the gear side shaft portion 14a from the worm 33 through the worm wheel 31 with respect to the pulley side shaft portion 14b. Torsion is applied between the shaft portion 14 b and a load torque is applied to the gear pair 10.

Therefore, the load torque applied to the gear pair 10 can be adjusted by adjusting the rotation of the worm 33.
Here, the load torque applied to the gear pair 10 by the torsion mechanism 19 is held by a self-locking function between the worm wheel 31 and the worm 33 that mesh with each other in the torsion mechanism 19.
That is, the worm wheel 31 and the worm 33 meshed with each other in the torsion mechanism 19 can be rotated from the worm 33 side by setting the advance angle of the worm 33, but the worm wheel 31 can be rotated from the worm wheel 31 side. A self-locking function that the 33 cannot be rotated can be provided. Thus, the load torque applied to the gear pair 10 by rotating the worm 33 is maintained. In addition, it can also be set as the structure which hold | maintains the application state of the load torque to the gear pair 10 by rotating the worm 33 by screwing the support shaft 34 of the worm 33 with respect to the case body 32. FIG.

Further, in the torsion mechanism 19, the load torque applied to the gear pair 10 by the torsion mechanism 19 is confirmed by providing a torque scale indicating the load torque corresponding to the rotation of the worm 33 on the support shaft 34. It can also be.
The state in which a predetermined load torque is applied to the gear pair 10 is maintained by the torsion mechanism 19 configured as described above. In the second rotating shaft 14, the gear side shaft portion 14a, the torsion mechanism 19, and the pulley side shaft portion are maintained. 14b rotate integrally.
The torsion mechanism 19 is not limited to the configuration described with reference to FIG. 3, and a state in which a load torque is applied to the gear pair 10 by the torsion mechanism 19 is maintained, and is integrated with a rotating shaft on which the torsion mechanism 19 is provided. Any configuration that can be rotated is acceptable. As another configuration, for example, a configuration in which a load torque is generated by applying a twist between the divided rotary shafts using a hydraulic mechanism such as a hydraulic cylinder or an elastic member such as a spring is conceivable.

With the configuration described above, the rotation of the first gear 11 and the second gear 12 in the gear pair 10 is performed by the drive motor 18 via the pulley mechanism 20, and the load torque is applied to the gear pair 10 by the torsion mechanism 19. Is done. Then, the first gear 11 and the second gear 12 are continuously rotated in a state where a load torque is applied to the gear pair 10 by the torsion mechanism 19 using the drive motor 18 as a drive source.
As a result, the drive motor 18 can be reduced in size, and it is not necessary to separately provide a motor for applying load torque to the gear pair 10, so that the apparatus can be reduced in size and cost.
That is, the first motor 11 and the first gear 11 are supplied from the drive motor 18 by supplying only the power such as the resistance of each part of the rotary shafts 13 and 14 and the pulley mechanism 20 and the friction loss of the gear in the gear pair 10 as described above. Since the two gears 12 can be rotated, the drive motor 18 can be reduced in size, and the load torque for the gear pair 10 can be applied by the torsion mechanism 19. Therefore, the load torque is applied to the gear pair 10. This eliminates the need for a motor.

The rotary encoders 21 and 22 detect the rotation of the first gear 11 and the second gear 12 as described above, and detect the rotation of the first gear 11 (hereinafter, “first rotary encoder 21”). Is provided at one end of the first rotary shaft 13 and detects the rotation of the first gear 13 via the first rotary shaft 13. A rotary encoder 22 (hereinafter referred to as “second rotary encoder 22”) that detects the rotation of the second rotary shaft 14 is provided at one end of the second rotary shaft 14 and passes through the second rotary shaft 14. Then, the rotation of the second gear 12 is detected.
The rotation speed and rotation angle of the first gear 11 detected by the first rotary encoder 21 and the rotation speed and rotation angle of the second gear 12 detected by the second rotary encoder 22 are input to the analysis device 30 as detection values. Is done.

Then, the detection value detected by the first rotary encoder 21 and the second rotary encoder 22 is analyzed by the analysis device 30, and the gear pair 10 is evaluated and measured.
That is, in the analysis device 30, the first gear detected by the first rotary encoder 21 under the evaluation conditions such as the rotational speed of the gear pair 10 rotated by the drive motor 18 and the load torque applied by the torsion mechanism 19. 11 and the rotation of the second gear 12 detected by the second rotary encoder 22 are detected, and this is detected between the first gear 11 and the second gear 12. Acquired as a rotation error including a mesh transmission error.

  Here, as a method of acquiring the rotation error between the first gear 11 and the second gear 12 in the analysis device 30, the pulse detected by the first rotary encoder 21 and the pulse detected by the second rotary encoder 22 are mainly used. The comparison between the external clocks, the reference pulse stored in advance in the analysis device 30, and the respective pulses detected by the first rotary encoder 21 and the second rotary encoder 22 are compared. There is a method based on comparison between an internal clock and an external clock. However, from the viewpoint of obtaining the rotation error with higher accuracy, a method using a high-speed internal clock is preferable.

As described above, the rotation error acquired based on the detection values from the first rotary encoder 21 and the second rotary encoder 22 includes the rotation caused by the motor ripple (minute rotation fluctuation, torque fluctuation) of the drive motor 18. Although the fluctuation influences, such a rotational fluctuation is partially attenuated via the pulley mechanism 20 and is equally transmitted to the first gear 11 and the second gear 12. Therefore, in the analysis device 30, when the rotation angle fluctuation detected by the first rotary encoder 21 and the second rotary encoder 22 is relatively calculated, the pulley ratio between the first pulley 15 and the second pulley 16 is taken into account. , Such rotational fluctuations are offset.
In other words, in the case of a configuration that requires a motor for applying load torque to the gear pair in addition to the motor for rotating the gear pair as in the conventional device, the motor ripple of each motor is affected. Therefore, it is necessary to perform calculations so as to cancel each component, and it has been difficult to reduce the influence of rotational fluctuations. However, this configuration is a configuration in which one drive motor 18 is used. The rotation fluctuation of the motor can be easily canceled out.
Thus, the vibration forcing force of the gear pair 10 (static characteristics such as meshing transmission error caused by the shape error of the tooth surface of the gear) and dynamic characteristics such as resonance due to the natural vibration and rigidity of the gear. It is possible to detect only the rotational angle fluctuation component due to the force generated by

  In the gear evaluation apparatus described above, it is possible to reduce the size and cost by reducing spatial constraints, and without being affected by the resonance and vibration of the apparatus in a wide continuous rotation range. By detecting a rotation error or the like of the gear rotating in mesh, the vibration forcing force of the gear can be efficiently evaluated and measured with high accuracy.

That is, as described above, since the gear pair 10 is rotated by the drive motor 18 and the load torque is applied to the gear pair 10 by the torsion mechanism 19, the gear pair 10 is applied to the gear pair as in the conventional device. Compared with configurations that require a separate motor to apply load torque, and configurations in which weight torque is applied by suspending a weight from a rotating body, space constraints are reduced and size and cost are reduced. Can be achieved.
Further, since there is no portion that generates vibration such as a reduction gear between the motor and the gear pair as in the conventional configuration, the gear has a difficulty in reproducing in the conventional device. Continuously rotating gear pairs in the actual transmission, including phenomena unique to dynamic gear pairs such as resonance due to natural vibration and rigidity, can be reproduced in a wide continuous rotation range. It becomes possible to acquire the vibration forcing force in the pair efficiently and with high accuracy.
As a result, dynamic characteristics such as resonance due to natural vibration and rigidity including interaction with elements having the frequency characteristics of the gear are added to the mesh transmission error that is a static characteristic of the gear pair. The vibration forcing force can be measured, and evaluation that leads to a dramatic improvement in the vibration design of the gears can be performed.

As shown in FIG. 1, the gear evaluation apparatus according to the present embodiment includes a torque meter 26 as torque detection means for detecting the load torque applied by the torsion mechanism 19.
In the present embodiment, the torque meter 26 is provided between the first gear 11 and the first pulley 15 in the first rotating shaft 13. As the torque meter 26, a known configuration can be used, and the torque meter 26 detects the load torque applied to the gear pair 10 by the torsion mechanism 19.
The position where the torque meter 26 is provided is not limited to the present embodiment as long as the load torque applied by the torsion mechanism 19 by the torque meter 26 can be detected.

Thus, by providing the torque meter 26, it is possible to accurately reproduce the torque state to which the predetermined load torque is applied in the gear pair 10, so that the evaluation according to the actual behavior of the gear pair is performed. It is possible to obtain the vibration forcing force in the gear pair more efficiently and with high accuracy.
That is, in an actual vehicle or the like, where the load torque applied to the gear pair in the transmission varies depending on the accelerator opening or the like, the meshing transmission error in the gear pair 10 depends on the load torque and varies depending on the magnitude. Therefore, the vibration forcing force of the gear pair corresponding to the actual torque state is acquired by acquiring the vibration forcing force in the gear pair 10 while detecting the load torque applied to the gear pair 10 by the torque meter 26. It is possible to obtain the vibration forcing force in the gear pair more efficiently and with high accuracy.

Next, 2nd embodiment of the gear evaluation apparatus which concerns on this invention is described using FIG. In addition, about the part which is common in 1st embodiment, or an equivalent part, the same code | symbol is attached | subjected and description is abbreviate | omitted suitably.
The gear evaluation device according to the present embodiment is for evaluating a gear pair 10 composed of a first gear 11 and a second gear 12 that mesh with each other, and is attached to the rotary shafts 13 and 14 of the gears 11 and 12. The first gear 11 and the second gear 12 are connected via pulleys 15 and 16 as rotating bodies rotating in synchronization with the gears 11 and 12 in the pair 10 and a belt 17 as a transmission member engaged with the pulleys 15 and 16. A drive motor 18 as a drive source for rotating the shaft and a load torque (meshing load) applied to the gear pair 10 via the rotation shaft provided between the gear and the pulley on any one of the rotation shafts 13 and 14. A torsion mechanism 19 as a torque applying means for applying a rotation, and a rotary encoder 35 as a rotation detecting means for detecting the rotation of one of the first gear 11 and the second gear 12; Torque meter 36 serving as torque detecting means for detecting the load torque applied by the torsion mechanism 19, and analysis means for analyzing the detected value detected by the rotary encoder 35 and the load torque value detected by the torque meter 36. And an analysis device 40.

As shown in FIG. 4, in the present embodiment, the torsion mechanism 19 is provided between the first gear 11 and the first pulley 15 in the first rotating shaft 13, and the gear pair 10 is interposed via the first rotating shaft 13. Is given load torque.
That is, the first rotating shaft 13 in the present embodiment includes a portion on the first gear 11 side (hereinafter referred to as “gear side shaft portion 13a”) and a portion on the first pulley 15 side (hereinafter referred to as “the gear side shaft portion 13a”). , Referred to as “pulley side shaft portion 13 b”), and the torsion mechanism 19 shifts the phase of rotation between the gear side shaft portion 13 a and the pulley side shaft portion 13 b to apply load torque. Thereby, the load torque is applied in any rotation direction in the gear pair 10 (direction in which the load torque is to be applied to the meshing of the gears). That is, in the first rotating shaft 13, the state in which the load torque is applied to the gear pair 10 by the torsion mechanism 19 is maintained, and the torsion mechanism 19, the gear side shaft portion 13a, and the pulley side shaft portion 13b are integrally formed. Rotate.

The rotary encoder 35 detects the rotation of any one of the first gear 11 and the second gear 12 as described above, and is provided at one end of the second rotating shaft 14 in the present embodiment. The rotation of the second gear 12 is detected via the second rotating shaft 14.
The rotation speed and rotation angle of the second gear 12 detected by the rotary encoder 35 are input to the analysis device 40 as detection values.

The torque meter 36 detects the load torque applied by the torsion mechanism 19 as described above. In the present embodiment, the torque meter 36 is provided between the second gear 12 and the second pulley 16 on the second rotating shaft 14. It has been. As the torque meter 36, a known configuration can be used, and the torque meter 36 detects a load torque applied to the gear pair 10 by the torsion mechanism 19.
The load torque detected by the torque meter 36 is input to the analysis device 40 as a load torque value.
The position where the torque meter 36 is provided is not limited to the present embodiment as long as the load torque applied by the torsion mechanism 19 by the torque meter 36 can be detected.

Then, the detection value detected by the rotary encoder 35 and the load torque value detected by the torque meter 36 are analyzed by the analysis device 40, and the gear pair 10 is evaluated and measured.
That is, in the analysis device 40, the second gear 12 detected by the rotary encoder 35 under the evaluation conditions such as the rotational speed of the gear pair 10 rotated by the drive motor 18 and the load torque applied by the torsion mechanism 19. The rotation and the load torque applied by the torsion mechanism 19 detected by the torque meter 36 are detected, and these are acquired as a rotation error including an engagement transmission error between the first gear 11 and the second gear 12. .

  Here, when acquiring the rotation error between the first gear 11 and the second gear 12 in the analysis device 40, the detection value (pulse) detected by the rotary encoder 35 and the load torque value detected by the torque meter 36 Is used.

As described above, the rotation error acquired based on the detection values from the rotary encoder 35 and the torque meter 36 is affected by the torque fluctuation caused by the motor ripple (minute rotation fluctuation, torque fluctuation) of the drive motor 18. However, such torque fluctuations are partially attenuated via the pulley mechanism 20 and are equally transmitted to the first gear 11 and the second gear 12. Therefore, in the analysis device 40, the load torque detected by the torque meter 36 is canceled and not detected.
Therefore, the analysis device 40 analyzes the torque fluctuation component detected by the torque meter 36 in the meshing order of the gear pair 10 based on the detection value detected by the rotary encoder 35, thereby forcing the vibration of the gear pair 10 to be forced. Only the torque fluctuation component caused by the force can be detected with high accuracy.

The gear evaluation apparatus of this embodiment can be used, for example, when performing relative evaluation of a gear meshing with a certain gear.
That is, in the present embodiment, the second gear 12 on the side whose rotation is detected by the rotary encoder 35 is used as a gear to be evaluated, and the second gear 12 is appropriately replaced to perform evaluation / measurement and compare them. The relative evaluation of the plurality of gears (second gear 12) with respect to the first gear 11 can be performed.

Subsequently, a more preferable mode (specific configuration) of the gear evaluation device according to the present invention will be described with reference to FIGS. 5 and 6. In addition, the same code | symbol is attached | subjected about the part which is common in the embodiment mentioned above, or an equivalent part, and description is abbreviate | omitted suitably.
As shown in FIG. 5, the gear evaluation device according to the present embodiment (hereinafter simply referred to as “this device”) includes a torque meter 46 on the first rotary shaft 13 and the torsion mechanism 19 on the second rotary shaft 14. The torsion mechanism 19 applies a load torque to the gear pair 10 via the second rotating shaft 14, and this load torque is detected by the torque meter 46.
The load torque detected by the torque meter 46 is input to the analysis device 50 as analysis means as a load torque value.

Further, in this apparatus, portions of the first rotating shaft 13 and the second rotating shaft 14 on the opposite side to the pulley mechanism 20 with respect to the gear pair 10 are supported by the base 29 via bearings 37 and 38, respectively. Yes. That is, one end portion side of the first rotating shaft 13 is supported by the base 29 via the bearing 37, and one end portion side of the second rotating shaft 14 is similarly supported by the base 29 via the bearing 38.
Here, cushion members 47 and 48 are interposed between the bearings 37 and 38 and the base 29, respectively. The cushion members 47 and 48 are for vibrationally insulating the bearings 37 and 38 and the base 29 by absorbing vibration. For example, an elastic member such as rubber or a cushion material using air is used. .
The cushion members 47 and 48 eliminate the vibration of the apparatus as a disturbance transmitted through the base 29 due to the vibration of the drive motor 18 when the gear pair 10 is evaluated and measured.

In addition, this apparatus is provided at one end of the first rotary shaft 13 and detects the rotation of the first gear 11, and the rotation of the second gear 12 provided at one end of the second rotary shaft 14. And a second rotary encoder 42 for detecting.
The rotation speed and rotation angle of the first gear 11 detected by the first rotary encoder 41 and the rotation speed and rotation angle of the second gear 12 detected by the second rotary encoder 42 are input to the analysis device 50 as detection values. Is done.

In addition, this apparatus includes acceleration pickups 43 and 44 as acceleration detection means for detecting the acceleration of vibration of the gear pair 10.
In this apparatus, an acceleration pickup 43 that detects the acceleration of vibration of the first gear 11 (hereinafter referred to as “first acceleration pickup 43”) and an acceleration pickup 44 that detects the acceleration of vibration of the second gear 12 (hereinafter referred to as “first acceleration pickup 43”). And “second acceleration pickup 44”).

The first acceleration pickup 43 is provided in the vicinity of the bearing 37 on the first rotating shaft 13 and detects the acceleration of vibration of the first gear 11 through the rotation of the first rotating shaft 13. The second acceleration pickup 44 is provided in the vicinity of the bearing 38 on the second rotating shaft 14 and detects the acceleration of the vibration of the second gear 12 through the rotation of the second rotating shaft 14.
The accelerations of the vibrations of the first gear 11 and the second gear 12 detected by the acceleration pickups 43 and 44 are input to the analysis device 50 as acceleration values.
The acceleration pickup may be provided only on one of the rotation axes.
The acceleration pickups 43 and 44 are preferably three-axis ones. That is, for example, when the gears in the gear pair 10 are bevel gears, the rotation of the first gear 11 and the second gear 12 in the gear pair 10 is in addition to the fluctuation component in the rotation direction and the fluctuation component in the radial direction, Since a fluctuation component in the thrust direction is also generated, from the viewpoint of performing detection corresponding to each of these components, the acceleration pickups 43 and 44 may be of a three-axis type rather than a one-axis type. preferable.

As described above, this apparatus has a configuration in which the acceleration pickups 43 and 44 are added to the gear evaluation apparatus of the first embodiment and the second embodiment described above.
The second embodiment further includes a rotary encoder (first rotary encoder 41) that detects the rotation of the first gear 11. That is, in the second embodiment, when the second gear 12 whose rotation is detected by the rotary encoder 35 (corresponding to the second rotary encoder 42 in the present apparatus) is defined as “one gear”, The first rotary encoder 41 that detects the rotation detects the rotation of the “other gear”.

As shown in FIG. 6, the analysis device 50 in the present apparatus is based on the detection values detected by the first rotary encoder 41 and the second rotary encoder 42, and the gear pair 10 (the first gear 11 and the second gear 12). A rotation angle fluctuation analyzing device 51 as a rotation angle fluctuation analyzing means for analyzing fluctuations in the rotation angle, a first rotary encoder 41 (or second rotary encoder 42), a torque meter 46, a first acceleration pickup 43 (second acceleration pickup) 44) and a rotation order analysis device 52 as a rotation order analysis means for analyzing the rotation order of the gear pair 10 based on the detection value detected by the rotation angle fluctuation analysis device 51.
The analysis device 50 has a data output device 53 as data output means for outputting the value analyzed by the rotation order analysis device 52.

  In the rotation angle fluctuation analyzing device 51, the rotation angle fluctuations of the first gear 11 and the second gear 12, that is, the first gear 11 and the second gear 12, based on the detection values from the first rotary encoder 41 and the second rotary encoder 42. Rotational delay advance (rotational deviation) with respect to the gear 12 is detected, and this is acquired as a rotation error including an engagement transmission error between the first gear 11 and the second gear 12.

  The rotation order analyzer 52 includes a load torque value applied to the gear pair 10 detected by the torque meter 46, an acceleration value of vibration in the gear pair 10 detected by the acceleration pickups 43 and 44, and the first rotary encoder 41. The detection value detected by (or the second rotary encoder 42) and the analysis value from the rotation angle variation analyzer 51 are input, and the rotation order analyzer 52 performs the rotation order analysis based on these values.

That is, in the rotation order analyzer 52, the load torque value input from the torque meter 46 is detected as a torque fluctuation component in the gear pair 10, and this is one of the rotation fluctuation components (the fluctuation component in the rotation direction) in the gear pair 10. Analyzed as one element.
The acceleration value input from the acceleration pickups 43 and 44 is detected as a radial direction fluctuation component (or a thrust direction fluctuation component) in the gear pair 10 and is analyzed as a vibration component in the gear pair 10.
The detection value input from the first rotary encoder 41 is analyzed as a rotational fluctuation component in the gear pair 10.
The analysis value input from the rotation angle variation analyzer 51 is analyzed as a relative variation component between the first gear 11 and the second gear 12.
Based on these values, the rotational order analyzer 52 uses, for example, FFT processing (fast Fourier transform processing), and the rotational order (frequency) of the gear pair 10 and the magnitude of vibration noise (amplitude) of the order component. Rotational order ratio analysis that expresses the relationship between

  The value output from the rotation order analyzer 52 is output from the data output device 53. In the data output device, the analysis result in the rotation order analyzer 52 is displayed on a monitor in a graph or a table or output from a printer to output data. Note that data may be stored in a storage medium as necessary.

  In the present apparatus described above, this causes the mesh transmission error, which is a static characteristic of the gear pair, to include natural vibration including interaction with elements having the frequency characteristic of the gear and resonance due to rigidity. With regard to the vibration forcing generated by adding dynamic characteristics, it is possible to evaluate and measure only the rotation angle fluctuation component, torque fluctuation component and vibration component with high accuracy without being affected by the resonance and vibration of the device. .

1 is an overall configuration diagram showing a first embodiment of a gear evaluation apparatus according to the present invention. The figure which shows the power transmission structure in a pulley mechanism. The figure which shows a twist mechanism. (A) is a partial sectional view of a side surface. (B) is the partial cross section seen from the axial direction. The whole block diagram which shows 2nd embodiment of the gear evaluation apparatus which concerns on this invention. The whole block diagram which shows the more preferable form of the gear evaluation apparatus which concerns on this invention. The block diagram which similarly shows a measurement and analysis structure.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Gear pair 11 1st gear 12 2nd gear 13 1st rotating shaft 14 2nd rotating shaft 15 1st pulley (rotary body)
16 Second pulley (rotating body)
17 Belt (power transmission member)
18 Drive motor (drive source)
19 Torsion mechanism (torque application means)
21.41 First rotary encoder (rotation detection means)
22.42 Second rotary encoder (rotation detection means)
26, 36, 46 Torque meter (torque detection means)
30, 40, 50 Analysis device (analysis means)
35 Rotary encoder (rotation detection means)
43 First Acceleration Pickup 44 Second Acceleration Pickup 51 Rotational Angle Fluctuation Analyzer (Rotational Angle Fluctuation Analysis Unit)
52 Rotational order analyzer (Rotational order analysis means)

Claims (5)

A gear evaluation device for evaluating a plurality of gears that mesh with each other and rotate,
A rotating body attached to the rotation shaft of each gear and rotating in synchronization with the gear;
A drive source for rotating the gear through a transmission member engaged with the rotating body;
A torque applying means that is provided between a gear and a rotating body on any one of the rotating shafts and applies a load torque to the gears via the rotating shaft;
Rotation detection means for detecting rotation of the gear;
Analyzing means for analyzing the detection value detected by the rotation detecting means;
A gear evaluation apparatus comprising:   The gear evaluation apparatus according to claim 1, further comprising a torque detection unit that detects a load torque applied by the torque application unit. An acceleration detecting means for detecting an acceleration of vibration of the gear;
The analysis means includes
A rotation angle fluctuation analyzing means for analyzing a fluctuation of the rotation angle of the gear based on a detection value detected by the rotation detection means;
A rotation order analysis means for analyzing the rotation order of the gear based on the detection values detected by the rotation detection means, the torque detection means, the acceleration detection means, and the rotation angle fluctuation analysis means;
The gear evaluation device according to claim 2, comprising: A gear evaluation device for evaluating a plurality of gears that mesh with each other and rotate,
A rotating body attached to the rotation shaft of each gear and rotating in synchronization with the gear;
A drive source for rotating the gear through a transmission member engaged with the rotating body;
A torque applying means that is provided between a gear and a rotating body on any one of the rotating shafts and applies a load torque to the gears via the rotating shaft;
Rotation detection means for detecting rotation of one of the gears;
Torque detecting means for detecting the load torque applied by the torque applying means;
Analyzing means for analyzing the detected value detected by the rotation detecting means and the load torque value detected by the torque detecting means;
A gear evaluation apparatus comprising: Acceleration detecting means for detecting acceleration of vibration of the gear;
Rotation detecting means for detecting rotation of another gear among the gears, and
The analysis means includes
A rotation angle fluctuation analyzing means for analyzing a fluctuation of the rotation angle of the gear based on a detection value detected by the rotation detection means;
A rotation order analysis means for analyzing the rotation order of the gear based on the detection values detected by the rotation detection means, the torque detection means, the acceleration detection means, and the rotation angle fluctuation analysis means;
The gear evaluation apparatus according to claim 4, comprising:

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