JP4780321B2 - Gear vibration forcing evaluation system - Google Patents

Gear vibration forcing evaluation system Download PDF

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JP4780321B2
JP4780321B2 JP2006203163A JP2006203163A JP4780321B2 JP 4780321 B2 JP4780321 B2 JP 4780321B2 JP 2006203163 A JP2006203163 A JP 2006203163A JP 2006203163 A JP2006203163 A JP 2006203163A JP 4780321 B2 JP4780321 B2 JP 4780321B2
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gear
torque
vibration forcing
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drive
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JP2008032416A (en
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勝之 北条
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Toyota Motor Corp
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Description

本発明は、歯車振動強制力評価装置に関するもので、自動車のトランスミッション等に用いられる歯車の回転方向の振動強制力を評価する装置に関する。   The present invention relates to a gear vibration forcing evaluation device, and more particularly to a device for evaluating a vibration forcing force in a rotation direction of a gear used in a transmission of an automobile or the like.

一般に、自動車のトランスミッションの騒音（振動）は、トランスミッションケース（ギヤボックス）に収容された歯車の振動強制力が主原因とされている。そこで、従来、歯車の振動強制力の主成分とされる歯車対の噛合い伝達誤差を測定し、該歯車対の噛合い伝達誤差に基づき歯車の振動強制力が評価されていた。この歯車対の噛合い伝達誤差は、各歯車の回転角度変動となって表れることから、２つの回転角度検出装置（ロータリーエンコーダ）によって測定された各歯車の回転角度変動成分に基づき導出されていた。例えば、特許文献１の噛合い伝達誤差測定装置は、各歯車の回転角度変動成分を相対する各回転角度検出装置によって測定し、各回転角度検出装置の出力信号を歯車のギヤ比によって補正することで歯車対の相対的な遅角／進角が演算処理されていた。このように、従来の噛合い伝達誤差測定装置は、２つの回転角度検出装置と複雑な演算処理とを必要とするため、設備が大型化される。また、噛合い伝達誤差を高い精度で測定するには、設備の共振領域を越えた高い回転速度領域の周波数帯での試験条件に限定される。   In general, the noise (vibration) of an automobile transmission is mainly caused by a vibration forcing force of a gear housed in a transmission case (gear box). Therefore, conventionally, the gear transmission error of the gear pair, which is a main component of the gear vibration forcing force, is measured, and the gear vibration forcing force is evaluated based on the gear transmission error of the gear pair. Since this gear pair meshing transmission error appears as a rotation angle variation of each gear, it was derived based on the rotation angle variation component of each gear measured by two rotation angle detection devices (rotary encoders). . For example, the meshing transmission error measuring device disclosed in Patent Document 1 measures the rotational angle variation component of each gear by the corresponding rotational angle detectors, and corrects the output signal of each rotational angle detector by the gear ratio of the gears. The relative retard / advance angle of the gear pair was calculated. As described above, the conventional meshing transmission error measuring device requires two rotation angle detecting devices and complicated calculation processing, so that the equipment is enlarged. Further, in order to measure the meshing transmission error with high accuracy, it is limited to the test conditions in the frequency band in the high rotational speed region exceeding the resonance region of the equipment.

また、従来、各歯車の各回転軸に錘やプーリを用いてトルクを負荷した状態で、一方（駆動側）の歯車を極めて低い回転数で回転させた場合の他方（従動側）の歯車の回転角度変動を検出し、検出された回転角度変動成分に基づき歯車対の噛合い伝達誤差を測定することが行われていた。この手法では、１つの回転角度検出装置にて歯車対の噛合い伝達誤差を測定することが可能になり、複雑な演算処理を廃止することができるが、連続的な回転を再現することができないため、動特性を含めた歯車の振動強制力を評価することができない。このように、従来の歯車振動強制力評価装置は、歯車の振動強制力の主成分とされる噛合い伝達誤差を回転角度変動成分に基づき測定することに主眼が置かれており、２つの回転角度検出装置の位相差を相対的に捉える必要がある。したがって、歯車の振動強制力を効率的に且つ高い精度で評価することが困難であった。   Further, conventionally, when torque is applied to each rotation shaft of each gear using a weight or a pulley, when one (drive side) gear is rotated at an extremely low rotational speed, the other (driven side) gear is The rotation angle variation is detected, and the meshing transmission error of the gear pair is measured based on the detected rotation angle variation component. In this method, it is possible to measure the meshing transmission error of the gear pair with one rotation angle detection device, and it is possible to eliminate complicated calculation processing, but it is not possible to reproduce continuous rotation. Therefore, it is impossible to evaluate the vibration forcing force of the gear including dynamic characteristics. As described above, the conventional gear vibration forcing evaluation apparatus mainly focuses on measuring the meshing transmission error, which is the main component of the gear vibration forcing, based on the rotation angle fluctuation component. It is necessary to relatively grasp the phase difference of the angle detection device. Therefore, it is difficult to evaluate the vibration forcing force of the gear efficiently and with high accuracy.

そこで、特許文献２には、駆動軸に装着された駆動側歯車と従動軸に装着された従動側歯車とを相互に噛合わせ、駆動軸に駆動用モータを連結すると共に従動軸にブレーキ用モータを連結しておいて、駆動用モータの駆動によって歯車対を回転させた時の従動側歯車の側面における並進方向の振動を計測し、計測された振動量から算出した噛合い時のトルクムラに基づき歯車の振動強制力を評価するトルクムラ評価装置の開示がある。このトルクムラ評価装置では、噛合い伝達誤差を噛合い周期のトルク変動として捉えることで、装置を簡素化することができると共に実機上の負荷を付与した状態における評価が可能である。しかしながら、このトルクムラ評価装置は、歯車の振動を振動測定装置によって直接計測する構造であるため、計測結果が装置全体の振動系を含んだものになり、トルク変動の計測精度に問題がある。また、このトルクムラ評価装置は、従動側歯車の並進振動量に基づきトルクムラを評価するものであり、歯車の伝達トルクの変動成分に基づき歯車の回転方向の振動強制力を評価するものではない。
特開平６−７４８６８号公報 特開２００５−１５６３２６号公報 Therefore, in Patent Document 2, the drive side gear mounted on the drive shaft and the driven side gear mounted on the driven shaft are meshed with each other, the drive motor is connected to the drive shaft, and the brake motor is connected to the driven shaft. , And measure the vibration in the translational direction on the side surface of the driven gear when the gear pair is rotated by driving the drive motor, and based on the torque unevenness at the time of meshing calculated from the measured vibration amount There is a disclosure of a torque unevenness evaluation apparatus that evaluates the vibration forcing force of a gear. In this torque unevenness evaluation device, the mesh transmission error is regarded as a torque fluctuation of the meshing cycle, whereby the device can be simplified and evaluation in a state where a load on an actual machine is applied is possible. However, since this torque unevenness evaluation apparatus has a structure in which the vibration of the gear is directly measured by the vibration measuring apparatus, the measurement result includes the vibration system of the entire apparatus, and there is a problem in the measurement accuracy of torque fluctuation. This torque unevenness evaluation apparatus evaluates torque unevenness based on the translational vibration amount of the driven gear, and does not evaluate the vibration forcing force in the rotational direction of the gear based on the fluctuation component of the transmission torque of the gear.
JP-A-6-74868 JP 2005-156326 A

そこで本発明は、上記事情に鑑みてなされたもので、歯車の回転方向の振動強制力を効率的に且つ高い精度で評価することが可能な歯車振動強制力評価装置を提供することを目的とする。   Therefore, the present invention has been made in view of the above circumstances, and an object thereof is to provide a gear vibration forcing evaluation device capable of efficiently and highly accurately evaluating vibration forcing in the rotation direction of a gear. To do.

上記目的を達成するために、本発明のうち請求項１に記載の発明は、駆動側歯車と従動側歯車とが噛合わされて構成される歯車対の振動強制力を、各歯車の歯数データ、出力軸の回転数検出データ、及び前記出力軸のトルク変動計測データを演算処理することで算出された前記歯車対の伝達トルクの変動成分に基づき評価する装置であって、前記駆動側歯車に駆動用モータを接続し、前記従動側歯車に吸収用モータを接続し、前記従動側歯車と同軸上の前記吸収用モータ側に制御用トルクメータを設けてなる機械制御系と、前記従動側歯車と同軸上の前記吸収用モータとは反対側に、回転角度検出手段、フライホイール、及び計測用トルクメータを設けてなる計測系と、によって構成されることを特徴とする。
In order to achieve the above object, according to the first aspect of the present invention, the vibration forcing force of a gear pair configured by meshing a driving side gear and a driven side gear is represented by tooth number data of each gear. rotational speed detection data of the output shaft, and a device for evaluation based on the fluctuation component of the transmission torque of the gear pair which is calculated by arithmetically processing the torque variation measurement data of the output shaft, to the drive-side gear connect the drive motor, and the connect the absorbing motor driven gear, the machine control system comprising providing a control torque meter to the absorption motor side on the driven gear coaxial with the driven gear the said absorption motor coaxial to the opposite side, characterized rotation angle detecting means, a flywheel, and formed by providing a measuring torque meter measuring system, to be composed of.

請求項２に記載の発明は、請求項１に記載の歯車振動強制力評価装置において、機械制御系の従動側歯車と制御用トルクメータとの間にカップリングを設けたことを特徴とする。   According to a second aspect of the present invention, in the gear vibration forcing evaluation device according to the first aspect, a coupling is provided between the driven gear of the machine control system and the control torque meter.

請求項３に記載の発明は、請求項１又は２に記載の歯車振動強制力評価装置において、機械制御系の駆動側歯車と同軸上の駆動用モータとは反対側にフライホイールを設けたことを特徴とする。   According to a third aspect of the present invention, in the gear vibration forcing evaluation device according to the first or second aspect, a flywheel is provided on the side opposite to the drive motor on the same axis as the drive gear of the machine control system. It is characterized by.

請求項４に記載の発明は、請求項１又は２に記載の歯車振動強制力評価装置において、駆動側歯車と同軸上の駆動用モータとは反対側に、回転角度検出手段、フライホイール、及び駆動側計測用トルクメータを設けてなる駆動側計測系を構成したことを特徴とする。   According to a fourth aspect of the present invention, in the gear vibration forcing evaluation device according to the first or second aspect, a rotation angle detecting means, a flywheel, and A drive-side measurement system including a drive-side measurement torque meter is configured.

したがって、請求項１に記載の歯車振動強制力評価装置では、計測された伝達トルクの変動成分に基づき歯車の回転方向の振動強制力を評価することができる。また、機械制御系と計測系とを分離したことで、装置の共振や振動が計測用トルクメータの計測値に影響するのを防ぐことができる。さらに、負荷トルクに相当する静的なトルク変動が機械制御系にて完結されるため、計測系には動的な伝達トルクの変動のみが発生し、計測用トルクメータによる計測のＳ／Ｎ比を高めることができる。
請求項２に記載の歯車振動強制力評価装置では、歯車の振動強制力が制御用トルクメータに伝達されるのを防ぐことができる。また、吸収用モータのトルクリップル等による外乱（振動）をカップリングにより遮断することができる。
請求項３に記載の歯車振動強制力評価装置では、歯車の振動強制力が従動側歯車に集約され、計測用トルクメータによって計測される伝達トルクの変動を増幅させることができる。
請求項４に記載の歯車振動強制力評価装置では、歯車の振動強制力を２つの伝達トルクの変動成分に基づき評価することが可能になり、ケーシングの伝達感度を含めた複合的な解析を実施することができる。 Therefore, in the gear vibration forcing force evaluation device according to the first aspect, the vibration forcing force in the rotation direction of the gear can be evaluated based on the measured fluctuation component of the transmission torque. Further, by separating the machine control system and the measurement system, it is possible to prevent the resonance and vibration of the apparatus from affecting the measurement value of the measurement torque meter. Furthermore, since the static torque fluctuation corresponding to the load torque is completed in the machine control system, only the dynamic transmission torque fluctuation occurs in the measurement system, and the S / N ratio of the measurement by the measurement torque meter Can be increased.
In the gear vibration forcing force evaluation device according to the second aspect, it is possible to prevent the gear vibration forcing force from being transmitted to the control torque meter. Also, disturbance (vibration) due to torque ripple of the absorption motor can be blocked by coupling.
In the gear vibration forcing force evaluation device according to the third aspect, the vibration forcing force of the gear is concentrated on the driven gear, and the fluctuation of the transmission torque measured by the measuring torque meter can be amplified.
In the gear vibration forcing force evaluation device according to claim 4, it becomes possible to evaluate the gear vibration forcing force based on fluctuation components of two transmission torques, and perform a complex analysis including the transmission sensitivity of the casing. can do.

歯車の回転方向の振動強制力を効率的に且つ高い精度で評価することが可能な歯車振動強制力評価装置を提供することができる。   It is possible to provide a gear vibration forcing evaluation device that can efficiently and highly accurately evaluate the vibration forcing in the rotation direction of the gear.

本発明の一実施形態を図１に基づいて説明する。本歯車振動強制力評価装置１は、噛合わされた歯車対２，３の回転方向の振動強制力を評価するものであって、機械制御系Ａと計測系Ｂとに分離されて構成される。そして、機械制御系Ａは、駆動側歯車２に駆動用モータ４を接続し、従動側歯車３に吸収用モータ５を接続し、従動側歯車３と同軸上の吸収用モータ５側に制御用トルクメータ６を設けて構成される。また、計測系Ｂは、従動側歯車３と同軸上の吸収用モータ５とは反対側に、ロータリーエンコーダ７（回転角度検出手段）、フライホイール８、及び計測用トルクメータ９を設けて構成される。これにより、本歯車振動強制力評価装置１は、計測系Ｂによって計測された歯車対２，３の伝達トルクの変動成分に基づき歯車対２，３の回転方向の振動強制力が評価される。また、本歯車振動強制力評価装置１は、伝達トルクの変動成分を計測する系（計測系Ｂ）を回転負荷を発生させる系（機械制御系Ａ）と分離したことで、計測用トルクメータ９による計測のＳ／Ｎ比が高められる。   An embodiment of the present invention will be described with reference to FIG. This gear vibration forcing evaluation apparatus 1 evaluates the vibration forcing in the rotational direction of the meshed gear pairs 2 and 3, and is configured to be separated into a machine control system A and a measurement system B. The machine control system A connects the driving motor 4 to the driving gear 2, connects the absorbing motor 5 to the driven gear 3, and controls the absorbing motor 5 on the same side as the driven gear 3. A torque meter 6 is provided. The measuring system B is configured by providing a rotary encoder 7 (rotation angle detecting means), a flywheel 8 and a measuring torque meter 9 on the opposite side of the driven gear 3 and the absorption motor 5 coaxially. The As a result, the gear vibration forcing evaluation apparatus 1 evaluates the vibration forcing in the rotational direction of the gear pairs 2 and 3 based on the fluctuation component of the transmission torque of the gear pairs 2 and 3 measured by the measurement system B. In addition, the gear vibration forcing evaluation device 1 separates the system (measurement system B) that measures the fluctuation component of the transmission torque from the system (machine control system A) that generates the rotational load, so that the measurement torque meter 9 The S / N ratio of measurement due to is increased.

機械制御系Ａは、一対の軸受け１０，１０によって軸支された入力軸１１の一端にプーリ１２が装着され、該プーリ１２と駆動用モータ４の回転軸に装着されたプーリ１３とにプーリベルト１４が巻回される。また、機械制御系Ａは、４つの軸受け１５によって軸支された出力軸１６の一端にプーリ１７が装着され、該プーリ１７と吸収用モータ５の回転軸に装着されたプーリ１８とにプーリベルト１９が巻回される。また、機械制御系Ａは、入力軸１１の一対の軸受け１０，１０間に駆動歯車２が取り付けられると共に、出力軸１６の中央の軸受け１５，１５間に従動歯車３が取り付けられる。さらに、機械制御系Ａは、出力軸１６と同軸上の吸収用モータ５側、即ち出力軸１６の従動歯車３とプーリ１７との間に、歯車対２，３にかかる負荷トルクが計測される制御用トルクメータ６が設けられる。   In the machine control system A, a pulley 12 is attached to one end of an input shaft 11 supported by a pair of bearings 10, 10, and a pulley belt is attached to the pulley 12 and a pulley 13 attached to a rotating shaft of the drive motor 4. 14 is wound. Further, the machine control system A has a pulley 17 attached to one end of an output shaft 16 supported by four bearings 15, and a pulley belt attached to the pulley 17 and a pulley 18 attached to a rotating shaft of the absorption motor 5. 19 is wound. In the machine control system A, the drive gear 2 is attached between the pair of bearings 10, 10 of the input shaft 11, and the driven gear 3 is attached between the bearings 15, 15 at the center of the output shaft 16. Further, the machine control system A measures the load torque applied to the gear pairs 2, 3 between the absorption motor 5 coaxially with the output shaft 16, that is, between the driven gear 3 and the pulley 17 of the output shaft 16. A control torque meter 6 is provided.

そして、吸収用モータ５は、制御装置２０によって、制御用トルクメータ６の出力信号（負荷トルクデータ）に基づきフィードバック制御される。駆動用モータ４は、制御装置２０によって制御され、吸収用モータ５は、制御用トルクメータ６の出力信号（計測値）に基づき制御装置２０によって制御される。なお、駆動用モータ４、吸収用モータ５、及び各軸受け１０，１５は、所定の防振対策がなされて（例えば、防振プレートを介して）ベースプレート上に固定される。計測系Ｂは、出力軸１６の吸収用モータ５と反対側、即ち図１における従動歯車３の左側に構成され、出力軸１６の他端にロータリーエンコーダ７が接続される。また、計測系Ｂは、ロータリーエンコーダ７と４つの軸受け１５のうちの図１において最も左側に配置された軸受け１５との間にフライホイール８が装着される。さらに、出力軸１６と同軸上の従動歯車３とフライホイール８との間には計測用トルクメータ９が設けられる。   The absorption motor 5 is feedback-controlled by the control device 20 based on the output signal (load torque data) of the control torque meter 6. The drive motor 4 is controlled by the control device 20, and the absorption motor 5 is controlled by the control device 20 based on the output signal (measured value) of the control torque meter 6. The drive motor 4, the absorption motor 5, and the bearings 10 and 15 are fixed on the base plate with a predetermined anti-vibration measure (for example, via an anti-vibration plate). The measurement system B is configured on the opposite side of the output shaft 16 from the absorption motor 5, that is, on the left side of the driven gear 3 in FIG. 1, and the rotary encoder 7 is connected to the other end of the output shaft 16. In the measurement system B, the flywheel 8 is mounted between the rotary encoder 7 and the bearing 15 disposed on the leftmost side in FIG. Further, a measuring torque meter 9 is provided between the driven gear 3 coaxial with the output shaft 16 and the flywheel 8.

そして、計測系Ｂは、ロータリーエンコーダ７によって検出された出力軸１６の回転数（従動歯車３の回転数）及び計測用トルクメータ９によって計測された出力軸１６のトルク変動（歯車対２，３における伝達トルク変動）に基づき、演算装置２１によって歯車対２，３の伝達トルクの変動成分が算出される構造になっている。なお、演算装置２１では、記憶部（マイクロコンピュータのメモリ）に記憶された歯車２，３の歯数データ、ロータリーエンコーダ７から出力された出力軸１６の回転数検出データ、及び計測用トルクメータ９から出力された出力軸１６のトルク変動計測データが回転次数分析処理（ＦＦＴ処理）されることにより歯車対２，３の伝達トルクの変動成分が算出される。   The measuring system B then detects the rotational speed of the output shaft 16 (the rotational speed of the driven gear 3) detected by the rotary encoder 7 and the torque fluctuation (gear pairs 2 and 3) of the output shaft 16 measured by the measuring torque meter 9. The variation component of the transmission torque of the gear pairs 2 and 3 is calculated by the arithmetic unit 21 based on the transmission torque variation in FIG. In the arithmetic unit 21, the tooth number data of the gears 2 and 3 stored in the storage unit (microcomputer memory), the rotation speed detection data of the output shaft 16 output from the rotary encoder 7, and the measurement torque meter 9. The torque fluctuation measurement data output from the output shaft 16 is subjected to rotational order analysis processing (FFT processing), whereby the fluctuation component of the transmission torque of the gear pairs 2 and 3 is calculated.

次に、本歯車振動強制力評価装置１の作用を説明する。まず、駆動側歯車２を入力軸１１の所定位置に取り付けると共に従動側歯車３を出力軸１６の所定位置に取り付ける。これにより、駆動側歯車２と従動側歯車３とが噛合わされた歯車対２，３が形成される。次に、吸収用モータ５によって出力軸１６に回転負荷（負荷トルク）をかけつつ、駆動用モータ４によって入力軸１１を軸心回りに回転させる。これにより、歯車対２，３がそれぞれ軸心回りに回転し、駆動側歯車２から従動側歯車３へ所定の回転トルクが伝達される。なお、本歯車振動強制力評価装置１では、制御装置２０によって制御用トルクメータ６の出力信号（負荷トルクデータ）に基づき吸収用モータ５をフィードバック制御することで、歯車対２，３に一定の伝達トルクを発生させる。   Next, the operation of the gear vibration forcing evaluation device 1 will be described. First, the driving gear 2 is attached to a predetermined position of the input shaft 11 and the driven gear 3 is attached to a predetermined position of the output shaft 16. Thereby, the gear pairs 2 and 3 in which the driving gear 2 and the driven gear 3 are meshed are formed. Next, while applying a rotational load (load torque) to the output shaft 16 by the absorption motor 5, the input shaft 11 is rotated around the axis by the drive motor 4. As a result, the gear pairs 2 and 3 rotate about their respective axes, and a predetermined rotational torque is transmitted from the driving gear 2 to the driven gear 3. In this gear vibration forcing evaluation device 1, the control motor 20 performs feedback control of the absorption motor 5 based on the output signal (load torque data) of the control torque meter 6, so that the gear pairs 2 and 3 are fixed. Generate transmission torque.

そして、トルク伝達時における出力軸１６の回転数をロータリーエンコーダ７（回転角度検出手段）によって検出すると共に、歯車対２，３の伝達トルク変動を計測用トルクメータ９によって計測する。また、記憶部（マイクロコンピュータのメモリ）に記憶された歯車２，３の歯数データ、ロータリーエンコーダ７から出力された出力軸１６の回転数検出データ、及び計測用トルクメータ９から出力された出力軸１６のトルク変動計測データを、演算装置２１によって回転次数分析処理（ＦＦＴ処理）し、歯車対２，３の伝達トルクの変動成分を算出する。そして、得られた歯車対２，３の伝達トルクの変動成分に基づき当該歯車対２，３の回転方向の振動強制力を評価する。   Then, the rotational speed of the output shaft 16 at the time of torque transmission is detected by the rotary encoder 7 (rotation angle detecting means), and the transmission torque fluctuation of the gear pairs 2 and 3 is measured by the measuring torque meter 9. Further, the number of teeth data of the gears 2 and 3 stored in the storage unit (microcomputer memory), the rotation number detection data of the output shaft 16 output from the rotary encoder 7, and the output output from the measuring torque meter 9. The torque fluctuation measurement data of the shaft 16 is subjected to rotational order analysis processing (FFT processing) by the arithmetic unit 21 to calculate the fluctuation component of the transmission torque of the gear pairs 2 and 3. Then, based on the obtained fluctuation component of the transmission torque of the gear pairs 2 and 3, the vibration forcing force in the rotational direction of the gear pairs 2 and 3 is evaluated.

ここで、本歯車振動強制力評価装置１では、歯車対２，３によって発生した振動強制力が計測用トルクメータ９を介してフライホイール８に伝達される。そして、本歯車振動強制力評価装置１では、当該振動強制力に対して十分大きい慣性を有するフライホイール８を用いることにより、振動強制力はフライホイール８に入力されず、図１における従動側歯車３の左側（吸収用モータ５と反対側）の出力軸１６にねじれとなって現れる。そして、本歯車振動強制力評価装置１は、該出力軸１６のねじれを計測用トルクメータ９によって伝達トルク変動として計測することで、歯車対２，３の回転方向の伝達トルクの変動成分が得られる。   Here, in the gear vibration forcing force evaluation device 1, the vibration forcing force generated by the gear pairs 2 and 3 is transmitted to the flywheel 8 through the measuring torque meter 9. And in this gear vibration forcing evaluation apparatus 1, by using the flywheel 8 which has a inertia large enough with respect to the said vibration forcing, a vibration forcing is not input into the flywheel 8, but the driven side gear in FIG. 3 appears as a twist on the output shaft 16 on the left side of 3 (the side opposite to the absorption motor 5). Then, the gear vibration forcing evaluation device 1 measures the torsion of the output shaft 16 as a transmission torque fluctuation by the measuring torque meter 9 to obtain a fluctuation component of the transmission torque in the rotational direction of the gear pairs 2 and 3. It is done.

この実施形態では以下の効果を奏する。
本歯車振動強制力評価装置１は、駆動側歯車２に駆動用モータ４を接続し、従動側歯車３に吸収用モータ５を接続し、従動側歯車３と同軸上の吸収用モータ５側に制御用トルクメータ６を設けてなる機械制御系Ａと、従動側歯車３と同軸上の吸収用モータ５とは反対側に構成され、ロータリーエンコーダ７（回転角度検出手段）、フライホイール８、及び計測用トルクメータ９を設けてなる計測系Ｂと、が分離されて構成される。
したがって、本歯車振動強制力評価装置１は、伝達トルクの変動成分を計測する系（計測系Ｂ）を、回転負荷を発生させる系（機械制御系Ａ）と分離したことで、当該装置１の共振や振動（駆動用モータ４及び吸収用モータ５のトルクリップル等）の計測用トルクメータ９への影響が排除される。これにより、計測用トルクメータ９による計測のＳ／Ｎ比が高められ、評価の精度を向上させることができる。
また、本歯車振動強制力評価装置１は、負荷トルクに相当する静的なトルク変動が機械制御系Ａにて完結されるため、計測系Ｂには動的な伝達トルクの変動のみを発生させることが可能になる。これにより、計測用トルクメータ９におけるフルスケールを計測したい動的な伝達トルク変動の最大値に設定することができ、計測用トルクメータ９による計測のＳ／Ｎ比が高められ、評価の精度を向上させることができる。
さらに、本歯車振動強制力評価装置１は、計測系Ｂによって計測された歯車対２，３の伝達トルクの変動成分に基づき歯車対２，３の回転方向の振動強制力が評価されるため、歯車対２，３の噛合い伝達誤差に基づき振動強制力が評価される従来の装置と比較して、当該歯車対２，３の回転方向の振動強制力の評価を効率化することができる。 This embodiment has the following effects.
In this gear vibration forcing evaluation device 1, a driving motor 4 is connected to a driving gear 2, an absorption motor 5 is connected to a driven gear 3, and the absorbing motor 5 is coaxial with the driven gear 3. The machine control system A provided with the control torque meter 6 is configured on the opposite side of the absorption gear 5 coaxially with the driven gear 3, and includes a rotary encoder 7 (rotation angle detection means), a flywheel 8, and A measuring system B provided with a measuring torque meter 9 is separated from the measuring system B.
Therefore, this gear vibration forcing evaluation device 1 separates the system (measurement system B) for measuring the fluctuation component of the transmission torque from the system (mechanical control system A) for generating a rotational load. The influence of the resonance and vibration (such as torque ripples of the driving motor 4 and the absorption motor 5) on the measuring torque meter 9 is eliminated. Thereby, the S / N ratio of measurement by the measuring torque meter 9 is increased, and the accuracy of evaluation can be improved.
In addition, since the static torque fluctuation corresponding to the load torque is completed in the machine control system A, the gear vibration forcing evaluation apparatus 1 generates only the dynamic transmission torque fluctuation in the measurement system B. It becomes possible. Thereby, the full scale in the measurement torque meter 9 can be set to the maximum value of the dynamic transmission torque fluctuation to be measured, the S / N ratio of measurement by the measurement torque meter 9 can be increased, and the accuracy of the evaluation can be improved. Can be improved.
Further, the gear vibration forcing evaluation apparatus 1 evaluates the vibration forcing force in the rotational direction of the gear pairs 2 and 3 based on the fluctuation component of the transmission torque of the gear pairs 2 and 3 measured by the measurement system B. Compared with the conventional apparatus in which the vibration forcing force is evaluated based on the meshing transmission error of the gear pairs 2 and 3, the evaluation of the vibration forcing force in the rotation direction of the gear pairs 2 and 3 can be made more efficient.

なお、実施形態は上記に限定されるものではなく、例えば次のように構成してもよい。また、以下に示す実施形態の構成要素には、図１に示した構成要素と同じの際は同一符号を付与して詳細な説明を省略する。
（他の実施形態１）
図２に示されるように、機械制御系Ａにおける出力軸１６の従動側歯車３と制御用トルクメータ６との間（出力軸１６と同軸上の吸収用モータ５側）にカップリング２２を設けて歯車振動強制力評価装置１を構成してもよい。
この場合、歯車対２，３の振動強制力が制御用トルクメータ６に伝達されるのを防ぐことができる。また、吸収用モータ５のトルクリップル等による外乱（振動）が歯車対２，３側に伝達されるのを防ぐことができる。 In addition, embodiment is not limited above, For example, you may comprise as follows. In addition, the same reference numerals are given to the constituent elements of the embodiment shown below when they are the same as the constituent elements shown in FIG.
(Other embodiment 1)
As shown in FIG. 2, a coupling 22 is provided between the driven gear 3 of the output shaft 16 and the control torque meter 6 (on the side of the absorption motor 5 coaxial with the output shaft 16) in the machine control system A. Thus, the gear vibration forcing evaluation device 1 may be configured.
In this case, the vibration forcing force of the gear pairs 2 and 3 can be prevented from being transmitted to the control torque meter 6. Further, it is possible to prevent disturbance (vibration) due to torque ripple or the like of the absorption motor 5 from being transmitted to the gear pairs 2 and 3 side.

（他の実施形態２）
図３に示されるように、機械制御系Ａにおける入力軸１１の駆動用モータ４とは反対側（駆動側歯車２と同軸上の駆動用モータ４とは反対側）にフライホイール２３を設けて歯車振動強制力評価装置１を構成してもよい。
この場合、歯車対２，３の振動強制力に対して十分大きい慣性を有するフライホイール２３を用いることにより、振動強制力はフライホイール２３に入力されず、従動側歯車３に集約され、図３における従動側歯車３の左側（吸収用モータ５と反対側）の出力軸１６にねじれとなって現れる。これにより、計測用トルクメータ９によって計測される伝達トルク変動が増幅され、計測用トルクメータ９による計測のＳ／Ｎ比が高められ、評価の精度を向上させることができる。
また、この実施形態では、駆動側歯車２のマスター部品を入力軸１１に固定することで、従動側歯車３に起因する振動強制力のみを評価することが可能になり、従動側歯車３の単体での品質保証を実現する評価装置としても用いることができる。 (Other embodiment 2)
As shown in FIG. 3, a flywheel 23 is provided on the side opposite to the drive motor 4 of the input shaft 11 in the machine control system A (the side opposite to the drive motor 4 coaxial with the drive side gear 2). The gear vibration forcing evaluation device 1 may be configured.
In this case, by using the flywheel 23 having a sufficiently large inertia with respect to the vibration forcing force of the gear pairs 2 and 3, the vibration forcing force is not input to the flywheel 23, but is concentrated on the driven gear 3 as shown in FIG. Appear to be twisted on the output shaft 16 on the left side of the driven gear 3 (opposite side to the absorption motor 5). Thereby, the transmission torque fluctuation measured by the measurement torque meter 9 is amplified, the S / N ratio of measurement by the measurement torque meter 9 is increased, and the accuracy of evaluation can be improved.
Further, in this embodiment, by fixing the master part of the driving side gear 2 to the input shaft 11, it becomes possible to evaluate only the vibration forcing force caused by the driven side gear 3. It can also be used as an evaluation device that realizes quality assurance in Japan.

（他の実施形態３）
図４に示されるように、駆動側歯車２と同軸上の駆動側歯車２に対して駆動用モータ４とは反対側（図４における右側）に、ロータリーエンコーダ２４（回転角度検出手段）、フライホイール２３、及び駆動側計測用トルクメータ２５を設けてなる駆動側計測系Ｃを構成して歯車振動強制力評価装置１を構成してもよい。
この場合、歯車対２，３の振動強制力を、計測系Ｂ及び計測系Ｃによって得られた２つの伝達トルクの変動成分に基づき評価することが可能になり、ケーシング（例えば、歯車対２，３が収容されるトランスミッションケース）の伝達感度を含めた複合的な解析を実施することができる。 (Other embodiment 3)
As shown in FIG. 4, a rotary encoder 24 (rotation angle detecting means), a fly on the opposite side (right side in FIG. 4) of the driving motor 4 with respect to the driving side gear 2 coaxial with the driving side gear 2. The gear vibration forcing evaluation apparatus 1 may be configured by configuring a drive side measurement system C including a wheel 23 and a drive side measurement torque meter 25.
In this case, it becomes possible to evaluate the vibration forcing force of the gear pairs 2 and 3 based on the fluctuation components of the two transmission torques obtained by the measurement system B and the measurement system C. 3 can be analyzed including the transmission sensitivity of the transmission case (3).

本実施形態の歯車振動強制力評価装置の説明図である。It is explanatory drawing of the gear vibration forcing force evaluation apparatus of this embodiment. 他の実施形態１の歯車振動強制力評価装置の説明図であって、出力軸と同軸上の吸収用モータ側にカップリングを設けてなる歯車振動強制力評価装置の図である。It is explanatory drawing of the gear vibration forcing force evaluation apparatus of other Embodiment 1, Comprising: It is a figure of the gear vibration forcing force evaluation apparatus which provides a coupling in the absorption motor side coaxial with an output shaft. 他の実施形態２の歯車振動強制力評価装置の説明図であって、駆動側歯車と同軸上の駆動用モータとは反対側にフライホイールを設けてなる歯車振動強制力評価装置の図である。It is explanatory drawing of the gear vibration forcing force evaluation apparatus of other Embodiment 2, Comprising: It is a figure of the gear vibration forcing force evaluation apparatus which provides a flywheel on the opposite side to the drive motor coaxial with a drive side gearwheel. . 他の実施形態３の歯車振動強制力評価装置の説明図であって、駆動側歯車と同軸上の駆動用モータとは反対側に計測系Ｃを設けてなる歯車振動強制力評価装置の図である。It is explanatory drawing of the gear vibration forcing force evaluation apparatus of other Embodiment 3, Comprising: It is a figure of the gear vibration forcing force evaluation apparatus which provides the measurement system C on the opposite side to the drive motor coaxial with a drive side gear. is there.

符号の説明Explanation of symbols

１ 歯車振動強制力評価装置、２ 駆動側歯車、３ 従動側歯車、４ 駆動用モータ、５ 吸収用モータ、６ 制御用トルクメータ、７ ロータリーエンコーダ（回転角度検出手段）、８ フライホイール、９ 計測用トルクメータ DESCRIPTION OF SYMBOLS 1 Gear vibration forcing evaluation apparatus, 2 Drive side gear, 3 Driven side gear, 4 Drive motor, 5 Absorption motor, 6 Control torque meter, 7 Rotary encoder (rotation angle detection means), 8 Flywheel, 9 Measurement Torque meter

Claims (4)

駆動側歯車と従動側歯車とが噛合わされて構成される歯車対の振動強制力を、各歯車の歯数データ、出力軸の回転数検出データ、及び前記出力軸のトルク変動計測データを演算処理することで算出された前記歯車対の伝達トルクの変動成分に基づき評価する装置であって、
前記駆動側歯車に駆動用モータを接続し、前記従動側歯車に吸収用モータを接続し、前記従動側歯車と同軸上の前記吸収用モータ側に制御用トルクメータを設けてなる機械制御系と、
前記従動側歯車と同軸上の前記吸収用モータとは反対側に、回転角度検出手段、フライホイール、及び計測用トルクメータを設けてなる計測系と、
によって構成されることを特徴とする歯車振動強制力評価装置。 Calculates the vibration forcing force of the gear pair configured by meshing the drive side gear and the driven side gear , tooth number data of each gear, output speed detection data of the output shaft, and torque fluctuation measurement data of the output shaft An apparatus for evaluating based on the fluctuation component of the transmission torque of the gear pair calculated by
A mechanical control system in which a driving motor is connected to the driving gear, an absorption motor is connected to the driven gear, and a control torque meter is provided on the absorption motor side coaxial with the driven gear; ,
A measurement system comprising a rotation angle detection means, a flywheel, and a measurement torque meter on the opposite side of the driven gear coaxially with the absorption motor;
A gear vibration forcing evaluation device comprising: 前記機械制御系の前記従動側歯車と前記制御用トルクメータとの間にカップリングを設けたことを特徴とする請求項１に記載の歯車振動強制力評価装置。   The gear vibration forcing evaluation device according to claim 1, wherein a coupling is provided between the driven gear of the mechanical control system and the control torque meter. 前記機械制御系の前記駆動側歯車と同軸上の前記駆動用モータとは反対側にフライホイールを設けたことを特徴とする請求項１又は２に記載の歯車振動強制力評価装置。   The gear vibration forcing evaluation device according to claim 1, wherein a flywheel is provided on a side opposite to the drive motor coaxial with the drive side gear of the mechanical control system. 前記駆動側歯車と同軸上の前記駆動用モータとは反対側に、回転角度検出手段、フライホイール、及び駆動側計測用トルクメータを設けてなる駆動側計測系を構成したことを特徴とする請求項１又は２に記載の歯車振動強制力評価装置。   The drive-side measurement system comprising a rotation angle detection means, a flywheel, and a drive-side measurement torque meter on the opposite side of the drive-side gear and the drive motor on the same axis is provided. Item 3. The gear vibration forcing evaluation device according to Item 1 or 2.
JP2006203163A 2006-07-26 2006-07-26 Gear vibration forcing evaluation system Expired - Fee Related JP4780321B2 (en)

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