JP2008069812A - Driving-power transfer system - Google Patents

Driving-power transfer system Download PDF

Info

Publication number
JP2008069812A
JP2008069812A JP2006247176A JP2006247176A JP2008069812A JP 2008069812 A JP2008069812 A JP 2008069812A JP 2006247176 A JP2006247176 A JP 2006247176A JP 2006247176 A JP2006247176 A JP 2006247176A JP 2008069812 A JP2008069812 A JP 2008069812A
Authority
JP
Japan
Prior art keywords
differential
planetary gear
driving force
planetary
motor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP2006247176A
Other languages
Japanese (ja)
Other versions
JP4961919B2 (en
Inventor
Minoru Onitake
稔 鬼武
Isao Ito
功 伊藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
JTEKT Corp
Original Assignee
JTEKT Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by JTEKT Corp filed Critical JTEKT Corp
Priority to JP2006247176A priority Critical patent/JP4961919B2/en
Publication of JP2008069812A publication Critical patent/JP2008069812A/en
Application granted granted Critical
Publication of JP4961919B2 publication Critical patent/JP4961919B2/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/36—Differential gearings characterised by intentionally generating speed difference between outputs
    • F16H2048/364—Differential gearings characterised by intentionally generating speed difference between outputs using electric or hydraulic motors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

Landscapes

  • Hybrid Electric Vehicles (AREA)
  • Retarders (AREA)
  • Arrangement And Driving Of Transmission Devices (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a driving-power transfer system improved in vehicle-mountability and in the balance of weight. <P>SOLUTION: A rear differential 8 as driving-power transfer system comprises a differential mechanism 11 for transmitting the inputted driving power to the right and left rear-axles 9L, 9R, while allowing a differential between them, a planetary-gear mechanism 21 placed between both the rear axles 9L, 9R to be connected to a driving motor 20, and a transmission mechanism 31 for correcting a transmission-gear ratio set in the planetary-gear mechanism 21. The transmission mechanism 31 is placed on the opposite side to the planetary gear mechanism 21 with the differential mechanism 11 in between. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、駆動源から入力された駆動力の第１及び第２の出力軸への配分比率を制御可能な駆動力配分装置に関するものである。   The present invention relates to a driving force distribution device capable of controlling a distribution ratio of driving force input from a driving source to first and second output shafts.

上記のような駆動力配分装置として、従来、入力された駆動力を相互の差動を許容しつつ第１及び第２の出力軸に伝達する差動機構（ディファレンシャル）と、第１及び第２の出力軸間に介在されるとともにモータに駆動連結された遊星歯車機構とを備えたものがある（例えば、特許文献１参照）。即ち、このような駆動力配分装置は、制御用駆動源であるモータのトルクを遊星歯車機構を介して第１又は第２の出力軸に伝達する。そして、そのモータトルクに基づき第１及び第２の出力軸間に差回転を生じさせることにより差動機構に入力される駆動力の第１及び第２の出力軸への配分比率を制御可能な構成となっている。そして、さらには、上記のような遊星歯車機構に設定された変速比を補正するための変速機構が設けられている。   Conventionally, as the driving force distribution device as described above, a differential mechanism (differential) that transmits the input driving force to the first and second output shafts while allowing mutual differential, and the first and second And a planetary gear mechanism that is drive-coupled to a motor (see, for example, Patent Document 1). That is, such a driving force distribution device transmits the torque of the motor, which is a control drive source, to the first or second output shaft via the planetary gear mechanism. Then, by causing a differential rotation between the first and second output shafts based on the motor torque, the distribution ratio of the driving force input to the differential mechanism to the first and second output shafts can be controlled. It has a configuration. Further, there is provided a speed change mechanism for correcting the speed ratio set in the planetary gear mechanism as described above.

具体的には、この駆動力配分装置において、遊星歯車機構は、同軸配置されたピッチ円径及び歯数の異なる一対のサンギヤと、両サンギヤに噛合する二連ピニオンと、この二連ピニオンを自転可能且つ公転可能に支承するプラネタリキャリヤとにより構成され、そのうちのプラネタリキャリヤがモータに駆動連結される入力要素として設定されている。そして、その変速比を補正するための変速機構は、モータに駆動連結された遊星歯車機構と同一の構成を有する遊星歯車機構を反転させて直列に接続し、そのプラネタリキャリヤを回転不能に固定することにより形成されている。即ち、同一の構成を有する二つの遊星歯車機構を反転させて直列に接続、つまり双方の二つのサンギヤのうち歯数の等しいサンギヤ同士を駆動連結することで、両者の変速比を相殺している。そして、変速機構を構成する側のプラネタリキャリヤを回転不能に固定することにより、入力軸及び第１及び第２の出力軸が回転しても、出力軸間において差動が生じない限り、モータは回転しない。したがって、信頼性及び耐久性の向上、並びにモータ負荷の低減が可能であり、ひいては、これによるモータ及び装置全体の小型化が可能な構成となっている。
特開２００６−１１２４７４号公報 Specifically, in this driving force distribution device, the planetary gear mechanism includes a pair of sun gears that are coaxially arranged with different pitch circle diameters and different numbers of teeth, a double pinion that meshes with both sun gears, and the double pinion that rotates. The planetary carrier is supported so as to be capable of revolving and is capable of revolving, and the planetary carrier is set as an input element that is drivingly connected to the motor. And the speed change mechanism for correcting the speed change ratio reverses the planetary gear mechanism having the same configuration as that of the planetary gear mechanism drivingly connected to the motor and connects it in series, and fixes the planetary carrier so that it cannot rotate. It is formed by. In other words, two planetary gear mechanisms having the same configuration are inverted and connected in series, that is, the two gears of the two sun gears are driven and connected to each other to cancel the gear ratio. . Then, by fixing the planetary carrier on the side constituting the speed change mechanism so as not to rotate, even if the input shaft and the first and second output shafts rotate, the motor can be used as long as there is no differential between the output shafts. Does not rotate. Therefore, the reliability and durability can be improved, and the motor load can be reduced. As a result, the motor and the entire apparatus can be reduced in size.
JP 2006-112474 A

しかしながら、上記従来の構成では、遊星歯車機構と変速機構とが直列に連結、即ち差動機構の片側に集約して配置される構成であるため、車両への搭載性に難がある。加えて、差動機構から変速機構までの距離が開くことで各ギヤの潤滑の観点からも不利である。そして、特に、左右駆動力配分装置として用いた場合には、その左右の重量バランスの偏りが車両操縦安定性向上の妨げとなるという問題がある。   However, in the above-described conventional configuration, the planetary gear mechanism and the transmission mechanism are connected in series, that is, arranged so as to be concentrated on one side of the differential mechanism, so that mounting on a vehicle is difficult. In addition, since the distance from the differential mechanism to the transmission mechanism is increased, it is disadvantageous from the viewpoint of lubrication of each gear. In particular, when used as a left / right driving force distribution device, there is a problem that the deviation of the left / right weight balance hinders the improvement of vehicle handling stability.

本発明は、上記問題点を解決するためになされたものであって、その目的は、車両搭載性及び重量バランスに優れた駆動力配分装置を提供することにある。   The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a driving force distribution device that is excellent in vehicle mountability and weight balance.

上記問題点を解決するために、請求項１に記載の発明は、入力される駆動力を相互の差動を許容しつつ車両の左右の車輪にそれぞれ連結された第１及び第２の出力軸に伝達する差動機構と、前記第１及び第２の出力軸間に介在されるとともにモータに駆動連結された遊星歯車機構と、前記遊星歯車機構に設定された変速比を補正するための変速機構とを備え、モータトルクに基づき前記第１及び第２の出力軸間に差回転を生じさせることにより前記入力される駆動力の前記第１及び第２の出力軸への配分比率を制御可能な駆動力配分装置において、前記変速機構は、前記差動機構を挟んで前記遊星歯車機構の反対側に配置されること、を要旨とする。   In order to solve the above-mentioned problems, the invention according to claim 1 is characterized in that the first and second output shafts respectively connected to the left and right wheels of the vehicle while allowing the input driving force to be mutually differential. A planetary gear mechanism that is interposed between the first and second output shafts and is drivingly connected to the motor, and a speed change for correcting a gear ratio set in the planetary gear mechanism. And a distribution ratio of the input driving force to the first and second output shafts can be controlled by causing a differential rotation between the first and second output shafts based on a motor torque. The gist of the present invention is that the speed change mechanism is arranged on the opposite side of the planetary gear mechanism with the differential mechanism interposed therebetween.

上記構成によれば、差動機構を挟んで遊星歯車機構と変速機構とを対称的に配置することで、重量バランスを改善することができるとともに、良好な車両搭載性を実現することができる。そして、更には、これに加え、潤滑状態の向上を図ることもできる。   According to the above configuration, by arranging the planetary gear mechanism and the speed change mechanism symmetrically with the differential mechanism interposed therebetween, it is possible to improve the weight balance and realize good vehicle mountability. In addition to this, the lubrication state can be improved.

請求項２に記載の発明は、前記遊星歯車機構は、何れか一方の出力軸と同軸配置された一対のサンギヤと、両サンギヤに噛合する二連ピニオンと、該二連ピニオンを自転及び公転可能に支承するプラネタリキャリヤとにより構成されるとともに、前記プラネタリキャリヤにより前記モータに駆動連結される入力要素が構成されるものであって、前記変速機構は、前記遊星歯車機構と同一の構成を有する遊星歯車を前記差動機構を介して対称に連結し、そのプラネタリキャリヤを回転不能に固定することにより構成されること、を要旨とする。   According to a second aspect of the present invention, the planetary gear mechanism includes a pair of sun gears coaxially arranged with any one of the output shafts, a double pinion that meshes with both sun gears, and the double pinion that can rotate and revolve. A planetary carrier that is supported by the planetary carrier and an input element that is drivingly connected to the motor by the planetary carrier. The planetary gear mechanism has the same configuration as the planetary gear mechanism. The gist of the present invention is that the gears are connected symmetrically via the differential mechanism and the planetary carrier is fixed so as not to rotate.

上記構成によれば、遊星歯車機構の変速比を補正するための最適な変速機構を容易に形成することができる。
請求項３に記載の発明は、前記モータは、前記出力軸と同軸に配置されること、を要旨とする。 According to the above configuration, an optimum speed change mechanism for correcting the speed ratio of the planetary gear mechanism can be easily formed.
The gist of the invention described in claim 3 is that the motor is arranged coaxially with the output shaft.

上記構成によれば、より一層、装置の小型化を図ることができる。
請求項４に記載の発明は、前記差動機構には、遊星歯車が用いられること、を要旨とする。 According to the said structure, size reduction of an apparatus can be achieved further.
The gist of the invention of claim 4 is that a planetary gear is used for the differential mechanism.

即ち、差動機構を挟んで遊星歯車機構の反対側に変速機構を配置した構成では、差動機構に遊星歯車を用いることで、両出力軸が同速度で同方向に回転する場合、即ち車両の直進状態でも同差動機構の二出力軸間に回転差が生じ、そのプラネタリギヤが公転することになる。その結果、各プラネタリギヤによってケーシング内の潤滑油が攪拌され、これにより各ギヤの潤滑状態をより良好なものとすることができる。   That is, in the configuration in which the speed change mechanism is arranged on the opposite side of the planetary gear mechanism across the differential mechanism, the planetary gear is used for the differential mechanism, so that both output shafts rotate in the same direction at the same speed, that is, the vehicle Even in the straight traveling state, a difference in rotation occurs between the two output shafts of the differential mechanism, and the planetary gear revolves. As a result, the lubricating oil in the casing is agitated by each planetary gear, and thereby the lubrication state of each gear can be improved.

本発明によれば、車両搭載性及び重量バランスに優れた駆動力配分装置を提供することができる。   ADVANTAGE OF THE INVENTION According to this invention, the driving force distribution apparatus excellent in vehicle mounting property and weight balance can be provided.

以下、本発明を具体化した一実施形態を図面に従って説明する。
図１に示すように、車両１は、前輪駆動車をベースとする四輪駆動車であり、エンジン２の片側に組み付けられたトランスアクスル３には、一対のフロントアクスル４Ｌ，４Ｒが連結されており、エンジン２の駆動力は、これらフロントアクスル４Ｌ，４Ｒを介して前輪５Ｌ，５Ｒに伝達される。また、トランスアクスル３には、上記各フロントアクスル４Ｌ，４Ｒとともにプロペラシャフト６が連結されており、同プロペラシャフト６は、トルクカップリング７及びリヤディファレンシャル８を介して一対のリヤアクスル９Ｌ，９Ｒと連結されている。そして、これらプロペラシャフト６、リヤディファレンシャル８、及びリヤアクスル９Ｌ，９Ｒを介して、後輪１０Ｌ，１０Ｒにも駆動力が伝達されるようになっている。 DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, an embodiment of the invention will be described with reference to the drawings.
As shown in FIG. 1, a vehicle 1 is a four-wheel drive vehicle based on a front-wheel drive vehicle, and a pair of front axles 4L and 4R are connected to a transaxle 3 assembled on one side of an engine 2. The driving force of the engine 2 is transmitted to the front wheels 5L and 5R via the front axles 4L and 4R. A propeller shaft 6 is connected to the transaxle 3 together with the front axles 4L and 4R. The propeller shaft 6 is connected to a pair of rear axles 9L and 9R via a torque coupling 7 and a rear differential 8. Has been. The driving force is also transmitted to the rear wheels 10L and 10R via the propeller shaft 6, the rear differential 8, and the rear axles 9L and 9R.

図２に示すように、本実施形態のリヤディファレンシャル８は、遊星歯車式の差動機構１１を備えている。具体的には、差動機構１１は、外歯ギヤ１２と一体に形成されたリングギヤ１３を有しており、同リングギヤ１３の内側にはサンギヤ１４が同軸に配置されている。また、これらリングギヤ１３及びサンギヤ１４の間には、第１プラネタリギヤ１５ａ及び第２プラネタリギヤ１５ｂからなる複数のプラネタリギヤ対１５が介在されており、各第１プラネタリギヤ１５ａはリングギヤ１３に、各第２プラネタリギヤ１５ｂはサンギヤ１４にそれぞれ噛合されている。そして、これら各プラネタリギヤ対１５を構成する第１プラネタリギヤ１５ａ及び第２プラネタリギヤ１５ｂは、互いに噛合された状態で、プラネタリキャリヤ１６によりそれぞれ自転可能且つ公転可能に支承されている。   As shown in FIG. 2, the rear differential 8 of this embodiment includes a planetary gear type differential mechanism 11. Specifically, the differential mechanism 11 has a ring gear 13 formed integrally with the external gear 12, and a sun gear 14 is coaxially disposed inside the ring gear 13. Further, between the ring gear 13 and the sun gear 14, a plurality of planetary gear pairs 15 including a first planetary gear 15a and a second planetary gear 15b are interposed. Are respectively meshed with the sun gear 14. The first planetary gear 15a and the second planetary gear 15b constituting each planetary gear pair 15 are supported by the planetary carrier 16 so as to be capable of rotating and revolving, respectively, while being engaged with each other.

本実施形態では、トルクカップリング７を介してプロペラシャフト６に連結された入力軸１７の一端には、ドライブピニオン１８が設けられており、リングギヤ１３は、その外周に形成された外歯ギヤ１２が、このドライブピニオン１８に噛合されることにより同ドライブピニオン１８と駆動連結されている。そして、サンギヤ１４は、左のリヤアクスル９Ｌの軸端に、プラネタリキャリヤ１６は、右のリヤアクスル９Ｒの軸端に固定されることにより、対応する各リヤアクスル９Ｌ，９Ｒとともに一体回転可能に設けられている。   In this embodiment, a drive pinion 18 is provided at one end of the input shaft 17 connected to the propeller shaft 6 via the torque coupling 7, and the ring gear 13 is an external gear 12 formed on the outer periphery thereof. Are connected to the drive pinion 18 by being engaged with the drive pinion 18. The sun gear 14 is fixed to the shaft end of the left rear axle 9L, and the planetary carrier 16 is fixed to the shaft end of the right rear axle 9R, so that the sun gear 14 and the corresponding rear axles 9L and 9R can rotate together. .

即ち、プロペラシャフト６の回転は、トルクカップリング７及び入力軸１７からドライブピニオン１８を介してリングギヤ１３へと伝達され、同リングギヤ１３とともにサンギヤ１４及びプラネタリキャリヤ１６が一体的に回転することにより、その駆動力が両リヤアクスル９Ｌ，９Ｒから左右の後輪１０Ｌ，１０Ｒへと伝達される。そして、車両旋回時等、左右の後輪１０Ｌ，１０Ｒに生ずる回転差は、各第１プラネタリギヤ１５ａ及び各第２プラネタリギヤ１５ｂのそれぞれが、自転しつつサンギヤ１４の周りを公転することにより、これを許容する構成となっている。   That is, the rotation of the propeller shaft 6 is transmitted from the torque coupling 7 and the input shaft 17 to the ring gear 13 through the drive pinion 18, and the sun gear 14 and the planetary carrier 16 rotate together with the ring gear 13. The driving force is transmitted from the rear axles 9L, 9R to the left and right rear wheels 10L, 10R. The difference in rotation that occurs between the left and right rear wheels 10L, 10R, such as when the vehicle is turning, is caused by each of the first planetary gears 15a and the second planetary gears 15b revolving around the sun gear 14 while rotating. It is an acceptable configuration.

また、本実施形態のリヤディファレンシャル８は、エンジン２の駆動力の左右の後輪１０Ｌ，１０Ｒへの配分比率を制御可能な駆動力配分装置としての機能を有している。
詳述すると、本実施形態では、駆動力配分装置の第１及び第２の出力軸を構成する両リヤアクスル９Ｌ，９Ｒ間には、制御用駆動源であるモータ２０と駆動連結された遊星歯車機構２１が介在されている。そして、そのモータトルクに基づき両リヤアクスル９Ｌ，９Ｒ間に差回転を生じさせることによりプロペラシャフト６からドライブピニオン１８を介して入力されるエンジン２の駆動力の両リヤアクスル９Ｌ，９Ｒへの配分比率を制御可能な構成となっている。 Further, the rear differential 8 of the present embodiment has a function as a driving force distribution device capable of controlling a distribution ratio of the driving force of the engine 2 to the left and right rear wheels 10L, 10R.
More specifically, in this embodiment, a planetary gear mechanism that is drivingly connected to the motor 20 that is a control drive source is provided between the rear axles 9L and 9R constituting the first and second output shafts of the driving force distribution device. 21 is interposed. Then, by causing a differential rotation between the rear axles 9L and 9R based on the motor torque, the distribution ratio of the driving force of the engine 2 input from the propeller shaft 6 via the drive pinion 18 to the rear axles 9L and 9R is changed. It has a controllable configuration.

さらに詳述すると、本実施形態では、遊星歯車機構２１は、左側のリヤアクスル９Ｌと同軸配置されるとともに互いに歯数の異なる一対のサンギヤ２２，２３と、これら両サンギヤ２２，２３に噛合する複数の二連ピニオン２４と、これら各二連ピニオン２４を自転可能且つ公転可能に支承するプラネタリキャリヤ２５とにより構成されている。尚、本実施形態では、第１のサンギヤ２２の方が第２のサンギヤ２３よりも僅かに歯数が大きく設定されている。具体的には、第１のサンギヤ２２の歯数は３２、第２のサンギヤ２３の歯数は３０であり、これらの歯数の比は、第１のサンギヤ２２の歯数：第２のサンギヤ２３の歯数＝１：０．９〜１．１が望ましい。また、この歯数の比は両サンギヤのピッチ円径の比に等しい。つまり、第１のサンギヤ２２は第２のサンギヤ２３よりも大きな径を有している。そして、二連ピニオン２４は、これら第１及び第２のサンギヤ２２，２３に噛合する第１及び第２ピニオン２４ａ，２４ｂを一体回転可能に連結することにより形成されている。   More specifically, in the present embodiment, the planetary gear mechanism 21 includes a pair of sun gears 22 and 23 that are coaxially arranged with the left rear axle 9L and have a different number of teeth, and a plurality of meshing gears. A double pinion 24 and a planetary carrier 25 that supports each double pinion 24 so as to be capable of rotating and revolving are constituted. In the present embodiment, the first sun gear 22 has a slightly larger number of teeth than the second sun gear 23. Specifically, the number of teeth of the first sun gear 22 is 32, the number of teeth of the second sun gear 23 is 30, and the ratio of the number of teeth is the number of teeth of the first sun gear 22: second sun gear. The number of teeth of 23 = 1: 0.9 to 1.1 is desirable. The ratio of the number of teeth is equal to the ratio of the pitch circle diameters of both sun gears. That is, the first sun gear 22 has a larger diameter than the second sun gear 23. The double pinion 24 is formed by connecting the first and second pinions 24a and 24b meshing with the first and second sun gears 22 and 23 so as to be integrally rotatable.

本実施形態では、第１のサンギヤ２２は、左側のリヤアクスル９Ｌと同軸配置された中空状のスリーブ２６を介して差動機構１１のプラネタリキャリヤ１６と一体回転可能に連結されており、第２のサンギヤ２３は、左側のリヤアクスル９Ｌと一体回転可能に設けられている。そして、これら第１及び第２のサンギヤ２２，２３に噛合された二連ピニオン２４を支承するプラネタリキャリヤ２５が、モータ２０に駆動連結される入力要素として設定されている。尚、本実施形態のモータ２０には、中空状のモータ軸２０ａを有するブラシレスモータが採用されており、同モータ２０は、遊星歯車機構２１よりも左の後輪１０Ｌ側において左側のリヤアクスル９Ｌと同軸に配置されている。   In the present embodiment, the first sun gear 22 is coupled to the planetary carrier 16 of the differential mechanism 11 through a hollow sleeve 26 coaxially disposed with the left rear axle 9L so as to be integrally rotatable. The sun gear 23 is provided so as to be rotatable integrally with the left rear axle 9L. A planetary carrier 25 that supports the double pinion 24 meshed with the first and second sun gears 22 and 23 is set as an input element that is drivingly connected to the motor 20. The motor 20 of this embodiment employs a brushless motor having a hollow motor shaft 20a. The motor 20 is connected to the left rear axle 9L on the left rear wheel 10L side of the planetary gear mechanism 21. It is arranged coaxially.

即ち、モータ２０を作動させ、そのモータトルクに基づいてプラネタリキャリヤ２５を回転させることにより、第１及び第２の出力軸間に差回転が生ずる。そして、このモータトルクに基づく差回転を制御することにより、エンジン２の駆動力の両リヤアクスル９Ｌ，９Ｒへの配分比率を制御することが可能となっている。   That is, by operating the motor 20 and rotating the planetary carrier 25 based on the motor torque, a differential rotation occurs between the first and second output shafts. Then, by controlling the differential rotation based on the motor torque, it is possible to control the distribution ratio of the driving force of the engine 2 to the rear axles 9L and 9R.

一方、本実施形態では、右側のリヤアクスル９Ｒは、第１アクスル９Ｒａ及び第２アクスル９Ｒｂにより構成されており、これら第１アクスル９Ｒａ及び第２アクスル９Ｒｂは、変速機構３１を介して連結されている。そして、この変速機構３１により、遊星歯車機構２１に設定された変速比を補正して、非モータ駆動時におけるプラネタリキャリヤの回転を防止する構成となっている。   On the other hand, in the present embodiment, the right rear axle 9R is constituted by a first axle 9Ra and a second axle 9Rb, and the first axle 9Ra and the second axle 9Rb are connected via a transmission mechanism 31. . The speed change mechanism 31 corrects the speed change ratio set in the planetary gear mechanism 21 to prevent rotation of the planetary carrier during non-motor drive.

詳述すると、本実施形態の変速機構３１は、遊星歯車機構２１と同一の構成を有する遊星歯車を差動機構１１を介して対称に連結することにより形成されている。具体的には、本実施形態の変速機構３１は、遊星歯車機構２１と同様の第１及び第２のサンギヤ３２，３３、これら両サンギヤ３２，３３に噛合する複数の二連ピニオン３４、及びこれら各二連ピニオン３４を自転可能且つ公転可能に支承するプラネタリキャリヤ３５を備えている。そして、第１のサンギヤ３２は、差動機構１１のプラネタリキャリヤ１６に連結された第１アクスル９Ｒａと、第２のサンギヤ３３は、右側の後輪１０Ｒに連結された第２アクスル９Ｒｂに連結され、そのプラネタリキャリヤ３５は、図示しないケーシングに対して回転不能に固定されている。   More specifically, the speed change mechanism 31 of the present embodiment is formed by connecting planetary gears having the same configuration as the planetary gear mechanism 21 symmetrically via the differential mechanism 11. Specifically, the speed change mechanism 31 of the present embodiment includes first and second sun gears 32 and 33 similar to the planetary gear mechanism 21, a plurality of double pinions 34 that mesh with both the sun gears 32 and 33, and these A planetary carrier 35 is provided for supporting each double pinion 34 so that it can rotate and revolve. The first sun gear 32 is connected to the first axle 9Ra connected to the planetary carrier 16 of the differential mechanism 11, and the second sun gear 33 is connected to the second axle 9Rb connected to the right rear wheel 10R. The planetary carrier 35 is fixed so as not to rotate with respect to a casing (not shown).

即ち、プラネタリキャリヤ３５を回転不能に固定することにより、第１アクスル９Ｒａと第２アクスル９Ｒｂとの間に回転差が生ずる。そして、車両直進時においては、左右の後輪１０Ｌ，１０Ｒに回転差がないことから、左側のリヤアクスル９Ｌは、第２アクスル９Ｒｂと同一の速度で回転することになる。つまり、第１アクスル９Ｒａに連結された差動機構１１のプラネタリキャリヤ１６と左側のリヤアクスル９Ｌとの間には、変速機構３１の変速比に相当する回転差が生ずる。そして、この回転差により遊星歯車機構２１に設定された相殺して、非モータ駆動時における同遊星歯車機構２１のプラネタリキャリヤ２５の回転を防止する構成となっている。   That is, by fixing the planetary carrier 35 so as not to rotate, a difference in rotation is generated between the first axle 9Ra and the second axle 9Rb. When the vehicle is traveling straight, there is no difference in rotation between the left and right rear wheels 10L, 10R, so the left rear axle 9L rotates at the same speed as the second axle 9Rb. That is, a rotational difference corresponding to the transmission ratio of the transmission mechanism 31 is generated between the planetary carrier 16 of the differential mechanism 11 connected to the first axle 9Ra and the left rear axle 9L. Then, the planetary gear mechanism 21 is offset by this rotational difference to prevent the planetary carrier 25 of the planetary gear mechanism 21 from rotating when the motor is not driven.

以上、本実施形態によれば、以下のような作用・効果を得ることができる。
（１）駆動力配分装置としてのリヤディファレンシャル８は、入力される駆動力を相互の差動を許容しつつ左右のリヤアクスル９Ｌ，９Ｒに伝達する差動機構１１と、両リヤアクスル９Ｌ，９Ｒ間に介在されるとともにモータ２０に駆動連結された遊星歯車機構２１と、該遊星歯車機構２１に設定された変速比を補正するための変速機構３１とを備える。そして、変速機構３１は、差動機構１１を挟んで遊星歯車機構２１の反対側に配置される。 As described above, according to the present embodiment, the following operations and effects can be obtained.
(1) A rear differential 8 as a driving force distribution device includes a differential mechanism 11 that transmits an input driving force to the left and right rear axles 9L and 9R while allowing mutual differentials, and between the rear axles 9L and 9R. A planetary gear mechanism 21 interposed between the planetary gear mechanism 21 and the motor 20 is interposed between the planetary gear mechanism 21 and the speed change mechanism 31 for correcting the gear ratio set in the planetary gear mechanism 21. The transmission mechanism 31 is disposed on the opposite side of the planetary gear mechanism 21 with the differential mechanism 11 interposed therebetween.

上記構成によれば、差動機構１１を挟んで遊星歯車機構２１と変速機構３１とを対称的に配置することで、重量バランスを改善することができるとともに、良好な車両搭載性を実現することができる。そして、更には、これに加えて潤滑状態の向上を図ることもできる。   According to the above configuration, the planetary gear mechanism 21 and the speed change mechanism 31 are arranged symmetrically with the differential mechanism 11 in between, so that the weight balance can be improved and good vehicle mountability can be realized. Can do. In addition to this, the lubrication state can be improved.

（２）遊星歯車機構２１は、リヤアクスル９Ｌと同軸配置された一対のサンギヤ２２，２３と、両サンギヤ２２，２３に噛合する複数の二連ピニオン２４と、各二連ピニオン２４を自転可能且つ公転可能に支承するプラネタリキャリヤ２５とからなり、モータ２０に駆動連結される入力要素は、そのプラネタリキャリヤ２５により構成される。そして、変速機構３１は、遊星歯車機構２１と同一の構成を有する遊星歯車を差動機構１１を介して対称に連結し、そのプラネタリキャリヤ３５を回転不能に固定することにより構成される。   (2) The planetary gear mechanism 21 includes a pair of sun gears 22 and 23 arranged coaxially with the rear axle 9L, a plurality of double pinions 24 meshing with the sun gears 22 and 23, and each double pinion 24 can rotate and revolve. The input element which is composed of a planetary carrier 25 which can be supported and is drivingly connected to the motor 20 is constituted by the planetary carrier 25. The transmission mechanism 31 is configured by connecting planetary gears having the same configuration as the planetary gear mechanism 21 symmetrically via the differential mechanism 11 and fixing the planetary carrier 35 so as not to rotate.

上記構成によれば、遊星歯車機構２１の変速比を補正するため変速機構３１を容易に形成することができる。
（３）モータ２０は、リヤアクスル９Ｌと同軸に配置される。これにより、その車両搭載性及び、より一層の小型化を図ることができる。 According to the above configuration, the speed change mechanism 31 can be easily formed to correct the gear ratio of the planetary gear mechanism 21.
(3) The motor 20 is disposed coaxially with the rear axle 9L. Thereby, the vehicle mounting property and further size reduction can be achieved.

（４）差動機構１１は、遊星歯車により構成される。即ち、差動機構１１を挟んで遊星歯車機構２１の反対側に変速機構３１を配置した構成では、差動機構１１の出力軸であるリヤアクスル９Ｌ，９Ｒ（第１アクスル９Ｒａ）間に回転差が生じ、そのプラネタリギヤ対１５（１５ａ，１５ｂ）が公転することになる。その結果、各プラネタリギヤ対１５によってケーシング４０内の潤滑油が攪拌され、これにより各ギヤの潤滑状態をより良好なものとすることができる（図３参照）。   (4) The differential mechanism 11 is constituted by a planetary gear. That is, in the configuration in which the speed change mechanism 31 is disposed on the opposite side of the planetary gear mechanism 21 across the differential mechanism 11, there is a rotational difference between the rear axles 9L and 9R (first axle 9Ra) that are the output shafts of the differential mechanism 11. As a result, the planetary gear pair 15 (15a, 15b) revolves. As a result, the lubricating oil in the casing 40 is agitated by each planetary gear pair 15, whereby the lubrication state of each gear can be improved (see FIG. 3).

なお、本実施形態は以下のように変更してもよい。
・本実施形態では、本発明を左右駆動力配分装置としてリヤディファレンシャル８に具体化したが、例えば、車両前後の駆動力を配分する駆動力配分装置等に具体化してもよい。 In addition, you may change this embodiment as follows.
In the present embodiment, the present invention is embodied in the rear differential 8 as a left and right driving force distribution device, but may be embodied in, for example, a driving force distribution device that distributes the driving force in the front and rear of the vehicle.

・本実施形態では、一対のサンギヤ２２，２３と、両サンギヤ２２，２３に噛合する複数の二連ピニオン２４と、各二連ピニオン２４を自転可能且つ公転可能に支承するプラネタリキャリヤ２５とを備えた遊星歯車機構２１を採用し、そのプラネタリキャリヤ２５をモータ２０に駆動連結される入力要素とした。しかし、遊星歯車機構の構成は、これに限るものではなく、その入力要素もプラネタリキャリヤに限るものではない。   In the present embodiment, a pair of sun gears 22, 23, a plurality of double pinions 24 meshing with both sun gears 22, 23, and a planetary carrier 25 that supports each double pinion 24 so as to be capable of rotating and revolving are provided. The planetary gear mechanism 21 is employed, and the planetary carrier 25 is used as an input element that is drivingly connected to the motor 20. However, the configuration of the planetary gear mechanism is not limited to this, and the input element thereof is not limited to the planetary carrier.

・本実施形態では、遊星歯車機構２１と同一の構成を有する遊星歯車を差動機構１１を介して対称に連結することにより変速機構３１を形成したが、変速機構の構成は、これに限るものではない。   In the present embodiment, the planetary gear having the same configuration as that of the planetary gear mechanism 21 is symmetrically connected via the differential mechanism 11 to form the transmission mechanism 31. However, the configuration of the transmission mechanism is not limited to this. is not.

・本実施形態では、モータ２０をリヤアクスル９Ｌと同軸に配置したが、これに限らず、例えば、連結機構を介して遊星歯車機構２１と駆動連結する構成であってもよい。
・本実施形態では、左のリヤアクスル９Ｌ側に遊星歯車機構２１を、右のリヤアクスル９Ｒ側に変速機構３１を配置したが、この配置は左右逆転させてもよい。 In the present embodiment, the motor 20 is arranged coaxially with the rear axle 9L. However, the present invention is not limited to this. For example, a configuration in which the motor 20 is drivingly connected to the planetary gear mechanism 21 via a connecting mechanism may be used.
In the present embodiment, the planetary gear mechanism 21 is disposed on the left rear axle 9L side, and the transmission mechanism 31 is disposed on the right rear axle 9R side. However, this arrangement may be reversed left and right.

・本実施形態では、差動機構１１には、遊星歯車を用いることとしたが、図４に示すように、ベベルギヤ４１を用いるものに適用してもよい。例えば、同図に示すベベルギヤ４１は、外周に外歯ギヤ１２が設けられた筒状のデフケース４２と、該デフケース４２と一体に公転するとともに自転可能に設けられたデフピニオン４３ａ，４３ｂと、これら各デフピニオン４３ａ，４３ｂに噛合される一対のデフサイドギヤ４４Ｒ，４４Ｌとを備える。そして、左右のリヤアクスル９Ｌ，９Ｒは、それぞれ、その軸端がデフサイドギヤ４４Ｒ，４４Ｌに連結される。この場合、遊星歯車機構２１の第１のサンギヤ２２は、デフケース４２に連結し、第２のサンギヤ２３は、左側のリヤアクスル９Ｌに連結する。そして、変速機構３１の第１のサンギヤ３２は、デフケース４２に連結し、第２のサンギヤ３３は、右側のリヤアクスル９Ｒに連結するとよい。   In the present embodiment, a planetary gear is used for the differential mechanism 11. However, the differential mechanism 11 may be applied to a mechanism using a bevel gear 41 as shown in FIG. 4. For example, a bevel gear 41 shown in the figure includes a cylindrical differential case 42 having an external gear 12 provided on the outer periphery, differential pinions 43a and 43b that revolve integrally with the differential case 42 and that can rotate. A pair of differential side gears 44R, 44L meshed with the differential pinions 43a, 43b are provided. The shaft ends of the left and right rear axles 9L and 9R are coupled to the differential side gears 44R and 44L, respectively. In this case, the first sun gear 22 of the planetary gear mechanism 21 is connected to the differential case 42, and the second sun gear 23 is connected to the left rear axle 9L. The first sun gear 32 of the speed change mechanism 31 is preferably connected to the differential case 42, and the second sun gear 33 is preferably connected to the right rear axle 9R.

・本実施形態では、二連ピニオン２４，３４に噛み合う各ギヤをサンギヤで構成したが、その一部または全部を内周側に歯が形成されたリングギヤで構成してもよい。
・モータは、電気モータに限らず、油圧モータを使用してもよい。 In the present embodiment, each gear meshing with the double pinions 24 and 34 is configured by a sun gear, but part or all of the gear may be configured by a ring gear having teeth formed on the inner peripheral side.
The motor is not limited to an electric motor, and a hydraulic motor may be used.

車両の概略構成図。The schematic block diagram of a vehicle. リヤディファレンシャルの概略構成図。The schematic block diagram of a rear differential. ケーシング内の潤滑油の流れを示す説明図。Explanatory drawing which shows the flow of the lubricating oil in a casing. 別例のリヤディファレンシャルの概略構成図。The schematic block diagram of the rear differential of another example.

符号の説明Explanation of symbols

２…エンジン、６…プロペラシャフト、８…リヤディファレンシャル、９Ｌ，９Ｒ…リヤアクスル、１０Ｌ，１０Ｒ…後輪、１１…差動機構、２０…モータ、２１…遊星歯車機構、２２，３２…第１のサンギヤ、２３，３３…第２のサンギヤ、２４，３４…二連ピニオン、２５，３５…プラネタリキャリヤ、３１…変速機構。   DESCRIPTION OF SYMBOLS 2 ... Engine, 6 ... Propeller shaft, 8 ... Rear differential, 9L, 9R ... Rear axle, 10L, 10R ... Rear wheel, 11 ... Differential mechanism, 20 ... Motor, 21 ... Planetary gear mechanism, 22, 32 ... First Sun gear, 23, 33 ... second sun gear, 24, 34 ... double pinion, 25, 35 ... planetary carrier, 31 ... transmission mechanism.

Claims (4)

入力される駆動力を相互の差動を許容しつつ車両の左右の車輪にそれぞれ連結された第１及び第２の出力軸に伝達する差動機構と、前記第１及び第２の出力軸間に介在されるとともにモータに駆動連結された遊星歯車機構と、前記遊星歯車機構に設定された変速比を補正するための変速機構とを備え、モータトルクに基づき前記第１及び第２の出力軸間に差回転を生じさせることにより前記入力される駆動力の前記第１及び第２の出力軸への配分比率を制御可能な駆動力配分装置において、
前記変速機構は、前記差動機構を挟んで前記遊星歯車機構の反対側に配置されること、
を特徴とする駆動力配分装置。 A differential mechanism for transmitting the input driving force to the first and second output shafts connected to the left and right wheels of the vehicle while allowing mutual differential, and between the first and second output shafts And a planetary gear mechanism that is drive-coupled to the motor and a transmission mechanism that corrects a transmission gear ratio set in the planetary gear mechanism, and the first and second output shafts are based on motor torque. In the driving force distribution device capable of controlling a distribution ratio of the input driving force to the first and second output shafts by causing a differential rotation therebetween,
The speed change mechanism is disposed on the opposite side of the planetary gear mechanism across the differential mechanism;
A driving force distribution device characterized by the above. 請求項１に記載の駆動力配分装置において、
前記遊星歯車機構は、異なる径を有する二つの歯車を相対回転不能に連結した二連ピニオンと、前記二つの歯車にそれぞれ噛合し何れか一方の出力軸と同軸配置された一対の歯車と、前記二連ピニオンを自転及び公転可能に支承するプラネタリキャリヤとにより構成されるとともに、前記プラネタリキャリヤにより前記モータに駆動連結される入力要素が構成されるものであって、
前記変速機構は、前記遊星歯車機構と同一の構成を有する遊星歯車を前記差動機構を介して対称に連結し、そのプラネタリキャリヤを回転不能に固定することにより構成されること、を特徴とする駆動力配分装置。 The driving force distribution device according to claim 1,
The planetary gear mechanism includes a double pinion in which two gears having different diameters are connected in a relatively non-rotatable manner, a pair of gears meshed with the two gears and arranged coaxially with one of the output shafts, A planetary carrier that supports the double pinion so as to rotate and revolve, and an input element that is drivingly connected to the motor by the planetary carrier,
The speed change mechanism is configured by connecting planetary gears having the same configuration as the planetary gear mechanism symmetrically through the differential mechanism and fixing the planetary carrier so as not to rotate. Driving force distribution device. 請求項２に記載の駆動力配分装置において、
前記モータは、前記出力軸と同軸に配置されること、を特徴とする駆動力配分装置。 The driving force distribution device according to claim 2,
The motor is disposed coaxially with the output shaft. 請求項１〜請求項３の何れか一項に記載の駆動力配分装置において、
前記差動機構には、遊星歯車が用いられること、を特徴とする駆動力配分装置。 In the driving force distribution device according to any one of claims 1 to 3,
A planetary gear is used for the differential mechanism.
JP2006247176A 2006-09-12 2006-09-12 Driving force distribution device Expired - Fee Related JP4961919B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2006247176A JP4961919B2 (en) 2006-09-12 2006-09-12 Driving force distribution device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006247176A JP4961919B2 (en) 2006-09-12 2006-09-12 Driving force distribution device

Publications (2)

Publication Number Publication Date
JP2008069812A true JP2008069812A (en) 2008-03-27
JP4961919B2 JP4961919B2 (en) 2012-06-27

Family

ID=39291582

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2006247176A Expired - Fee Related JP4961919B2 (en) 2006-09-12 2006-09-12 Driving force distribution device

Country Status (1)

Country Link
JP (1) JP4961919B2 (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010116083A (en) * 2008-11-14 2010-05-27 Honda Motor Co Ltd Power system
CN109723767A (en) * 2019-01-23 2019-05-07 胡捷 Dynamic branch output and the automobile-used retarder with differential function
CN113864420A (en) * 2020-06-30 2021-12-31 丰田自动车株式会社 Compound planetary gear device
JP2022008619A (en) * 2017-11-14 2022-01-13 ダイハツ工業株式会社 Hybrid system
CN114228483A (en) * 2021-12-24 2022-03-25 易如(山东)智能科技有限公司 Disconnected front steering drive axle capable of realizing left-right forward and reverse rotation

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05262250A (en) * 1992-03-19 1993-10-12 Mitsubishi Motors Corp Vehicle with driving force distribution interlocking power steering device
JPH06300096A (en) * 1993-04-16 1994-10-25 Honda Motor Co Ltd Torque distributing mechanism for differential gear
JPH0719318A (en) * 1993-04-16 1995-01-20 Honda Motor Co Ltd Torque distribution mechanism of differential gear
JPH10151951A (en) * 1996-11-22 1998-06-09 Kenji Mimura Differential gear
JP2001039179A (en) * 1999-05-25 2001-02-13 Toyota Motor Corp Driving force distributing device
JP2005351471A (en) * 2004-05-10 2005-12-22 Toyoda Mach Works Ltd Differential gear, front and rear wheel drive device using the differential gear, and control method for the front and rear wheel drive device
JP2006112474A (en) * 2004-10-13 2006-04-27 Toyoda Mach Works Ltd Differential gear and driving force transmission unit for vehicle using it

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05262250A (en) * 1992-03-19 1993-10-12 Mitsubishi Motors Corp Vehicle with driving force distribution interlocking power steering device
JPH06300096A (en) * 1993-04-16 1994-10-25 Honda Motor Co Ltd Torque distributing mechanism for differential gear
JPH0719318A (en) * 1993-04-16 1995-01-20 Honda Motor Co Ltd Torque distribution mechanism of differential gear
JPH10151951A (en) * 1996-11-22 1998-06-09 Kenji Mimura Differential gear
JP2001039179A (en) * 1999-05-25 2001-02-13 Toyota Motor Corp Driving force distributing device
JP2005351471A (en) * 2004-05-10 2005-12-22 Toyoda Mach Works Ltd Differential gear, front and rear wheel drive device using the differential gear, and control method for the front and rear wheel drive device
JP2006112474A (en) * 2004-10-13 2006-04-27 Toyoda Mach Works Ltd Differential gear and driving force transmission unit for vehicle using it

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010116083A (en) * 2008-11-14 2010-05-27 Honda Motor Co Ltd Power system
JP2022008619A (en) * 2017-11-14 2022-01-13 ダイハツ工業株式会社 Hybrid system
JP7234325B2 (en) 2017-11-14 2023-03-07 ダイハツ工業株式会社 hybrid system
CN109723767A (en) * 2019-01-23 2019-05-07 胡捷 Dynamic branch output and the automobile-used retarder with differential function
CN113864420A (en) * 2020-06-30 2021-12-31 丰田自动车株式会社 Compound planetary gear device
CN113864420B (en) * 2020-06-30 2024-04-16 丰田自动车株式会社 Composite planetary gear device
CN114228483A (en) * 2021-12-24 2022-03-25 易如(山东)智能科技有限公司 Disconnected front steering drive axle capable of realizing left-right forward and reverse rotation

Also Published As

Publication number Publication date
JP4961919B2 (en) 2012-06-27

Similar Documents

Publication Publication Date Title
JP3103779B2 (en) Differential device
JP4980786B2 (en) Vehicle differential device
JP2008501920A (en) Planetary differential transmission
JP2004001682A (en) Driving system for electric vehicle
JPH10138773A (en) Power transmission device
JP4961919B2 (en) Driving force distribution device
JP2011133110A (en) Right and left wheel drive gear, front and rear wheel drive gear, and method for controlling the same
WO1988000300A1 (en) Torque retaining and proportioning differential drive assembly
JPH06185582A (en) Differential gear
US7357747B2 (en) Apparatus for differential power distribution
JP4958113B2 (en) Power transmission mechanism
JP2010144762A (en) Driving force distributing device
JP2876376B2 (en) Differential torque distribution mechanism
CN116101054A (en) Electric drive bridge provided with three-gear speed change mechanism
JP3998932B2 (en) Four-wheel drive system for vehicles
JP4910587B2 (en) Driving force distribution device
JP2009030626A (en) Drive force distribution device
JP5302811B2 (en) transfer
JP2006029438A (en) Driving device for vehicle and automobile comprising the same
JPH0195941A (en) Power transmitting gear for for four-wheel-drive vehicle
JP4142768B2 (en) Differential device
JP2020121708A (en) Intermediate differential gear device, power transmission device of rear biaxial drive vehicle provided with the intermediate differential gear device, and power transmission device of four wheel drive vehicle provided with the intermediate differential gear device
KR100279985B1 (en) Compound Differential Device for Four Wheel Drive Vehicle
JP4998117B2 (en) Driving force distribution device
JP2005133758A (en) Power transmitting device for vehicles

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20090825

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20110516

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20110524

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20110711

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20120228

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20120312

R150 Certificate of patent or registration of utility model

Free format text: JAPANESE INTERMEDIATE CODE: R150

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20150406

Year of fee payment: 3

LAPS Cancellation because of no payment of annual fees