JPS60184750A - Flexible mesh type power transmission unit - Google Patents
Flexible mesh type power transmission unitInfo
- Publication number
- JPS60184750A JPS60184750A JP4004184A JP4004184A JPS60184750A JP S60184750 A JPS60184750 A JP S60184750A JP 4004184 A JP4004184 A JP 4004184A JP 4004184 A JP4004184 A JP 4004184A JP S60184750 A JPS60184750 A JP S60184750A
- Authority
- JP
- Japan
- Prior art keywords
- wave generator
- flexible
- power transmission
- boss
- cam
- 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.)
- Pending
Links
- 230000005540 biological transmission Effects 0.000 title abstract description 20
- 125000006850 spacer group Chemical group 0.000 abstract description 3
- 230000002093 peripheral effect Effects 0.000 abstract 3
- 238000004519 manufacturing process Methods 0.000 abstract 1
- 230000033001 locomotion Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000003754 machining Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 239000011888 foil Substances 0.000 description 1
- 238000010348 incorporation Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
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
- F16H49/00—Other gearings
- F16H49/001—Wave gearings, e.g. harmonic drive transmissions
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
Description
【発明の詳細な説明】
に箔上の利用分野
本発明はハーモニックドライブ（登録商標）の商品名で
知られている撓み噛合式動力伝達装置（以１・伝達’Ａ
’＋に：という。）Ｇこ関する。DETAILED DESCRIPTION OF THE INVENTION Field of Application of Foil The present invention relates to a flexible mesh power transmission device (hereinafter referred to as 1. Transmission 'A') known under the trade name of Harmonic Drive (registered trademark).
'+: Saying. )G related.
従来例の構成とその問題点
従来の噛合式動力伝達装置を第１図、第２図および第３
図にその具体構成を示す。The structure of the conventional example and its problems The conventional meshing type power transmission device is shown in Figs. 1, 2, and 3.
The figure shows its specific configuration.
第１図は部品展開斜視図、第２図は噛合状態断面図、第
３図は伝達装置に入力軸と従動軸を装着して実機に取付
けた断面図を示す。FIG. 1 is an exploded perspective view of the parts, FIG. 2 is a sectional view of the gear in a meshed state, and FIG. 3 is a sectional view of the transmission device with an input shaft and a driven shaft attached to an actual machine.
図において、楕円状の外周とボスをもつカムの外周部に
ボールベアリングを取剃りだウェーブゼネレータ（１）
と、微少な歯数差をもつ２個の内歯歯車（２）、（３）
と、薄肉円筒状の撓み外歯歯車（４）で構成されていた
。そしてその使用Ｇこおいては機器本俸側（５）に固定
された内歯歯車（２）と、従動軸（７）に固定された内
歯歯車（３）、人力軸（６）に固定連結されたウェーブ
ゼネレータ（１）と、内周においてウェーブゼネレータ
（１）と嵌合し楕円状に撓み、かつ楕円の長軸側２ケ所
において２個の内歯車（２１、（ａ）と噛合う撓み外歯
歯車（４）で組立てられる。In the figure, a wave generator (1) with a ball bearing removed from the outer periphery of the cam with an elliptical outer periphery and a boss.
and two internal gears (2) and (3) with a slight difference in the number of teeth.
It consisted of a thin cylindrical flexible external gear (4). In this case, the internal gear (2) fixed to the main side of the equipment (5), the internal gear (3) fixed to the driven shaft (7), and the fixed connection to the human power shaft (6). The wave generator (1) is fitted with the wave generator (1) on the inner periphery and is bent in an elliptical shape, and is bent to mesh with two internal gears (21, (a) at two locations on the long axis side of the ellipse). It is assembled with external gears (4).
前記構成の動作は、入力軸（６）によりＮ、 ｒｐｍで
駆動されたウェーブゼネレータ＋１＋はウェーブゼネレ
ータ（１）の長軸側で噛合う撓み外歯歯車（４）と２個
の内歯歯車＋２＋、［３１に回転力を伝達し、固定側内
歯歯車（２）の数Ｚ７、従動側内歯歯車（３）の数２２
におい式で表わされる回転数に減速され回転するもので
ある。The operation of the above configuration is as follows: The wave generator +1+ driven by the input shaft (6) at N rpm is a flexible external gear (4) and two internal gears +2+ that mesh on the long axis side of the wave generator (1). , [Transmit the rotational force to 31, the number of fixed side internal gears (2) Z7, the number of driven side internal gears (3) 22
It rotates at a speed determined by the odor formula.
しかしなから、前記のような構成では、２つの内歯歯車
＋２１ 、＋３＋及びウェーブゼネレータ＋１１の同心
ずれに対して調整機構を持たないため入力軸（６）のト
ルク変動の発生の原因となり、加工、組立精度について
充分な注意を必要とした。さらに、回転中においては撓
み外歯歯車（４）は内歯歯車（２）、（３）と噛合い回
転するが、左右軸方向の摺動を抑制する装置がないので
、撓み外歯歯車（４）には軸方向の力が発生し本体側（
５）及び撓み外歯歯車（４）端面の摩耗の発生たりでな
く効率低下の主因となっていた。However, with the above configuration, there is no adjustment mechanism for the concentricity of the two internal gears +21 and +3+ and the wave generator +11, which causes torque fluctuations on the input shaft (6), resulting in processing problems. , required careful attention to assembly accuracy. Furthermore, during rotation, the flexible external gear (4) meshes with the internal gears (2) and (3) and rotates, but since there is no device to suppress sliding in the left-right axis direction, the flexible external gear ( 4), an axial force is generated and the main body side (
5) and the flexible external gear (4) This was the main cause of the decrease in efficiency, rather than the occurrence of wear on the end face.
発明の目的
本発明は前記欠点に鑑み、数句側（本体側）の加工精度
、組立精度を必要とせずトルク変動が少なく、かつ効率
の高い撓み撓合式動力伝達装置を提供するものである。OBJECTS OF THE INVENTION In view of the above-mentioned drawbacks, the present invention provides a flexible flexible power transmission device that does not require high machining accuracy or assembly accuracy on the side (main body side), has little torque fluctuation, and is highly efficient.
発明の構成
本発明は、入力軸を連結するボスと、楕円形状で前記ボ
スに対して楕円の長４１＋方向に摺動可能に取付けられ
た外周にボールベアリング分取イ」けた２個のカムとで
構成されたウェーブゼネ、レークと、前記ウェーブゼネ
レーク外周に組込まれ楕円状に撓まされる撓み外歯歯車
を組込み、前記カムの楕円の長軸で撓み外歯歯車と噛合
う２個の微少なｍ数差をもつ内歯歯車を設けて噛合わせ
、前記撓み外歯歯車の内周面中央には環状凸部を設けて
１ｊす記環状凸部を挾さんで前記カムを配設したことを
特徴とし、本発明は前記構成により撓み外歯歯車と内歯
歯車の噛合いにおいてカムは楕円の長１１ｑ１＋側２点
の噛合いの強さに応じて自動的に長軸方向に摺動し噛合
いによるトルク変動を抑制、均一化する作用を２個の内
歯歯車に対し各個に行ない、著しいトルク変動の抑制、
均一化が可能である効果を生ずる。Structure of the Invention The present invention comprises a boss connecting an input shaft, and two cams each having an elliptical shape and having a ball bearing disposed on the outer periphery, which are slidably attached to the boss in the direction of the length 41 of the ellipse. A wave generator consisting of a rake, and a flexible external gear that is built into the outer periphery of the wave generator rake and is deflected in an elliptical shape, and two microscopic gears that mesh with the flexible external gear at the long axis of the ellipse of the cam. Internal gears having a difference in the number of m are provided and meshed, an annular protrusion is provided at the center of the inner circumferential surface of the flexible external gear, and the cam is disposed between the annular protrusions. A feature of the present invention is that when the flexible external gear and the internal gear engage with each other, the cam automatically slides in the longitudinal direction according to the engagement strength of the two points on the long 11q1+ side of the ellipse and engages. The effect of suppressing and equalizing the torque fluctuation caused by
This produces an effect that allows for uniformity.
実施例の説明
以下本発明の一実施例について、図面を参１ｉｊｉ シ
ながら説ψ１する。DESCRIPTION OF EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings.
第４図は本発明の第１の実施例における撓み噛合式動力
伝達装置の部品展開斜視図を示す。FIG. 4 shows an exploded perspective view of parts of a flexible mesh type power transmission device according to a first embodiment of the present invention.
第４図において＋８１、ｆ９）は微少なｍ数差をもつ２
個の内歯歯車、θ０）は撓み外歯歯車、Ｑｌｌはフラン
ジ部（１１，１） ）に角溝（ｉｘａ）を持つボス、（
１２ａ）、（＋ｚｂ）はスペーサ、（１３ａ ）、（１
３ｂ ）は止め輪、（１４ａ）、（１４ｂ）は外周にボ
ールベアリング（１４Ａ）（１４Ｂ ）を持つ楕円形状
のカム、を示す。In Figure 4, +81, f9) is 2 with a slight difference in m number.
θ0) is a flexible external gear, Qll is a boss with a square groove (ixa) on the flange part (11, 1),
12a), (+zb) are spacers, (13a), (1
3b) shows a retaining ring, and (14a) and (14b) show an elliptical cam with ball bearings (14A) and (14B) on the outer periphery.
本発明の伝達装置の構成を説明する。The configuration of the transmission device of the present invention will be explained.
カム（１４ａ ）、（＋４ｂ ）は片側面に楕円の長ｉ
１１＋ Ｊｉ向に角形突起部（１！１を設ける。カム（
］４ａ ）、（＋４ｂ）はボスＣＩＩＮこ対してボス（
ＩＩ）の角溝（］１ａ）にカム（，１４ａ）（＋、ｉｂ
）の角形突起部（１！１が合致するようスペーサ（＋
２ａ）、（＋２ｂ ）及び止め輪（１３ａ ）、（＋３
ｂ ） ｃこ」ニリボス（１１）に連糸古される。カム
（１４ａ ）、（＋４ｂ ）の角月琺突起部０１力とボ
ス（１））の角ｔｒ＆ （１ｔａ ）は微少す間隙をも
つためカム（１４ａ ）、（＋４’ｂ ）はボス（１１
）にス、Ｉして、ボス（１１）の径とカム（４４ａ ）
、（１４ｋ） ）の穴径の差の範囲において楕円の長軸
方向に摺動可能、回転不能に連結される。ボス（Ｉｌｌ
と２個の力１、（１４ａ）（１４ｂ）を組合わせたもの
をウェーブゼネレータ（１５１と呼ぶ。撓み外歯歯車（
１０）は薄肉円筒状であり、内周部に中央環状の凸部（
ＩＯＡ ）をもち、この凸部（ＩＯＡ ）を２個のカム
（１４ａ）、（１４１） ）で挾む形でウェーブゼネレ
ータ（＋５１の外周に組込まれ、撓み外歯歯車０１ｌ）
の凸部（］ｏＡ、 ）とカム（１４ａ）、（１４１））
のボールベアリング間隔の差の範囲に撓み外歯歯車００
の軸方向への動きは制限されるようにＨＩＩ成されてい
る。The cams (14a) and (+4b) have an oval length i on one side.
11+ A square protrusion (1!1 is provided in the direction of Ji. A cam (
] 4a ), (+4b) are the boss CIIN and the boss (
The cam (, 14a) (+, ib
) to match the square protrusion (1!1) with the spacer (+
2a), (+2b) and retaining ring (13a), (+3
b) It is connected to Nilibos (11). Since there is a slight gap between the angle tr & (1ta) of the cam (14a), (+4b) and the angle tr&(1ta) of the boss (1), the cam (14a), (+4'b) is
), the diameter of the boss (11) and the cam (44a)
, (14k) ) are slidably connected in the long axis direction of the ellipse, but are non-rotatably connected. Boss (Ill
The combination of the two forces 1, (14a) and (14b) is called a wave generator (151).A flexible external gear (
10) has a thin-walled cylindrical shape, and has a central annular convex part (
IOA ), and this convex part (IOA ) is sandwiched between two cams (14a), (141) ) to form a wave generator (built into the outer periphery of +51, flexible external gear 01l).
The convex part (]oA, ) and the cam (14a), (141))
Flexible external gear in the range of ball bearing spacing difference 00
The HII is configured such that movement in the axial direction is restricted.
以上のように構成された伝達装置について、以下機器へ
の組込み及びその動作について説明する。Regarding the transmission device configured as above, the incorporation into equipment and its operation will be explained below.
第５図は本発明の伝達装置に入力軸と従動軸を装着して
機器に取イ」けた状態の断面図を示す。FIG. 5 shows a sectional view of the transmission device of the present invention with an input shaft and a driven shaft attached and installed in a device.
第５図において、本体側０（＋）に内歯歯車（８）と、
従動軸ＯＱへ内歯歯車（９）か固定されている。人力＋
ｌｌ＋ Ｏｎにウェーブゼネレータ０ωが固定連結され
ており、撓み外歯歯車００）はウェーブゼネレータ０９
の外周部に組込まれ、楕円状に撓められており、その楕
円の長軸方向２ケ所において２個の内歯歯車（８）、（
り）と噛合っている。人力軸０力の回転駆動により、内
歯歯車（８）、（９）の歯数差から従動軸θ樽は本体側
１６１に対して人力回転より減速した回転を行なうもの
である。この時、本体側０６）に固定された内歯歯車（
８）と、従動１ｑ１１吐に固定された内歯歯車（９）と
、入力軸０７）か同心ずれで組立てられていた場合、カ
ム（１４ａ）（１４ｂ ）は同心ずれに対応し噛合方向
に摺動し入力１１１１＋ Ｈのトルク変化を均一化、低
下せしめる働きをするものである。また、撓み外歯歯車
（１ｏ）は回転時の軸方向の力に対し、撓み外歯歯車（
１０）は内周に設Ｊｌた凸部（ＩＯＡ、 ）によりカム
（１４ａ ）、（１４ｂ）のボールベアリング（１４Ａ
、） 、（１４Ｂ ）間に抑制され、左右の摺動が抑制
されるので、撓み外ｍ ｒＭ車（Ｉｔηのイ一体側（１
６）及び従動軸０樽への接触を防ぎ、軸方向の力をころ
かり摩擦により対応している。In Fig. 5, an internal gear (8) is located on the main body side 0 (+),
An internal gear (9) is fixed to the driven shaft OQ. Human power +
Wave generator 0ω is fixedly connected to ll+ On, and flexible external gear 00) is connected to wave generator 09.
The internal gear (8) is bent into an elliptical shape, and two internal gears (8), (
It meshes with ri). Due to the rotational drive of the human shaft with zero force, the driven shaft θ barrel rotates at a slower speed than the manual rotation with respect to the main body side 161 due to the difference in the number of teeth of the internal gears (8) and (9). At this time, the internal gear (
8), the internal gear (9) fixed to the driven shaft 1q11, and the input shaft 07) are assembled so that they are misaligned, the cams (14a) and (14b) will slide in the meshing direction in response to the misalignment. It functions to equalize and reduce the torque change of the motion input 1111+H. In addition, the flexible external gear (1o) resists the axial force during rotation.
10) is a ball bearing (14A,
, ) , (14B), and the left and right sliding is suppressed, so that the outside deflection m rM car (Itη's I integral side (1
6) and the driven shaft 0 is prevented from coming into contact with the barrel, and the axial force is dealt with by rolling friction.
以上の」＝うに人力軸（１７）を連結するボス（１υと
、楕円杉状で前記ボスに対して楕円の長軸方向に摺動可
能に数例けられた外周にボールベアリングを取（、Ｊ’
ｉ−１だ２個のカム（１４ａ ）、（’１４ｂ）とで
構成されたウェーブゼネレータ（１（５）と、微少な歯
数差をもっ２個の内歯歯車（８）、（９）と、薄肉円筒
状の撓み外歯歯車００）で伝達装置を構成することによ
り、本発明の伝達装置は取（ｑ側の加工精度及び組立精
度を必要とぜず、同心ずれに自動対応して人カニＩｆｂ
のトルク変動を均一化、低下せしめることができ、さら
に撓み外歯歯車ａＯ＋の内１ｔｉ１部に凸部（ＩＯＡ
）を設ｉｔ 。A boss (1υ) that connects the human-powered shaft (17) and a ball bearing ( J'
A wave generator (1 (5)) consisting of two cams (14a) and ('14b) and two internal gears (8) and (9) with a slight difference in the number of teeth. By configuring the transmission device with a thin-walled cylindrical flexible external gear 00), the transmission device of the present invention does not require machining accuracy and assembly accuracy on the q side, and can automatically accommodate misalignment. Human Crab Ifb
It is possible to equalize and reduce the torque fluctuation of the flexible external gear aO+.
) is set up.
ウェーブゼネレータ０（ト）に対し軸方向への移動を制
限することにより、撓み外歯歯車（１０）偏向の接触を
防ぎ、摩耗と摩擦によるトルクロスを減少ゼしめるもの
である。By restricting the movement of the wave generator 0 (g) in the axial direction, contact of deflection of the flexible external gear (10) is prevented, and torque loss due to wear and friction is reduced.
発明の効果
本発明は前記の構成により、撓み噛合式動力伝達装置数
句側の加工精度、組立精度を必要とゼずトルク変動を少
なくてき、さらに撓み外爾爾１１ξ内ｊ、！、Ｊ部に凸
部を設け、ウェーブゼネレータに対して１＋１１方向の
移動を制限することにより、撓み外歯歯車の接触による
摩擦トルクロスを減少せしめ効率向上する効果を生ずる
。Effects of the Invention With the above-described configuration, the present invention eliminates the need for machining accuracy and assembly accuracy on the side of the flexible mesh power transmission device, reduces torque fluctuations, and furthermore reduces the torque fluctuation within 11ξ of the flexible mesh type power transmission device. By providing a convex portion in the J portion and restricting the movement of the wave generator in the 1+11 direction, it is possible to reduce frictional torque loss due to contact of the flexible external gear and improve efficiency.
第１図は従来の撓み噛合式動力伝達装置の部品展開斜視
＋９、第２図は従来の撓み噛合式動刃伝達装置６′噛合
図、第３図は従来の撓み噛合式動力伝達装置機器への取
イ」図、第４図は本発明の伝達装置６の一実施例の部品
展開斜視図、第５図は本発明の伝達装置ｉ’ｉを機器へ
の取イ」図、を示す。
１ ウェーブゼネレータ ２ 、 ３ ： 内（ｆｔｆ
Ｍ車４°撓み外歯歯車 ８，９゛内歯爾車 ］ｏ：撓み
外歯１４ａ −Ｒ’ｊ ＩＯＡ 、：環状の凸部 １１
：ボス １４ａ 、 １４ｂ、カム １４Ａ 、 １４
Ｂ ：ボールベアリング １５゛ウエーブゼネレータ
１．５゛許出願人 松下電器産業株式会社代理人ブ１理
士 阿 部 功Figure 1 is a perspective +9 exploded view of parts of a conventional flexible mesh power transmission device, Figure 2 is a 6' engagement diagram of a conventional flexible mesh power transmission device, and Figure 3 is a diagram of a conventional flexible mesh power transmission device. FIG. 4 is a exploded perspective view of parts of an embodiment of the transmission device 6 of the present invention, and FIG. 5 is a view of how the transmission device i'i of the present invention is installed in a device. 1 Wave generator 2, 3: Inside (ftf
M wheel 4° deflection external gear 8, 9゛ internal gear] o: Deflection external tooth 14a -R'j IOA ,: Annular convex portion 11
: Boss 14a, 14b, cam 14A, 14
B: Ball bearing 15゛Wave generator 1.5゛Applicant: Matsushita Electric Industrial Co., Ltd. Agent B1: Isao Abe, Physician
Claims (1)
楕円の長軸方向Ｇこ摺動可能に取イ」けられた外周にボ
ールベアリングを取付けた２個のカムとで構成されたウ
ェーブゼネレータと、前記ウェーブゼネレータ外周に楕
円状に撓まれた撓み外歯爾１１（を絹込み、前記カムの
楕円の長軸で撓み外歯歯１−Ｉ戦と噛合う２個の微少な
歯数差をもつ内歯歯車を設りて噛合わせ、前記−み外歯
歯車の内周面中央には環状凸部を設りて１〕ｈ記環状凸
部を挾さんで前記カムを配設したことを特徴とする撓み
噛合式％式％A wave consisting of a boss that connects the human power shaft, and two cams that have an elliptical shape and have ball bearings attached to their outer peripheries so that they can slide in the long axis direction G of the ellipse with respect to the boss. A generator, and a flexible external tooth 11 bent in an elliptical shape on the outer periphery of the wave generator, and two small number of teeth meshing with the flexible external tooth 1-I on the long axis of the ellipse of the cam. Internal gears with a difference were provided and meshed, an annular convex portion was provided at the center of the inner circumferential surface of the external gear, and the cam was placed between the annular convex portions. Flexible meshing type % type % characterized by
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4004184A JPS60184750A (en) | 1984-03-01 | 1984-03-01 | Flexible mesh type power transmission unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4004184A JPS60184750A (en) | 1984-03-01 | 1984-03-01 | Flexible mesh type power transmission unit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS60184750A true JPS60184750A (en) | 1985-09-20 |
Family
ID=12569823
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4004184A Pending JPS60184750A (en) | 1984-03-01 | 1984-03-01 | Flexible mesh type power transmission unit |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60184750A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5123300A (en) * | 1991-08-28 | 1992-06-23 | Dynamics Research & Development Corp. | Phasing transmission |
| US6167783B1 (en) | 1997-11-28 | 2001-01-02 | Harmonic Drive Systems, Inc. | Flexible meshing type gearing having three-dimensional, non-interactive wide-area intermeshing tooth profile |
| WO2002063187A1 (en) * | 2001-02-08 | 2002-08-15 | Oechsler Aktiengesellschaft | Harmonic drive with crowned drive ring |
| JP2006509970A (en) * | 2002-12-12 | 2006-03-23 | シーメンス アクチエンゲゼルシヤフト | Transmission |
| EP3306054A4 (en) * | 2015-06-02 | 2018-05-23 | Nissan Motor Co., Ltd. | Variable compression ratio mechanism for internal combustion engine |
| EP3306053A4 (en) * | 2015-06-02 | 2018-05-23 | Nissan Motor Co., Ltd. | Variable compression ratio mechanism for internal combustion engine |
-
1984
- 1984-03-01 JP JP4004184A patent/JPS60184750A/en active Pending
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5123300A (en) * | 1991-08-28 | 1992-06-23 | Dynamics Research & Development Corp. | Phasing transmission |
| US6167783B1 (en) | 1997-11-28 | 2001-01-02 | Harmonic Drive Systems, Inc. | Flexible meshing type gearing having three-dimensional, non-interactive wide-area intermeshing tooth profile |
| WO2002063187A1 (en) * | 2001-02-08 | 2002-08-15 | Oechsler Aktiengesellschaft | Harmonic drive with crowned drive ring |
| US6786112B2 (en) | 2001-02-08 | 2004-09-07 | Oechsler Ag | Harmonic drive with crowned drive ring |
| JP2006509970A (en) * | 2002-12-12 | 2006-03-23 | シーメンス アクチエンゲゼルシヤフト | Transmission |
| EP3306054A4 (en) * | 2015-06-02 | 2018-05-23 | Nissan Motor Co., Ltd. | Variable compression ratio mechanism for internal combustion engine |
| EP3306053A4 (en) * | 2015-06-02 | 2018-05-23 | Nissan Motor Co., Ltd. | Variable compression ratio mechanism for internal combustion engine |
| US10400666B2 (en) | 2015-06-02 | 2019-09-03 | Nissan Motor Co., Ltd. | Variable compression ratio mechanism for internal combustion engine |
| US10400667B2 (en) | 2015-06-02 | 2019-09-03 | Nissan Motor Co., Ltd. | Variable compression ratio mechanism for internal combustion engine |
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