JPS58174743A - Torque transmission - Google Patents
Torque transmissionInfo
- Publication number
- JPS58174743A JPS58174743A JP57056730A JP5673082A JPS58174743A JP S58174743 A JPS58174743 A JP S58174743A JP 57056730 A JP57056730 A JP 57056730A JP 5673082 A JP5673082 A JP 5673082A JP S58174743 A JPS58174743 A JP S58174743A
- Authority
- JP
- Japan
- Prior art keywords
- intermediary
- gear
- ring
- internal gear
- intermediate ring
- 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
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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
-
- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/10—Constructively simple tooth shapes, e.g. shaped as pins, as balls
-
- 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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/34—Toothed gearings for conveying rotary motion with gears having orbital motion involving gears essentially having intermeshing elements other than involute or cycloidal teeth
-
- 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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
- F16H2001/322—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear comprising at least one universal joint, e.g. a Cardan joint
-
- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/17—Toothed wheels
- F16H2055/176—Ring gears with inner teeth
-
- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/17—Toothed wheels
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】
本発明は円弧歯形をもつ内歯車とトロコイド系（エビト
ロコイド平行−線）歯形をもつ外歯形との組合せよシな
るトロコイド系内接噛ｅｌｌのトルク伝達装置の改良に
関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a torque transmission device for a trochoidal internal gear, which is a combination of an internal gear having a circular arc tooth profile and an external tooth profile having a trochoidal tooth profile. It is something.
油圧モータ或いは油圧ポンプその他の回転装置として利
用される従来のトロコイド系内接噛合型のトルク伝達装
置は第１図に示すような構造を有していた。す々わち、
同図は油圧モータの例示として示されるものであるが、
全体が出力機構部ａ／、変位機構室部ｂ′及びバルブ機
構部Ｃ′の５つの部分よ口Ｄ、出力機構部ａ′と変位機
構室部ｂ′はドライブ１′によシ回転力が伝達され、変
位機構室部ｂ′とバルブ機構部Ｃ′はバルブ切換用ドラ
イブ２′によシ囲転力が伝達されている。そのためにド
ライブ１′とバルブ切換用ドライブ２′はその両端にス
プライン部を有する。さらに出力機構部ａ′は、主にそ
の内側に内スプラインを有し、変位機構室部ｂ′により
発生する偏心運動を伴う外歯車３′の自転をドライブ１
′を介することによシ偏心運動を除き、自転のみを１転
力として取出す出力軸４′と、・・ウジング５′及び出
力軸４′を支承する軸受６′とからなシ、出力を相手側
に伝達すると共に外部荷重を支持するものであシ、バル
ブ機構部Ｃ′は主にその内側に内スプラインを有し、変
位機構室部ｂ／ Ｋよ多発生する偏心運動を伴う外歯車
３′の自転を、バルブ切換用ドライブ２′を介すること
によ郵偏心運動を除き自転のみを取出して回転するバル
ブ７′と、リング８′に固定され、バルブ７′との協働
によシ圧油の流路を切換えるバルブプレート９′と、及
びバルブハウジング１０′とからなり、ポンプよシ供給
された圧油を変位機構室部ｂ′の変位機構室１１′に分
配供給すると共に、戻シ側の油を変位機構室１１′から
回収するものである。A conventional trochoid internal mesh type torque transmission device used as a hydraulic motor, hydraulic pump, or other rotating device has a structure as shown in FIG. Suwachi,
The figure is shown as an example of a hydraulic motor, but
The whole consists of five parts: output mechanism part a/, displacement mechanism chamber part b', and valve mechanism part C'. The rotation force is transmitted to the displacement mechanism chamber b' and the valve mechanism C' by the valve switching drive 2'. For this purpose, the drive 1' and the valve switching drive 2' have spline portions at both ends thereof. Furthermore, the output mechanism section a' mainly has an internal spline on its inside, and the drive 1
The output shaft 4' extracts only the rotation as one rotational force by removing the eccentric movement through the bearing 5' and the bearing 6' that supports the housing 5' and the output shaft 4'. The valve mechanism section C' mainly has an internal spline on its inside, and the external gear 3 has an eccentric movement that occurs more often than the displacement mechanism chamber section B/K. A valve 7' rotates by removing eccentric movement and extracting only the rotation through a valve switching drive 2', and a valve 7' that is fixed to a ring 8' and cooperates with the valve 7' It consists of a valve plate 9' that switches the flow path of pressure oil, and a valve housing 10', and distributes and supplies the pressure oil supplied by the pump to the displacement mechanism chamber 11' of the displacement mechanism chamber b', and also distributes and returns the pressure oil supplied by the pump to the displacement mechanism chamber 11'. The oil on the side is recovered from the displacement mechanism chamber 11'.
而して、変位機構室部ｂ′は本発明の対象とされる部分
であシ、第２図に見るように、内歯車１２′の歯形とし
てローラ１５′よりなる円弧歯形を、またこの内歯車１
２′に内接噛合する外歯車３′の歯形としてトロコイド
系（エビトロコイド平行曲線）歯形を採用しておシ、シ
かも外歯車３′の歯数は内歯車１２′の歯数よシ１個少
ない。さらに内歯車中心１４′と外歯車中心１５′とは
偏心量ｅだけ偏心しており、外−車５′と内歯車１２′
は、その接触点により内歯車１２′の歯数（＠２図の場
合７個）と同数の変位機構室１１′を形成している。そ
して、バルブ機構部Ｃ′を介して圧油を変位機構室１１
′に送ることによシ、変位機構室１１′は膨張及び収縮
を〈シ返し、外歯車３′が内歯車中心１４′の周シに公
転しながら外歯車中心１５′の周ヤに自転し、圧油の圧
力エネルギーを回転力に変換する。この回転力は外歯車
３′の内スプラインからドライブ１′を介して出力軸４
′の内スプラインに伝潰され、偏心運動を伴わない自転
のみが外部に取出されるのである。As shown in FIG. 2, the displacement mechanism chamber b' is a part to which the present invention is applied, and as shown in FIG. gear 1
It is also possible to adopt a trochoidal (ebi-trochoid parallel curve) tooth profile as the tooth profile of the external gear 3' which internally meshes with the external gear 3'. There aren't many. Further, the center 14' of the internal gear and the center 15' of the external gear are eccentric by an amount of eccentricity e, and the center 14' of the internal gear 5' and the center 15' of the external gear are eccentric.
The contact points form the same number of displacement mechanism chambers 11' as the number of teeth of the internal gear 12' (7 in the case of Figure 2). Then, the pressure oil is transferred to the displacement mechanism chamber 11 via the valve mechanism section C'.
', the displacement mechanism chamber 11' undergoes expansion and contraction, and the external gear 3' rotates around the external gear center 15' while revolving around the internal gear center 14'. , converts the pressure energy of pressure oil into rotational force. This rotational force is transmitted from the internal spline of the external gear 3' to the output shaft 4 via the drive 1'.
' is transmitted through the internal spline, and only rotation without eccentric movement is extracted to the outside.
上述したような従来公知の油圧モーターは外歯車３′が
出力軸４′に対して偏心運動をする丸めに、
（１） 両端に外スプラインを有するドライブ１′が
必要であると共に、外歯車５′と出力軸４′に内スプラ
イン加工が必要である。The conventionally known hydraulic motor as described above requires (1) a drive 1' having external splines at both ends; ' and output shaft 4' require internal spline machining.
（２）スプラインの噛合は、偏心運動を伴うために歳事
の機構学的噛合条件から外れ理論噛合しないので、その
軸方向の接触幅にはおのずから限界がらシ、スプライン
の歯幅を広くしても、有効な歯幅は大きくできない。(2) Because spline engagement involves eccentric movement, it deviates from the established mechanical engagement conditions and does not engage theoretically. Therefore, there is a natural limit to the axial contact width, and the spline face width is widened. However, the effective tooth width cannot be increased.
（３）外−車５′の内スプラインと、出力軸４′の内ス
プラインまたはバルブ７′の内スプラインとの距−は偏
心の影響を小さくするためにある程度以上長くする必要
がある。(3) The distance between the inner spline of the outer wheel 5' and the inner spline of the output shaft 4' or the inner spline of the valve 7' must be longer than a certain degree in order to reduce the influence of eccentricity.
（４） ドライブ１′の軸径は出力軸４′の内部で偏
心運動をするため必ず出力軸径よシもあるａｔ細くしな
ければならない。(4) The shaft diameter of the drive 1' must be smaller than the output shaft diameter by a certain amount since eccentric movement occurs inside the output shaft 4'.
などの制約があシ、この種の油圧モーターは歳事の歯形
も共通で変位機構３ｉＩ部ｂ′の軸方向の幅を変えるだ
けで、他の部品は共通のまま、吸収量を変えてシリーズ
化で龜るという特長を有する反面、ドライブ１′とスズ
ラインの間に出力トルクの限界がある丸めに、変位機構
ｉｉ１１１’の幅を大きくとり吸収量を大きくした場合
にその使用圧力を低くしなければ表らないという問題が
あった。However, this type of hydraulic motor has the same tooth profile and only changes the axial width of the displacement mechanism 3iI part b', and the other parts remain the same and the absorption amount is changed. On the other hand, there is a limit to the output torque between the drive 1' and the tin line, so when the width of the displacement mechanism ii111' is increased to increase the absorption amount, the operating pressure must be lowered. The problem was that it was not publicly disclosed.
本発明の目的は、前記変位機構室部の構造を改良して、
小形で出力トルクが大きく、高性能かつ長寿命のトルク
伝達装置を安価に提供することにある。The object of the present invention is to improve the structure of the displacement mechanism chamber,
The purpose of the present invention is to provide a torque transmission device that is small in size, has a large output torque, has high performance, and has a long life at a low cost.
以下、本発明の一実施例を第３図以下によって説明する
。An embodiment of the present invention will be described below with reference to FIG. 3 and subsequent figures.
第３図は本発明による油圧モーターの場合の縦断面図で
あシ、第４図は第３図のＢ−Ｂ線における拡大断面図、
ＪＩ５図は中間リング、１ＩＸ６図は固定リングの断面
図である。これらの図に示すように、外歯車１は従来ど
お６トロコイド系（エビトロコイド平行曲線）歯形を有
し、またこの外歯車１が内接噛合する内歯車２も従来ど
おシ中間リング４と該リング４に保持したローラ３から
なる円弧歯形を有しており、がっ中間リング４の内径ｄ
５はローラ３のピッチ円径ｄ６より小径としく第５図）
、ローラ３を中間リング４に離脱しないように保持して
いる。そして、外歯車１と内歯車２０閏に従来のものと
同様の変位機構室５が形成されている。ま九、この内歯
車２は外側の固定リング６内で偏心運動可能に配設され
、該歯車２の中間リング４の外周に仲介ビン７を等ピッ
チで配置し、これらの仲介ビン７により円弧歯形の外画
を形成しておシ、かつ、中間リング４の外周部は、その
両端部に大径の仲介ピン保持部４ａを、中間部に小径の
中間リング逃は部４ｂを形成し九段付形状とすると共に
（第５図）、仲介ピン保持部４＆の外径ｄｓｉ；ｉ固定
り／グ４の歯先円径ｄ４より小さく、仲介ビン７のピッ
チ円径ｄ７よｐ大きく形成している。FIG. 3 is a longitudinal sectional view of the hydraulic motor according to the present invention, and FIG. 4 is an enlarged sectional view taken along line B-B in FIG.
Figure JI5 is a sectional view of the intermediate ring, and Figure 1IX6 is a sectional view of the fixed ring. As shown in these figures, the external gear 1 conventionally has a six-trochoidal tooth profile (epitrochoid parallel curve), and the internal gear 2 with which the external gear 1 internally meshes also conventionally has an intermediate ring 4. The inner diameter d of the intermediate ring 4 is
5 is smaller than the pitch circle diameter d6 of roller 3 (Fig. 5)
, the roller 3 is held by the intermediate ring 4 so as not to come off. A displacement mechanism chamber 5 similar to the conventional one is formed in the external gear 1 and the internal gear 20. (9) This internal gear 2 is arranged so as to be eccentrically movable within an outer fixed ring 6, and intermediary pins 7 are arranged at equal pitches around the outer periphery of an intermediate ring 4 of the gear 2, and these intermediary pins 7 allow circular arc The outer periphery of the intermediate ring 4 has a large diameter intermediate pin holding portion 4a at both ends thereof, and a small diameter intermediate ring relief portion 4b at the intermediate portion, forming nine steps. (Fig. 5), and the outer diameter dsi of the intermediate pin holding portion 4&; There is.
一方、固定リング６の内周には仲介ビン７が噛合する仲
介ビン７と同数Ｏ円弧歯形の仲介穴８を設け、これらの
仲介穴８によシ内歯を形成しておシ、かつ固定リング６
の内周部は、その両端部に大径の固定リング逃げ部６ａ
を、中間部に小径の固定リング内−軍部６ｂを形成した
段付形状とすると共に、同定リング逃は部６ａの径ｄ８
を中間リング仲介ビン保持部４ａの径ｄ３に対し、ｄ８
＞ ｄｉ＋ ２ｅ （・は偏心量）としている。従って
、中間リング４を仲介ビン７を外した状態において、固
定リング６に軸方向から挿入で龜、仲介ピ／７を保持し
た状態においては外れることはなく、中間リング４に仲
介ビン７を保持して運動可能である。また、仲介ビン７
のピッチ円中・−心は内歯車２のロー２３のピッチ円中
心を同一であシ、固定リング６の仲介穴８のピッチ円中
心は外歯車１の中心９と同一で、さらに本実施例の場合
、出力軸１１の中心とも同一である。仲介穴８のピッチ
円径は仲介ビン７のピッチ円径と等しくされ、しかも仲
介穴８の内径ｄ２Ｆｉ、仲介ピン７の外径ｄ１に対して
、次の条件式を満足するようにされる。On the other hand, on the inner periphery of the fixing ring 6, there are provided the same number of intermediary holes 8 having an O-arc tooth shape as the intermediary pins 7 that the intermediary pins 7 engage with, and internal teeth are formed in these intermediary holes 8 to fix the ring. ring 6
The inner periphery of the ring has a large diameter fixing ring relief part 6a at both ends thereof.
has a stepped shape with a small diameter fixing ring inner part 6b formed in the middle part, and the diameter d8 of the identification ring relief part 6a.
d8 for the diameter d3 of the intermediate ring intermediate bottle holding part 4a
> di+ 2e (・ is the amount of eccentricity). Therefore, when the intermediate ring 4 is inserted from the axial direction into the fixed ring 6 with the intermediate pin 7 removed, it will not come off and the intermediate pin 7 will be retained in the intermediate ring 4. It is possible to exercise by doing this. Also, intermediary bin 7
The center of the pitch circle is the same as the center of the pitch circle of the row 23 of the internal gear 2, and the center of the pitch circle of the intermediary hole 8 of the fixing ring 6 is the same as the center 9 of the external gear 1. In this case, the center of the output shaft 11 is also the same. The pitch circle diameter of the intermediate hole 8 is made equal to the pitch circle diameter of the intermediate bottle 7, and the following conditional expression is satisfied for the inner diameter d2Fi of the intermediate hole 8 and the outer diameter d1 of the intermediate pin 7.
（ｌｚ ＝ ｄ＋ ＋２８
但し、θ：中間リング４の固定リング６に対する偏心量
画して、仲介ビン７と仲介穴８は、ピッチ円直径及び肯
数の等しい等速度ｆｒ＊機構を構成する。々オ、図中１
２は同定リング６のボルト挿４孔である。(lz = d+ +28 where θ is the amount of eccentricity of the intermediate ring 4 with respect to the fixed ring 6. The intermediary bottle 7 and the intermediary hole 8 constitute a constant velocity fr* mechanism with the same pitch circle diameter and positive number. E, 1 in the diagram
Reference numeral 2 designates four bolt insertion holes of the identification ring 6.
本発明による油圧モーターの場合、公知のものと同じく
出力機構部ａ、変位機構室部ｂ、パルプ機構部Ｃから成
ってお夛、パルプ機構部Ｃを介して、変位機構室５に圧
油を供給すると、変位機構室５Ｆｉ膨張及び収縮を行う
。これにょ夛中閲リング４からなる内歯車２は仲介ピ／
７と仲介穴８との噛合のために自転を阻止され、外歳車
中心９の周シに公転のみを行う偏心運動をする。仁の時
、仲介ビン７は仲介穴８に沿ってその内側を公転し、か
つ両者間に発生する荷重によシ弾性変形する。外蘭車１
＃′ｉ、中間リング４が偏心運動を行うために、出力軸
１１の中心９の周シの偏心運動が吸収され、自転のみを
行い、その回転が出方軸１２に取出される（この場合、
外歯車１＃−ｉ中間リング４に対してはそ０中心１０の
周シに公転し偏心運動をしている）。In the case of the hydraulic motor according to the present invention, it is composed of an output mechanism part a, a displacement mechanism chamber part B, and a pulp mechanism part C, like the known ones. Pressure oil is supplied to the displacement mechanism chamber 5 through the pulp mechanism part C. When supplied, the displacement mechanism chamber 5Fi expands and contracts. The internal gear 2 consisting of the inner gear ring 4 is an intermediary pin/
7 and the intermediary hole 8, rotation is prevented, and eccentric movement occurs only around the circumference of the outer wheel center 9. At the time of rotation, the intermediary bottle 7 revolves inside the intermediary hole 8 and is elastically deformed by the load generated between the two. Gairan car 1
#'i, since the intermediate ring 4 performs eccentric movement, the eccentric movement around the center 9 of the output shaft 11 is absorbed and only rotates, and the rotation is taken out to the output shaft 12 (in this case ,
The external gear 1#-i revolves around the circumference of the center 10 and moves eccentrically with respect to the intermediate ring 4).
したがって本発明によれば次のど七き効果を奏する。Therefore, according to the present invention, the following effects can be achieved.
（１）外歯車１に直接出力軸１１をスグンインにょ多結
合で番るので、従来必要であったドライブ及びパルプ切
換用ドライブを省略することができる。(1) Since the output shaft 11 is connected directly to the external gear 1 in a quick and easy multiple connection, the conventionally required drive and pulp switching drive can be omitted.
（２）外歯車１と内歯車２並びに仲介ビン７と仲介穴８
の噛合は、各々歯車の機構学的噛合条件を満足し理論噛
合をする。したがって、供給される圧油の圧力が一定な
らば、歯幅を大きくして、吸収量を大としても、各々に
作用する面圧は一定である。(2) External gear 1, internal gear 2, intermediary pin 7 and intermediary hole 8
The meshes satisfy the mechanical meshing conditions of each gear and are theoretically meshed. Therefore, if the pressure of the supplied pressure oil is constant, even if the tooth width is increased and the amount of absorption is increased, the surface pressure acting on each tooth remains constant.
（３）中間リング４Ｆｉその両端部の仲介ピン保持部４
ａによシ仲介ピン７を二点支持し中間リング逃げ部４ｂ
では支持しないため、仲介ビ／７はたわみやすいので噛
合本数が増加する。(3) Intermediate pin holding parts 4 at both ends of the intermediate ring 4Fi
A supports the intermediary pin 7 at two points, and the intermediate ring relief part 4b
Since it is not supported, the intermediary pin/7 is easy to bend, so the number of meshing pins increases.
（４）変位機構室５は外歯車中心９と白画車中心１０を
通る第４図のＯ−Ｑ線を境にして片側が高圧、他の片側
が低圧となるため、中間リング４Ｆｉ油圧により弾性変
形し、仲介ビン７のピッチ円祉理論円から変形し誤差を
発生するが、仲介ビン７が荷重（油圧）に応じて弾性変
形し糾差を吸収する。(4) Since the displacement mechanism chamber 5 has high pressure on one side and low pressure on the other side with the O-Q line in Figure 4 passing through the external gear center 9 and the white wheel center 10 as boundaries, the intermediate ring 4Fi hydraulic pressure Although the intermediary bin 7 is elastically deformed and deforms from the pitch circularity theory circle and causes an error, the intermediary bin 7 elastically deforms according to the load (hydraulic pressure) and absorbs the difference.
（５）仲介穴８と仲介ビン７の関係は円弧歯形よシ成る
郷速度内歯車機構を形成するが、中間リング４と固定リ
ング６を段付構造とし、固定リング側の仲介穴日による
内歯車部６ｂの歯丈を大きくしているので理論的に噛合
本数が多くなる。(5) The relationship between the intermediary hole 8 and the intermediary pin 7 forms a high-speed internal gear mechanism with a circular arc tooth profile, but the intermediate ring 4 and the fixed ring 6 have a stepped structure, and the Since the tooth height of the gear portion 6b is increased, the number of meshing teeth is theoretically increased.
（６）以上によシ、ドライブがあることによる出力トル
クの制限がなくなり、出力トルクが大きくできると共に
、小形化、軽量化が計れる。(6) In addition to the above, there is no restriction on the output torque due to the presence of a drive, and the output torque can be increased, and the device can be made smaller and lighter.
Ｃ）歯車の噛合が理論噛合であ夛、かつ仲介ビン７と仲
介穴８Ｖｉ噛合本数が多いので作動が円滑であシ長寿命
であると共に荷重受持本数が多くなシ、個々の仲介ビン
と仲介穴に作用する荷重は小さくなる。C) The meshing of the gears is theoretical meshing, and the number of interlocking pins 7 and the intermediary holes 8Vi is large, so the operation is smooth, the life is long, and the number of load bearings is large. The load acting on the intermediate hole becomes smaller.
（８） スプライン加工を大巾に省略できるので安価
にできる。(8) Since spline processing can be largely omitted, the cost can be reduced.
第１図は従来のトルク伝達装置の縦断面図、第２図は第
１図のＡ−ム線における拡大断面図、第５図は本発明に
よるトルク伝達装置の縦断面図、請４図は第５図のＢ−
Ｂ線における拡大断面図、第５図は中間リング、第６図
は固定リングの断面図である。
１：外爾車 ２：内歯車 ３：ローラ ４：中間リング
５：変位機構室 ６：固定リング７：仲介ビ／ ８：
仲介穴
代理人 弁理士辻 三 部
第１図
第２図
第５図
７
第６図FIG. 1 is a longitudinal sectional view of a conventional torque transmission device, FIG. 2 is an enlarged sectional view taken along line A--M in FIG. 1, FIG. 5 is a longitudinal sectional view of a torque transmission device according to the present invention, and FIG. B- in Figure 5
FIG. 5 is an enlarged cross-sectional view taken along line B, FIG. 5 is a cross-sectional view of the intermediate ring, and FIG. 6 is a cross-sectional view of the fixed ring. 1: External gear 2: Internal gear 3: Roller 4: Intermediate ring 5: Displacement mechanism chamber 6: Fixed ring 7: Intermediate gear 8:
Intermediary Agent Patent Attorney Tsuji San Department Figure 1 Figure 2 Figure 5 Figure 7 Figure 6
Claims (1)
コイド系歯形をもつ外歯車とからなシ、前記内歯車と外
歯車の間に＃内歯車の歯数と同数の膨張及び収縮を行う
変位機構室を形成したトロコイド系内接噛合型のトルク
伝達装置において、前記内歯車を固定リング内で偏心運
動可能表中間リングとすると共に該中間リングの外周に
仲介ビンを保持し、前記固定リングの内周に骸仲介ビン
が噛合する円弧歯形の仲介穴を設け、しかも該仲介穴の
内径ｄ！は仲介ビンの外径ｄ１に対して、 ｄ２＝ ｄ＋＋２８ 但し、ｅ：中間リングの固定リン
グに対する偏 ６量 であシ、かつ、仲介穴のピッチ、円径及び個数がそれぞ
れ仲介ビンのピッチ円径及び個数と等しく、前記外歯車
が偏心運動を行うことなく自転のみを行うことを特徴と
するトルク伝達装置。[Scope of Claims] An internal gear with an arcuate tooth profile and an external gear with a trochoidal tooth profile that internally meshes with the wrinkled internal gear, and between the internal gear and the external gear, the number of teeth of the internal gear and In a trochoidal internal meshing type torque transmission device that has a displacement mechanism chamber that expands and contracts the same number of times, the internal gear is an intermediate ring capable of eccentric movement within a fixed ring, and an intermediate ring is attached to the outer periphery of the intermediate ring. , and an arc tooth-shaped intermediary hole in which the skeleton intermediary bottle engages is provided on the inner periphery of the fixing ring, and the inner diameter of the intermediary hole is d! is relative to the outer diameter d1 of the intermediary bottle, d2 = d++28 However, e: The offset of the intermediate ring with respect to the fixed ring is 6, and the pitch, circular diameter, and number of intermediary holes are respectively the pitch circle diameter of the intermediary bottle. and the number of the external gears is equal to each other, and the torque transmission device is characterized in that the external gear only rotates on its own axis without performing eccentric movement.
Priority Applications (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57056730A JPS58174743A (en) | 1982-04-07 | 1982-04-07 | Torque transmission |
| DE8383301932T DE3364162D1 (en) | 1982-04-07 | 1983-04-06 | Planetary rotation machine |
| DK153383A DK165462C (en) | 1982-04-07 | 1983-04-06 | HYDRAULIC ENGINE |
| US06/482,485 US4561833A (en) | 1982-04-07 | 1983-04-06 | Fluid pressure device |
| EP83301932A EP0098682B1 (en) | 1982-04-07 | 1983-04-06 | Planetary rotation machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57056730A JPS58174743A (en) | 1982-04-07 | 1982-04-07 | Torque transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS58174743A true JPS58174743A (en) | 1983-10-13 |
Family
ID=13035617
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57056730A Pending JPS58174743A (en) | 1982-04-07 | 1982-04-07 | Torque transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58174743A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60129454A (en) * | 1983-12-19 | 1985-07-10 | Sumitomo Heavy Ind Ltd | Planetary speed-up and reduction gear |
| JPS60146939A (en) * | 1983-12-31 | 1985-08-02 | Sumitomo Heavy Ind Ltd | Planetary gear-type speed multiply and reduction gear |
| WO2010018821A1 (en) * | 2008-08-12 | 2010-02-18 | Ntn株式会社 | Variable valve timing device |
| JP2010090889A (en) * | 2008-09-10 | 2010-04-22 | Ntn Corp | Variable valve timing device |
| JP2010159738A (en) * | 2008-12-09 | 2010-07-22 | Ntn Corp | Variable valve timing device |
| WO2010113747A1 (en) * | 2009-04-03 | 2010-10-07 | Ntn株式会社 | Variable valve timing device |
-
1982
- 1982-04-07 JP JP57056730A patent/JPS58174743A/en active Pending
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60129454A (en) * | 1983-12-19 | 1985-07-10 | Sumitomo Heavy Ind Ltd | Planetary speed-up and reduction gear |
| JPH0338459B2 (en) * | 1983-12-19 | 1991-06-10 | Sumitomo Heavy Industries | |
| JPS60146939A (en) * | 1983-12-31 | 1985-08-02 | Sumitomo Heavy Ind Ltd | Planetary gear-type speed multiply and reduction gear |
| JPH0570013B2 (en) * | 1983-12-31 | 1993-10-04 | Sumitomo Heavy Industries | |
| WO2010018821A1 (en) * | 2008-08-12 | 2010-02-18 | Ntn株式会社 | Variable valve timing device |
| JP2010090889A (en) * | 2008-09-10 | 2010-04-22 | Ntn Corp | Variable valve timing device |
| JP2010159738A (en) * | 2008-12-09 | 2010-07-22 | Ntn Corp | Variable valve timing device |
| WO2010113747A1 (en) * | 2009-04-03 | 2010-10-07 | Ntn株式会社 | Variable valve timing device |
| JP2010242585A (en) * | 2009-04-03 | 2010-10-28 | Ntn Corp | Variable valve timing device |
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