JPS5846246A - Stepless speed change gear - Google Patents
Stepless speed change gearInfo
- Publication number
- JPS5846246A JPS5846246A JP56145769A JP14576981A JPS5846246A JP S5846246 A JPS5846246 A JP S5846246A JP 56145769 A JP56145769 A JP 56145769A JP 14576981 A JP14576981 A JP 14576981A JP S5846246 A JPS5846246 A JP S5846246A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- ring
- hydraulic
- hydraulic pump
- rotational speed
- 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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
【発明の詳細な説明】 に組み込んだ無段変速装置に関する。[Detailed description of the invention] This invention relates to a continuously variable transmission incorporated into a vehicle.
最適回転数を選定したシ、段階的変速による′ショック
或は切換えの手間をーなくす目的で無段変速装置が用い
られているが、従来の無段変速装置はバンドブレーキで
締る方式を採用した機械式のもの、流体を利用した油圧
式或は流体継手類等である。Continuously variable transmissions are used to select the optimal rotational speed and eliminate the shock and trouble of shifting in stages, but conventional continuously variable transmissions use a band brake system. These include mechanical types, hydraulic types that use fluid, and fluid couplings.
機械式のものは摩擦力により動力伝達をするため速度制
御が不安定であると共に、上記バンドブレーキや全体の
構造が複雑となシ製造コストが高くなる欠点があった。Mechanical types have disadvantages in that speed control is unstable because power is transmitted by frictional force, and the band brake and overall structure are complicated, resulting in high manufacturing costs.
又、油圧式のも・のけ動力伝達ー構に油圧抵抗並に漏洩
損失があるためエネルギー損失が大きく、省エネルギー
上問題があると共に配管を多数必要とするため広いスペ
ースを要する。更に流体継手は作動油量の加減によって
すベシ量を変化させるので、すべらせた分がすべてエネ
ルギーの損失となるため、全体として効率が悪い。In addition, the hydraulic power transmission mechanism has hydraulic resistance and leakage loss, resulting in large energy loss, which poses problems in terms of energy conservation, and requires a large amount of space because it requires a large number of piping. Furthermore, since the fluid coupling changes the amount of slippage depending on the amount of hydraulic oil, all the amount of slippage results in energy loss, resulting in poor overall efficiency.
本発明は上述の従来の無段変速装置の欠点を解決し、機
械式と油圧式の長所を併せもつことにより、無段階制御
を確実とし、操作が容易で構造の簡単な無段変速装置の
提供を目的としたものであり、中空軸に所要数の遊星歯
車を回転自在に設け、内外周に歯を有するリング状歯車
を該遊里歯車を包囲する如く設けてその内歯を前記遊星
歯車に噛合せしめ、太陽歯車を設けた動力軸を前記遊星
歯車と噛合するように前記中空軸に挿入し、該動力軸に
より駆動される油圧ポンプを設け、該油圧ポンプからの
圧油により作動する油圧モータの出力軸に設けたピニオ
／を前記リング状歯車の外歯に噛合せしめてなることを
特徴上する無段変速装置にかかるものである。The present invention solves the above-mentioned drawbacks of the conventional continuously variable transmission, combines the advantages of mechanical and hydraulic systems, ensures continuous control, is easy to operate, and has a simple structure. The purpose is to provide a system in which a required number of planetary gears are rotatably mounted on a hollow shaft, a ring-shaped gear having teeth on the inner and outer peripheries is provided to surround the planetary gear, and the inner teeth are attached to the planetary gear. A power shaft fitted with a sun gear is inserted into the hollow shaft so as to mesh with the planetary gear, a hydraulic pump driven by the power shaft is provided, and a hydraulic motor is operated by pressure oil from the hydraulic pump. The continuously variable transmission is characterized in that a pinio provided on the output shaft of the gearbox is meshed with external teeth of the ring-shaped gear.
以下、本発明の実施例を図面を参照しつつ説明する。Embodiments of the present invention will be described below with reference to the drawings.
中空軸（１）の−側端面の同一円周上に４本のピン（２
）の一端を夫々植設し、該各ビン（２）に所要径を有す
る遊星歯車（３）を回転自在に取シ付け、該各ピン（２
）の他端を支持する中空軸（４）を前記中空軸（１）と
一体に設け、該６中空軸（ＩＯ２）を軸受（５）により
回転自在に支持せしめる。Four pins (2
), one end of each pin (2) is rotatably attached to each pin (2), and a planetary gear (3) having a required diameter is rotatably attached to each pin (2).
) is provided integrally with the hollow shaft (1), and the six hollow shafts (IO2) are rotatably supported by bearings (5).
該一体に構成した中空軸（１）（４）に動力軸（６）を
貫通し、該動力”軸（６）の所要位置に前記遊星歯車（
３）と噛合し得るよう太陽歯車（７）を設け、該動力軸
（６）の端部軸受（５）側に油圧ポンプ（８）を取り付
け、該油圧ポンプ（８）の入力軸（９）を前記動力軸（
６）と接続”する。A power shaft (6) passes through the integrally constructed hollow shafts (1) and (4), and the planetary gear (
A sun gear (7) is provided so as to mesh with the hydraulic pump (8), and a hydraulic pump (8) is attached to the end bearing (5) side of the power shaft (6), and the input shaft (9) of the hydraulic pump (8) The said power shaft (
6).
更に、所要径を有するリング状部材の内周と外周の両方
に歯を設けたリング状歯車ａＱの内歯に前記遊星歯車（
３）が噛合するよう、前記各中空軸（］）（４）の外周
面に設けた軸受（１１） （１１５に前記リング状歯車
ａ〔を嵌合せしめ、該リング状歯車Ｑｌの外周を貫通孔
を有し且つ図示していないフレームと固定棒によシ接続
してその回転を防止した円柱状のケーシングＱ２で覆い
、該ケーシングａ２の前記中空軸（ＩＯ４１と接する゛
部分に軸受（＋３ ＜１３１を設け、該ケーシング０３
の側面所要位置４箇所に前記油圧ポンプ（８）から送ら
れる圧油により駆動される油圧モータＩを取り付け、該
各油圧モータ（１４）の各出力軸ａ９にピニオンαのを
夫々設け、該各ピニオンａｅを前記リング状歯車ａ１の
外歯と噛合せしめである。Furthermore, the planetary gear (
The ring-shaped gear a [is fitted to the bearings (11) (115) provided on the outer circumferential surface of each of the hollow shafts (]) (4) so that the bearings (11) and (4) are engaged with each other, and the ring-shaped gear Ql is passed through the outer circumference It is covered with a cylindrical casing Q2 which has a hole and is connected to a frame and a fixed rod (not shown) to prevent its rotation, and a bearing (+3 < 131 is provided, and the casing 03
Hydraulic motors I driven by pressure oil sent from the hydraulic pump (8) are installed at four required positions on the side of the hydraulic motor (14), and a pinion α is provided on each output shaft a9 of each hydraulic motor (14). The pinion ae is meshed with the external teeth of the ring-shaped gear a1.
次に、本発明の作動について説明する。Next, the operation of the present invention will be explained.
駆動装置によシ動力軸（６）を駆動すると動力軸（６）
及び太陽歯車（７）が一体となって回転され、該太陽歯
ｉａ （７）と噛合する各遊星歯車（３１ｔｉ第２図（
イ）に示すように該太陽歯車（７）の回転方向んとは逆
の回転方向島へ回転されるが、該６遊星歯車（３）はリ
ング状歯車ａ・の内歯と噛合しているため、油圧モータ
Ｉを停止しておくと該油圧モータＩの出力軸ａ９に設け
たビニオフ（ｔｅが歯止めとなりリング状歯車ａＯハ回
転されないので、該６遊星歯車（３）は偽方向に全体と
して回転される。該遊星歯車（３）＃ｉ一体に接続され
た中空軸（１）（４）に夫々ビン（２）で回転自在・と
なる、よう取り付けであるので、該６遊星歯車（３）が
全体としてへ方向へ回転するとき、中空軸（１）（４）
も偽方向と同一の方向へ回転される。When the drive device drives the power shaft (6), the power shaft (6)
and the sun gear (7) are rotated together, and each planetary gear (31ti FIG. 2 (
As shown in a), the sun gear (7) is rotated in a direction opposite to that of the sun gear (7), but the six planetary gears (3) mesh with the internal teeth of the ring gear a. Therefore, when the hydraulic motor I is stopped, the ring-shaped gear aO is not rotated because the vinyl off (te) provided on the output shaft a9 of the hydraulic motor I becomes a pawl, and the six planetary gears (3) as a whole move in the false direction. The six planetary gears (3) #i are attached to the hollow shafts (1) and (4) integrally connected to each other so that they can rotate freely with the pins (2), respectively. ) rotates in the direction as a whole, the hollow shafts (1) (4)
is also rotated in the same direction as the false direction.
この時、前記動力軸（６）と接続された油圧ポンプ（８
）を作動させ油圧モータａ４に圧油を供給し、油圧％
−１０４）（Ｄ出力＄１１１Ｑ！１９１゜設けたｅ＝オ
フ０ｆ；Ｊを停止状態から偽方向へ回転させると、油圧
モータα滲は固定して回転を防止したケーシングａ３に
取り付けられているのでリング状歯車ａ０は偽方向へ回
転される結果、各遊星歯車（３）のら方向への全体的回
転速度は前記リング状歯車員の偽方向への回転速度分減
速されることとなシ、中空軸（１）（４）の回転も減速
される。更に、油圧ポンプ（８）の斜板の傾転角を変化
させて油圧モータ（１４）の偽方向への回転速度を次第
に大きくしていくと、リング状歯車員の偽方向への回転
が次第に増速される結果、各遊星歯車（３）の偽方向へ
の全体的回転速度及び中空軸（１）（４）の回転は連続
的に減速される。減速状態からピニオンａｅの偽方向へ
の回転速度を次第に小さくしていくと、同様に中空軸（
１）（４）のへ方向への回転速度は連続的に増速される
。At this time, the hydraulic pump (8) connected to the power shaft (6)
) to supply pressure oil to the hydraulic motor a4, and the hydraulic pressure %
-104) (D output $111Q! 191° set e = OFF 0f; When J is rotated in the false direction from the stopped state, the hydraulic motor α is fixed and attached to the casing a3 that prevents rotation. As a result of the ring gear a0 being rotated in the false direction, the overall rotation speed of each planetary gear (3) in the rear direction is reduced by the rotation speed of the ring gear member in the false direction; The rotation of the hollow shafts (1) and (4) is also decelerated.Furthermore, the rotational speed of the hydraulic motor (14) in the false direction is gradually increased by changing the tilt angle of the swash plate of the hydraulic pump (8). As a result, the rotation speed of the ring gear member in the false direction is gradually increased, so that the overall rotational speed of each planetary gear (3) in the false direction and the rotation of the hollow shafts (1) and (4) are continuous. When the rotation speed of the pinion ae in the false direction is gradually reduced from the deceleration state, the hollow shaft (
1) The rotation speed in the forward direction of (4) is continuously increased.
又、油圧モータＩの回転方向が逆向きとなるよう油圧ポ
ンプ（８）を操作すると、ピニオンａ６）！／ｉ馬方向
へ回転する結果、リング状歯車α〔は田方向へ回転し、
各遊星歯車（３）の偽方向への全体的回転は該す、ング
状歯車ａ〔の偽方向への回転速変分増速されることとな
り、中空軸（１）（４）の回転も増速される。Also, when the hydraulic pump (8) is operated so that the rotation direction of the hydraulic motor I is reversed, the pinion a6)! As a result of rotating in the /i direction, the ring gear α [rotates in the direction,
The overall rotation of each planetary gear (3) in the false direction is increased by the variation of the rotational speed of the ring-shaped gear a in the false direction, and the rotation of the hollow shafts (1) and (4) is also increased. The speed will be increased.
中空軸（１） （４）の回転方向を変えるときは、駆動
装置を切シ換え動力軸（６）及び太陽歯車（力を逆の回
転方向入方向に回転させる。そうすると、第２図（ロ）
に示すように、各遊星歯車（３）はＢ、方向に回転され
、同時に全体的に偽方向に回転されるので、中空軸（１
）（４１も偽方向へ回転される。この時、前記動力軸（
６）と接続された油圧ポンプ（８）を前記の場合と同様
に操作すると、ピニオンａＱが馬方向に回転されるとき
はリング状歯車Ｑ（Ｉがへ方向へ回転され中空軸（ＩＩ
４１のへ方向への回転は増速され、又ピニオン（ＩＩが
入方向に回転されるときはリング状歯車Ｑｌ）がハ方向
５回転−され、中空軸（１）（４）のへ方向への回転は
減速される。When changing the rotation direction of the hollow shafts (1) (4), switch the drive device and rotate the power shaft (6) and the sun gear (power in the opposite rotation direction). )
As shown in FIG.
) (41 is also rotated in the false direction. At this time, the power shaft (
6) is operated in the same manner as in the previous case, when the pinion aQ is rotated in the horse direction, the ring gear Q (I is rotated in the direction to the hollow shaft (II
The rotation of 41 in the forward direction is accelerated, and the pinion (ring gear Ql when II is rotated in the inward direction) is rotated 5 times in the direction C, and the hollow shafts (1) and (4) are rotated in the forward direction. The rotation of is decelerated.
各油圧モータＩの回転速度の調節は該油圧ポンプ（８）
の斜板の傾転角を変えて圧油の吐出量を手動或は遠隔操
作で変化させることにより無段階で行なう。又、前記油
圧ポンプ（８）の傾転角制御により油圧モータ（財）を
逆転適せ、前記駆動装置を切り換えることなしに中空軸
（ＩＩ４）の逆転を行なうこともできる。The rotational speed of each hydraulic motor I is adjusted by the hydraulic pump (8).
This is done steplessly by changing the inclination angle of the swash plate to change the amount of pressure oil discharged manually or by remote control. Further, by controlling the tilting angle of the hydraulic pump (8), the hydraulic motor can be reversely reversed, and the hollow shaft (II4) can be reversely reversed without switching the drive device.
このように、動力軸（６）に接続された油圧ポンプ（８
）々１ら油圧モータＯａに送られる圧油の流量と流れ方
向を制御することによシ、前記動力軸（６）から遊星歯
車装置を介１て伝達される中空軸（１）（４）の回転速
度を遅くしたり或は早くしたり任意の速度に無段階操作
することができる。In this way, the hydraulic pump (8) connected to the power shaft (6)
) by controlling the flow rate and flow direction of the pressure oil sent to the hydraulic motor Oa, the hollow shafts (1) (4) are transmitted from the power shaft (6) through the planetary gear device (1). The rotation speed can be made slow or fast, and can be operated steplessly to any desired speed.
なお、本発明の無段変速装置は上述の実施例に限定され
るものではなく、遊星歯車４個、油圧モータ４個を使用
する場合に限られず夫々任意の個数であれば′よいと表
、各種の機械の無段変速装置として使用し得ること、等
、本発明の要旨を逸脱しない範囲内において種々変更を
加え得ることは勿論である。Note that the continuously variable transmission of the present invention is not limited to the above-described embodiment, and may be any number of planetary gears or four hydraulic motors. Of course, various modifications can be made without departing from the spirit of the present invention, such as being able to be used as a continuously variable transmission device for various machines.
以上、述べたように本発明の無段変速装置によれば、
■）動力軸の回転力をリング状歯車を有する遊星歯車装
置を介して中空軸に伝達すると共に、該動力軸の回転力
を動・力源とする油圧ポンプにより駆動゛される油圧モ
ータにより前記中空軸の回転数を制御するので、回転速
度を任意に変えることができる。As described above, according to the continuously variable transmission of the present invention, (1) the rotational force of the power shaft is transmitted to the hollow shaft via the planetary gear device having a ring-shaped gear; Since the rotational speed of the hollow shaft is controlled by a hydraulic motor driven by a hydraulic pump serving as a power source, the rotational speed can be changed arbitrarily.
■）回転速度の伝達、制御はリング状歯車、ピニオン、
遊星歯車及び太陽歯車によシ機械的に行なうので作動が
確実となる。■) Rotational speed is transmitted and controlled using ring gears, pinions,
Since this is done mechanically using planetary gears and sun gears, the operation is reliable.
■）ピニオンの回転は、動力軸によって駆動される油圧
ポンプを操作することにょシ、油圧゛モータに送る圧油
の向きと流量を連続的に変化させられるので無段階に制
御することができる。(2) The rotation of the pinion can be controlled steplessly by operating the hydraulic pump driven by the power shaft, since the direction and flow rate of the pressure oil sent to the hydraulic motor can be continuously changed.
■）遊星歯車装置と油圧装置とを一体的に組み込み、両
者の長所を利用するので、装置がクローズドとなり、エ
ネルギー損失が少なく効率的である。(2) Since the planetary gear system and the hydraulic system are integrated and the advantages of both are utilized, the system is closed and is efficient with little energy loss.
■）遊星歯車装置と油圧装置とを一体に組み込んである
ので、従来の全機械式のもの或は全油圧式のものに比べ
装置が簡略化されると共に製造コストが安価となる。(2) Since the planetary gear system and the hydraulic system are integrated, the system is simpler and the manufacturing cost is lower than conventional all-mechanical or all-hydraulic systems.
等、種々の優れた効果を発揮する。etc., exhibits various excellent effects.
第１図は本発明の無段変速装置の説明図、第２図（イ）
（０１は第１図の卜」方向矢視図であシ作動状態を合わ
せて示す図である。
図中、（１）（４）は中空軸、（２）はピン、（３）は
遊星歯車、（５）ａυα６ （＋３１ｔＡは軸受、（６
）は動力軸、（７）は太陽歯車、（８）は油圧ポンプ、
α〔はリング状歯車、Ｑ３はケーシング、ａ４）は油圧
モータ、ａｅはピニオンを示す。
特許出願人
石川島播磨重工業株式会社
特許出願人
石川島建機株式会社
特許出願人代理人Figure 1 is an explanatory diagram of the continuously variable transmission of the present invention, Figure 2 (A)
(01 is a view taken in the direction of the arrow in Figure 1 and also shows the operating state. In the figure, (1) and (4) are hollow shafts, (2) is a pin, and (3) is a planet. Gear, (5) aυα6 (+31tA is bearing, (6
) is the power shaft, (7) is the sun gear, (8) is the hydraulic pump,
α[ is a ring gear, Q3 is a casing, a4) is a hydraulic motor, and ae is a pinion. Patent applicant Ishikawajima Harima Heavy Industries Co., Ltd. Patent applicant Ishikawajima Construction Machinery Co., Ltd. Patent applicant agent
Claims (1)
周に歯を有するリング状歯車を該遊星歯車を包囲する如
く設けてその内歯を前記遊星歯車に噛合せしめ、太陽歯
車を設けた動力軸を前記遊星歯車と噛合するよう前記中
空軸に挿入し、該動力軸により駆動される油圧ポンプを
設け、該油圧ポンプからの圧油によシ作動する油圧モー
タの出力軸に設けたピニオンを前記リング状歯車の外歯
に噛合せしめてなることを特徴とする無段変速装置。1) A required number of planetary gears are rotatably provided on a hollow shaft, a ring-shaped gear having teeth on the inner and outer peripheries is provided so as to surround the planetary gears, and its internal teeth are meshed with the planetary gears to provide a sun gear. A power shaft is inserted into the hollow shaft so as to mesh with the planetary gear, a hydraulic pump driven by the power shaft is provided, and the output shaft of a hydraulic motor operated by pressure oil from the hydraulic pump is provided. A continuously variable transmission characterized in that a pinion is meshed with external teeth of the ring-shaped gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56145769A JPS5846246A (en) | 1981-09-16 | 1981-09-16 | Stepless speed change gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56145769A JPS5846246A (en) | 1981-09-16 | 1981-09-16 | Stepless speed change gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS5846246A true JPS5846246A (en) | 1983-03-17 |
Family
ID=15392731
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP56145769A Pending JPS5846246A (en) | 1981-09-16 | 1981-09-16 | Stepless speed change gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5846246A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6174941A (en) * | 1984-09-18 | 1986-04-17 | Ishikawajima Harima Heavy Ind Co Ltd | Connecting and disconnecting device |
| JPS6359512A (en) * | 1986-08-29 | 1988-03-15 | Kao Corp | Manufacture of polyurethane film |
| US5203747A (en) * | 1991-10-10 | 1993-04-20 | Warren Walter S | Integrated hydro-mechanical transmission |
| US5569110A (en) * | 1991-10-10 | 1996-10-29 | Warren; Walter S. | Integrated hydro-mechanical automobile transmission |
| US5616091A (en) * | 1991-10-10 | 1997-04-01 | Warren; Walter S. | Integrated hydro-mechanical multiple lockup transmission |
| EP1900973A1 (en) * | 2006-09-13 | 2008-03-19 | Services Pétroliers Schlumberger | Transmission system for pump drive |
-
1981
- 1981-09-16 JP JP56145769A patent/JPS5846246A/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6174941A (en) * | 1984-09-18 | 1986-04-17 | Ishikawajima Harima Heavy Ind Co Ltd | Connecting and disconnecting device |
| JPS6359512A (en) * | 1986-08-29 | 1988-03-15 | Kao Corp | Manufacture of polyurethane film |
| JPH0570570B2 (en) * | 1986-08-29 | 1993-10-05 | Kao Corp | |
| US5203747A (en) * | 1991-10-10 | 1993-04-20 | Warren Walter S | Integrated hydro-mechanical transmission |
| US5569110A (en) * | 1991-10-10 | 1996-10-29 | Warren; Walter S. | Integrated hydro-mechanical automobile transmission |
| US5616091A (en) * | 1991-10-10 | 1997-04-01 | Warren; Walter S. | Integrated hydro-mechanical multiple lockup transmission |
| EP1900973A1 (en) * | 2006-09-13 | 2008-03-19 | Services Pétroliers Schlumberger | Transmission system for pump drive |
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