JPH01269760A - Controller for belt type continuously variable transmission - Google Patents
Controller for belt type continuously variable transmissionInfo
- Publication number
- JPH01269760A JPH01269760A JP9868988A JP9868988A JPH01269760A JP H01269760 A JPH01269760 A JP H01269760A JP 9868988 A JP9868988 A JP 9868988A JP 9868988 A JP9868988 A JP 9868988A JP H01269760 A JPH01269760 A JP H01269760A
- Authority
- JP
- Japan
- Prior art keywords
- oil
- lubricating oil
- belt
- pulley
- temperature
- 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 claims description 17
- 239000003921 oil Substances 0.000 claims abstract description 59
- 239000010687 lubricating oil Substances 0.000 claims abstract description 35
- 229910000831 Steel Inorganic materials 0.000 claims abstract description 22
- 239000010959 steel Substances 0.000 claims abstract description 22
- 239000000314 lubricant Substances 0.000 claims description 8
- 238000001514 detection method Methods 0.000 claims description 7
- 230000008878 coupling Effects 0.000 description 5
- 238000010168 coupling process Methods 0.000 description 5
- 238000005859 coupling reaction Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 5
- 230000007246 mechanism Effects 0.000 description 4
- 239000002184 metal Substances 0.000 description 4
- 230000003746 surface roughness Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 230000001627 detrimental effect Effects 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 238000005507 spraying 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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
-
- 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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0456—Lubrication by injection; Injection nozzles or tubes therefor
-
- 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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0487—Friction gearings
- F16H57/0489—Friction gearings with endless flexible members, e.g. belt CVTs
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmissions By Endless Flexible Members (AREA)
- General Details Of Gearings (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明はベルト式無段変速機の制御装置に関するもので
ある。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a control device for a belt-type continuously variable transmission.
（従来の技術）
例えば特開昭５９−１２１２５４号公報に記載されるよ
うに、スリットを設けた断面台形状の多数の金属ブロッ
クの該スリット部に積層金属バンドを嵌め込んでなるＶ
ベルトを用いた無段変速機は知られている。(Prior Art) For example, as described in Japanese Patent Application Laid-Open No. 59-121254, a V made by fitting a laminated metal band into the slits of a large number of metal blocks each having a trapezoidal cross section provided with slits.
Continuously variable transmissions using belts are known.
そのようなものにおいては、ブロックの側面にプーリ面
を押付けてベルト、プーリ間のスリップを防止している
が、スリップ率をゼロとすることはできないため、油の
よる潤滑が必要であることから、Ｖベルトが常時通過す
る所定箇所に潤滑油を噴射するノズルを設け、Ｖベルト
の金属積層バンド部を潤滑することにより、Ｖベルトの
発熱および摩耗を抑制することが提案されている。なお
、そのときのベルト、プーリ間の潤滑油膜の厚さはベル
ト、プーリの接触面の表面の粗さ（深さ方向）に略等し
いことが望ましい。In such devices, the pulley surface is pressed against the side of the block to prevent slip between the belt and pulley, but since the slip ratio cannot be zero, oil lubrication is required. It has been proposed to suppress heat generation and wear of the V-belt by providing nozzles that spray lubricating oil at predetermined locations through which the V-belt always passes, and lubricating the metal laminated band portion of the V-belt. Note that the thickness of the lubricating oil film between the belt and the pulley at this time is preferably approximately equal to the surface roughness (in the depth direction) of the contact surface of the belt and the pulley.
ところで、この油膜厚さは、供給油量に比例するととも
に、油温にも関係しているため、次の関係式により表す
ことができる。By the way, this oil film thickness is proportional to the amount of oil supplied and is also related to the oil temperature, so it can be expressed by the following relational expression.
ｈ−ＡｘｍＪＴ７「 −−＝■
ｈ ／ ａ−１・・・・・・■
ｈ：油膜厚さ
ｍ−単位時間当たりの油供給量
ｔ：油温度
μ：油粘度
Ａ：定数
ａ：深さ方向の表面粗さ
（発明が解決しようとする課題）
ところが、そのようなものにおいては、ベルトとプーリ
との境界面に存在する潤滑油の油膜厚さが潤滑油供給量
、油温、粘度の関数となり、伝達効率に大きく影響する
にもかかわらず、その点については全く考慮されておら
ず、運転条件、油温条件によっては必ずしも満足な動力
伝達条件となっていない。よって、一定の油量とした場
合、油温が高いと、油膜が薄くなり、ベルト、プーリの
信頼性上不利な条件となっているおそれが多分にある。h-AxmJT7" --= ■ h / a-1 ...... ■ h: Oil film thickness m - Oil supply amount per unit time t: Oil temperature μ: Oil viscosity A: Constant a: Depth direction However, in such devices, the thickness of the lubricant film existing at the interface between the belt and the pulley is a function of the lubricant supply amount, oil temperature, and viscosity. Although this has a large effect on transmission efficiency, this point has not been taken into consideration at all, and depending on the operating conditions and oil temperature conditions, the power transmission conditions are not necessarily satisfactory. In this case, if the oil temperature is high, the oil film will become thinner, which is likely to be detrimental to the reliability of the belt and pulley.
本発明はかかる点に鑑みてなされたもので、油温に応じ
て最適油膜厚さとなるように潤滑油量を制御し、■ベル
トおよびプーリの耐久性を向上させることができるベル
ト式無段変速機の制御装置を提供することを目的とする
ものである。The present invention has been made in view of the above points, and is a belt type continuously variable transmission that can control the amount of lubricating oil to achieve the optimum oil film thickness according to the oil temperature, and improve the durability of belts and pulleys. The purpose is to provide a control device for a machine.
（課題を解決するための手段）
本発明は、上記目的を達成するために、一対の可変プー
リにスチールベルトが巻き掛けられてなり、油圧ポンプ
にて発生する油圧でもって上記可変プーリのプーリ比を
変化させる無段変速機を前提とするもので、上記可変プ
ーリとスチールベルトとの間に潤滑油を供給する潤滑油
供給手段と、潤滑油の温度を検出する油温検出センサと
、該油温検出センサの出力を受け上記潤滑油供給手段に
より供給される潤滑油量を油温に応じて設定する油供給
量設定手段とを有することを特徴とするものである。(Means for Solving the Problems) In order to achieve the above object, the present invention has a steel belt wrapped around a pair of variable pulleys, and the pulley ratio of the variable pulleys is adjusted by hydraulic pressure generated by a hydraulic pump. This system is based on a continuously variable transmission that changes the temperature of the lubricating oil, and includes a lubricating oil supply means that supplies lubricating oil between the variable pulley and the steel belt, an oil temperature detection sensor that detects the temperature of the lubricating oil, and The present invention is characterized by comprising an oil supply amount setting means for receiving the output of the temperature detection sensor and setting the amount of lubricating oil to be supplied by the lubricating oil supplying means in accordance with the oil temperature.
（作用）
油温検出センサにより検出された油温に応じて、潤滑油
供給手段よりの潤滑油供給量が設定され、ベルトとプー
リとの間の油膜厚さは最適な厚さとなる。(Function) The amount of lubricating oil supplied from the lubricating oil supply means is set according to the oil temperature detected by the oil temperature detection sensor, and the thickness of the oil film between the belt and the pulley becomes optimal.
（実施例） 以下、本発明の実施例を図面に基づいて説明する。(Example) Embodiments of the present invention will be described below based on the drawings.
ベルト式無段変速機の概略構成を示している第１図にお
いて、無段変速機１は、エンジン２の出力軸Ａに連結さ
れた流体継手１０と、その出力側に設けられた油圧ポン
プ２０およびクラッチ手段３０と、これらの出力を車両
側への出力軸Ｂに伝達するベルト伝動機構４０からなる
変速機構とを備えている。In FIG. 1 showing a schematic configuration of a belt-type continuously variable transmission, the continuously variable transmission 1 includes a fluid coupling 10 connected to an output shaft A of an engine 2, and a hydraulic pump 20 provided on the output side of the fluid coupling 10. A transmission mechanism includes a clutch means 30 and a belt transmission mechanism 40 that transmits these outputs to an output shaft B to the vehicle side.
上記流体継手１０は、エンジン２の出力軸Ａに連結され
たケース１１内の一側部に固設されて上記エンジン出力
軸Ａと一体回転するポンプ１２と、このポンプ１２に対
向するようにケース１１の他側部に回転自在に配置され
て、ポンプ１２の回転によりケース１１内に充填されて
いる作動油を介して回転駆動されるタービン１３と、該
タービン１３に結合された出力軸１４とを有している。The fluid coupling 10 includes a pump 12 that is fixed to one side of a case 11 connected to the output shaft A of the engine 2 and rotates integrally with the engine output shaft A, and a case that faces the pump 12. A turbine 13 rotatably disposed on the other side of the case 11 and rotationally driven by the rotation of the pump 12 via hydraulic oil filled in the case 11; and an output shaft 14 coupled to the turbine 13. have.
さらに、流体継手１０には、図示していないが、上記出
力軸１４に結合されて、ケース１１の内面に対して締結
、開放されることにより出力軸１４と上記エンジン出力
軸Ａとの直結、分離の切換えを行うロックアツプクラッ
チが装備されている。Although not shown, the fluid coupling 10 further includes a direct connection between the output shaft 14 and the engine output shaft A by being coupled to the output shaft 14 and being fastened to and released from the inner surface of the case 11. Equipped with a lock-up clutch that switches between separation and separation.
ベルト伝動機構４０は、プライマリプーリ４３およびセ
カンダリプーリ４４と、これらのプーリ４３．４４間に
巻き掛けられたスチールベルト４５により構成されてい
る。プライマリプーリ４３およびセカンダリプーリ４４
は、入力軸４１上およびこれに平行に配置された出力軸
４２上にそれぞれ配置されている。The belt transmission mechanism 40 includes a primary pulley 43, a secondary pulley 44, and a steel belt 45 wound between these pulleys 43 and 44. Primary pulley 43 and secondary pulley 44
are arranged on the input shaft 41 and the output shaft 42 arranged parallel thereto, respectively.
上記プライマリプーリ４３は、入力軸４１に固定された
固定円錐板４３ａと、この軸４１にスライド可能に嵌合
された可動円錐板４３ｂとを有し、これらの円錐板４３
ａ、４３ｂは、その円錐面が互いに対向した状態で配置
されている。そして、可動円錐板４３ｂの移動に応じて
、上記スチールベルト４５の挟持位置が変化することに
よって有効ピッチ径が変化するようになっており、可動
円錐板４３ｂが固定円錐板４３ａから離反したときには
有効ピッチ径が小さくなる。同様に、セカンダリブーリ
４４も、固定円錐板４４ａと可動円錐板４４ｂとを有し
、可動円錐板４４ｂが出力軸４２上でスライドすること
によって有効ピッチ径が変化するようになっている。The primary pulley 43 has a fixed conical plate 43a fixed to the input shaft 41 and a movable conical plate 43b slidably fitted to the input shaft 41.
a and 43b are arranged with their conical surfaces facing each other. In accordance with the movement of the movable conical plate 43b, the clamping position of the steel belt 45 changes, thereby changing the effective pitch diameter. Pitch diameter becomes smaller. Similarly, the secondary boule 44 also has a fixed conical plate 44a and a movable conical plate 44b, and the effective pitch diameter changes as the movable conical plate 44b slides on the output shaft 42.
これらのプーリ４３，４４における可動円錐板４３ｂ、
４４ｂの各背部には、これらをスライドさせる油圧シリ
ンダ４６．４７が設けられている。Movable conical plate 43b in these pulleys 43, 44,
Each back of 44b is provided with a hydraulic cylinder 46,47 for sliding them.
そして、プライマリプーリ４３の油圧シリンダ４６に油
圧が導入されたときに、このプライマリプーリ４３の有
効ピッチ径が大きくなるとともに、これに伴ってセカン
ダリプーリ４４の有効ピッチ径が小さくなり、上記入出
力軸４１．４２間の変速比が増速方向に変化する。逆に
、上記油圧シリンダ４６内の油圧が排出されたときには
、プライマリプーリ４４の有効ピッチ径が大きくなり、
上記入出力軸４１．４２間の減速比が減速方向に変化す
るようになっている。また、セカンダリプーリ４４の油
圧シリンダ４７には、スチールベルト４５の張力を常に
適切に保持すべく所定の油圧が導入されるようになって
いる。Then, when hydraulic pressure is introduced into the hydraulic cylinder 46 of the primary pulley 43, the effective pitch diameter of the primary pulley 43 increases, and the effective pitch diameter of the secondary pulley 44 decreases accordingly. The gear ratio between 41 and 42 changes in the direction of speed increase. Conversely, when the hydraulic pressure in the hydraulic cylinder 46 is discharged, the effective pitch diameter of the primary pulley 44 increases,
The reduction ratio between the input and output shafts 41 and 42 changes in the direction of reduction. Further, a predetermined hydraulic pressure is introduced into the hydraulic cylinder 47 of the secondary pulley 44 in order to maintain the tension of the steel belt 45 appropriately at all times.
また、上記スチールベルト４５は、スチールバンド４５
ａに対し金属ブロック４５ｂが係合されてなるもので、
その通過経路に対応して、第２図に示すように、スチー
ルベルト４５の側面に、潤滑油を供給する油供給ノズル
５１．５１が配設され、スチールベルト４５の両側面に
潤滑油を供給してプーリ４３，４４とスチールベルト４
５との間を潤滑するようになっている。この潤滑油供給
量は、可変電磁バルブ５２．５２の開口量が変更される
ことで、最適な油供給量となるようになっている。なお
、この場合、スチールベルト４５の押し側と引張り側と
の両方において潤滑油を吹付けることで、両プーリ４３
，４４において同一条件で潤滑油膜厚さが形成されるよ
うにしている。Further, the steel belt 45 is
A metal block 45b is engaged with a,
Corresponding to the passage route, as shown in FIG. 2, oil supply nozzles 51 and 51 for supplying lubricating oil are arranged on the side surfaces of the steel belt 45 to supply lubricating oil to both sides of the steel belt 45. Then pulleys 43, 44 and steel belt 4
It is designed to lubricate the gap between the The amount of lubricating oil supplied is optimized by changing the opening amount of the variable electromagnetic valves 52,52. In this case, by spraying lubricating oil on both the pushing side and the pulling side of the steel belt 45, both pulleys 43
, 44, the lubricating oil film thickness is formed under the same conditions.
なお、スチールベルト４５は、両プーリ４３゜４４の変
速比の変化によりその位置が変化するが、第４図に示す
ように、その中間位置Ｐｉ、Ｐ２は常に一定であるので
、その位置に油供給ノズル５１．５１を設けるのが望ま
しい。Although the position of the steel belt 45 changes depending on the change in the gear ratio of both pulleys 43 and 44, as shown in FIG. Preferably, a supply nozzle 51.51 is provided.
上記流体継手１０、クラッチ手段３０、プライマリプー
リ４３、セカンダリプーリ４４および油供給ノズル５１
．５１には、エンジン２により駆動される油圧ポンプ２
０から吐出される作動油がバルブボディ５４を介して給
排される。The fluid coupling 10, the clutch means 30, the primary pulley 43, the secondary pulley 44, and the oil supply nozzle 51
．． 51 includes a hydraulic pump 2 driven by the engine 2.
Hydraulic oil discharged from the valve body 54 is supplied and discharged through the valve body 54.
６０はコントローラで、潤滑油の温度を検出する油温検
出センサ６１の出力を受け可変電磁バルブ５２．５２の
開口量を制御して上記油供給ノズル５１．５１を通じて
スチールベルト４５の各側面に供給される潤滑油量を油
温によって設定する油供給量設定手段１０１を有する。60 is a controller that receives the output of an oil temperature detection sensor 61 that detects the temperature of lubricating oil, controls the opening amount of a variable electromagnetic valve 52.52, and supplies oil to each side of the steel belt 45 through the oil supply nozzle 51.51. It has an oil supply amount setting means 101 for setting the amount of lubricating oil supplied according to the oil temperature.
すなわち、コントローラ６０は、検出された油温に応じ
て、上述した■式を満足する油膜厚さを形成しうる０式
のｍ（単位時間当たりの油供給量）を算出し、それに応
じてスチールベルト、プーリ間に潤滑油を供給すること
でスリップ率が少なく、スカッフィング等が生じにくく
なるように制御するようになっている。That is, the controller 60 calculates m (oil supply amount per unit time) of the formula 0 that can form an oil film thickness that satisfies the above-mentioned formula (2) according to the detected oil temperature, and accordingly By supplying lubricating oil between the belt and the pulleys, the slip rate is kept low and control is achieved so that scuffing and the like are less likely to occur.
また、コントローラ６０には、エンジン回転数を検出す
る回転数センサ６２の出力も受け、エンジン回転数をも
考慮して潤滑油供給量を設定するようになっている。こ
れは、エンジン回転数が高いと、ベルト側面に潤滑油を
供給しても遠心力により油が吹飛ばされるので、所望の
油膜厚さを得るために、油供給量をエンジン回転数が増
加するほど、増量方向に補正してやることが望ましいか
らである。The controller 60 also receives an output from a rotational speed sensor 62 that detects the engine rotational speed, and sets the lubricant supply amount taking the engine rotational speed into consideration. This is because when the engine speed is high, even if lubricating oil is supplied to the side of the belt, the oil will be blown away by centrifugal force, so in order to obtain the desired oil film thickness, the oil supply amount must be increased at the engine speed. This is because it is desirable to make the correction in the direction of increasing the amount.
続いて、上記コントローラ６０における処理の流れを第
５図に沿って説明する。Next, the flow of processing in the controller 60 will be explained with reference to FIG.
先ず、スタートすると、エンジン回転数有無によりエン
ジンが駆動しているか否かを判定する（ステップＳＬ）
。First, when starting, it is determined whether the engine is running based on the presence or absence of engine rotation speed (step SL).
.
エンジンが駆動していれば、それからエンジン回転数を
ＩＰＩ定しくステップＳ２）、潤滑油温度を測定しくス
テップＳ３）、それから、測定された潤滑油温度から油
の粘度μを演算する（ステップＳ４）。If the engine is running, then set the engine speed to IPI (step S2), measure the lubricating oil temperature (step S3), and calculate the oil viscosity μ from the measured lubricating oil temperature (step S4). .
しかして、上記０式に基づいて、プーリ４３゜４４とス
チールベルト４５との間へ供給すべき油供給量を演算す
る（ステップＳ５）。Then, based on the above equation 0, the amount of oil to be supplied between the pulleys 43 and 44 and the steel belt 45 is calculated (step S5).
その後、演算された単位時間当たりの油供給量ｍを、エ
ンジン回転数により補正する（ステップＳ６）。すなわ
ち、第６図に示すように、エンジン回転数が大きいほど
油付着量が少なくなるので、■式における定数Ａを大き
くする。Thereafter, the calculated oil supply amount m per unit time is corrected based on the engine rotation speed (step S6). That is, as shown in FIG. 6, as the engine speed increases, the amount of oil adhesion decreases, so the constant A in equation (2) is increased.
このようにして設定された潤滑油供給量に基づいて、可
変電磁バルブ５２．５２の開口量が設定されて、リター
ンする。Based on the lubricant supply amount set in this way, the opening amount of the variable electromagnetic valves 52, 52 is set, and the process returns.
これによって、潤滑油供給量が適量゛に制御され、両プ
ーリ４３，４４とスチールベルト４５との間に形成され
る油膜厚さが、油温が考慮された最適な厚さとなる。As a result, the amount of lubricating oil supplied is controlled to an appropriate amount, and the thickness of the oil film formed between both pulleys 43, 44 and the steel belt 45 becomes an optimal thickness taking into account the oil temperature.
また、ステップＳ１の判定で、エンジンが駆動していな
ければ、そのまま終了する。Further, if it is determined in step S1 that the engine is not running, the process ends immediately.
なお、プーリ４Ｂ、４４およびスチールベルト４５とも
に長期間の使用においては表面の摩耗などにより表面粗
さが変化するため。経時的に潤滑油量を増加する補正を
加えるか、あるいは表面粗さ計によりプーリ表面をモニ
タして粗さ変化の相当分だけ潤滑油量を補正することも
できる、（発明の効果）
本発明は上記のように構成したから、潤滑油の油温に応
じて最適の油膜厚さとなるように潤滑油量が設定され、
プーリおよびスチールベルトの摩耗が抑制され、それら
の耐久性が向上する。Note that the surface roughness of both the pulleys 4B, 44 and the steel belt 45 changes due to surface wear and the like when used for a long period of time. The amount of lubricating oil can be corrected by increasing the amount of lubricating oil over time, or the pulley surface can be monitored with a surface roughness meter and the amount of lubricating oil can be corrected by the amount corresponding to the change in roughness. (Effects of the Invention) The present invention Since it is configured as above, the amount of lubricating oil is set so that the optimum oil film thickness is achieved according to the oil temperature of the lubricating oil.
Wear of pulleys and steel belts is suppressed and their durability is improved.
図面は本発明の実施例を示し、第１図はベルト式無段変
速機の全体構成図、第２図および第３図は潤滑油供給系
の説明図、第４図は油供給ノズルの取付位置についての
説明図、第５図はコントローラの処理の流れを示す図、
第６図は油供給量と油付着量との関係を示す図である。
１・・・・・・無段変速機、４０・・・・・・ベルト伝
動機構、４３・・・・・・プライマリプーリ、４４・・
・・・・セカンダリプーリ、４５・・・・・・スチール
ベルト、５１・・・・・・油供給ノズル、５２・・・・
・・可変電磁バルブ、６０・・・・・・コントローラ、
６１・・・・・・油温検出センサ、１０１・・・・・・
油供給量設定手段
蚤１図
第２図
第３図The drawings show an embodiment of the present invention, in which Fig. 1 is an overall configuration diagram of a belt-type continuously variable transmission, Figs. 2 and 3 are explanatory diagrams of a lubricating oil supply system, and Fig. 4 is an illustration of the installation of an oil supply nozzle. An explanatory diagram regarding the position, FIG. 5 is a diagram showing the flow of processing of the controller,
FIG. 6 is a diagram showing the relationship between the amount of oil supplied and the amount of oil deposited. 1...Continuously variable transmission, 40...Belt transmission mechanism, 43...Primary pulley, 44...
...Secondary pulley, 45...Steel belt, 51...Oil supply nozzle, 52...
...Variable electromagnetic valve, 60... Controller,
61...Oil temperature detection sensor, 101...
Oil supply amount setting means Fig. 1 Fig. 2 Fig. 3
Claims (1)
れてなり、油圧ポンプにて発生する油圧でもって上記可
変プーリのプーリ比を変化させる無段変速機において、
上記可変プーリとスチールベルトとの間に潤滑油を供給
する潤滑油供給手段と、潤滑油の温度を検出する油温検
出センサと、該油温検出センサの出力を受け上記潤滑油
供給手段により供給される潤滑油量を油温に応じて設定
する油供給量設定手段とを有することを特徴とするベル
ト式無段変速機の制御装置。(1) In a continuously variable transmission in which a steel belt is wound around a pair of variable pulleys, and the pulley ratio of the variable pulleys is changed by hydraulic pressure generated by a hydraulic pump,
A lubricant supply means for supplying lubricant between the variable pulley and the steel belt, an oil temperature detection sensor for detecting the temperature of the lubricant, and an output of the oil temperature detection sensor and supplied by the lubricant supply means. 1. A control device for a belt-type continuously variable transmission, comprising an oil supply amount setting means for setting the amount of lubricating oil supplied according to the oil temperature.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9868988A JPH01269760A (en) | 1988-04-21 | 1988-04-21 | Controller for belt type continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9868988A JPH01269760A (en) | 1988-04-21 | 1988-04-21 | Controller for belt type continuously variable transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH01269760A true JPH01269760A (en) | 1989-10-27 |
Family
ID=14226476
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9868988A Pending JPH01269760A (en) | 1988-04-21 | 1988-04-21 | Controller for belt type continuously variable transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH01269760A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BE1005995A3 (en) * | 1992-06-11 | 1994-04-12 | Vcst Nv | Transmission unit for motor vehicles. |
| US7351172B2 (en) * | 2000-12-28 | 2008-04-01 | Van Doorne's Transmissie B.V. | Scratch preventing metal push belt and oil specification |
-
1988
- 1988-04-21 JP JP9868988A patent/JPH01269760A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BE1005995A3 (en) * | 1992-06-11 | 1994-04-12 | Vcst Nv | Transmission unit for motor vehicles. |
| US7351172B2 (en) * | 2000-12-28 | 2008-04-01 | Van Doorne's Transmissie B.V. | Scratch preventing metal push belt and oil specification |
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