JPH0979366A - Oil pressure control device for automatic transmission - Google Patents
Oil pressure control device for automatic transmissionInfo
- Publication number
- JPH0979366A JPH0979366A JP7231795A JP23179595A JPH0979366A JP H0979366 A JPH0979366 A JP H0979366A JP 7231795 A JP7231795 A JP 7231795A JP 23179595 A JP23179595 A JP 23179595A JP H0979366 A JPH0979366 A JP H0979366A
- Authority
- JP
- Japan
- Prior art keywords
- oil
- pressure
- hydraulic servo
- oil temperature
- hydraulic
- 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
Links
Landscapes
- Control Of Transmission Device (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、自動変速機の油圧
制御装置に係り、詳しくは摩擦係合手段用油圧サーボに
油圧を充填するための油圧制御装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic control device for an automatic transmission, and more particularly to a hydraulic control device for charging a hydraulic servo for friction engagement means with hydraulic pressure.
【０００２】[0002]
【従来の技術】一般に、自動車に搭載される自動変速機
は、トルクコンバータ及びプラネタリギヤユニット等の
変速ギヤ機構を有しており、該変速ギヤ機構は、クラッ
チ及びブレーキ等の摩擦係合手段によりその伝動経路が
切換えられ、前進３速、４速又はそれ以上の前進変速段
及び後進に変速される。2. Description of the Related Art Generally, an automatic transmission mounted on an automobile has a speed change gear mechanism such as a torque converter and a planetary gear unit, and the speed change gear mechanism is provided by a friction engagement means such as a clutch and a brake. The transmission path is switched, and the vehicle is shifted to the third forward speed, the fourth forward speed or higher, and the reverse speed.
【０００３】上記摩擦係合手段は、車速及び運転者の意
志を表わすアクセル開度に基づき、制御部から適宜信号
が発信され、該信号に基づき所定シフトバルブが操作さ
れることにより油圧サーボに油圧が供給又は排出され
て、切換えられる。該摩擦係合手段の切換えは、質の高
い変速作動（シフト）を行うためには、正確なタイミン
グにより適正な油圧が供給される必要がある。そして、
該正確なタイミングは、油圧サーボに油圧供給が開始さ
れてピストンを伸長し、摩擦係合手段を接触して加圧・
係合するまで、摩擦係合手段はトルク伝達をしないた
め、油圧サーボへの流体の充填時間が重要な要素とな
る。In the friction engagement means, a signal is appropriately transmitted from the control section based on the vehicle speed and the accelerator opening degree indicating the driver's intention, and a predetermined shift valve is operated based on the signal, so that the hydraulic servo operates hydraulically. Are supplied or discharged and switched. In order to perform a high-quality shift operation (shift), the switching of the friction engagement means needs to be supplied with an appropriate hydraulic pressure at an accurate timing. And
As for the accurate timing, the hydraulic servo starts to supply the hydraulic pressure to extend the piston, and the friction engagement means is contacted to apply pressure.
Since the friction engagement means does not transmit torque until the engagement, the filling time of the hydraulic servo with the fluid becomes an important factor.
【０００４】従来、例えば特公平６−５０１４４号公報
に示されるように、油圧サーボへの流体の充填時間を正
確に予測するため、油圧サーボへ流体を供給するときの
圧送速度及び流体温度との関数として有効圧送速度を決
定することに基づき、油圧サーボへの流体の充填時間を
決定する充填時間決定方法及びそのための装置が案出さ
れている。Conventionally, for example, as disclosed in Japanese Patent Publication No. 6-50144, in order to accurately predict the filling time of the fluid into the hydraulic servo, the pressure feed rate and the fluid temperature when the fluid is supplied to the hydraulic servo are A filling time determination method and a device therefor have been devised for determining the filling time of a hydraulic servo with fluid based on determining the effective pumping speed as a function.
【０００５】該充填時間決定方法及び装置は、若干の外
部因数として流体の温度（油温）が考慮されており、こ
れは、ポンプ効率損失が高温で増加することを補償する
ためと、有効圧送速度の高い領域において流体の粘度が
温度に関連することを補償するためである。The filling time determining method and apparatus considers the temperature of the fluid (oil temperature) as a slight external factor, in order to compensate for the increase in pump efficiency loss at high temperature and effective pumping. This is to compensate for the fact that the viscosity of the fluid is temperature-related in the high velocity region.
【０００６】[0006]
【発明が解決しようとする課題】上記充填時間決定方法
及び装置は、該流体（油）温により油圧サーボへの充填
時間が変更されるものであり、従って該充填時間が、油
圧サーボへの充填開始（変判断開始）後、摩擦係合手段
が係合開始する変速開始（回転変化開始）時点までに正
確に一致する場合は望ましいが、実際は、正確に一致す
るのは困難であり、シフト指令時に正確に係合タイミン
グが取れない場合があり、この場合例えばクラッチの入
出側の回転数差が大きくなってシフトショックを生ずる
虞れがある。In the filling time determining method and apparatus, the filling time for the hydraulic servo is changed depending on the fluid (oil) temperature. Therefore, the filling time is filled for the hydraulic servo. After the start (change determination start), it is desirable that the friction engagement means be in exact agreement by the shift start time (rotational change initiation) when the engagement is started, but in reality, it is difficult to obtain exact agreement, and the shift command At times, the engagement timing may not be accurately set, and in this case, for example, the rotational speed difference on the inlet and outlet sides of the clutch may become large and shift shock may occur.
【０００７】また、油温により油圧サーボへの充填時間
が変化するため、変速判断から変速開始（回転変化開
始）までの時間が油温に応じてばらつき、これにより運
転者に違和感を与えてシフトフィーリングが充分ではな
く、かつ回転変化開始（係合開始）時点が油温により変
化して、変速判断時に行う回転変化開始時の入力トルク
の設定方法が複雑で困難になる虞れがある。Further, since the filling time of the hydraulic servo changes depending on the oil temperature, the time from the shift determination to the shift start (start of rotation change) varies depending on the oil temperature, which gives the driver a feeling of discomfort. The feeling is not sufficient, and the rotation change start (engagement start) time point changes depending on the oil temperature, which may complicate and difficult the method of setting the input torque at the start of rotation change at the time of gear shift determination.
【０００８】そこで、本発明は、油圧サーボに、油温に
応じて変更される油圧を所定時間供給することにより、
上述課題を解決した自動変速機の油圧制御装置を提供す
ることを目的とするものである。Therefore, according to the present invention, by supplying the hydraulic servo with the hydraulic pressure that is changed according to the oil temperature for a predetermined time,
It is an object of the present invention to provide a hydraulic control device for an automatic transmission that solves the above problems.
【０００９】[0009]
【課題を解決するための手段】本発明は、上述事情に鑑
みなされたものであって、変速ギヤ機構の伝動経路を変
更する摩擦係合手段と、油室及びピストンを有し、前記
油室に供給又は排出される油量に応じて前記ピストンを
移動し、前記摩擦係合手段を接離する油圧サーボ（１）
と、を備えた自動変速機の油圧制御装置（Ｕ）におい
て、前記油圧サーボ（１）に供給される油の温度を検出
する油温検出手段（２）と、前記油圧サーボ（１）に供
給される油圧を調節する調圧手段（３，５）と、変速判
断から所定時間（ｔ1 ）に前記油圧サーボに供給される
油量が油温に拘らず略々一定となるように、前記油温検
出手段に基づき前記調圧手段を制御する制御手段（Ｅ）
と、を備えたことを特徴とする。SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has friction engagement means for changing the transmission path of a speed change gear mechanism, an oil chamber and a piston, and the oil chamber A hydraulic servo (1) that moves the piston according to the amount of oil supplied to or discharged from the piston to bring the friction engagement means into and out of contact.
And a hydraulic temperature control device (U) for an automatic transmission including: an oil temperature detecting means (2) for detecting a temperature of oil supplied to the hydraulic servo (1); The pressure adjusting means (3, 5) for adjusting the hydraulic pressure to be applied, and the oil amount supplied to the hydraulic servo within a predetermined time (t 1 ) from the determination of the shift are substantially constant regardless of the oil temperature. Control means (E) for controlling the pressure adjusting means based on the oil temperature detecting means
And are provided.
【００１０】望ましくは、前記変速判断からの所定時間
（ｔ1 ）と、該変速判断から前記摩擦係合手段が係合し
て変速開始するまでの時間（ｔ2 ）との間に、前記調圧
手段を低圧状態とする待機時間（ｔ1 −ｔ2 ）がある。[0010] Preferably, the a predetermined time from shift decision (t 1), between the time from the speed change judgment to the frictional engagement means is shift start engaging (t 2), said timing There is a waiting time (t 1 -t 2 ) for keeping the pressure means in a low pressure state.
【００１１】更に、前記自動変速機の入力トルクを検出
する入力トルク検出手段（６，７）を備え、前記制御手
段は、前記待機時間において前記調圧手段を前記入力ト
ルク検出手段に基づき制御してなる。 ［作用］以上構成に基づき、油圧サーボ（１）に供給さ
れる油温が検出され、これに基づき、所定時間（ｔ1 ）
に油室に供給される油量が油温に拘らず略々一定になる
ように、即ち油温が高くて油の流動抵抗が低い場合、低
目の油圧（Ｐａl ）になるように、また油温が低くて油
の流動抵抗が高い場合、高目の油圧（Ｐａｈ）になるよ
うに、調圧手段（３，５）が適宜調圧される。そして、
油圧サーボ（１）の油室に、変速判断時から所定時間
（ｔ1 ）、上記調圧された油圧（Ｐａ）が供給され、該
油室内に油温に拘りなく略々一定の油量が供給される
（ファーストフィル）。Further, an input torque detecting means (6, 7) for detecting an input torque of the automatic transmission is provided, and the control means controls the pressure adjusting means based on the input torque detecting means during the waiting time. It becomes. [Operation] Based on the above configuration, the oil temperature supplied to the hydraulic servo (1) is detected, and based on this, a predetermined time (t 1 )
So that the amount of oil supplied to the oil chamber is substantially constant regardless of the oil temperature, that is, when the oil temperature is high and the flow resistance of the oil is low, a low hydraulic pressure (Pa1) is used. When the oil temperature is low and the oil flow resistance is high, the pressure adjusting means (3, 5) is appropriately adjusted so as to obtain a higher hydraulic pressure (Pah). And
The regulated hydraulic pressure (Pa) is supplied to the oil chamber of the hydraulic servo (1) for a predetermined time (t 1 ) from the time of shift determination, and a substantially constant oil amount is maintained in the oil chamber regardless of the oil temperature. Supplied (first fill).
【００１２】所定時間（ｔ1 ）経過後、調圧手段（３，
５）は所定低圧状態（Ｐｂ）に保持され（待機時間）、
そしてシフト指令点にて、摩擦係合手段が係合を開始し
て変速開始（回転変化）するように該低圧状態が調圧さ
れ、更に油圧が徐々に増加して、摩擦係合手段が完全に
係合した時点で変速が完了する。この際、上記所定低圧
（Ｐｂ）は、入力トルク比に応じて定められ、即ち入力
トルクが大きくて、係合開始するために大きな伝達トル
ク容量を必要とする場合、高目の油圧（Ｐｂｈ）とな
り、また反対に入力トルクが小さく、係合開始のための
大きな伝達トルク容量を必要としない場合、低目の油圧
（Ｐｂl ）が設定される。After a lapse of a predetermined time (t 1 ), the pressure adjusting means (3, 3
5) is maintained at a predetermined low pressure state (Pb) (standby time),
Then, at the shift command point, the low pressure state is regulated so that the friction engagement means starts engagement and starts shifting (rotational change), and the hydraulic pressure is gradually increased to complete the friction engagement means. The shift is completed when the gear is engaged with. At this time, the predetermined low pressure (Pb) is determined according to the input torque ratio, that is, when the input torque is large and a large transmission torque capacity is required to start the engagement, the higher hydraulic pressure (Pbh). On the contrary, when the input torque is small and a large transmission torque capacity for starting the engagement is not required, the lower hydraulic pressure (Pbl) is set.
【００１３】なお、上記カッコ内の符号は、図面と対照
するためのものであるが、本発明の構成を何等限定する
ものではない。The reference numerals in parentheses are for comparison with the drawings, but do not limit the structure of the present invention in any way.
【００１４】[0014]
【発明の効果】請求項１に係る本発明によると、油温の
変化に拘りなく、油圧サーボの油室に、所定時間に略々
一定の油量が供給されて、ピストンの移動位置が略々一
定となるので、変速判断から変速開始までの時間を常に
略々一定とすることができ、運転者に違和感を与えるこ
となくフィーリングのよい変速作動を行うことができ、
更に変速開始（回転変化開始）時点が略々一定となるた
め、変速判断時等における変速開始時点での入力トルク
の設定を容易かつ確実に行うことができる。According to the first aspect of the present invention, a substantially constant amount of oil is supplied to the oil chamber of the hydraulic servo for a predetermined time regardless of the change in the oil temperature, and the moving position of the piston is substantially the same. Since it is constant, the time from the shift judgment to the start of the shift can be made substantially constant at all times, and the shift operation with a good feeling can be performed without giving the driver a feeling of discomfort.
Further, since the shift start (rotational change start) time is substantially constant, it is possible to easily and reliably set the input torque at the shift start time at the time of shift determination or the like.
【００１５】請求項２に係る本発明によると、前記油温
に関連する高い油圧が油圧サーボに供給される時間と変
速開始時間との間に、所定待機時間があるので、前記高
い油圧の供給によるピストン移動位置に余裕があり、上
記高い油圧により摩擦係合手段が係合開始して、早く変
速開始する等の不具合を確実に防止することができる。According to the second aspect of the present invention, there is a predetermined waiting time between the time when the high hydraulic pressure related to the oil temperature is supplied to the hydraulic servo and the shift start time, so that the high hydraulic pressure is supplied. There is a margin in the piston movement position due to the above, and it is possible to reliably prevent a problem such that the frictional engagement means starts to be engaged by the high hydraulic pressure and the gear shift starts early.
【００１６】請求項３に係る本発明によると、前記待機
時間における低圧を、入力トルクに基づき設定するの
で、例えば入力トルクに対して上記保持低圧が高過ぎ
て、摩擦係合手段がトルクを担持したり、また入力トル
クに対して上記保持低圧が低過ぎて、摩擦係合手段係合
時のトルク変動が大きくなって変速ショックを発生する
等の不具合を解消して、常に安定した変速特性を得るこ
とができる。According to the third aspect of the present invention, the low pressure during the standby time is set based on the input torque. Therefore, for example, the holding low pressure is too high for the input torque, and the friction engagement means carries the torque. In addition, the above-mentioned low holding pressure against input torque is too low, and torque fluctuations during engagement of the frictional engagement means become large, which eliminates problems such as a gear shift shock. Obtainable.
【００１７】[0017]
【発明の実施の形態】本発明に係る実施の形態は、図示
しない自動変速機に係るものであって、プラネタリギヤ
ユニットの伝動経路を変更する多数のクラッチ及びブレ
ーキ（摩擦係合手段）を操作する油圧サーボに関する。
各油圧サーボ１は、油室及びピストンを有しており、か
つ図１に示すように、各シフトバルブ９を介してその油
室に油圧が供給され又は排出されて、ピストンを介して
それぞれクラッチ又はブレーキを係合又は解放して各変
速段を達成する。BEST MODE FOR CARRYING OUT THE INVENTION An embodiment according to the present invention relates to an automatic transmission (not shown), and operates a number of clutches and brakes (friction engagement means) for changing the transmission path of a planetary gear unit. Regarding hydraulic servo.
Each hydraulic servo 1 has an oil chamber and a piston, and as shown in FIG. 1, the oil pressure is supplied to or discharged from the oil chamber via each shift valve 9, and the clutch is respectively engaged via the piston. Alternatively, the brake is engaged or released to achieve each shift speed.
【００１８】各油圧サーボ１へは、プレッシャコントロ
ールバルブ（調圧バルブ）５により適宜調圧された油圧
が供給され、かつ該プレッシャコントロールバルブ５
は、その調圧室５ａにリニアソレノイドバルブ３からの
制御圧が供給されて、ライン圧ポート５ｂのライン圧を
適宜調圧して出力ポート５ｃから出力する。また、リニ
アソレノイドバルブ３は、リニアソレノイド３ａ、入力
ポート３ｂ及び出力ポート３ｃを有しており、電子制御
部Ｅからのリニアソレノイド３ａへの信号に基づき、ソ
レノイドモジュレータ圧が供給されている入力ポート３
ｂの油圧を適宜調圧した制御圧として出力ポート３ｃに
出力する。A hydraulic pressure appropriately adjusted by a pressure control valve (pressure adjusting valve) 5 is supplied to each hydraulic servo 1, and the pressure control valve 5 is also provided.
The control pressure from the linear solenoid valve 3 is supplied to the pressure adjusting chamber 5a, the line pressure of the line pressure port 5b is adjusted appropriately, and the pressure is output from the output port 5c. The linear solenoid valve 3 has a linear solenoid 3a, an input port 3b, and an output port 3c, and an input port to which solenoid modulator pressure is supplied based on a signal from the electronic control unit E to the linear solenoid 3a. Three
The hydraulic pressure of b is output to the output port 3c as a control pressure adjusted appropriately.
【００１９】そして、電子制御部Ｅには、前記ライン圧
等の油圧サーボ１に供給する油の温度を検出する油温セ
ンサ２、自動変速機の入力軸の回転を検出するインプッ
トセンサ６及び出力軸の回転を検出するアウトプットセ
ンサ７等からの信号が入力されており、前記インプット
センサ６及びアウトプットセンサ７に基づき負荷トル
ク、即ち接続作動する摩擦係合手段の入力トルク（クラ
ッチトルク容量、ブレーキトルク容量）が検出・演算さ
れる。The electronic control unit E has an oil temperature sensor 2 for detecting the temperature of the oil supplied to the hydraulic servo 1 such as the line pressure, an input sensor 6 for detecting the rotation of the input shaft of the automatic transmission, and an output. A signal from an output sensor 7 or the like for detecting rotation of the shaft is input, and a load torque based on the input sensor 6 and the output sensor 7, that is, an input torque (clutch torque capacity, Brake torque capacity) is detected and calculated.
【００２０】ついで、図２及び図３に沿って、本実施の
形態に係る作用について説明する。電子制御部Ｅに入力
される車速及びスロットル開度に基づき、変速マップに
従って変速判断がなされる（Ｓ１）。そして、油温セン
サ２による油温の検出に基づき、所定油圧サーボ１に供
給される油圧比Ｐａが計算され（Ｓ２）、更に該計算値
に基づく電子制御部Ｅからの信号により、リニアソレノ
イドバルブ３が適宜調圧制御されて所定制御圧が出力
し、プレッシャコントロールバルブ５は、上記制御圧に
対応した所定油圧比Ｐａを出力する（Ｓ３）。この際、
油温と油圧比の関係は、図４に示すような関係にあり、
この関係は油の粘性係数（油温に依存）の特性に基づい
て決まるものであって、上記油圧比Ｐａの計算は、図４
に示すグラフに対応して又はその関数を計算して、或い
は所定油温範囲に基づき油圧比を複数のステップ状に変
化して、油温変化に拘りなく、所定時間ｔ1 に油圧サー
ボ１の油室に供給される油量が略々一定になるように設
定される。即ち、油圧が低くて粘度が高い場合、油圧比
が高目（Ｐａｈ）に設定され、また反対に油温が高く粘
度が低い場合、油圧比が低目（Ｐａl ）に設定され、こ
れにより、所定時間ｔ1 に油圧サーボ１の油室に供給さ
れる油量が、油温の変化（従ってそれに伴う流動抵抗変
化）に拘りなく、略々一定になるように設定される。Next, the operation according to the present embodiment will be described with reference to FIGS. 2 and 3. Based on the vehicle speed and throttle opening input to the electronic control unit E, a shift determination is made according to a shift map (S1). Then, the hydraulic pressure ratio Pa supplied to the predetermined hydraulic servo 1 is calculated based on the detection of the oil temperature by the oil temperature sensor 2 (S2), and the signal from the electronic control unit E based on the calculated value is used to calculate the linear solenoid valve. 3 is appropriately pressure-controlled to output a predetermined control pressure, and the pressure control valve 5 outputs a predetermined hydraulic pressure ratio Pa corresponding to the control pressure (S3). On this occasion,
The relationship between the oil temperature and the oil pressure ratio is as shown in FIG.
This relationship is determined based on the characteristic of the viscosity coefficient of oil (depending on the oil temperature), and the calculation of the hydraulic pressure ratio Pa is as shown in FIG.
Corresponding to the graph shown in FIG. 2 or the function thereof is calculated, or the hydraulic pressure ratio is changed in a plurality of steps based on the predetermined oil temperature range to change the hydraulic servo 1 at the predetermined time t 1 regardless of the change in the oil temperature. The amount of oil supplied to the oil chamber is set to be substantially constant. That is, when the oil pressure is low and the viscosity is high, the oil pressure ratio is set to a high value (Pah), and conversely, when the oil temperature is high and the viscosity is low, the oil pressure ratio is set to a low value (Pal). The amount of oil supplied to the oil chamber of the hydraulic servo 1 at the predetermined time t 1 is set to be substantially constant regardless of the change in the oil temperature (and hence the change in the flow resistance).
【００２１】そして、該設定された油圧比Ｐａが、変速
判断時から所定時間ｔ1 、油圧サーボ１の油室に供給さ
れる（Ｓ４）。これにより、上述したように、所定時間
ｔ1に供給される油量は、油温に拘りなく略々一定なの
で、油圧サーボ１のピストンは略々一定の所定位置まで
伸長する。なお、上記所定時間ｔ1 は、油圧サーボのピ
ストンが摩擦係合手段を係合開始（変速開始）するまで
の時間ｔ2 よりも短く設定されており、従って上記両時
間の差（ｔ2 −ｔ1 ）だけ、待機時間を有するようにな
っている。Then, the set hydraulic pressure ratio Pa is supplied to the oil chamber of the hydraulic servo 1 for a predetermined time t 1 from the time of the shift judgment (S4). As a result, as described above, the amount of oil supplied at the predetermined time t 1 is substantially constant regardless of the oil temperature, so that the piston of the hydraulic servo 1 extends to a substantially constant predetermined position. The predetermined time t 1 is set to be shorter than the time t 2 until the piston of the hydraulic servo starts engaging the friction engagement means (start of gear shift), and therefore the difference between the both times (t 2 − It has a waiting time of t 1 ).
【００２２】該待機時間（ｔ2 −ｔ1 ）では、摩擦係合
手段が係合しない低い油圧Ｐｂに設定されている。更
に、変速判断時において、前記インプットセンサ６及び
アウトプットセンサ７からの信号に基づき、該変速作動
に関与する摩擦係合手段の入力トルク（トルク容量）が
検出・演算され（Ｓ５）、更に該入力トルク値に基づき
該摩擦係合手段用油圧サーボ１の油圧比Ｐｂが設定され
る（Ｓ６）。即ち、該油圧比Ｐｂは、入力トルクが大き
い場合、それに対応して高目（Ｐｂｈ）に設定され、ま
た入力トルクが小さい場合、それに対応して低目（Ｐｂ
l ）に設定される。During the waiting time (t 2 -t 1 ), the hydraulic pressure Pb is set to a low level so that the friction engagement means does not engage. Further, at the time of determining the shift, the input torque (torque capacity) of the friction engagement means involved in the shift operation is detected and calculated based on the signals from the input sensor 6 and the output sensor 7 (S5), and further The hydraulic pressure ratio Pb of the friction engagement means hydraulic servo 1 is set based on the input torque value (S6). That is, when the input torque is large, the oil pressure ratio Pb is set to a high value (Pbh), and when the input torque is small, the oil pressure ratio Pb is set to a low value (Pbh).
l) is set.
【００２３】該低油圧Ｐｂ状態は、略々一定時間からな
る待機時間（ｔ2 −ｔ1 ）保持され、そして変速開始時
（ｔ2 ）に合せるように、電子制御部Ｅからの信号に基
づき、リニアソレノイドバルブ３の制御圧によりプレッ
シャコントロールバルブ５が調圧制御されて、油圧サー
ボ１への供給油圧を徐々に上昇し、摩擦係合手段が係合
を開始してトルクを伝達する（変速開始）（Ｓ７）。更
に、上述プレッシャコントロールバルブ５により油圧比
が上昇され、摩擦係合手段の係合圧が増加してその伝達
トルクを徐々に増加し、そして摩擦係合手段が完全に係
合して変速作動が完了する（変速完了）。この際、自動
変速機の入力軸の回転数、従って上記油圧サーボにより
制御される摩擦係合手段の入力側回転数は、図３に示す
ように、エンジン回転数の増加に伴い徐々に増加し、そ
してアップシフトへの変速開始に伴い、上記摩擦係合手
段のトルク容量が増大するに従いそのギヤ変速差だけ徐
々に低下し、そして変速完了した時点で、再びエンジン
回転数の増加に伴い増加する。The low oil pressure Pb state is maintained for a standby time (t 2 -t 1 ) which is a substantially constant time, and based on a signal from the electronic control unit E so as to match with the shift start time (t 2 ). The pressure control valve 5 is pressure-controlled by the control pressure of the linear solenoid valve 3, the hydraulic pressure supplied to the hydraulic servo 1 is gradually increased, and the friction engagement means starts engagement to transmit torque (speed change). Start) (S7). Furthermore, the hydraulic pressure ratio is increased by the pressure control valve 5 described above, the engagement pressure of the friction engagement means is increased and the transmission torque thereof is gradually increased, and the friction engagement means is completely engaged to perform the gear shift operation. Completed (shift completed). At this time, the rotational speed of the input shaft of the automatic transmission, and hence the input rotational speed of the friction engagement means controlled by the hydraulic servo, gradually increases as the engine rotational speed increases, as shown in FIG. As the torque capacity of the friction engagement means increases with the start of the shift to the upshift, the gear shift difference gradually decreases, and when the shift is completed, it increases with the increase in the engine speed. .
【図１】本発明に係る油圧制御装置を示す図。FIG. 1 is a diagram showing a hydraulic control device according to the present invention.
【図２】その作動を示すフローチャート。FIG. 2 is a flowchart showing the operation.
【図３】そのタイムチャート。FIG. 3 is a time chart thereof.
【図４】油温と油圧比の関係を示す図。FIG. 4 is a diagram showing a relationship between an oil temperature and an oil pressure ratio.
１ 油圧サーボ ２ 油温検出手段（油温センサ） ３ 調圧手段（リニアソレノイドバルブ） ５ 調圧手段（プレッシャコントロールバルブ） ６ インプットセンサ（入力トルク検出手段） ７ アウトプットセンサ（入力トルク検出手段） Ｅ 制御手段（電子制御部） ｔ1 所定時間 ｔ2 変速開始時間 Ｐａ 油圧比 Ｐｂ 低圧状態油圧比 Ｕ 油圧制御装置1 Hydraulic Servo 2 Oil Temperature Detector (Oil Temperature Sensor) 3 Pressure Regulator (Linear Solenoid Valve) 5 Pressure Regulator (Pressure Control Valve) 6 Input Sensor (Input Torque Detector) 7 Output Sensor (Input Torque Detector) E control means (electronic control unit) t 1 predetermined time t 2 shift start time Pa hydraulic pressure ratio Pb low pressure state hydraulic pressure ratio U hydraulic control device
───────────────────────────────────────────────────── フロントページの続き (72)発明者 西田 正明 愛知県安城市藤井町高根10番地 アイシ ン・エィ・ダブリュ株式会社内 (72)発明者 早渕 正宏 愛知県安城市藤井町高根10番地 アイシ ン・エィ・ダブリュ株式会社内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Masaaki Nishida, 10 Takane, Fujii-cho, Anjo, Aichi Prefecture, Aisin AW Co., Ltd. (72) Masahiro Hayabuchi, Takane, Fujii-cho, Anjo, Aichi Prefecture, Aisin・ AW Co., Ltd.
Claims (3)
係合手段と、 油室及びピストンを有し、前記油室に供給又は排出され
る油量に応じて前記ピストンを移動し、前記摩擦係合手
段を接離する油圧サーボと、 を備えた自動変速機の油圧制御装置において、 前記油圧サーボに供給される油の温度を検出する油温検
出手段と、 前記油圧サーボに供給される油圧を調圧する調圧手段
と、 変速判断から所定時間に前記油圧サーボに供給される油
量が油温に拘らず略々一定となるように、前記油温検出
手段に基づき前記調圧手段を制御する制御手段と、 を備えたことを特徴とする自動変速機の油圧制御装置。1. A friction engagement means for changing a transmission path of a speed change gear mechanism, an oil chamber and a piston, wherein the piston is moved according to the amount of oil supplied to or discharged from the oil chamber, In a hydraulic control device for an automatic transmission, comprising: a hydraulic servo that engages and disengages the engaging means, an oil temperature detecting means that detects a temperature of oil supplied to the hydraulic servo, and a hydraulic pressure supplied to the hydraulic servo. And a pressure adjusting means for controlling the pressure adjusting means based on the oil temperature detecting means so that the amount of oil supplied to the hydraulic servo within a predetermined time after the shift is determined is substantially constant regardless of the oil temperature. A hydraulic control device for an automatic transmission, comprising:
判断から前記摩擦係合手段が係合して変速開始するまで
の時間との間に、前記調圧手段を低圧状態とする待機時
間がある、 請求項１記載の自動変速機の油圧制御装置。2. A standby time for keeping the pressure adjusting means in a low pressure state between a predetermined time from the shift determination and a time from the shift determination until the friction engagement means is engaged and a shift is started. The hydraulic control device for the automatic transmission according to claim 1.
る入力トルク検出手段を備え、 前記制御手段は、前記待機時間において前記調圧手段を
前記入力トルク検出手段に基づき制御してなる、 請求項２記載の自動変速機の油圧制御装置。3. An input torque detection means for detecting an input torque of the friction engagement means is provided, and the control means controls the pressure adjusting means based on the input torque detection means during the waiting time. Item 2. A hydraulic control device for an automatic transmission according to item 2.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23179595A JP3393460B2 (en) | 1995-09-08 | 1995-09-08 | Hydraulic control device for automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23179595A JP3393460B2 (en) | 1995-09-08 | 1995-09-08 | Hydraulic control device for automatic transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0979366A true JPH0979366A (en) | 1997-03-25 |
| JP3393460B2 JP3393460B2 (en) | 2003-04-07 |
Family
ID=16929146
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP23179595A Expired - Fee Related JP3393460B2 (en) | 1995-09-08 | 1995-09-08 | Hydraulic control device for automatic transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3393460B2 (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03209051A (en) * | 1990-04-27 | 1991-09-12 | Nissan Motor Co Ltd | Automatic transmission |
| JPH03288061A (en) * | 1990-04-04 | 1991-12-18 | Aisin Seiki Co Ltd | Oil pressure control device for automatic transmission |
| JPH04102761A (en) * | 1989-12-26 | 1992-04-03 | General Motors Corp <Gm> | Transmission-clutch and method and device for determining filling time of brake oil |
| JPH04366063A (en) * | 1991-06-13 | 1992-12-17 | Mitsubishi Electric Corp | Controller for automatic transmission |
| JPH08326897A (en) * | 1995-05-29 | 1996-12-10 | Jatco Corp | Hydraulic controller for automatic transmission |
-
1995
- 1995-09-08 JP JP23179595A patent/JP3393460B2/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04102761A (en) * | 1989-12-26 | 1992-04-03 | General Motors Corp <Gm> | Transmission-clutch and method and device for determining filling time of brake oil |
| JPH0650144B2 (en) * | 1989-12-26 | 1994-06-29 | ゼネラル・モーターズ・コーポレーション | METHOD FOR DETERMINING FLUID FILLING TIME OF TORQUE TRANSMISSION DEVICE AND DEVICE FOR THE SAME |
| JPH03288061A (en) * | 1990-04-04 | 1991-12-18 | Aisin Seiki Co Ltd | Oil pressure control device for automatic transmission |
| JPH03209051A (en) * | 1990-04-27 | 1991-09-12 | Nissan Motor Co Ltd | Automatic transmission |
| JPH04366063A (en) * | 1991-06-13 | 1992-12-17 | Mitsubishi Electric Corp | Controller for automatic transmission |
| JPH08326897A (en) * | 1995-05-29 | 1996-12-10 | Jatco Corp | Hydraulic controller for automatic transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3393460B2 (en) | 2003-04-07 |
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