JP2001241541A - Hydraulic pressure controller for automatic transmission - Google Patents
Hydraulic pressure controller for automatic transmissionInfo
- Publication number
- JP2001241541A JP2001241541A JP2000051916A JP2000051916A JP2001241541A JP 2001241541 A JP2001241541 A JP 2001241541A JP 2000051916 A JP2000051916 A JP 2000051916A JP 2000051916 A JP2000051916 A JP 2000051916A JP 2001241541 A JP2001241541 A JP 2001241541A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- precharge
- hydraulic
- engagement element
- hydraulic pressure
- 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
御装置に関し、詳しくは、クラッチ等の摩擦係合要素の
締結時に、油圧をプリチャージする構成の油圧制御装置
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 configured to precharge hydraulic pressure when a friction engagement element such as a clutch is engaged.
【0002】[0002]
【従来の技術】従来から、車両用の自動変速機におい
て、クラッチ等の摩擦係合要素を締結させるときに、油
圧を摩擦係合要素に対してプリチャージすることで、摩
擦係合要素の動作遅れを防止する構成が知られている
(特開平5−106722号公報参照)。2. Description of the Related Art Conventionally, in an automatic transmission for a vehicle, when a frictional engagement element such as a clutch is engaged, a hydraulic pressure is precharged to the frictional engagement element to thereby operate the frictional engagement element. A configuration for preventing the delay is known (see Japanese Patent Application Laid-Open No. 5-106722).
【0003】[0003]
【発明が解決しようとする課題】しかし、従来では、締
結しようとする摩擦係合要素が直前に解放制御された摩
擦係合要素であった場合などにおいて、油圧が抜け切っ
ていない状態でプリチャージが行われる可能性があっ
た。プリチャージは、通常、油圧が抜け切った状態の摩
擦係合要素に対して行われ、係る条件に適合してプリチ
ャージ圧・プリチャージ時間が設定されるため、前述の
ように、油圧が抜け切っていない状態でプリチャージが
行われると、プリチャージによって過剰に油圧が上昇
し、大きな変速ショックを発生させてしまう可能性があ
った。However, in the prior art, when the frictional engagement element to be fastened is a frictional engagement element whose release has been controlled just before, for example, the precharge is performed in a state where the hydraulic pressure has not been completely released. Could have been done. The precharge is usually performed on the friction engagement element in a state where the hydraulic pressure is completely released, and since the precharge pressure and the precharge time are set in conformity with the conditions, as described above, the hydraulic pressure is released. If the precharge is performed in a state where the vehicle is not turned off, there is a possibility that the hydraulic pressure excessively increases due to the precharge and a large shift shock is generated.
【0004】本発明は上記問題点に鑑みなされたもので
あり、油圧が抜け切っていない状態でプリチャージが行
われることがあっても、油圧の過剰上昇を回避でき、以
って、変速ショックの発生を回避できる自動変速機の油
圧制御装置を提供することを目的とする。[0004] The present invention has been made in view of the above problems, and even if the precharge is performed in a state where the hydraulic pressure has not been completely released, an excessive increase in the hydraulic pressure can be avoided. It is an object of the present invention to provide a hydraulic control device for an automatic transmission capable of avoiding the occurrence of a wobble.
【0005】[0005]
【課題を解決するための手段】そのため請求項1記載の
発明では、摩擦係合要素を締結させるときに油圧のプリ
チャージを行う自動変速機の油圧制御装置であって、前
記プリチャージ開始直前の摩擦係合要素の係合油圧に基
づいてプリチャージを補正制御する構成とした。According to the first aspect of the present invention, there is provided a hydraulic control device for an automatic transmission for precharging hydraulic pressure when a frictional engagement element is engaged, the hydraulic control device comprising: The precharge is corrected and controlled based on the engagement hydraulic pressure of the friction engagement element.
【0006】かかる構成によると、プリチャージを開始
する前に、締結させる摩擦係合要素の残圧を判定し、該
残圧に応じた特性でプリチャージを行わせる。請求項2
記載の発明では、前記摩擦係合要素に対する指示油圧に
対して遅れ補正を施して、前記プリチャージ開始直前の
摩擦係合要素の係合油圧を推定する構成とした。According to this configuration, before starting the precharge, the residual pressure of the friction engagement element to be fastened is determined, and the precharge is performed with characteristics according to the residual pressure. Claim 2
In the invention described above, a configuration is adopted in which delay correction is performed on the command oil pressure for the friction engagement element to estimate the engagement oil pressure of the friction engagement element immediately before the start of the precharge.
【0007】かかる構成によると、指示油圧に対して実
際の係合油圧は遅れを有して変化するので、指示油圧に
対して遅れ補正を施すことで実際の係合油圧を推定す
る。請求項3記載の発明では、前記締結させる摩擦係合
要素に油圧を供給する油圧配管内の油圧を検出する油圧
センサの検出値に対して遅れ補正を施して、前記プリチ
ャージ開始直前の摩擦係合要素の係合油圧を推定する構
成とした。According to such a configuration, since the actual engagement oil pressure changes with a delay with respect to the instruction oil pressure, the actual engagement oil pressure is estimated by performing a delay correction on the instruction oil pressure. According to the third aspect of the present invention, a delay correction is performed on a detection value of a hydraulic pressure sensor that detects a hydraulic pressure in a hydraulic pipe that supplies a hydraulic pressure to the friction engagement element to be fastened, so that a frictional engagement immediately before the start of the precharge is performed. The configuration was such that the engagement oil pressure of the joint element was estimated.
【0008】かかる構成によると、油圧配管内の油圧に
対して実際の係合油圧は遅れを有して変化するので、油
圧配管内の油圧の検出値に対して遅れ補正を施すことで
実際の係合油圧を推定する。According to this configuration, the actual engagement oil pressure changes with a delay with respect to the oil pressure in the hydraulic pipe. Estimate the engagement hydraulic pressure.
【0009】請求項4記載の発明では、前記摩擦係合要
素に対する指示油圧がゼロになってからの経過時間に基
づき、前記プリチャージ開始直前の摩擦係合要素の係合
油圧を推定する構成とした。According to a fourth aspect of the present invention, a configuration is provided in which the engagement oil pressure of the friction engagement element immediately before the start of the precharge is estimated based on the elapsed time from when the command oil pressure for the friction engagement element becomes zero. did.
【0010】かかる構成によると、摩擦係合要素に対す
る指示油圧がゼロになってから、遅れて摩擦係合要素の
係合油圧がゼロにまで低下することから、指示油圧がゼ
ロになってからプリチャージを開始するまでの経過時間
に基づき、プリチャージ開始直前の摩擦係合要素の係合
油圧を推定する。With this configuration, since the engagement oil pressure of the friction engagement element drops to zero with a delay after the instruction oil pressure for the friction engagement element has become zero, the pre-pressing operation is performed after the instruction oil pressure becomes zero. The engagement oil pressure of the friction engagement element immediately before the start of the precharge is estimated based on the elapsed time until the start of the charging.
【0011】請求項5記載の発明では、前記指示油圧が
ゼロになるまでの変化速度及びゼロになってからの経過
時間に応じて、前記プリチャージ開始直前の摩擦係合要
素の係合油圧を推定する構成とした。According to the fifth aspect of the present invention, the engagement hydraulic pressure of the friction engagement element immediately before the start of the precharge is changed according to the change speed until the command oil pressure becomes zero and the elapsed time after the instruction oil pressure becomes zero. It was configured to be estimated.
【0012】かかる構成によると、指示油圧をゼロに向
けて減少変化させるときの変化速度によって実際の係合
油圧の遅れが変化し、指示油圧がゼロになってからの経
過時間が同じでも指示油圧の変化速度が異なっていた場
合には、摩擦係合要素の係合油圧が異なる値を示すの
で、指示油圧がゼロになるまでの変化速度及びゼロにな
ってからの経過時間に応じてプリチャージ開始直前の係
合油圧を推定する。According to this configuration, the delay of the actual engagement oil pressure changes depending on the change speed when the instruction oil pressure is decreased toward zero, and even if the elapsed time after the instruction oil pressure becomes zero is the same, the instruction oil pressure is reduced. If the change speed of the friction engagement element is different, the pre-charge is performed according to the change speed until the indicated oil pressure becomes zero and the elapsed time after the change to zero. Estimate the engagement oil pressure immediately before the start.
【0013】請求項6記載の発明では、前記締結させる
摩擦係合要素に油圧を供給する油圧配管内の油圧を検出
する油圧センサの検出値がゼロになってからの経過時間
に応じて、前記プリチャージ開始直前の摩擦係合要素の
係合油圧を推定する構成とした。According to the present invention, the hydraulic pressure sensor for detecting the hydraulic pressure in the hydraulic pipe for supplying the hydraulic pressure to the frictional engagement element to be fastened has a function of detecting the hydraulic pressure in the hydraulic pipe. The configuration is such that the engagement hydraulic pressure of the friction engagement element immediately before the start of precharge is estimated.
【0014】かかる構成によると、摩擦係合要素に油圧
を供給する油圧配管内の油圧を検出する油圧センサが設
けられるが、該油圧センサで検出される油圧配管内の油
圧に対して摩擦係合要素の係合油圧が遅れて変化し、油
圧配管内の油圧がゼロになってから遅れて係合油圧がゼ
ロになるので、センサの検出油圧(油圧配管内の油圧)
がゼロになってからプリチャージを開始するまでの経過
時間に基づき、プリチャージ開始直前の摩擦係合要素の
係合油圧を推定する。According to this structure, the oil pressure sensor for detecting the oil pressure in the hydraulic pipe for supplying the oil pressure to the friction engagement element is provided. Since the engagement hydraulic pressure of the element changes with a delay and the hydraulic pressure in the hydraulic piping becomes zero after the hydraulic pressure in the hydraulic piping becomes zero, the hydraulic pressure detected by the sensor (the hydraulic pressure in the hydraulic piping)
Estimates the engagement oil pressure of the friction engagement element immediately before the start of the precharge, based on the elapsed time from the time when the pressure becomes zero to the start of the precharge.
【0015】請求項7記載の発明では、前記摩擦係合要
素に対する指示油圧がゼロになってからの経過時間に応
じて、前記締結させる摩擦係合要素に油圧を供給する油
圧配管内の油圧がゼロになるタイミングを推定し、該推
定したタイミングからの経過時間に応じて、前記プリチ
ャージ開始直前の摩擦係合要素の係合油圧を推定する構
成とした。According to the present invention, the hydraulic pressure in the hydraulic pipe for supplying the hydraulic pressure to the friction engagement element to be engaged is changed according to the elapsed time from when the command hydraulic pressure for the friction engagement element becomes zero. The timing at which it becomes zero is estimated, and the engagement hydraulic pressure of the friction engagement element immediately before the start of the precharge is estimated in accordance with the elapsed time from the estimated timing.
【0016】かかる構成によると、指示油圧がゼロにな
ってから遅れて油圧配管内の油圧がゼロになり、更に遅
れて摩擦係合要素の係合油圧がゼロになることから、指
示油圧がゼロになってからの経過時間に基づいて油圧配
管内の油圧がゼロになるタイミングを推定し、該推定し
た油圧配管内の油圧がゼロになった時点からプリチャー
ジ開始直前までの経過時間によって、摩擦係合要素の係
合油圧を推定する。According to such a configuration, the hydraulic pressure in the hydraulic pipe becomes zero with a delay after the indicated hydraulic pressure becomes zero, and the engagement hydraulic pressure of the friction engagement element becomes zero with a further delay. The timing at which the hydraulic pressure in the hydraulic piping becomes zero is estimated based on the elapsed time since the hydraulic pressure became zero. The engagement oil pressure of the engagement element is estimated.
【0017】請求項8記載の発明では、前記プリチャー
ジ開始直前の摩擦係合要素の係合油圧が高いときほど、
プリチャージにおける指示油圧をより低く、及び/又
は、プリチャージ時間をより短く補正する構成とした。According to the present invention, as the engagement oil pressure of the friction engagement element immediately before the start of the precharge becomes higher,
The configuration is such that the command oil pressure in the precharge is made lower and / or the precharge time is corrected to be shorter.
【0018】かかる構成によると、プリチャージ開始直
前の摩擦係合要素の係合油圧が高く残圧がある場合に
は、過剰な油圧の供給が行われないように、プリチャー
ジの指示油圧を低く補正するか、又は、プリチャージ時
間をより短く補正するか、又は、プリチャージ指示油圧
の低下とプリチャージ時間の短縮とを同時に行う。According to this configuration, when the engagement oil pressure of the friction engagement element immediately before the start of the precharge is high and there is a residual pressure, the precharge command oil pressure is lowered so as not to supply an excessive oil pressure. The correction is performed, or the precharge time is corrected to be shorter, or the reduction of the precharge instruction oil pressure and the reduction of the precharge time are simultaneously performed.
【0019】[0019]
【発明の効果】請求項1記載の発明によると、プリチャ
ージの開始時に残圧がある場合に、プリチャージを補正
することで、過剰な油圧の供給が行われることを回避で
き、以って、変速ショックの発生を防止できるという効
果がある。According to the first aspect of the invention, when there is a residual pressure at the start of the precharge, by correcting the precharge, it is possible to avoid the supply of an excessive hydraulic pressure. This has the effect of preventing the occurrence of a shift shock.
【0020】請求項2,4記載の発明によると、指示油
圧に対して遅れて変化する実際の係合油圧を推定して、
プリチャージを適正に補正できるという効果がある。請
求項5記載の発明によると、指示油圧の変化速度による
係合油圧の遅れの変化に対応して、プリチャージ開始時
の残圧を精度良く推定できるという効果がある。According to the second and fourth aspects of the present invention, the actual engagement oil pressure that changes with a delay from the command oil pressure is estimated,
There is an effect that the precharge can be properly corrected. According to the fifth aspect of the invention, there is an effect that the residual pressure at the start of the precharge can be accurately estimated in accordance with the change in the delay of the engagement oil pressure due to the change speed of the command oil pressure.
【0021】請求項3,6記載の発明によると、油圧配
管内の油圧に対して遅れて変化する実際の係合油圧を推
定して、プリチャージを適正に補正できるという効果が
ある。According to the third and sixth aspects of the present invention, there is an effect that the precharge can be properly corrected by estimating the actual engagement oil pressure which changes with a delay with respect to the oil pressure in the hydraulic pipe.
【0022】請求項7記載の発明によると、指示油圧の
変化に対して遅れて変化する油圧配管内の油圧を推定
し、更に、油圧配管内の油圧変化に対して遅れて変化す
る摩擦係合要素の係合油圧を推定することで、プリチャ
ージ開始時の残圧を精度良く推定できるという効果があ
る。According to the seventh aspect of the invention, the hydraulic pressure in the hydraulic pipe which changes with a delay with respect to the change in the command hydraulic pressure is estimated, and the frictional engagement which changes with a delay with the hydraulic pressure in the hydraulic pipe changes. Estimating the engagement hydraulic pressure of the element has the effect of accurately estimating the residual pressure at the start of precharge.
【0023】請求項8記載の発明によると、プリチャー
ジ開始時に残圧がある場合に、プリチャージ指示油圧の
低下及び/又はプリチャージ時間の短縮を行うことで、
プリチャージによる係合油圧の過剰上昇を回避できると
いう効果がある。According to the eighth aspect of the present invention, if there is a residual pressure at the start of precharge, the precharge command oil pressure is reduced and / or the precharge time is reduced.
There is an effect that an excessive increase in the engagement hydraulic pressure due to the precharge can be avoided.
【0024】[0024]
【発明の実施の形態】以下に本発明の実施の形態を説明
する。図1は、本発明に係る油圧制御装置が適用される
車両用の自動変速機を示す図であり、図示しない車両に
搭載されるエンジン1の出力トルクは、自動変速機2の
出力軸2aを介して駆動輪(図示省略)に伝達される。Embodiments of the present invention will be described below. FIG. 1 is a diagram showing an automatic transmission for a vehicle to which a hydraulic control device according to the present invention is applied. An output torque of an engine 1 mounted on a vehicle (not shown) is controlled by an output shaft 2a of the automatic transmission 2. The driving force is transmitted to the driving wheels (not shown) via the motor.
【0025】前記自動変速機2は、各種クラッチ,ブレ
ーキなどの摩擦係合要素に対する係合油圧の供給をソレ
ノイドバルブユニット3によって制御することで変速が
行われる構成のものである。本実施の形態では、1方向
クラッチを用いずに、2つの摩擦係合要素の締結と解放
とを油圧制御によって同時に行わせる変速を実行する構
成となっており、図2に示すように、解放させる摩擦係
合要素の係合油圧を徐々に減少させつつ、締結させる摩
擦係合要素の係合油圧を徐々に増大させ、解放側摩擦係
合要素から締結側摩擦係合要素へのトルクの掛け替えが
行われるようになっている。The automatic transmission 2 has a structure in which a shift is performed by controlling the supply of engagement hydraulic pressure to friction engagement elements such as various clutches and brakes by a solenoid valve unit 3. In the present embodiment, a shift is executed to simultaneously perform engagement and release of two friction engagement elements by hydraulic control without using a one-way clutch. As shown in FIG. While gradually decreasing the engagement oil pressure of the friction engagement element to be engaged, gradually increasing the engagement oil pressure of the friction engagement element to be engaged, and switching the torque from the release-side friction engagement element to the engagement-side friction engagement element Is performed.
【0026】具体的には、自動変速機2は図3に示すよ
うに、トルクコンバータT/Cを介してエンジンの出力
トルクを入力する構成であって、フロント遊星歯車組8
3,リヤ遊星歯車組84を備えると共に、摩擦係合要素
として、リバースクラッチR/C,ハイクラッチH/
C,バンドブレーキB/B,ロー&リバースブレーキL
&R/B,フォワードクラッチFWD/Cを備える。
尚、図3において、81は変速機の入力軸,82は変速
機の出力軸を示し、また、Neはエンジン回転速度,N
tはタービン回転速度,Noは出力軸回転速度を示す。More specifically, as shown in FIG. 3, the automatic transmission 2 is configured to receive the output torque of the engine via a torque converter T / C.
3, a rear planetary gear set 84 and a reverse clutch R / C, a high clutch H /
C, band brake B / B, low & reverse brake L
& R / B and a forward clutch FWD / C.
In FIG. 3, reference numeral 81 denotes an input shaft of the transmission, 82 denotes an output shaft of the transmission, Ne denotes an engine rotation speed, and N denotes
t indicates the turbine rotation speed, and No indicates the output shaft rotation speed.
【0027】上記構成において、図4に示すように、前
記リバースクラッチR/C,ハイクラッチH/C,バン
ドブレーキB/B,ロー&リバースブレーキL&R/
B,フォワードクラッチFWD/Cの締結,解放の組み
合わせに応じて変速が行われ、例えば、3速→4速のア
ップシフト時には、フォワードクラッチFWD/Cの解
放と、バンドブレーキB/Bの締結とが同時に行われる
ことになる。In the above configuration, as shown in FIG. 4, the reverse clutch R / C, high clutch H / C, band brake B / B, low & reverse brake L & R /
B, a shift is performed in accordance with a combination of engagement and disengagement of the forward clutch FWD / C. For example, at the time of an upshift from the third speed to the fourth speed, release of the forward clutch FWD / C and engagement of the band brake B / B are performed. Will be performed simultaneously.
【0028】前記ソレノイドバルブユニット3の各ソレ
ノイドバルブは、マイクロコンピュータを内蔵したコン
トロールユニット4によって制御されるが、クラッチ等
の摩擦係合要素の締結制御においては、係合油圧のプリ
チャージを行って、クラッチ板とピストンとの隙間を予
め埋めるよう構成されている。Each solenoid valve of the solenoid valve unit 3 is controlled by a control unit 4 having a built-in microcomputer. In engagement control of a friction engagement element such as a clutch, engagement hydraulic pressure is precharged. The gap between the clutch plate and the piston is filled in advance.
【0029】即ち、クラッチ等の摩擦係合要素の締結動
作を必要とする変速要求が発生すると、まず、プリチャ
ージを行って摩擦係合要素を接触直前まで無効ストロー
クさせた後、係合油圧を締結力が発生するぎりぎりの臨
界圧に保持し、その後、摩擦係合要素の締結が解放制御
にタイミングを合わせて行われる。That is, when a speed change request that requires the engagement operation of a friction engagement element such as a clutch is generated, first, a precharge is performed to invalidate the friction engagement element until immediately before contact, and then the engagement hydraulic pressure is reduced. The critical pressure is maintained just before the engagement force is generated, and then the engagement of the friction engagement element is performed in synchronization with the release control.
【0030】ここで、前記プリチャージ制御の詳細を図
5のフローチャートに従って説明する。図5のフローチ
ャートにおいて、まず、ステップS1では、直前の変速
で締結制御した摩擦係合要素の指示圧Pが0になってい
るか否かを判別する。尚、指示圧P=0は、本実施形態
において完全解放制御状態を示すものであるから、完全
解放制御状態において指示圧P=0でない場合には、完
全解放制御状態に相当する値になっているか否かを判別
させる構成とすれば良い。Here, the precharge control will be described in detail with reference to the flowchart of FIG. In the flowchart of FIG. 5, first, in step S1, it is determined whether or not the command pressure P of the friction engagement element that has been subjected to the engagement control in the immediately preceding shift has become zero. Since the command pressure P = 0 indicates the complete release control state in the present embodiment, if the command pressure P is not 0 in the complete release control state, it becomes a value corresponding to the complete release control state. It may be configured to determine whether or not there is.
【0031】指示圧Pが0(完全解放相当値)になって
いない場合には、ステップS12へ進み、指示圧Pが0
になってからの経過時間を計測するためのタイマーTM
R1をゼロにリセットする。If the command pressure P is not 0 (corresponding to complete release), the process proceeds to step S12, where the command pressure P is 0.
Timer TM for measuring the elapsed time since
Reset R1 to zero.
【0032】上記タイマーTMR1及び後述するタイマ
ーTMR2は、図6のフローチャートのステップS5
1,52で、単位時間毎に1アップされる。ステップS
11で指示圧P=0であると判別されると、ステップS
13へ進み、前記タイマーTMR1の値が予め記憶され
た所定値T1以上になっているか否か、換言すれば、指
示圧P=0になってから所定時間T1だけ経過したか否
かを判別する。The timer TMR1 and the timer TMR2 to be described later correspond to step S5 in the flowchart of FIG.
At 1,52, it is incremented by one every unit time. Step S
If it is determined in step 11 that the command pressure P = 0, the process proceeds to step S
Proceeding to 13, it is determined whether or not the value of the timer TMR1 is equal to or more than a predetermined value T1 stored in advance, in other words, whether or not a predetermined time T1 has elapsed since the indicated pressure P = 0. .
【0033】そして、前記タイマーTMR1の値が予め
記憶された所定値T1未満であれば、ステップS14へ
進み、前記タイマーTMR1の値が所定値T1になって
からの経過時間を計測するためのタイマーTMR2をゼ
ロにリセットする。If the value of the timer TMR1 is less than the predetermined value T1 stored in advance, the process proceeds to step S14, and a timer for measuring the elapsed time from when the value of the timer TMR1 reaches the predetermined value T1. Reset TMR2 to zero.
【0034】ステップS12で前記タイマーTMR1の
値が予め記憶された所定値T1以上になっていると判別
されると、ステップS15へ進み、前回の変速で解放制
御した摩擦係合要素について今回の変速で締結制御を開
始させるか否かを判別する。If it is determined in step S12 that the value of the timer TMR1 is equal to or greater than a predetermined value T1 stored in advance, the process proceeds to step S15, and the current shift of the frictional engagement element that has been released in the previous shift is performed. It is determined whether or not to start the engagement control.
【0035】締結制御を行う場合には、ステップS16
へ進み、プリチャージにおける指示圧の基本値を補正す
る補正係数Pαを、前記タイマーTMR2の値に基づい
て設定し、次のステップS17では、プリチャージ時間
の基本値を補正する補正係数Tαを、前記タイマーTM
R2の値に基づいて設定する。When performing the fastening control, step S16
Then, a correction coefficient Pα for correcting the basic value of the command pressure in the precharge is set based on the value of the timer TMR2. In the next step S17, a correction coefficient Tα for correcting the basic value of the precharge time is set as The timer TM
Set based on the value of R2.
【0036】前記補正係数Pα,Tαは、タイマーTM
R2による計測時間が長いほど、プリチャージにおける
指示圧をより高く、プリチャージ時間をより長くするよ
うに設定される(図7,8参照)。The correction coefficients Pα and Tα are determined by a timer TM
The instruction pressure in the precharge is set to be higher and the precharge time is set to be longer as the measurement time by R2 is longer (see FIGS. 7 and 8).
【0037】そして、ステップS18では、前記補正係
数Pα,Tαでプリチャージにおける指示圧及びプリチ
ャージ時間を決定し、締結させる摩擦係合要素の指示圧
を出力する。In step S18, the command pressure and the precharge time in precharging are determined based on the correction coefficients Pα and Tα, and the command pressure of the friction engagement element to be engaged is output.
【0038】前記所定値T1は、指示圧Pが0になって
から、摩擦係合要素に油圧を供給する油圧配管内の油圧
が遅れて0になるまでの遅れ時間として予め設定されて
おり、更に、摩擦係合要素の係合油圧は、前記油圧配管
内の油圧に対して遅れて0にまで変化するので、前記タ
イマーTMR2によって計測される油圧配管内の油圧が
0になってからの時間から、摩擦係合要素の係合油圧
(残圧)を推定できる。The predetermined value T1 is set in advance as a delay time from when the command pressure P becomes 0 to when the oil pressure in the hydraulic pipe for supplying the oil pressure to the friction engagement element becomes 0 with a delay. Further, since the engagement oil pressure of the friction engagement element changes to 0 with a delay with respect to the oil pressure in the hydraulic pipe, the time from when the oil pressure in the hydraulic pipe measured by the timer TMR2 becomes 0 becomes zero. From this, the engagement hydraulic pressure (residual pressure) of the friction engagement element can be estimated.
【0039】一方、摩擦係合要素の残圧が高い場合に
は、残圧がないときと同様にしてプリチャージを行う
と、過剰な油圧上昇を招くことになる。そこで、前記タ
イマーTMR2の値が小さく、摩擦係合要素の係合油圧
が0にまで低下していないと推定されるときには、プリ
チャージにおける指示圧を低く、プリチャージ時間を短
くするものであり、前記タイマーTMR2の値が大きく
なるに従って摩擦係合要素の係合油圧が0に近づく(残
圧が低くなる)ので、これに応じてプリチャージにおけ
る指示圧をより高く、プリチャージ時間をより長くす
る。On the other hand, when the residual pressure of the friction engagement element is high, if the precharge is performed in the same manner as when there is no residual pressure, an excessive increase in the hydraulic pressure will be caused. Therefore, when the value of the timer TMR2 is small and it is estimated that the engagement oil pressure of the friction engagement element has not decreased to 0, the command pressure in the precharge is reduced and the precharge time is shortened. As the value of the timer TMR2 increases, the engagement oil pressure of the friction engagement element approaches 0 (residual pressure decreases), and accordingly, the command pressure in precharge is increased, and the precharge time is lengthened. .
【0040】尚、プリチャージにおける指示圧とプリチ
ャージ時間とのいずれか一方のみを、タイマーTMR2
の値に応じて補正する構成としても良い。また、指示圧
Pに対して遅れ補正を施して油圧配管内の油圧推定値を
求め、更に、油圧配管内の油圧推定値に遅れ補正を施し
て、摩擦係合要素の係合油圧を推定し、該推定した摩擦
係合要素の係合油圧(残圧)から、プリチャージにおけ
る指示圧及び/又はプリチャージ時間を補正する構成と
しても良い。It should be noted that only one of the command pressure and the precharge time in the precharge is determined by the timer TMR2.
The correction may be made according to the value of. Further, a delay correction is performed on the command pressure P to obtain an estimated oil pressure value in the hydraulic pipe, and further, a delay correction is performed on the estimated oil pressure value in the hydraulic pipe to estimate the engagement oil pressure of the friction engagement element. The command pressure and / or the precharge time in the precharge may be corrected from the estimated engagement hydraulic pressure (residual pressure) of the friction engagement element.
【0041】図9は、プリチャージ制御の第2の実施形
態を示すものであり、ステップS21では、指示圧Pが
0(完全解放相当値)になっているか否かを判別し、指
示圧Pが0になっていない場合には、ステップS22へ
進み、単位時間毎に1アップされるタイマーTMR1を
0にリセットする。FIG. 9 shows a second embodiment of the precharge control. In step S21, it is determined whether or not the command pressure P is 0 (a value corresponding to complete release). If is not 0, the process proceeds to step S22, and the timer TMR1 that is incremented by 1 every unit time is reset to 0.
【0042】更に、ステップS23では、指示圧Pが0
まで減少する過程における指示圧Pの降下速度ΔPを算
出する。一方、ステップS21で指示圧Pが0になって
いると判別されると、ステップS24へ進み、前回の変
速で解放制御した摩擦係合要素について今回の変速で締
結制御を開始させるか否かを判別する。Further, in step S23, the command pressure P becomes 0
Then, the descending speed ΔP of the command pressure P in the process of decreasing the pressure is calculated. On the other hand, if it is determined in step S21 that the command pressure P is 0, the process proceeds to step S24, in which it is determined whether or not to start the engagement control in the current shift with respect to the friction engagement element that has been released in the previous shift. Determine.
【0043】締結制御を行う場合には、ステップS25
へ進み、プリチャージにおける指示圧の基本値を補正す
る補正係数Pαを、前記タイマーTMR2の値及び指示
圧Pの降下速度ΔPに基づいて設定し、次のステップS
26では、プリチャージ時間の基本値を補正する補正係
数Tαを、前記タイマーTMR2の値及び指示圧Pの降
下速度ΔPに基づいて設定し、ステップS27では、前
記補正係数Pα,Tαでプリチャージにおける指示圧及
びプリチャージ時間を決定し、締結させる摩擦係合要素
の指示圧を出力する。When performing the fastening control, step S25 is performed.
Then, a correction coefficient Pα for correcting the basic value of the command pressure in the precharge is set based on the value of the timer TMR2 and the descending speed ΔP of the command pressure P, and the next step S
In step 26, a correction coefficient Tα for correcting the basic value of the precharge time is set based on the value of the timer TMR2 and the descending speed ΔP of the command pressure P, and in step S27, the correction coefficient Pα, Tα The command pressure and the precharge time are determined, and the command pressure of the friction engagement element to be engaged is output.
【0044】前記補正係数Pα,Tαは、図10,11
に示すように、タイマーTMR2による計測時間が長い
ほど、プリチャージにおける指示圧をより高く、プリチ
ャージ時間をより長くするように設定される一方、指示
圧Pの降下速度ΔPが速いほど、同じタイマーTMR2
に対して、プリチャージにおける指示圧をより低く、プ
リチャージ時間をより短くするように設定される。The correction coefficients Pα and Tα are shown in FIGS.
As shown in the figure, the longer the time measured by the timer TMR2, the higher the instruction pressure in precharge and the longer the precharge time, the longer the precharge time .DELTA. TMR2
In contrast, the setting is made such that the command pressure in the precharge is lower and the precharge time is shorter.
【0045】上記の第1実施形態では、指示圧Pから油
圧配管内の油圧を推定し、更に、油圧配管内の油圧から
摩擦係合要素の係合油圧を推定する構成としたが、上記
第2の実施形態では、指示圧Pから直接に摩擦係合要素
の係合油圧を推定する構成とし、更に、指示圧Pに対す
る摩擦係合要素の係合油圧の遅れ時間が、指示圧Pの変
化速度に影響されることから、タイマーTMR2と共
に、指示圧Pの降下速度ΔPに応じて補正係数Pα,T
αを設定する構成としてある。In the first embodiment, the oil pressure in the hydraulic pipe is estimated from the command pressure P, and the engagement oil pressure of the friction engagement element is estimated from the oil pressure in the hydraulic pipe. In the second embodiment, the engagement oil pressure of the friction engagement element is directly estimated from the instruction pressure P. Further, the delay time of the engagement oil pressure of the friction engagement element with respect to the instruction pressure P is determined by the change in the instruction pressure P. Since the speed is affected, the correction coefficients Pα, T
α is set.
【0046】指示圧Pが0にまで低下する速度が速かっ
た場合には、実際の摩擦係合要素の係合油圧の降下遅れ
が大きくなり、速度が遅かった場合に比べて同じ経過時
間に対する残圧が高くなるので、指示圧Pが0にまで低
下する速度が速かったときほど、プリチャージにおける
指示圧をより低く、プリチャージ時間をより短くするよ
うにしてある。When the speed at which the command pressure P decreases to 0 is high, the delay in the decrease of the actual engagement hydraulic pressure of the frictional engagement element is large, and the remaining time for the same elapsed time is shorter than when the speed is low. Since the pressure increases, the higher the speed at which the command pressure P decreases to zero, the lower the command pressure in precharge and the shorter the precharge time.
【0047】次に、プリチャージ制御の第3の実施形態
を示す。第3の実施形態では、各摩擦係合要素に油圧を
供給する油圧配管のそれぞれに、油圧を検出する油圧セ
ンサ5を設け(図1参照)、図12のフローチャートに
示すようにしてプリチャージ制御を行う。Next, a third embodiment of the precharge control will be described. In the third embodiment, a hydraulic pressure sensor 5 for detecting the hydraulic pressure is provided in each of the hydraulic pipes for supplying the hydraulic pressure to each friction engagement element (see FIG. 1), and the precharge control is performed as shown in the flowchart of FIG. I do.
【0048】ステップS31では、直前の変速で締結制
御した摩擦係合要素の油圧配管に設けられた油圧センサ
5の検出値Psが0(完全解放油圧)になっているか否
かを判別し、検出値Psが0(完全解放相当値)になっ
ていない場合には、ステップS32へ進み、単位時間毎
に1アップされるタイマーTMR1を0にリセットす
る。In step S31, it is determined whether or not the detection value Ps of the hydraulic pressure sensor 5 provided in the hydraulic pipe of the frictional engagement element that has been engaged in the immediately preceding shift has become 0 (completely released hydraulic pressure). If the value Ps has not become 0 (a value corresponding to complete release), the process proceeds to step S32, and the timer TMR1 that is incremented by 1 every unit time is reset to 0.
【0049】一方、ステップS31で検出値Psが0に
なっていると判別されると、ステップS33へ進み、前
回の変速で解放制御した摩擦係合要素について今回の変
速で締結制御を開始させるか否かを判別する。On the other hand, if it is determined in step S31 that the detected value Ps is 0, the flow advances to step S33 to determine whether to start the engagement control in the current shift with respect to the friction engagement element that was released in the previous shift. It is determined whether or not.
【0050】締結制御を行う場合には、ステップS34
へ進み、プリチャージにおける指示圧の基本値を補正す
る補正係数Pαを前記タイマーTMR2の値に基づいて
設定し、次のステップS35では、プリチャージ時間の
基本値を補正する補正係数Tαを前記タイマーTMR2
の値に基づいて設定し、ステップS36では、前記補正
係数Pα,Tαでプリチャージにおける指示圧及びプリ
チャージ時間を決定し、締結させる摩擦係合要素の指示
圧を出力する。When performing the fastening control, step S34
Then, a correction coefficient Pα for correcting the basic value of the command pressure in the precharge is set based on the value of the timer TMR2, and in the next step S35, a correction coefficient Tα for correcting the basic value of the precharge time is set in the timer. TMR2
In step S36, the command pressure and the precharge time in the precharge are determined by the correction coefficients Pα and Tα, and the command pressure of the friction engagement element to be engaged is output.
【0051】前記補正係数Pα,Tαは、図7,8に示
すように、タイマーTMR2による計測時間が長いほ
ど、プリチャージにおける指示圧をより高く、プリチャ
ージ時間をより長くするように設定される。As shown in FIGS. 7 and 8, the correction coefficients Pα and Tα are set so that the longer the time measured by the timer TMR2, the higher the pre-charge command pressure and the longer the precharge time. .
【0052】尚、前記油圧センサ5の検出値に対して遅
れ補正を施して摩擦係合要素の係合油圧の推定値を演算
し、該推定される係合油圧からプリチャージにおける指
示圧、及び/又はプリチャージ時間を補正するようにし
ても良い。The detected value of the hydraulic pressure sensor 5 is subjected to delay correction to calculate an estimated value of the engagement oil pressure of the friction engagement element. And / or the precharge time may be corrected.
【図1】本発明が適用される自動変速機を示すシステム
図。FIG. 1 is a system diagram showing an automatic transmission to which the present invention is applied.
【図2】変速時の油圧制御の様子を示すタイムチャー
ト。FIG. 2 is a time chart showing a state of hydraulic control during shifting.
【図3】自動変速機の詳細を示す構成図。FIG. 3 is a configuration diagram showing details of an automatic transmission.
【図4】上記自動変速機における摩擦係合要素の締結状
態の組み合わせによる変速の様子を示す図。FIG. 4 is a view showing a state of shifting by a combination of engagement states of friction engagement elements in the automatic transmission.
【図5】プリチャージ制御の第1実施形態を示すフロー
チャート。FIG. 5 is a flowchart illustrating a first embodiment of precharge control.
【図6】プリチャージ制御におけるタイマー値のカウン
トアップ制御を示すフローチャート。FIG. 6 is a flowchart showing count-up control of a timer value in precharge control.
【図7】前記第1実施形態におけるプリチャージ指示圧
の特性を示す線図。FIG. 7 is a diagram showing characteristics of a precharge command pressure in the first embodiment.
【図8】前記第1実施形態におけるプリチャージ時間の
特性を示す線図。FIG. 8 is a diagram showing characteristics of a precharge time in the first embodiment.
【図9】プリチャージ制御の第2実施形態を示すフロー
チャート。FIG. 9 is a flowchart showing a second embodiment of the precharge control.
【図10】前記第2実施形態におけるプリチャージ指示
圧の特性を示す線図。FIG. 10 is a diagram showing characteristics of a precharge command pressure in the second embodiment.
【図11】前記第2実施形態におけるプリチャージ時間
の特性を示す線図。FIG. 11 is a diagram showing characteristics of a precharge time in the second embodiment.
【図12】プリチャージ制御の第3実施形態を示すフロ
ーチャート。FIG. 12 is a flowchart showing a third embodiment of the precharge control.
1…エンジン 2…自動変速機 3…ソレノイドバルブユニット 4…コントロールユニット 5…油圧センサ 83…フロント遊星歯車組 84…リヤ遊星歯車組 R/C…リバースクラッチ H/C…ハイクラッチ B/B…バンドブレーキ L&R/B…ロー&リバースブレーキ FWD/C…フォワードクラッチ DESCRIPTION OF SYMBOLS 1 ... Engine 2 ... Automatic transmission 3 ... Solenoid valve unit 4 ... Control unit 5 ... Hydraulic sensor 83 ... Front planetary gear set 84 ... Rear planetary gear set R / C ... Reverse clutch H / C ... High clutch B / B ... Band Brake L & R / B ... Low & reverse brake FWD / C ... Forward clutch
Claims (8)
リチャージを行う自動変速機の油圧制御装置であって、 前記プリチャージ開始直前の摩擦係合要素の係合油圧に
基づいてプリチャージを補正制御することを特徴とする
自動変速機の油圧制御装置。1. A hydraulic control device for an automatic transmission for precharging hydraulic pressure when engaging a friction engagement element, wherein the precharge is performed based on an engagement hydraulic pressure of the friction engagement element immediately before the start of the precharge. A hydraulic control device for an automatic transmission, wherein the hydraulic control device performs correction control on the hydraulic pressure.
て遅れ補正を施して、前記プリチャージ開始直前の摩擦
係合要素の係合油圧を推定することを特徴とする請求項
1記載の自動変速機の油圧制御装置。2. The automatic hydraulic system according to claim 1, wherein a delay correction is performed on the command oil pressure for the friction engagement element to estimate an engagement oil pressure of the friction engagement element immediately before the start of the precharge. Transmission hydraulic control unit.
する油圧配管内の油圧を検出する油圧センサの検出値に
対して遅れ補正を施して、前記プリチャージ開始直前の
摩擦係合要素の係合油圧を推定することを特徴とする請
求項1記載の自動変速機の油圧制御装置。3. A delay correction is performed on a value detected by a hydraulic pressure sensor for detecting a hydraulic pressure in a hydraulic pipe for supplying a hydraulic pressure to the frictional engagement element to be fastened, so that the frictional engagement element immediately before the start of the precharge starts. The hydraulic control device for an automatic transmission according to claim 1, wherein the engagement hydraulic pressure is estimated.
になってからの経過時間に基づき、前記プリチャージ開
始直前の摩擦係合要素の係合油圧を推定することを特徴
とする請求項1記載の自動変速機の油圧制御装置。4. An engagement hydraulic pressure of the friction engagement element immediately before the start of the precharge is estimated based on an elapsed time from when a command oil pressure for the friction engagement element becomes zero. A hydraulic control device for an automatic transmission according to claim 1.
及びゼロになってからの経過時間に応じて、前記プリチ
ャージ開始直前の摩擦係合要素の係合油圧を推定するこ
とを特徴とする請求項4記載の自動変速機の油圧制御装
置。5. An engagement oil pressure of a friction engagement element immediately before the start of the precharge is estimated according to a change speed until the command oil pressure becomes zero and an elapsed time after the instruction oil pressure becomes zero. The hydraulic control device for an automatic transmission according to claim 4, wherein
する油圧配管内の油圧を検出する油圧センサの検出値が
ゼロになってからの経過時間に応じて、前記プリチャー
ジ開始直前の摩擦係合要素の係合油圧を推定することを
特徴とする請求項1記載の自動変速機の油圧制御装置。6. A friction immediately before the start of the precharge according to an elapsed time from a time when a detection value of a hydraulic pressure sensor for detecting a hydraulic pressure in a hydraulic pipe for supplying a hydraulic pressure to the friction engagement element to be fastened becomes zero. The hydraulic pressure control device for an automatic transmission according to claim 1, wherein the hydraulic pressure of the engagement element is estimated.
になってからの経過時間に応じて、前記締結させる摩擦
係合要素に油圧を供給する油圧配管内の油圧がゼロにな
るタイミングを推定し、該推定したタイミングからの経
過時間に応じて、前記プリチャージ開始直前の摩擦係合
要素の係合油圧を推定することを特徴とする請求項1記
載の自動変速機の油圧制御装置。7. A timing for estimating a timing at which a hydraulic pressure in a hydraulic pipe for supplying a hydraulic pressure to the friction engagement element to be engaged becomes zero in accordance with an elapsed time from when an instruction hydraulic pressure for the friction engagement element becomes zero. 2. The hydraulic pressure control device for an automatic transmission according to claim 1, wherein an engagement hydraulic pressure of the friction engagement element immediately before the start of the precharge is estimated according to an elapsed time from the estimated timing.
の係合油圧が高いときほど、プリチャージにおける指示
油圧をより低く、及び/又は、プリチャージ時間をより
短く補正することを特徴とする請求項1〜7のいずれか
1つに記載の自動変速機の油圧制御装置。8. The system according to claim 1, wherein the higher the engagement oil pressure of the friction engagement element immediately before the start of the precharge, the lower the command oil pressure in the precharge and / or the shorter the precharge time. A hydraulic control device for an automatic transmission according to any one of claims 1 to 7.
Priority Applications (1)
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JP2000051916A JP4011255B2 (en) | 2000-02-28 | 2000-02-28 | Hydraulic control device for automatic transmission |
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JP2000051916A JP4011255B2 (en) | 2000-02-28 | 2000-02-28 | Hydraulic control device for automatic transmission |
Publications (2)
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JP2001241541A true JP2001241541A (en) | 2001-09-07 |
JP4011255B2 JP4011255B2 (en) | 2007-11-21 |
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JP2000051916A Expired - Fee Related JP4011255B2 (en) | 2000-02-28 | 2000-02-28 | Hydraulic control device for automatic transmission |
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