JPH08277929A - Transmission control device for beltless continuous variable transmission - Google Patents
Transmission control device for beltless continuous variable transmissionInfo
- Publication number
- JPH08277929A JPH08277929A JP7754395A JP7754395A JPH08277929A JP H08277929 A JPH08277929 A JP H08277929A JP 7754395 A JP7754395 A JP 7754395A JP 7754395 A JP7754395 A JP 7754395A JP H08277929 A JPH08277929 A JP H08277929A
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic
- pressure
- side pulley
- shift control
- input side
- 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]
【産業上の利用分野】本発明は、ベルト式無段変速機に
用いる変速制御装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a shift control device used in a belt type continuously variable transmission.
【０００２】[0002]
【従来の技術】従来、種々のベルト式無段変速機の変速
制御装置が提案されており、例えば、特開昭56-134658
号公報では、変速制御用の２個のソレノイド弁により調
圧された油圧を変速制御弁に入力し、これらソレノイド
弁により調圧された油圧の大きさに関連して入力側プー
リの油圧サーボへの圧油供給油路を油圧源と連通する第
１の位置と、入力側プーリの油圧サーボへの圧油供給油
路を排出路と連通する第２の位置と、入力側プーリの油
圧サーボへの圧油供給油路を閉じる第３の位置を設定
し、第３の位置では、入力側プーリの油圧サーボへの油
圧供給油路と、油圧源とをオリフィスを介して連通する
構造となっている。2. Description of the Related Art Conventionally, various belt type continuously variable transmission gear shift control devices have been proposed, for example, Japanese Patent Laid-Open No. 56-134658.
In the publication, the hydraulic pressure regulated by two solenoid valves for shift control is input to the shift control valve, and the hydraulic servo of the input side pulley is related to the magnitude of the hydraulic pressure regulated by these solenoid valves. To the hydraulic servo of the input side pulley, to the hydraulic servo of the input side pulley, to the hydraulic servo of the input side, and to the hydraulic servo of the input side pulley to the hydraulic servo of the input side. The third position for closing the pressure oil supply oil passage is set, and at the third position, the oil pressure supply oil passage to the hydraulic servo of the input side pulley and the hydraulic pressure source are connected via an orifice. There is.
【０００３】[0003]
【発明が解決しようとする課題】このような変速制御装
置では、ソレノイド弁、コントローラ等の故障が原因の
電制のフェールによる急変速を回避するために、電制の
フェール時に変速制御弁が上記第３の位置になるように
設定する。このように設定することにより、入力側プー
リの油圧サーボの油圧供給油路の漏れと、オリフィスか
らの油供給量がバランスする変速比に徐々に変化する。
しかしながら、この変速比がどのような値となるかわか
らないため、電制のフェール状態では車両を発進、登板
及び中高速走行させることができない。In such a speed change control device, in order to avoid a sudden speed change due to a failure of electric control due to a failure of a solenoid valve, a controller or the like, the speed change control valve is operated when the electric control fails. Set it so that it is in the third position. By setting in this way, the transmission ratio gradually changes so that the leakage of the hydraulic oil supply passage of the hydraulic servo of the input side pulley and the oil supply amount from the orifice are balanced.
However, since it is not known what the gear ratio will be, the vehicle cannot be started, climbed, or run at a medium or high speed in the electric failure state.
【０００４】本発明の目的は、電制のフェール状態でも
車両を発進、登板及び中高速走行させることができるベ
ルト式無段変速機の変速制御装置を提供することであ
る。It is an object of the present invention to provide a shift control device for a belt type continuously variable transmission which can start, climb a plate and run at medium and high speeds even in an electrically controlled fail state.
【０００５】[0005]
【課題を解決するための手段】本発明による請求項１の
ベルト式無段変速機の変速制御装置は、車両の走行状態
に応じてライン圧を発生させる油圧供給源と、油の給排
を行うとともに二つの油室が形成された変速制御弁と、
これら二つの油室の油圧を調圧する二つの変速制御ソレ
ノイド弁と、前記変速制御弁により油の給排が行われる
油圧サーボを有する入力側プーリと、前記ライン圧が導
かれ、前記入力プーリの油圧サーボのピストン面積より
も小さいピストン面積の油圧サーボを有する出力側プー
リと、これら入力側プーリ及び出力側プーリとの間に巻
かれたベルトとを具え、前記入力側プーリの油圧サーボ
への油の給排により前記ベルトの走行半径が変化して変
速比が変化するベルト式無段変速機の変速制御装置にお
いて、前記変速制御弁は、前記二つの油室をそれぞれ形
成するスプールを具え、前記スプールを介して前記入力
側プーリの油圧サーボと前記油圧供給源とを連通させる
第１の状態と、前記スプールを介して前記入力側プーリ
の油圧サーボの油を排出する第２の状態と、前記入力側
プーリの油圧サーボの油圧を、前記ライン圧の変化に対
して所定の割合で変化する圧力に、前記スプールを用い
て調圧する第３の状態とに設定され、電制のフェールが
発生した場合には前記第３の状態にして車両の走行状態
に応じた変速比の決定をすることを特徴とするものであ
る。According to another aspect of the present invention, there is provided a shift control device for a belt type continuously variable transmission, comprising: a hydraulic pressure supply source for generating a line pressure according to a running state of a vehicle; And a shift control valve in which two oil chambers are formed,
Two speed change control solenoid valves for adjusting the oil pressures of these two oil chambers, an input side pulley having a hydraulic servo that supplies and discharges oil by the speed change control valve, and the line pressure is guided to the input pulley. The hydraulic servo of the input side pulley is provided with an output side pulley having a hydraulic servo having a piston area smaller than the piston area of the hydraulic servo, and a belt wound between the input side pulley and the output side pulley. In a speed change control device for a belt type continuously variable transmission in which the traveling radius of the belt changes and the speed change ratio changes depending on the supply and discharge of, the speed change control valve includes spools that respectively form the two oil chambers, A first state in which the hydraulic servo of the input side pulley communicates with the hydraulic pressure supply source via a spool, and the oil of the hydraulic servo of the input side pulley via the spool Set to the second state of discharging and the third state of adjusting the hydraulic pressure of the hydraulic servo of the input side pulley to a pressure that changes at a predetermined rate with respect to the change of the line pressure using the spool. When a failure of electric control occurs, the gear ratio is determined in the third state according to the running state of the vehicle.
【０００６】本発明による請求項２のベルト式無段変速
機の変速制御装置は、前記二つの油室の油圧の受圧面積
を等しくすることを特徴とするものである。A shift control device for a belt type continuously variable transmission according to a second aspect of the present invention is characterized in that the hydraulic pressure receiving areas of the two oil chambers are equalized.
【０００７】本発明による請求項３のベルト式無段変速
機の変速制御装置は、前記変速制御弁は前記スプールを
弾性支持する二つのばねを具えかつそれらを対抗させて
配設されていることを特徴とするものである。In the shift control device for a belt type continuously variable transmission according to a third aspect of the present invention, the shift control valve is provided with two springs elastically supporting the spool and arranged so as to oppose each other. It is characterized by.
【０００８】本発明による請求項４のベルト式無段変速
機の変速制御装置は、前記変速制御弁は、前記油圧供給
源により発生したライン圧が作用するライン圧受圧部
と、前記入力側プーリの油圧サーボへの油圧が作用する
サーボ油圧受圧部と、前記入力側プーリの油圧サーボの
油が排出される排出部とを有し、前記ライン圧受圧部に
作用する圧力により、前記油圧供給源により発生したラ
イン圧が前記入力側プーリの油圧サーボに連通するよう
にし、かつ、前記サーボ油圧受圧部に作用する圧力が、
前記排出部が前記入力側プーリの油圧サーボに連通する
ように設定したことを特徴とするものである。According to a fourth aspect of the present invention, there is provided a shift control device for a belt type continuously variable transmission, wherein the shift control valve includes a line pressure receiving portion on which a line pressure generated by the hydraulic pressure source acts, and the input pulley. Of the hydraulic servo of the input side pulley and a discharge portion for discharging the oil of the hydraulic servo of the input side pulley, and the hydraulic pressure supply source is provided by the pressure acting on the line pressure receiving portion. The line pressure generated by is communicated with the hydraulic servo of the input side pulley, and the pressure acting on the servo hydraulic pressure receiving portion is
The discharge part is set to communicate with the hydraulic servo of the input side pulley.
【０００９】[0009]
【作用】本発明による請求項１のベルト式無段変速機の
変速制御装置では、変速制御ソレノイド弁、コントロー
ラ等の故障が原因の電制のフェールが発生すると、入力
側プーリの油圧サーボの油圧を、ライン圧の変化に対し
て所定の割合で変化する圧力に調圧する第３の状態に設
定し、車両の走行状態に応じて変速比を決定する。した
がって、電制のフェール状態でも変速比を決定すること
ができ、その結果車両を発進、登板及び中高速走行させ
ることができる。In the speed change control device for the belt type continuously variable transmission according to the present invention, when an electrically controlled failure occurs due to a failure of the speed change control solenoid valve, controller, etc., the hydraulic pressure of the hydraulic servo of the input side pulley is increased. Is set to a third state in which the pressure is adjusted to a pressure that changes at a predetermined rate with respect to the change in line pressure, and the gear ratio is determined according to the running state of the vehicle. Therefore, it is possible to determine the gear ratio even in the electric-controlled fail state, and as a result, the vehicle can be started, climbed, and run at medium and high speeds.
【００１０】本発明による請求項２のベルト式無段変速
機の変速制御装置では、二つの油室の油圧の受圧面積を
等しくしているので、電制のフェール発生時に電源をオ
フにすると二つの油室の油圧が等しくなる。したがっ
て、変速制御弁が第３の状態となり、入力側プーリの油
圧サーボの油圧を、ライン圧の変化に対して所定の割合
で変化する圧力に調圧でき、本発明による制御を良好に
行うことができる。In the speed change control device for a belt type continuously variable transmission according to a second aspect of the present invention, since the hydraulic pressure receiving areas of the two oil chambers are made equal to each other, when the power supply is turned off when an electrically controlled failure occurs, The oil pressures in the two oil chambers are equal. Therefore, the shift control valve is brought into the third state, and the hydraulic pressure of the hydraulic servo of the input side pulley can be adjusted to a pressure that changes at a predetermined rate with respect to the change of the line pressure, so that the control according to the present invention can be satisfactorily performed. You can
【００１１】本発明による請求項３のベルト式無段変速
機の変速制御装置では、スプールをそれぞればねにより
弾性支持し、かつ、それらを対抗させて配設させること
により、スプールの移動による油路の連通量変化を小さ
くすることができるので、急な変速が起こるおそれがな
くなる。In the shift control device for a belt type continuously variable transmission according to a third aspect of the present invention, the spools are elastically supported by springs and are arranged so as to oppose each other. Since it is possible to reduce the change in the communication amount of, there is no possibility of sudden shift.
【００１２】本発明による請求項４のベルト式無段変速
機の変速制御装置では、ライン圧受圧部に作用する圧力
により、油圧供給源により発生したライン圧が入力側プ
ーリの油圧サーボに連通するようにし、かつ、サーボ油
圧受圧部に作用する圧力が、排出部が入力側プーリの油
圧サーボに連通することにより、入力プーリの油圧サー
ボへの油圧を、ライン圧の変化に対して所定の割合で変
化する圧力に調圧することができ、したがって電制のフ
ェール状態でも変速比を決定することができ、その結果
車両を発進、登板及び中高速走行させることができる。In the shift control device for a belt type continuously variable transmission according to a fourth aspect of the present invention, the line pressure generated by the hydraulic pressure supply source communicates with the hydraulic servo of the input side pulley due to the pressure acting on the line pressure receiving portion. In addition, the pressure acting on the servo hydraulic pressure receiving section causes the discharge section to communicate with the hydraulic servo of the input side pulley, so that the hydraulic pressure to the hydraulic servo of the input pulley is kept at a predetermined ratio with respect to the change of the line pressure. It is possible to adjust the pressure to change with, and therefore it is possible to determine the gear ratio even in the failure state of electric control, and as a result, the vehicle can be started, climbed, and run at medium and high speeds.
【００１３】[0013]
【実施例】本発明によるベルト式無段変速機の変速制御
装置の実施例を図面を参照して詳細に説明する。図１
は、本発明によるベルト式無段変速機の変速制御装置の
一実施例を示す図である。このベルト式無段変速機の変
速制御装置は、油圧源としてのオイルポンプ１と、この
オイルポンプ１から発生した油圧を車両の走行状態に応
じたライン圧ＰL に調圧するリリーフ弁２と、一定圧を
発生させる減圧弁３と、オイルポンプ１から供給される
油を給排する変速制御弁４と、この変速制御弁４の油室
４ａ及び４ｂの油圧を調圧する２個の変速制御ソレノイ
ド弁５ａ及び５ｂと、変速制御弁４により油の給排が行
われる入力側プーリ６と、ライン圧ＰL が導かれる出力
側プーリ７と、これら入力側プーリ６及び出力側プーリ
７との間に巻かれたベルト８とを具える。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a shift control device for a belt type continuously variable transmission according to the present invention will be described in detail with reference to the drawings. FIG.
FIG. 1 is a diagram showing an embodiment of a shift control device for a belt type continuously variable transmission according to the present invention. The shift control device for a belt type continuously variable transmission includes an oil pump 1 as a hydraulic pressure source, a relief valve 2 that regulates the hydraulic pressure generated from the oil pump 1 to a line pressure P L according to a running state of a vehicle, A pressure reducing valve 3 for generating a constant pressure, a speed change control valve 4 for supplying and discharging oil supplied from the oil pump 1, and two speed change control solenoids for adjusting the oil pressures in the oil chambers 4a and 4b of the speed change control valve 4. Between the valves 5a and 5b, the input side pulley 6 through which oil is supplied and discharged by the shift control valve 4, the output side pulley 7 through which the line pressure P L is introduced, and the input side pulley 6 and the output side pulley 7 And a belt 8 wound around.
【００１４】オイルポンプ１から吐出された油はリリー
フ弁２により変速比、入力トルク等に応じたライン圧Ｐ
L に調圧される。このようにして調圧されたライン圧Ｐ
L は、減圧弁３と、変速制御弁４のライン圧ポート４ｃ
及び４ｄと、出力側プーリ７の油圧サーボシリンダ室７
ａに導かれる。The oil discharged from the oil pump 1 is relieved by a relief valve 2 to a line pressure P according to a gear ratio, an input torque and the like.
The pressure is adjusted to L. The line pressure P regulated in this way
L is the pressure reducing valve 3 and the line pressure port 4c of the speed change control valve 4.
And 4d and the hydraulic servo cylinder chamber 7 of the output side pulley 7.
led to a.
【００１５】減圧弁３に導かれたライン圧ＰL は出力圧
ＰO に調圧される。このように調圧された出力圧Ｐ
O は、各オリフィス９ａ及び９ｂを介して油室４ａ及び
４ｂに連通するポート４ｅ及び４ｆにそれぞれ導かれ
る。The line pressure P L introduced to the pressure reducing valve 3 is adjusted to the output pressure P O. The output pressure P regulated in this way
O is guided to the ports 4e and 4f communicating with the oil chambers 4a and 4b through the orifices 9a and 9b, respectively.
【００１６】変速制御弁４は、２個のスプール４ｇ及び
４ｈと、これらスプール４ｇ及び４ｈをそれぞれ弾性支
持するばね４ｉ及び４ｊとを具える。スプール４ｇ及び
４ｈの位置は、ばね４ｉ及び４ｊの弾性力と、変速制御
ソレノイド弁５ａ及び５ｂによって調圧された油室４ａ
及び４ｂの油圧と、ライン圧ポート４ｄのライン圧Ｐ L
がスプール４ｈの段付部面積に作用する力と、油圧サー
ボシリンダ室６ａの油圧供給油路ポート４ｋの油圧がス
プール４ｇの段付部面積に作用する力との釣り合いによ
って決定される。The shift control valve 4 includes two spools 4g and
4h and the spools 4g and 4h are elastically supported respectively.
It has springs 4i and 4j to carry. 4g spool and
The position of 4h depends on the elastic force of the springs 4i and 4j and the shift control.
Oil chamber 4a regulated by solenoid valves 5a and 5b
And the hydraulic pressure of 4b and the line pressure P of the line pressure port 4d. L
Force on the stepped area of the spool 4h and the hydraulic
The hydraulic pressure in the hydraulic pressure supply oil passage port 4k in the cylinder cylinder 6a
By balancing the force acting on the stepped area of the pool 4g
Is decided.
【００１７】スプール４ｈ及び４ｇの段付部面積に作用
する力を、変速制御ソレノイド弁５ａ及び５ｂによって
調圧された油室４ａ及び４ｂの油圧に比べて小さくす
る。このような設定により、変速制御弁４を、変速制御
ソレノイド弁５ａ及び５ｂによって、油圧供給油路ポー
ト４ｋとライン圧ポート４ｃとを連通させる状態（以
下、「第１の状態」という）と、油圧供給油路ポート４
ｋと排出ポート４ｌとを連通させる状態（以下、「第２
の状態」という）と、入力側プーリ６の油圧サーボシリ
ンダ室６ａへの油圧を、ライン圧ＰL の変化に対して所
定の割合で変化する圧力に調圧する状態（以下、「第３
の状態」という）とにすることができる。The force acting on the stepped area of the spools 4h and 4g is made smaller than the hydraulic pressure of the oil chambers 4a and 4b regulated by the shift control solenoid valves 5a and 5b. With such settings, the shift control valve 4 is brought into a state (hereinafter, referred to as “first state”) in which the hydraulic pressure supply oil passage port 4k and the line pressure port 4c are communicated with each other by the shift control solenoid valves 5a and 5b. Hydraulic oil supply port 4
k and the discharge port 41 are in communication with each other (hereinafter, referred to as “second
"State of") and a state in which the hydraulic pressure to the hydraulic servo cylinder chamber 6a of the input side pulley 6 is adjusted to a pressure that changes at a predetermined ratio with respect to the change of the line pressure P L (hereinafter, referred to as "third state").
"State").
【００１８】油圧サーボシリンダ室６ａの油は油圧供給
油路ポート４ｋを介して給排される。この給排によりベ
ルト８の走行半径が変化して変速比が変わる。油圧サー
ボシリンダ室６ａ及び７ａにライン圧ＰL が導かれた状
態で変速比（減速比）の値を小さくすることができるよ
うに、油圧サーボシリンダ室６ａのピストン面積を、油
圧サーボシリンダ室７ａのピストン面積より大きくする
（本例ではほぼ２倍に設定する。）。Oil in the hydraulic servo cylinder chamber 6a is supplied and discharged via the hydraulic oil supply port 4k. Due to this supply and discharge, the traveling radius of the belt 8 changes and the gear ratio changes. The piston area of the hydraulic servo cylinder chamber 6a is set so that the value of the gear ratio (reduction ratio) can be reduced in a state where the line pressure P L is guided to the hydraulic servo cylinder chambers 6a and 7a. Larger than the piston area of (No. 2 in this example).
【００１９】油圧サーボシリンダ室７ａに遠心キャンセ
ルピストン７ｂを設け、車両の高速走行時の遠心油圧に
よる過大なプーリ推力によるベルト８の耐久性の低下及
び伝達効率の低下を防止する。A centrifugal cancel piston 7b is provided in the hydraulic servo cylinder chamber 7a to prevent the durability of the belt 8 and the transmission efficiency from being lowered by an excessive pulley thrust due to the centrifugal hydraulic pressure when the vehicle is traveling at high speed.
【００２０】本例の動作を説明する。変速制御ソレノイ
ド弁５ｂにより、油油室４ｂの油圧が低くなるように調
圧されると、スプール４ｇ及び４ｈが図１において下方
に移動し、油圧供給油路ポート４ｋとライン圧ポート４
ｃとが連通されて第１の状態となる。第１の状態では、
入力側プーリ６の油圧サーボシリンダ室６ａにライン圧
ＰL が供給されるので、変速比（減速比）の値が小さく
なるように変速する。The operation of this example will be described. When the oil pressure in the oil chamber 4b is adjusted by the shift control solenoid valve 5b to be low, the spools 4g and 4h move downward in FIG. 1, and the oil pressure supply oil passage port 4k and the line pressure port 4 are moved.
The first state is established by communicating with c. In the first state,
Since the line pressure P L is supplied to the hydraulic servo cylinder chamber 6a of the input side pulley 6, gear shifting is performed so that the value of the gear ratio (reduction ratio) becomes smaller.
【００２１】それに対して、変速制御ソレノイド弁５ａ
により、油室４ａの油圧が低くなるように調圧される
と、スプール４ｇ及び４ｈが図１において上方に移動
し、油圧供給油路ポート４ｋと排出ポート４ｌとが連通
されて第２の状態となる。第２の状態では、油圧サーボ
シリンダ室６ａの油が排出ポート４ｌから排出されるの
で、変速比（減速比）の値が大きくなるように変速す
る。On the other hand, the shift control solenoid valve 5a
When the oil pressure in the oil chamber 4a is adjusted to be low, the spools 4g and 4h move upward in FIG. 1 so that the oil pressure supply oil passage port 4k and the discharge port 4l are in communication with each other and are in the second state. Becomes In the second state, the oil in the hydraulic servo cylinder chamber 6a is discharged from the discharge port 4l, so the speed is changed so that the value of the gear ratio (reduction ratio) is increased.
【００２２】変速制御ソレノイド弁５ａ及び５ｂにより
それぞれ、油室４ａ及び４ｂの油圧を同一すなわち両油
室４ａ及び４ｂの油圧を高く又は低くすると、油圧サー
ボシリンダ室６ａへの油圧をライン圧ＰL の変化に対し
て所定の割合で変化する圧力に調圧する第３の状態とな
る。車両の通常の走行状態から、変速制御ソレノイド５
ａ又は５ｂ、コントローラ（図示せず）等が故障する電
制のフェール状態となり、コントローラ（図示せず）の
電源がオフされるとこのような第３の状態となるように
する。第３の状態では、変速制御ソレノイド弁５ａ及び
５ｂによって調圧された油室４ａ及び４ｂの油圧がほぼ
同一であるので、スプール４ｇ及び４ｈの位置は、ばね
４ｉ及び４ｊの弾性力と、ライン圧ポート４ｄのライン
圧ＰL がスプール４ｈの段付部面積に作用する力と、入
力側プーリ６の油圧サーボシリンダ室６ａの油圧供給油
路ポート４ｋの油圧がスプール４ｇの段付部面積に作用
する力との釣り合いによって決定される。When the oil pressures in the oil chambers 4a and 4b are made to be the same by the shift control solenoid valves 5a and 5b, that is, when the oil pressures in the oil chambers 4a and 4b are increased or decreased, the oil pressure to the hydraulic servo cylinder chamber 6a is changed to the line pressure P L. Is in the third state in which the pressure is adjusted to a pressure that changes at a predetermined rate with respect to the change of. From the normal running state of the vehicle, the shift control solenoid 5
When the power of the controller (not shown) is turned off and the controller (not shown) is turned off, the third state is set. In the third state, the oil pressures of the oil chambers 4a and 4b regulated by the shift control solenoid valves 5a and 5b are substantially the same, so that the positions of the spools 4g and 4h are the elastic forces of the springs 4i and 4j and the line. The line pressure P L of the pressure port 4d acts on the stepped portion area of the spool 4h, and the hydraulic pressure of the hydraulic supply oil passage port 4k of the hydraulic servo cylinder chamber 6a of the input side pulley 6 becomes the stepped portion area of the spool 4g. It is determined by the balance with the acting force.
【００２３】油圧供給油路ポート４ｋの油圧がこれらの
力が釣り合っている状態に比べて高くなると、スプール
４ｇに対する力が図１において上方に増加するため、ス
プール４ｇは図１において上方に移動する。その結果油
圧供給油路ポート４ｋと排出ポート４ｌとの連通量が増
加し、油圧供給油路ポート４ｋの油圧は低下する。When the hydraulic pressure of the hydraulic pressure supply oil passage port 4k becomes higher than that in the state where these forces are balanced, the force on the spool 4g increases upward in FIG. 1, so the spool 4g moves upward in FIG. . As a result, the amount of communication between the hydraulic pressure supply oil passage port 4k and the discharge port 4l increases, and the hydraulic pressure of the hydraulic pressure supply oil passage port 4k decreases.
【００２４】一方、油圧供給油路ポート４ｋの油圧がこ
れらの力が釣り合っている状態に比べて低くなると、ス
プール４ｇに対する上方への力が減少するため、スプー
ル４ｇは図１において下方に移動する。その結果油圧供
給油路ポート４ｋとライン圧ポート４ｃとの連通量が増
加し、油圧供給油路ポート４ｋの油圧は上昇する。On the other hand, when the hydraulic pressure of the hydraulic pressure supply oil passage port 4k becomes lower than that in the state where these forces are balanced, the upward force on the spool 4g decreases, so that the spool 4g moves downward in FIG. . As a result, the amount of communication between the hydraulic pressure supply oil passage port 4k and the line pressure port 4c increases, and the hydraulic pressure of the hydraulic pressure supply oil passage port 4k increases.
【００２５】この際のスプール４ｇの移動量に応じてば
ね４ｉ及び４ｊの弾性力は変化するので、油圧供給油路
ポート４ｋの油圧にはオーバライドが発生する。本例で
は、スプール４ｇの移動量の変化による連通量変化を小
さくするために、ライン圧ポート４ｃ及び排出ポート４
ｌにそれぞれノッチ４ｍ及び４ｎを設ける。Since the elastic forces of the springs 4i and 4j change in accordance with the amount of movement of the spool 4g at this time, an override occurs in the hydraulic pressure of the hydraulic pressure supply oil passage port 4k. In this example, in order to reduce the change in the communication amount due to the change in the movement amount of the spool 4g, the line pressure port 4c and the discharge port 4 are
Notches 4m and 4n are provided in each l.
【００２６】ベルト式無段変速機の変速比は入力側プー
リ６及び出力側プーリ７の推力並びに伝達トルクに応じ
て決まることが知られている。入力側プーリ６と出力側
プーリ７のうち推力の大きい側のベルト８の走行半径が
大きくなる。また、伝達トルクが大きくなるに従って変
速比（減速比）の値が大きくなる。It is known that the gear ratio of the belt type continuously variable transmission is determined according to the thrust and the transmission torque of the input side pulley 6 and the output side pulley 7. Of the input side pulley 6 and the output side pulley 7, the traveling radius of the belt 8 on the side with the larger thrust becomes larger. Further, the value of the gear ratio (reduction ratio) increases as the transmission torque increases.
【００２７】ここで、油圧サーボシリンダ室６ａの供給
圧を、ライン圧ＰL に対してサーボシリンダ室６ａ及び
６ｂのピストン面積比の逆数に等しく設定した場合を考
える。第３の状態において伝達トルクがゼロの場合、低
車速では遠心油圧の影響が小さいために変速比は１付近
となる。車速が高くなるに従って油圧サーボシリンダ室
６ａのピストンの遠心油圧による推力が大きくなり、変
速比が小さくなるように変化する。それに対して伝達ト
ルクがある場合、変速比は入力トルクが大きくなるに従
って小さくなる。Now, consider a case where the supply pressure of the hydraulic servo cylinder chamber 6a is set equal to the reciprocal of the piston area ratio of the servo cylinder chambers 6a and 6b with respect to the line pressure P L. When the transmission torque is zero in the third state, the gear ratio is close to 1 at a low vehicle speed because the influence of the centrifugal hydraulic pressure is small. As the vehicle speed increases, the thrust due to the centrifugal hydraulic pressure of the piston in the hydraulic servo cylinder chamber 6a increases, and the gear ratio changes so as to decrease. On the other hand, when there is a transmission torque, the gear ratio decreases as the input torque increases.
【００２８】レイアウトの関係で油圧サーボシリンダ室
６ａに発生する推力を遠心油圧キャンセルピストン７ｂ
がキャンセルする割合は、ユニットごとに異なる。ま
た、入力側プーリ６のサーボピストンをシングルピスト
ンにするかダブルピストンにするか等により推力の発生
量が異なる。これらのことを考慮して第３の状態におい
て油圧サーボシリンダ室６ａに供給する圧力を設定、す
なわちライン圧ＰL の変化に対する設定圧変化の割合
と、バネセット荷重によるオフセット圧とを設定するこ
とにより、変速特性は図２に示すようになる。Due to the layout, the thrust generated in the hydraulic servo cylinder chamber 6a is converted into the centrifugal hydraulic pressure cancel piston 7b.
The rate of canceling is different for each unit. Further, the amount of thrust generated differs depending on whether the servo piston of the input side pulley 6 is a single piston or a double piston. In consideration of these matters, the pressure supplied to the hydraulic servo cylinder chamber 6a is set in the third state, that is, the ratio of the set pressure change to the change of the line pressure P L and the offset pressure due to the spring set load are set. The shift characteristics are as shown in FIG.
【００２９】図２において、縦軸は入力回転速度を示
し、横軸は車速を示す。曲線ａは伝達トルクがゼロの場
合の第３の状態の変速線を、曲線ｂは伝達トルクが最大
すなわちスロットル開度が最大の場合の第３の状態の変
速線をそれぞれ示す。油圧サーボシリンダ室６ａのピス
トンの遠心油圧は入力回転の２乗に比例するので、曲線
ａ及びｂは図２に示すように変化する。変速比は図２の
斜線で示す部分の範囲内で変化し、直線ｃ方向に変化す
れば変速比が高くなり、それに対して直線ｄ方向に変化
すれば変速比が低くなる。In FIG. 2, the vertical axis represents the input rotation speed and the horizontal axis represents the vehicle speed. The curve a shows the shift line in the third state when the transmission torque is zero, and the curve b shows the shift line in the third state when the transmission torque is maximum, that is, the throttle opening is maximum. Since the centrifugal hydraulic pressure of the piston in the hydraulic servo cylinder chamber 6a is proportional to the square of the input rotation, the curves a and b change as shown in FIG. The gear ratio changes within the range of the shaded portion in FIG. 2, and if it changes in the straight line c direction, the gear ratio becomes high, whereas if it changes in the straight line d direction, the gear ratio becomes low.
【００３０】また、通常の走行状態からフェール状態と
なり、コントローラ（図示せず）の電源がオフされて
も、上記オーバライド特性により急激な変速が起こらな
い。Further, even if the normal running state is changed to the fail state and the power source of the controller (not shown) is turned off, the rapid shift does not occur due to the above-mentioned override characteristic.
【００３１】[0031]
【発明の効果】以上説明したように、本発明による請求
項１のベルト式無段変速機の変速制御装置によれば、電
制のフェール状態でも車両を発進、登板及び中高速走行
させることができる。As described above, according to the speed change control apparatus for a belt type continuously variable transmission of the first aspect of the present invention, the vehicle can be started, climbed, and run at medium and high speeds even in the electric failure state. it can.
【００３２】本発明による請求項２のベルト式無段変速
機の変速制御装置によれば、入力側プーリの油圧サーボ
の油圧を、ライン圧の変化に対して所定の割合で変化す
る圧力に調圧できるので、本発明による制御を良好に行
うことができる。According to the gear shift control device of the belt type continuously variable transmission of the second aspect of the present invention, the hydraulic pressure of the hydraulic servo of the input side pulley is adjusted to a pressure that changes at a predetermined rate with respect to the change of the line pressure. Since the pressure can be applied, the control according to the present invention can be favorably performed.
【００３３】本発明による請求項３のベルト式無段変速
機の変速制御装置によれば、スプールの移動による油路
の連通量変化を小さくすることができ、急な変速が起こ
るおそれがなくなる。According to the gear shift control device of the belt type continuously variable transmission of the third aspect of the present invention, the change in the communication amount of the oil passage due to the movement of the spool can be made small, and there is no fear of sudden gear shifting. .
【００３４】本発明による請求項４のベルト式無段変速
機の変速制御装置によれば、入力プーリの油圧サーボへ
の油圧を、ライン圧の変化に対して所定の割合で変化す
る圧力に調圧することにより、電制のフェール状態でも
変速比を決定し、車両を発進、登板及び中高速走行させ
ることができる。According to the shift control device for a belt type continuously variable transmission of the present invention, the hydraulic pressure to the hydraulic servo of the input pulley is adjusted to a pressure that changes at a predetermined rate with respect to the change in line pressure. By applying the pressure, the gear ratio can be determined even in a failure state of electric control, and the vehicle can be started, climbed, and run at medium and high speeds.
【図１】本発明によるベルト式無段変速機の変速制御装
置の一実施例を示す図である。FIG. 1 is a diagram showing an embodiment of a shift control device for a belt type continuously variable transmission according to the present invention.
【図２】本発明によるベルト式無段変速機の変速制御装
置によって得られる変速特性を示す図である。FIG. 2 is a diagram showing shift characteristics obtained by the shift control device for a belt type continuously variable transmission according to the present invention.
１ オイルポンプ ２ リリーフ弁 ３ 減圧弁 ４ 変速制御弁 ４ａ，４ｂ 油室 ４ｃ，４ｄ ライン圧ポート ４ｅ，４ｆ ポート ４ｇ，４ｈ スプール ４ｉ，４ｊ ばね ４ｋ 油圧供給油路ポート ４ｌ 排出ポート ４ｍ，４ｎ ノッチ ５ａ，５ｂ 変速制御ソレノイド ６ 入力側プーリ ７ 出力側プーリ ７ａ 油圧サーボシリンダ室 ７ｂ 遠心キャンセルピストン ８ ベルト ９ａ，９ｂ オリフィス ＰL ライン圧 ＰO 出力圧1 oil pump 2 relief valve 3 pressure reducing valve 4 speed change control valve 4a, 4b oil chamber 4c, 4d line pressure port 4e, 4f port 4g, 4h spool 4i, 4j spring 4k hydraulic oil supply port port 4l discharge port 4m, 4n notch 5a , 5b shift control solenoid 6 input pulley 7 output side pulley 7a hydraulic servo cylinder chamber 7b centrifugal cancel piston 8 belt 9a, 9b orifice P L line pressure P O output pressure
Claims (4)
させる油圧供給源と、油の給排を行うとともに二つの油
室が形成された変速制御弁と、これら二つの油室の油圧
を調圧する二つの変速制御ソレノイド弁と、前記変速制
御弁により油の給排が行われる油圧サーボを有する入力
側プーリと、前記ライン圧が導かれ、前記入力プーリの
油圧サーボのピストン面積よりも小さいピストン面積の
油圧サーボを有する出力側プーリと、これら入力側プー
リ及び出力側プーリとの間に巻かれたベルトとを具え、
前記入力側プーリの油圧サーボへの油の給排により前記
ベルトの走行半径が変化して変速比が変化するベルト式
無段変速機の変速制御装置において、 前記変速制御弁は、前記二つの油室をそれぞれ形成する
スプールを具え、前記スプールを介して前記入力側プー
リの油圧サーボと前記油圧供給源とを連通させる第１の
状態と、前記スプールを介して前記入力側プーリの油圧
サーボの油を排出する第２の状態と、前記入力側プーリ
の油圧サーボの油圧を、前記ライン圧の変化に対して所
定の割合で変化する圧力に、前記スプールを用いて調圧
する第３の状態とに設定され、電制のフェールが発生し
た場合には前記第３の状態にして車両の走行状態に応じ
た変速比の決定をすることを特徴とするベルト式無段変
速機の変速制御装置。1. A hydraulic pressure supply source for generating a line pressure according to a running state of a vehicle, a speed change control valve for supplying and discharging oil and having two oil chambers formed, and a hydraulic pressure for these two oil chambers. Two shift control solenoid valves for adjusting pressure, an input side pulley having a hydraulic servo that supplies and discharges oil by the shift control valve, and the line pressure is introduced and is smaller than the piston area of the hydraulic servo of the input pulley. An output side pulley having a hydraulic servo of the piston area, and a belt wound between the input side pulley and the output side pulley,
In a shift control device for a belt-type continuously variable transmission, in which a running radius of the belt changes and a gear ratio changes due to supply and discharge of oil to and from a hydraulic servo of the input side pulley, the shift control valve includes the two oils. A first state in which a spool forming each chamber is provided, and a hydraulic servo of the input side pulley communicates with the hydraulic pressure supply source via the spool; and an oil state of the hydraulic servo of the input side pulley via the spool To the second state in which the spool is discharged, and the third state in which the hydraulic pressure of the hydraulic servo of the input side pulley is adjusted to a pressure that changes at a predetermined rate with respect to the change in the line pressure using the spool. A gear shift control device for a belt-type continuously variable transmission, wherein a gear ratio is set according to a running state of a vehicle in the third state when a set electric failure occurs.
くすることを特徴とする請求項１記載のベルト式無段変
速機の変速制御装置2. The shift control device for a belt type continuously variable transmission according to claim 1, wherein the two hydraulic chambers have the same hydraulic pressure receiving area.
持する二つのばねを具えかつそれらを対抗させて配設さ
れていることを特徴とする請求項１又は２記載のベルト
式無段変速機の変速制御装置3. The belt type continuously variable transmission according to claim 1, wherein the speed change control valve comprises two springs elastically supporting the spool and is arranged so as to oppose each other. Shift control device
り発生したライン圧が作用するライン圧受圧部と、前記
入力側プーリの油圧サーボへの油圧が作用するサーボ油
圧受圧部と、前記入力側プーリの油圧サーボの油が排出
される排出部とを有し、前記ライン圧受圧部に作用する
圧力により、前記油圧供給源により発生したライン圧が
前記入力側プーリの油圧サーボに連通するようにし、か
つ、前記サーボ圧受圧部に作用する圧力が、前記排出部
が前記入力側プーリの油圧サーボに連通するように設定
したことを特徴とする請求項１から３のうちのいずれか
１項に記載のベルト式無段変速機の変速制御装置4. The shift control valve includes: a line pressure receiving portion on which a line pressure generated by the hydraulic pressure source acts; a servo hydraulic pressure receiving portion on which a hydraulic pressure to a hydraulic servo of the input side pulley acts; And a discharge portion for discharging the oil of the hydraulic servo of the side pulley, and the line pressure generated by the hydraulic pressure supply source is communicated with the hydraulic servo of the input side pulley by the pressure acting on the line pressure receiving portion. 4. The pressure acting on the servo pressure receiving portion is set so that the discharging portion communicates with the hydraulic servo of the input side pulley. Shift control device for belt type continuously variable transmission described in 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7754395A JP3458520B2 (en) | 1995-04-03 | 1995-04-03 | Transmission control device for belt-type continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7754395A JP3458520B2 (en) | 1995-04-03 | 1995-04-03 | Transmission control device for belt-type continuously variable transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH08277929A true JPH08277929A (en) | 1996-10-22 |
| JP3458520B2 JP3458520B2 (en) | 2003-10-20 |
Family
ID=13636924
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7754395A Expired - Lifetime JP3458520B2 (en) | 1995-04-03 | 1995-04-03 | Transmission control device for belt-type continuously variable transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3458520B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010159779A (en) * | 2009-01-06 | 2010-07-22 | Toyota Motor Corp | Continuously variable transmission device |
| JP2014114828A (en) * | 2012-12-06 | 2014-06-26 | Toyota Motor Corp | Hydraulic control device |
| JP2014211206A (en) * | 2013-04-19 | 2014-11-13 | トヨタ自動車株式会社 | Hydraulic controller of belt type continuously variable transmission |
-
1995
- 1995-04-03 JP JP7754395A patent/JP3458520B2/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010159779A (en) * | 2009-01-06 | 2010-07-22 | Toyota Motor Corp | Continuously variable transmission device |
| JP2014114828A (en) * | 2012-12-06 | 2014-06-26 | Toyota Motor Corp | Hydraulic control device |
| JP2014211206A (en) * | 2013-04-19 | 2014-11-13 | トヨタ自動車株式会社 | Hydraulic controller of belt type continuously variable transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3458520B2 (en) | 2003-10-20 |
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