JP2975082B2 - Hydraulic control device for V-belt continuously variable transmission - Google Patents

Hydraulic control device for V-belt continuously variable transmission

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Publication number
JP2975082B2
JP2975082B2 JP2278036A JP27803690A JP2975082B2 JP 2975082 B2 JP2975082 B2 JP 2975082B2 JP 2278036 A JP2278036 A JP 2278036A JP 27803690 A JP27803690 A JP 27803690A JP 2975082 B2 JP2975082 B2 JP 2975082B2
Authority
JP
Japan
Prior art keywords
oil
pressure
pulley
oil chamber
oil pump
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.)
Expired - Lifetime
Application number
JP2278036A
Other languages
Japanese (ja)
Other versions
JPH04157256A (en
Inventor
孝文 鴛渕
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daihatsu Motor Co Ltd
Original Assignee
Daihatsu Kogyo KK
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Filing date
Publication date
Application filed by Daihatsu Kogyo KK filed Critical Daihatsu Kogyo KK
Priority to JP2278036A priority Critical patent/JP2975082B2/en
Publication of JPH04157256A publication Critical patent/JPH04157256A/en
Application granted granted Critical
Publication of JP2975082B2 publication Critical patent/JP2975082B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
    • F16H2061/66286—Control for optimising pump efficiency

Landscapes

  • Control Of Transmission Device (AREA)
  • Transmissions By Endless Flexible Members (AREA)

Description

【発明の詳細な説明】 〔産業上の利用分野〕 本発明はＶベルト式無段変速機の油圧制御装置、特に
駆動側プーリと従動側プーリの双方にベルト巻き掛け径
を可変とする油圧サーボ装置を備えたＶベルト式無段変
速機を油圧制御装置に関するものである。Description: BACKGROUND OF THE INVENTION The present invention relates to a hydraulic control device for a V-belt type continuously variable transmission, and more particularly, to a hydraulic servo that makes a belt winding diameter variable on both a driving pulley and a driven pulley. The present invention relates to a V-belt type continuously variable transmission provided with a hydraulic control device.

〔従来の技術〕[Conventional technology]

従来、車両用のＶベルト式無段変速機として例えば特
開昭58−42862号公報のものが公知である。即ち、この
Ｖベルト式無段変速機は、第３図に示すようにエンジン
出力軸と接続された駆動側プーリ30と、車軸に接続され
た従動側プーリ31とを備え、駆動側プーリ30と従動側プ
ーリ31の双方にベルト巻き掛け径を可変とする７油圧サ
ーボ装置32,33を備えた構造となっている。そして、従
動側プーリ31の油室33aには調圧弁34で調圧されたライ
ン圧を常時導き、駆動側プーリ30を油室32aには変速制
御弁35によってライン圧を給排するように構成してあ
る。2. Description of the Related Art Conventionally, as a V-belt type continuously variable transmission for a vehicle, for example, Japanese Patent Application Laid-Open No. 58-42862 is known. That is, as shown in FIG. 3, the V-belt type continuously variable transmission includes a driving pulley 30 connected to an engine output shaft, and a driven pulley 31 connected to an axle. The driven pulley 31 is provided with seven hydraulic servo devices 32 and 33 that can change the belt winding diameter on both sides. The line pressure regulated by the pressure regulating valve 34 is always guided to the oil chamber 33a of the driven pulley 31, and the drive pulley 30 is configured to supply and discharge the line pressure to the oil chamber 32a by the transmission control valve 35. I have.

上記油圧制御装置において、低速比（Low）から高速
比（High）へ変速する場合には、変速制御弁35がライン
圧を駆動側プーリ30を油室32aにそのまま導く。駆動側
プーリ30の油室32aの受圧面積は従動側プーリ31の油室3
3aの受圧面積より大きいので、駆動側プーリ30のベルト
巻き掛け径が増大（従動側プーリ31のベルト巻き掛け径
が減少）し、高速比へ変速される。In the above hydraulic control device, when shifting from the low speed ratio (Low) to the high speed ratio (High), the shift control valve 35 directly guides the line pressure from the drive side pulley 30 to the oil chamber 32a. The pressure receiving area of the oil chamber 32a of the driving pulley 30 is equal to that of the oil chamber 3 of the driven pulley 31.
Since the pressure receiving area is larger than the pressure receiving area 3a, the belt winding diameter of the driving pulley 30 increases (the belt winding diameter of the driven pulley 31 decreases), and the gear is shifted to the high speed ratio.

一方、高速比（High）から低速比（Low）へ変速する
場合には、変速制御弁35のドレンポートを開き、駆動側
プーリ30の油室32aをドレーンさせる。従動側プーリ31
の油室33aにはライン圧が導かれているので、従動側プ
ーリ31のベルト巻き掛け径が増大（駆動側プーリ30のベ
ルト巻き掛け径が減少）し、低速比へ変速される。On the other hand, when shifting from the high speed ratio (High) to the low speed ratio (Low), the drain port of the shift control valve 35 is opened, and the oil chamber 32a of the drive side pulley 30 is drained. Driven pulley 31
Since the line pressure is introduced into the oil chamber 33a, the belt winding diameter of the driven pulley 31 increases (the belt winding diameter of the driving pulley 30 decreases), and the gear is shifted to the low speed ratio.

〔発明が解決しようとする課題〕[Problems to be solved by the invention]

上記油圧制御装置の場合、低速比から高速比への変速
時には従動側プーリ31の圧油を駆動側プーリ30へ利用で
きるが、高速比から低速比への変速時には、駆動側プー
リ30の圧油は変速制御弁35からドレーンされるのみであ
り、従動側プーリ31へは利用されない。したがって、不
足分の圧油をオイルポンプ36で供給してやる必要があ
る。In the case of the above hydraulic control device, the pressure oil of the driven pulley 31 can be used for the drive pulley 30 at the time of shifting from the low speed ratio to the high speed ratio, but the pressure oil of the drive pulley 30 can be used at the time of shifting from the high speed ratio to the low speed ratio. Is only drained from the shift control valve 35 and is not used for the driven pulley 31. Therefore, it is necessary to supply insufficient pressure oil by the oil pump 36.

オイルポンプ36を吐出流量Ｑは、次式のように潤滑流
量QLと変速必要流量QDNとの和で与えられる。Discharge flow rate Q of the oil pump 36 is given by the sum of the lubricating flow rate Q L and the transmission required flow rate Q DN as follows.

Ｑ＝QL＋QDN したがって、オイルポンプ36の駆動エネルギーＥは、 Ｅ＝PDN・Ｑ ＝PDN（QL＋QDN） ＝PDN・QL＋PDN・QDN …（１） となる。なお、PDNは従動側プーリ31の油室33aの油圧で
あり、この場合は、ライン圧に等しい。Q = Q L + Q DN Thus, driving energy E of the oil pump 36, E = P DN · Q = become P DN (Q L + Q DN ) = P DN · Q L + P DN · Q DN ... (1). Note that P DN is the oil pressure of the oil chamber 33a of the driven pulley 31, and in this case, is equal to the line pressure.

一方、変速しない時には駆動側プーリ30および従動側
プーリ31の双方の油室32a,33aに圧油を給排する必要が
ないので、オイルポンプ36は潤滑流量QL分だけ吐出すれ
ばよいのであるが、実際にはオイルポンプ36は変速必要
流量QDNの常時吐出しており、これを変速制御弁35から
ドレーンしている。つまり、オイルポンプ36の駆動エネ
ルギーがPDN・QDN分だけ無駄となっている。On the other hand, it is not necessary for supplying and discharging pressure oil to both oil chambers 32a, 33a of the drive pulley 30 and the driven pulley 31 when not in gear, the oil pump 36 is can I discharge only lubricant flow Q L min However, actually, the oil pump 36 constantly discharges the required flow rate QDN for shifting, and drains this from the shift control valve 35. In other words, the drive energy of the oil pump 36 is wasted by P DN and Q DN .

このように、従来の油圧制御装置ではオイルポンプ36
が変速に必要な流量を常時吐出しているので、変速時お
よび非変速時におけるオイルポンプ36の損失エネルギー
が非常に大きく、燃費を悪化させるという欠点があっ
た。Thus, in the conventional hydraulic control device, the oil pump 36
Always discharges the flow rate required for shifting, the energy loss of the oil pump 36 during shifting and non-shifting is extremely large, and there is a disadvantage that fuel efficiency is deteriorated.

そこで、本発明の目的は、オイルポンプの損失エネル
ギーを最低限に抑制し、燃費向上を実現できるＶベルト
式無段変速機の油圧制御装置を提供することにある。SUMMARY OF THE INVENTION It is an object of the present invention to provide a hydraulic control device for a V-belt type continuously variable transmission capable of minimizing energy loss of an oil pump and improving fuel efficiency.

〔課題を解決するための手段〕[Means for solving the problem]

上記目的を達成するため、本発明は、駆動側プーリと
従動側プーリの双方にベルト巻き付け径を可変とする油
圧サーボ装置を備えたＶベルト式無段変速機において、
第１オイルポンプの吐出圧を所定の油圧に調圧する調圧
弁と、該調圧弁の出力油圧を駆動側プーリの油室と従動
側プーリの油室とに夫々供給する一方弁と、一方弁の下
流側でかつ駆動側プーリの油室と従動側プーリの油室と
の間を結ぶ油路と、該油路中に設けられ、可逆的に油を
吐出する第２オイルポンプとを備え、該第２オイルポン
プを駆動することにより駆動側プーリを油室と従動側プ
ーリを油室とに相互に油圧を給排するようにしたもので
ある。In order to achieve the above object, the present invention provides a V-belt continuously variable transmission including a hydraulic servo device that varies a belt winding diameter on both a driving pulley and a driven pulley.
A pressure regulating valve for regulating the discharge pressure of the first oil pump to a predetermined oil pressure, a one-side valve for supplying an output oil pressure of the pressure-regulating valve to an oil chamber of a driving pulley and an oil chamber of a driven pulley, An oil passage connecting the oil chamber of the drive pulley and the oil chamber of the driven pulley on the downstream side, and a second oil pump provided in the oil passage and discharging oil reversibly, By driving the second oil pump, the driving side pulley supplies and discharges the hydraulic pressure to and from the oil chamber of the driven side pulley.

〔作用〕[Action]

第１オイルポンプの吐出圧は調圧弁でライン圧に調圧
される。このライン圧は、一方弁を介して駆動側プーリ
および従動側プーリの油室へ供給され、残りは潤滑部位
へ供給される。変速しない時には駆動側プーリおよび従
動側プーリの双方の油室に油を給排する必要がないの
で、第２オイルポンプは駆動されない。したがって、第
１オイルポンプは潤滑油量に相当する油量を吐出すれば
よい。変速時には第２オイルポンプが駆動され、ベルト
巻き掛け径が減少するプーリを油室から油圧を吸引し、
増大するプーリを油室へ油圧を供給する。油圧が吸引さ
れた側のプーリを油室の油圧がライン圧以下になれば、
不足分の圧油が一方弁を介して補給される。The discharge pressure of the first oil pump is regulated to a line pressure by a pressure regulating valve. This line pressure is supplied to the oil chambers of the driving pulley and the driven pulley via the one-way valve, and the rest is supplied to the lubrication part. When the gear is not shifted, there is no need to supply and discharge oil to both the oil chambers of the driving pulley and the driven pulley, so the second oil pump is not driven. Therefore, the first oil pump only needs to discharge an oil amount corresponding to the lubricating oil amount. At the time of shifting, the second oil pump is driven, and the pulley whose belt winding diameter is reduced sucks hydraulic pressure from the oil chamber,
The increasing pulley supplies hydraulic pressure to the oil chamber. If the oil pressure in the oil chamber falls below the line pressure,
Insufficient pressure oil is replenished via the one-way valve.

このように、従来の変速制御弁から排出されるドレー
ン油量をなくし、両方でプーリの油室間で油を給排する
ようにしたので、オイルポンプの損失をエネルギーを最
小限に抑制できる。As described above, the drain oil amount discharged from the conventional shift control valve is eliminated, and oil is supplied and discharged between the oil chambers of the pulleys at both ends, so that the energy loss of the oil pump can be suppressed to a minimum.

〔実施例〕〔Example〕

第１図は本発明にかかるＶベルト式無段変速機を油圧
回路を示す。FIG. 1 shows a hydraulic circuit of a V-belt type continuously variable transmission according to the present invention.

Ｖベルト式無段変速機１は駆動側プーリ２と、従動側
プーリ３と、両プーリ間に巻き掛けたＶベルト４とで構
成され、駆動側プーリ２および従動側プーリ３には夫々
ベルト巻き掛け径を可変とする油圧サーボ装置5,6が設
けられている。The V-belt type continuously variable transmission 1 includes a driving pulley 2, a driven pulley 3, and a V-belt 4 wound between the two pulleys. Hydraulic servo devices 5 and 6 that change the hanging diameter are provided.

第１オイルポンプ10の吐出圧は調圧弁11によってライ
ン圧PLに調圧され、このライン圧PLは一方弁12,13を介
して夫々油圧サーボ装置5,6を油室5a,6aへ供給されてい
る。なお、ライン圧PLはＶベルト４がプーリ2,3に対し
て滑らない程度の最低油圧に設定される。上記一方弁1
2,13の下流側で、かつ駆動側プーリ２の油室5aと従動側
プーリ３の油室6aとの間を結ぶ油路14中には可逆的に油
を吐出する第２オイルポンプ20が設けられており、この
第２オイルポンプ20を駆動することにより駆動側プーリ
２の油室5aと従動側プーリ３の油室6aとに相互に油圧を
給排できるようになっている。The discharge pressure of the first oil pump 10 is regulated to a line pressure P L by a pressure regulating valve 11, and this line pressure P L is supplied to hydraulic servo devices 5 and 6 via one-way valves 12 and 13 to oil chambers 5 a and 6 a, respectively. Supplied. Incidentally, the line pressure P L is the V-belt 4 is set to the lowest pressure that will not slip relative to the pulleys 2, 3. Above one-way valve 1
A second oil pump 20 for reversibly discharging oil is provided in an oil passage 14 downstream of the oil chambers 2 and 13 and between the oil chamber 5a of the driving pulley 2 and the oil chamber 6a of the driven pulley 3. By driving the second oil pump 20, oil pressure can be mutually supplied and discharged to and from the oil chamber 5a of the driving pulley 2 and the oil chamber 6a of the driven pulley 3.

上記第２オイルポンプ20は、例えば第２図に示すよう
な可変ベーンポンプで構成されている。即ち、カムリン
グ21の一端部は支軸22によって揺動自在に支持されてお
り、他端部には長孔23aを持つ操作片23が一体に形成さ
れている。カムリング21の内側には周囲に複数のベーン
24を持ったロータ25が配置されており、このロータ25は
矢印方向に駆動される。なお、ローラ25は第１オイルポ
ンプ10と独立に駆動してもよいし、同一の駆動源で駆動
してもよい。カムリング21およびロータ25の側部を支持
したポンプボデー（図示せず）には２個のポート26,27
が設けられ、一方のポート26は駆動側プーリ２の油室5a
と、他方のポート27は従動側プーリ３の油室6aと夫々接
続されている。上記操作片23の長孔23aにはステップモ
ータ等が直動式アクチュエータ28のシャフト29が連結さ
れており、アクチュエータ28によってシャフト29を前後
に動作させることにより、カムリング21を支軸22を支点
として左右に揺動させることができる。例えばカムリン
グ21を左方へ揺動させると、上側のポート26が吸込みポ
ート、下側のポート27が吐出ポートとなるので、駆動側
プーリ２の油室5aの油圧が低下、従動側プーリ３の油室
6aの油圧が上昇し、低速比（Low）へ変速される。逆
に、カムリング21を右方に揺動させると、高速比（Hig
h）へ変速される。また、カムリング21を中立位置で保
持すると、第２オイルポンプ20は油の吸引・吐出を行わ
ず、その変速比を保持する。なお、アクチュエータ28は
図示しない電子制御装置により、変速比，エンジン回転
速度，スロットル開度，車速等の因子から総合的に走行
状態を判定して制御される。The second oil pump 20 is constituted by, for example, a variable vane pump as shown in FIG. That is, one end of the cam ring 21 is swingably supported by the support shaft 22, and an operation piece 23 having a long hole 23a is integrally formed at the other end. Inside the cam ring 21 there are several vanes around
A rotor 25 having 24 is arranged, and this rotor 25 is driven in the direction of the arrow. Note that the roller 25 may be driven independently of the first oil pump 10, or may be driven by the same drive source. A pump body (not shown) supporting the cam ring 21 and the side of the rotor 25 has two ports 26, 27.
And one port 26 is connected to the oil chamber 5a of the driving pulley 2.
And the other port 27 is connected to the oil chamber 6a of the driven pulley 3 respectively. A shaft 29 of a direct-acting actuator 28 such as a step motor is connected to the elongated hole 23a of the operation piece 23, and the shaft 29 is moved back and forth by the actuator 28 so that the cam ring 21 is supported by the support shaft 22 as a fulcrum. It can be swung right and left. For example, when the cam ring 21 is swung to the left, the upper port 26 becomes a suction port and the lower port 27 becomes a discharge port. Therefore, the oil pressure in the oil chamber 5a of the driving pulley 2 decreases, Oil chamber
The hydraulic pressure of 6a rises and the gear is shifted to the low speed ratio (Low). Conversely, when the cam ring 21 is swung to the right, the high speed ratio (Hig
The gear is shifted to h). Further, when the cam ring 21 is held at the neutral position, the second oil pump 20 does not perform suction and discharge of oil, and maintains the gear ratio. The actuator 28 is controlled by an electronic control unit (not shown) which comprehensively determines the running state from factors such as the gear ratio, the engine speed, the throttle opening, and the vehicle speed.

上記Ｖベルト式無段変速機において、高速比から低速
比へ変速する場合を想定すると、第１オイルポンプ10の
吐出流量Q1は、一方弁12を経て油室5aに補充される流量
QPと潤滑流量QLとの和で与えられる。In the V-belt type continuously variable transmission, assuming that shifting from the high speed ratio to a lower speed ratio, the discharge flow rate to Q 1 first oil pump 10, whereas is replenished to the oil chamber 5a through valve 12 flow rate
It is given by the sum of the Q P and the lubricant flow rate Q L.

Q1＝QP＋QL なお、補充流量QP＝QDN−QDRである。Q 1 = Q P + Q L Note that it is supplemented flow Q P = Q DN -Q DR.

そのため、第１オイルポンプ10の駆動エネルギーE
1は、 E1＝PL・Q1 ＝PL（QDN−QDR＋QL） となる。なお、PLはライン圧である。Therefore, the driving energy E of the first oil pump 10
1 becomes E 1 = P L · Q 1 = P L (Q DN -Q DR + Q L). Incidentally, P L is a line pressure.

また、第２オイルポンプ20の吐出流量はQDNであるか
ら、その駆動エネルギーE2は、 E2＝（PDN−PL）QDN である。したがって、総駆動エネルギーＥは Ｅ＝E1＋E2 ＝PL（QDN＝QDR＋QL）＋（PDN−PL）QDN ＝PL・QL＋PDN・QDN−PL・QDR 駆動側プーリ２と従動側プーリ３の油室の受圧面積を
ほぼ同等にすると、QDN≒QDRであるから、変速時の総エ
ネルギーＥは Ｅ＝PL・QL＋（PDN−PL）QDN となる。いま、ΔＰ＝PDN−PLとすると、 Ｅ＝（PDN・QL−ΔＰ・QL）＋PDN・QDN−PL・QDN） …（２） となる。Further, since the discharge flow rate of the second oil pump 20 is Q DN, the driving energy E 2 is E 2 = (P DN -P L ) Q DN. Thus, the total drive energy E is E = E 1 + E 2 = P L (Q DN = Q DR + Q L) + (P DN -P L) Q DN = P L · Q L + P DN · Q DN -P L · If the pressure receiving areas of the oil chambers of the Q DR drive pulley 2 and the driven pulley 3 are made substantially equal, then Q DN ≒ Q DR , so that the total energy E at the time of shifting is E = P L · Q L + (P DN the -P L) Q DN. Now, when ΔP = P DN -P L, E = a (P DN · Q L -ΔP · Q L) + P DN · Q DN -P L · Q DN) ... (2).

また、変速しない時の総エネルギーＥはQDN≒０であ
るから、 Ｅ＝PL・QL ＝PD・QL−ΔＰ・QL …（３） となる。In addition, the total energy E of when not shifting Q because it is DN ≒ 0, the E = P L · Q L = P D · Q L -ΔP · Q L ... (3).

上記（２）式，（３）式と（１）式とを比較すると明
らかなように、オイルポンプの駆動エネルギーが従来に
比べて、変速時にはΔＰ・QL＋PL・QDNだけ、変速しな
い時にはPDN・QDN＋ΔＰ・QLだけ夫々削減される。この
ように変速時および変速しない時のいずれにおいてもオ
イルポンプの損失エネルギーを大幅に低減できる。Above (2), (3) and (1) and as is apparent from a comparison of expression, driving energy of an oil pump in comparison with the prior art, at the time of shifting by ΔP · Q L + P L · Q DN, no shift sometimes only respectively reduction P DN · Q DN + ΔP · Q L. In this manner, the energy loss of the oil pump can be significantly reduced both during shifting and when not shifting.

〔発明の効果〕〔The invention's effect〕

以上の説明で明らかなように、本発明によれば駆動側
プーリの従動側プーリの油室を第２オイルポンプを介し
て連結したので、変速時にはこの第２オイルポンプを駆
動し、両油室の圧油を給排すればよい。したがって、従
来の変速制御弁のように無駄に排油する油量が非常に少
なく、第１オイルポンプの駆動エネルギーを大幅に削減
できる。また、一方の油室の油圧がライン圧以下になれ
ば、一方弁を介して圧油が補給されるので、ベストスリ
ップを確実に防止できる。As is apparent from the above description, according to the present invention, the oil chamber of the driven pulley of the driving pulley is connected via the second oil pump. Pressure oil may be supplied and discharged. Therefore, the amount of wastefully drained oil like the conventional shift control valve is extremely small, and the driving energy of the first oil pump can be greatly reduced. Further, when the oil pressure in one oil chamber becomes equal to or lower than the line pressure, the pressure oil is supplied via the one valve, so that the best slip can be reliably prevented.

【図面の簡単な説明】[Brief description of the drawings]

第１図は本発明にかかるＶベルト式無段変速機を油圧回
路図、第２図は第２オイルポンプの詳細図、第３図は従
来例の油圧回路図である。 １……Ｖベルト式無段変速機、２……駆動側プーリ、３
……従動側プーリ、5,6……油圧サーボ装置、5a,6a……
油室、10……第１オイルポンプ、11……調圧弁、12,13
……一方弁、14……油路、20……第２オイルポンプ。FIG. 1 is a hydraulic circuit diagram of a V-belt type continuously variable transmission according to the present invention, FIG. 2 is a detailed view of a second oil pump, and FIG. 3 is a hydraulic circuit diagram of a conventional example. 1 ... V-belt type continuously variable transmission, 2 ... Driving pulley, 3
…… Driven pulley, 5,6 …… Hydraulic servo device, 5a, 6a ……
Oil chamber, 10 ... First oil pump, 11 ... Pressure regulating valve, 12,13
... one-way valve, 14 ... oil passage, 20 ... second oil pump.

フロントページの続き (58)調査した分野(Int.Cl.6，ＤＢ名) F16H 59/00 - 61/12 F16H 61/16 - 61/24 F16H 63/40 - 63/48 Continuation of the front page (58) Field surveyed (Int.Cl. 6 , DB name) F16H 59/00-61/12 F16H 61/16-61/24 F16H 63/40-63/48

Claims (1)

(57)【特許請求の範囲】(57) [Claims] 【請求項１】駆動側プーリと従動側プーリの双方にベル
ト巻き掛け径を可変とする油圧サーボ装置を備えたＶベ
ルト式無段変速機において、 第１オイルポンプ10の吐出圧を所定の油圧に調圧する調
圧弁11と、該調圧弁11の出力油圧を駆動側プーリ２の油
室5aと従動側プーリ３の油室6aとに夫々供給する一方弁
12,13と、一方弁12,13の下流側でかつ駆動側プーリ２の
油室5aと従動側プーリ３の油室6aとの間を結ぶ油路14
と、該油路14中に設けられ、可逆的に油を吐出する第２
オイルポンプ20とを備え、該第２オイルポンプ20を駆動
することにより駆動側プーリ２の油室5aと従動側プーリ
３の油室6aとに相互に油圧を給排するようにしたことを
特徴とするＶベルト式無段変速機の油圧制御装置。In a V-belt type continuously variable transmission provided with a hydraulic servo device capable of changing a belt winding diameter on both a driving pulley and a driven pulley, a discharge pressure of a first oil pump is adjusted to a predetermined hydraulic pressure. And a one-way valve for supplying the output oil pressure of the pressure regulating valve 11 to the oil chamber 5a of the driving pulley 2 and the oil chamber 6a of the driven pulley 3, respectively.
An oil passage 14 connecting the oil chamber 5a of the drive-side pulley 2 and the oil chamber 6a of the driven-side pulley 3 downstream of the one-way valves 12 and 13 and the one-way valves 12 and 13;
And a second, which is provided in the oil passage 14 and discharges oil reversibly.
An oil pump 20 is provided, and the second oil pump 20 is driven to mutually supply and discharge oil pressure to and from the oil chamber 5a of the driving pulley 2 and the oil chamber 6a of the driven pulley 3. A hydraulic control device for a V-belt type continuously variable transmission.
JP2278036A 1990-10-16 1990-10-16 Hydraulic control device for V-belt continuously variable transmission Expired - Lifetime JP2975082B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2278036A JP2975082B2 (en) 1990-10-16 1990-10-16 Hydraulic control device for V-belt continuously variable transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2278036A JP2975082B2 (en) 1990-10-16 1990-10-16 Hydraulic control device for V-belt continuously variable transmission

Publications (2)

Publication Number Publication Date
JPH04157256A JPH04157256A (en) 1992-05-29
JP2975082B2 true JP2975082B2 (en) 1999-11-10

Family

ID=17591755

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2278036A Expired - Lifetime JP2975082B2 (en) 1990-10-16 1990-10-16 Hydraulic control device for V-belt continuously variable transmission

Country Status (1)

Country Link
JP (1) JP2975082B2 (en)

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