JPH088356Y2 - Regulator valve device - Google Patents
Regulator valve deviceInfo
- Publication number
- JPH088356Y2 JPH088356Y2 JP1992054522U JP5452292U JPH088356Y2 JP H088356 Y2 JPH088356 Y2 JP H088356Y2 JP 1992054522 U JP1992054522 U JP 1992054522U JP 5452292 U JP5452292 U JP 5452292U JP H088356 Y2 JPH088356 Y2 JP H088356Y2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- spool
- hydraulic
- spring
- oil
- 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 - Fee Related
Links
- 230000001105 regulatory effect Effects 0.000 claims description 39
- 239000000872 buffer Substances 0.000 claims description 7
- 238000004904 shortening Methods 0.000 claims description 3
- 239000003921 oil Substances 0.000 description 69
- 230000005540 biological transmission Effects 0.000 description 10
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 239000010720 hydraulic oil Substances 0.000 description 4
- 230000007257 malfunction Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 230000007935 neutral effect Effects 0.000 description 3
- 238000009825 accumulation Methods 0.000 description 2
- 230000003139 buffering effect Effects 0.000 description 2
- 230000008602 contraction Effects 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 238000012508 change request Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000014509 gene expression Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Landscapes
- Safety Valves (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本考案は、例えば、舶用機関の発
生動力を推進用スクリューに伝達する伝動系に配された
油圧多板クラッチ等、速度２乗比例トルク負荷への駆動
力の係断動作をなす油圧多板クラッチの動作油圧を発生
する油圧回路において、ライン圧を調圧すべく用いられ
る調圧弁装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to, for example, engagement / disengagement of a driving force to a speed squared torque load, such as a hydraulic multi-plate clutch arranged in a transmission system for transmitting power generated by a marine engine to a propelling screw. The present invention relates to a pressure regulating valve device used for regulating a line pressure in a hydraulic circuit that generates an operating hydraulic pressure of an operating hydraulic multi-plate clutch.
【０００２】[0002]
【従来の技術】舶用機関の発生動力を推進用スクリュー
に伝達する船舶の伝動系においては、この伝動の係断手
段として、係合及び遮断が滑らかに行われる油圧多板ク
ラッチが一般的に用いられている。ところが、前記スク
リューは回転速度の２乗に比例するトルクを要する負荷
（速度２乗比例トルク負荷）であることから、前記伝動
系において用いる油圧多板クラッチにおいては、減速機
等の負荷側の伝動装置における係合ショックの発生及び
これに伴う損傷を防止すべく、係合操作がなされてから
定常の伝達トルクに達するまでの間、負荷側の加速度が
一定に保たれるような係合特性、換言すれば、負荷側の
回転速度が時間と共に比例的に増大するような係合特性
を有することが要求されている。2. Description of the Related Art In a transmission system of a ship that transmits the power generated by a marine engine to a propelling screw, a hydraulic multi-plate clutch, which is smoothly engaged and disengaged, is generally used as an engagement / disengagement means for this transmission. Has been. However, since the screw is a load that requires a torque proportional to the square of the rotational speed (speed squared proportional torque load), in the hydraulic multi-plate clutch used in the transmission system, the transmission on the load side such as a reduction gear is performed. In order to prevent the occurrence of engagement shock in the device and the resulting damage, the engagement characteristics such that the acceleration on the load side is kept constant from the time when the engagement operation is performed until the steady transmission torque is reached, In other words, it is required to have an engagement characteristic such that the rotation speed on the load side increases proportionally with time.
【０００３】この要求は、前記油圧多板クラッチの動作
油圧を発生する油圧回路において、動作油圧の送給開始
時点からの経過時間の２乗に比例して増大するライン圧
の増加特性を得ることにより達成される。このことに着
目し本願出願人は、前述したライン圧の増加特性を実現
する調圧弁装置を、特開平３−１６８４２０号に提案し
ている。図３は、この調圧弁装置及びこれを用いて構成
された油圧回路の模式図である。This demand is to obtain an increase characteristic of the line pressure which increases in proportion to the square of the elapsed time from the start of feeding the operating hydraulic pressure in the hydraulic circuit for generating the operating hydraulic pressure of the hydraulic multi-plate clutch. Achieved by With this in mind, the applicant of the present application has proposed a pressure regulating valve device that realizes the above-described increase characteristic of the line pressure in Japanese Patent Laid-Open No. 3-168420. FIG. 3 is a schematic diagram of this pressure regulating valve device and a hydraulic circuit configured using the same.
【０００４】図示の如く調圧弁装置１は、スプール室17
の内部に同軸的に配された排圧スプール10と制御スプー
ル13とを備え、これらのスプール10，13間に両者を離反
する向きに付勢する第１ばね11を介在させ、またスプー
ル室17内周の段部と制御スプール13との間に、第１ばね
11と同向きの付勢を行う第２ばね12を介在させた構成と
なっており、油圧ポンプ４からクローズドセンター形の
操作弁２を経て油圧多板クラッチに連なる油圧回路のラ
イン圧は、スプール室17の一側の油室14に導圧孔15を経
て導入され、排圧スプール10の一面に直接作用する一
方、スプール室17の他側の油室16に制御絞り５及び遅延
弁３を経て導入され、制御スプール13の一面に作用する
ようになしてある。As shown, the pressure regulating valve device 1 includes a spool chamber 17
Is equipped with a discharge pressure spool 10 and a control spool 13 which are coaxially arranged inside, and a first spring 11 for biasing the spools 10 and 13 in a direction to separate them is interposed, and a spool chamber 17 A first spring is provided between the step on the inner circumference and the control spool 13.
A second spring 12 that biases in the same direction as 11 is interposed, and the line pressure of the hydraulic circuit that connects the hydraulic pump 4 through the closed center type operation valve 2 to the hydraulic multi-plate clutch is the spool. It is introduced into the oil chamber 14 on one side of the chamber 17 through the pressure guide hole 15 and acts directly on one surface of the pressure exhaust spool 10, while the control throttle 5 and the delay valve 3 are provided on the oil chamber 16 on the other side of the spool chamber 17. The control spool 13 is introduced into the control spool 13 so as to act on one surface thereof.
【０００５】油圧多板クラッチへのライン圧の送給，非
送給の切換えは、切換レバ21の操作により操作弁２のス
プール20を移動させて行われる。一方遅延弁３は、コイ
ルばね31のばね力によるスプール30の付勢により、通常
は図示の切換え位置、即ち、調圧弁装置１の制御スプー
ル13の一側の油室16にライン圧を導入する切換え位置を
保っている。操作弁２のスプール20と遅延弁３のスプー
ル30とは、図示の如く関連させてあり、操作弁２の切換
え操作が行われた場合、これに伴うスプール20の移動に
よりスプール30が押圧される結果、遅延弁３の切換え位
置は一時的に他方に切り換わり、その後、コイルばね31
のばね力により図示の切換え位置に復帰するようになっ
ている。The line pressure is switched between being fed and not fed to the hydraulic multi-plate clutch by operating the switching lever 21 to move the spool 20 of the operating valve 2. On the other hand, the delay valve 3 normally introduces a line pressure into the switching position shown in the drawing, that is, the oil chamber 16 on one side of the control spool 13 of the pressure regulating valve device 1 by the biasing of the spool 30 by the spring force of the coil spring 31. The switching position is maintained. The spool 20 of the operation valve 2 and the spool 30 of the delay valve 3 are associated with each other as shown in the drawing. When the switching operation of the operation valve 2 is performed, the spool 30 is pressed by the movement of the spool 20 accompanying this. As a result, the switching position of the delay valve 3 is temporarily switched to the other, and then the coil spring 31
The spring force returns the switching position to the illustrated switching position.
【０００６】その他33は絞りであり、スプール30の復帰
動作はこの絞り33を介して油タンクの油を吸込みつつ行
われる。 The other 33 is an aperture for returning the spool 30.
The operation is performed while sucking the oil in the oil tank through this throttle 33.
Be seen.
【０００７】以上の如き構成の油圧回路においては、操
作弁２が図示のニュートラル位置にある場合、該操作弁
２がクローズドセンター形であることから所定のライン
圧が生じており、調圧弁装置１の排圧スプール10及び制
御スプール13は、前記ライン圧の受圧により夫々図示の
位置にある。そして、油圧多板クラッチを正転又は逆転
動作させるべく操作弁２の切換え操作が行われた場合、
この操作に伴う遅延弁３の切換え位置の変化により油室
16の内圧が一旦失われ、制御スプール13は、第２ばね12
の付勢によりスプール室17の左端にまで移動し、またこ
の移動に伴う第１ばね11の伸長により、該ばね11の付勢
力が減じられる結果、ライン圧を低圧源に排圧するリリ
ーフ動作が行われ、操作弁２を経て油圧多板クラッチに
送給されるライン圧は低圧状態に保たれる。In the hydraulic circuit configured as described above, when the operation valve 2 is in the neutral position shown in the figure, a predetermined line pressure is generated because the operation valve 2 is a closed center type, and the pressure regulating valve device 1 The exhaust pressure spool 10 and the control spool 13 are in the positions shown in the figure due to the reception of the line pressure. When the switching operation of the operation valve 2 is performed to rotate the hydraulic multi-plate clutch in the normal or reverse direction,
Due to the change in the switching position of the delay valve 3 accompanying this operation, the oil chamber
Once the internal pressure of 16 is lost, the control spool 13 moves to the second spring 12
Is moved to the left end of the spool chamber 17, and the extension of the first spring 11 due to this movement reduces the urging force of the spring 11, resulting in a relief operation for discharging the line pressure to a low pressure source. The line pressure sent to the hydraulic multi-plate clutch via the operation valve 2 is kept low.
【０００８】その後、遅延弁３の前述した復帰と共に油
室16へのライン圧の供給が再開されるが、この供給は制
御絞り５を経て行われるため、油室16の内圧を受圧する
制御スプール13は除々に右方に移動し、この移動に伴う
第１ばね11の縮短により排圧スプール10への付勢力が高
まる結果、操作弁２を経て油圧多板クラッチに送給され
るライン圧は除々に増大する。以上の如き動作の間、油
圧多板クラッチへの潤滑油の供給は、操作弁２の上流側
にて分岐された油路により絞り６を経て安定して行われ
ている。After that, the supply of the line pressure to the oil chamber 16 is restarted when the delay valve 3 is restored as described above. Since this supply is performed via the control throttle 5, the control spool for receiving the internal pressure of the oil chamber 16 is restarted. 13 gradually moves to the right, and the urging force to the exhaust pressure spool 10 increases due to the contraction of the first spring 11 due to this movement, and as a result, the line pressure sent to the hydraulic multi-plate clutch via the operation valve 2 is reduced. It gradually increases. During the operation as described above, the supply of the lubricating oil to the hydraulic multi-plate clutch is stably performed via the throttle 6 by the oil passage branched on the upstream side of the operation valve 2.
【０００９】前記特開平３−１６８４２０号公報には、
送給開始時点からの経過時間の２乗に比例して増大する
ライン圧の増加特性、即ち、ライン圧Ｐ＝α＋βｔ2 な
る特性は、リリーフ動作が生じるまでの排圧スプール10
の移動距離をａ、第２ばね12の与圧縮長さをｂとし、ま
た制御絞り５の流量係数をｃ、同じく絞り面積をｓ0と
し、更に油の比重をρとするとき、第１ばね11及び第２
ばね12夫々のばね定数ｋ1 及びｋ2 と、排圧スプール10
及び制御スプール13夫々の受圧面積ｓ及びＳとを、前記
α及びβを含む次式の関係を満足するように設定するこ
とにより実現し得ることが示されている。Japanese Patent Laid-Open No. 168420/1993 discloses that
The increase characteristic of the line pressure that increases in proportion to the square of the elapsed time from the start of feeding, that is, the characteristic of the line pressure P = α + βt 2 is that the exhaust pressure spool 10 until the relief operation occurs.
Is a, the compression length of the second spring 12 is b, the flow coefficient of the control throttle 5 is c, the throttle area is s 0, and the specific gravity of the oil is ρ. 11 and 2
The springs 12 have spring constants k 1 and k 2 , respectively, and the exhaust pressure spool 10
It is shown that it can be realized by setting the pressure receiving areas s and S of the control spool 13 and the pressure receiving areas s and S of the control spool 13 so as to satisfy the relationship of the following equation including α and β.
【００１０】[0010]
【数１】 [Equation 1]
【００１１】図４は、以上の各式の関係を満たす調圧弁
装置１を備えた前述の油圧回路において得られるライン
圧の増加特性を示すグラフである。調圧弁装置１及び遅
延弁３の前述した動作により、ライン圧Ｐは、操作弁２
の係合側への切換え操作がなされた直後においては低圧
（＝α）に保たれ、所定の遅延時間ｔ0 の経過後に増加
を始め、以後は、所定の増加率（＝β）にて経過時間ｔ
の２乗に比例して増加し、所定時間ｔE の経過後に定常
ライン圧Ｐ0 に達して安定化する。このような増加特性
は、駆動源と速度２乗比例負荷とを係断する油圧多板ク
ラッチにおいて好ましいことは前述した如くである。FIG. 4 is a graph showing an increase characteristic of the line pressure obtained in the above hydraulic circuit provided with the pressure regulating valve device 1 satisfying the relationships of the above equations. Due to the above-described operations of the pressure regulating valve device 1 and the delay valve 3, the line pressure P is reduced to the operating valve 2
Immediately after the switching operation to the engaging side is performed, the pressure is maintained at a low pressure (= α) and starts increasing after the elapse of a predetermined delay time t 0 , and thereafter, at a predetermined increase rate (= β). Time t
Increases in proportion to the square of, and reaches a steady line pressure P 0 and stabilizes after a lapse of a predetermined time t E. As described above, such an increasing characteristic is preferable in the hydraulic multi-plate clutch that disconnects the drive source and the speed-squared proportional load.
【００１２】また、遅延弁３の動作により得られる前記
遅延時間ｔ0 により、油圧多板クラッチにおける実際の
係合の開始と共にライン圧の増加が始まることから、油
圧多板クラッチのサイズ、摩擦板相互間の初期隙間の大
小、定常回転数の高低及び油温の高低等、油圧多板クラ
ッチ側での条件の如何に拘わらず適正な係合特性が得ら
れることになる。Further, since the delay time t 0 obtained by the operation of the delay valve 3 causes the line pressure to start increasing with the actual engagement of the hydraulic multi-plate clutch, the size of the hydraulic multi-plate clutch and the friction plate are increased. Appropriate engagement characteristics can be obtained regardless of the conditions on the hydraulic multi-disc clutch side, such as the size of the initial clearance between them, the level of steady-state rotation speed, and the level of oil temperature.
【００１３】[0013]
【考案が解決しようとする課題】ところが、以上の如き
調圧弁装置１においては、第１ばね11及び第２ばね12夫
々のばね定数ｋ1 及びｋ2 と、排圧スプール10及び制御
スプール13夫々の受圧面積ｓ及びＳとは、主として (3)
式を満たすべく決定されており、その後の変更が困難で
ある一方、これらの各値を含む (2)式により定まるライ
ン圧Ｐの増加率βは、負荷側の要求に合わせて種々に変
更することが要求され、この変更要求に応えるには、
(2)式中のＫ0 を変更すべく、高精度での加工を要する
制御絞り５の絞り面積ｓ0 を種々に変更することが必要
となる難点があった。However, in the pressure regulating valve device 1 as described above, the spring constants k 1 and k 2 of the first spring 11 and the second spring 12, respectively, and the exhaust pressure spool 10 and the control spool 13 are respectively provided. The pressure receiving areas s and S of (3)
Although it is determined to satisfy the formula and it is difficult to change it thereafter, the increase rate β of the line pressure P determined by the formula (2) including each of these values is changed variously according to the demand on the load side. To meet this change request,
In order to change K 0 in the equation (2), there is a drawback that it is necessary to change variously the aperture area s 0 of the control aperture 5 which requires highly accurate processing.
【００１４】また、特に、ライン圧の緩やかな増加が要
求される場合には、前記制御絞り５の絞り面積ｓ0 を可
及的に０に近づけることが必要とされ、極小径の絞り孔
の加工に多大の工数を要する。また、制御スプール13の
わずかな加工誤差に伴って生じる外周からの漏れにより
所望の特性が得られなくなる難点があり、特に、前記漏
れ量が制御絞り５からの流入量に等しくなった場合には
作動停止に至る。更には、油中のわずかな異物により制
御絞り５の絞り孔に詰まりが生じ、作動不良に陥る虞も
ある。従って、制御絞り５の絞り面積ｓ0 を小さくする
ことには限度がある。更に従来装置にあっては、例えば
油圧多板クラッチの機種を大型のもの又は小型のもの等
に変更する都度、夫々に応じた遅延動作を得るために夫
々の機種に応じた油圧流量に応じて絞り33を適正に選定
する必要があるという問題があった。 Further, particularly when a gradual increase in the line pressure is required, it is necessary to make the throttle area s 0 of the control throttle 5 as close to 0 as possible, and it is possible to reduce the diameter of the throttle hole having an extremely small diameter. A large number of man-hours are required for processing. Further, there is a problem that desired characteristics cannot be obtained due to leakage from the outer circumference caused by a slight machining error of the control spool 13. Especially, when the leakage amount becomes equal to the inflow amount from the control throttle 5, Leading to a shutdown. Furthermore, there is a possibility that a small amount of foreign matter in the oil may cause clogging of the throttle hole of the control throttle 5, resulting in malfunction. Therefore, there is a limit to reducing the aperture area s 0 of the control aperture 5. Further, in the conventional device, for example,
Large or small hydraulic multi-disc clutch model
Every time you change to a husband to get a delay action according to each
Properly select the throttle 33 according to the hydraulic flow rate according to each model
There was a problem that I had to do.
【００１５】本考案は斯かる事情に鑑みてなされたもの
であり、制御絞りの絞り面積の変更によらずに特性の変
更が可能であり、また緩やかな増加率での増加特性を確
実に得ることができ、更に油中の異物の影響による動作
不良の発生の虞もなく、加えて油圧多板クラッチの機種
変更等に際しても絞りの交換の必要のない調圧弁装置を
提供することを目的とする。The present invention has been made in view of such circumstances, and the characteristics can be changed without changing the throttle area of the control diaphragm, and the increasing characteristics at a moderate increasing rate can be reliably obtained. In addition, there is no risk of malfunction occurring due to the influence of foreign matter in the oil , and in addition to the hydraulic multi-disc clutch model
It is an object of the present invention to provide a pressure regulating valve device that does not require replacement of the throttle even when changing .
【００１６】[0016]
【課題を解決するための手段】本考案に係る調圧弁装置
は、油圧回路のライン圧を受圧して移動し、リリーフ動
作をなす排圧スプールと、その一側の油室に制御絞りを
介して導入される前記ライン圧を受圧し、第２ばねの付
勢に抗して移動する制御スプールとの間に、夫々の移動
を制限する向きに付勢する第１ばねを介装してなり、前
記制御スプールの移動に伴う第１ばねの縮短により前記
排圧スプールへの付勢力を抑制し、駆動源と速度２乗比
例トルク負荷とを係断する油圧多板クラッチに送給され
る前記ライン圧を調圧する調圧弁装置において、前記油
圧多板クラッチへの前記動作油圧の送給，非送給の切換
えを行う操作弁と、該操作弁の切換え動作開始に伴うそ
のスプールの移動により、前記制御絞りを閉止し、切換
え動作終了に伴うそのスプールの復帰により前記制御絞
りを開放する遅延弁と、前記油圧多板クラッチへの送給
油量に応じた圧力差をその前，後に発生し、その圧力差
に対応して前記遅延弁のスプールの復帰動作を緩衝する
緩衝絞りとを備えると共に、前記油室に並設されて、該
油室への導入流量を分流して蓄圧するアキュムレータを
具備することを特徴とする。SUMMARY OF THE INVENTION A pressure regulating valve device according to the present invention receives a line pressure of a hydraulic circuit and moves to perform a relief operation of an exhaust pressure spool and an oil chamber on one side thereof via a control throttle. And a control spool that receives the line pressure introduced by the second spring and moves against the urging of the second spring. The reduction of the first spring caused by the movement of the control spool suppresses the urging force to the exhaust pressure spool, and is fed to the hydraulic multi-plate clutch that disconnects the drive source and the speed squared proportional torque load. In the pressure regulating valve device for regulating the line pressure, the oil
Switching between feeding and non-feeding of the operating hydraulic pressure to the pressure plate clutch
Operation valve and the operation valve that starts switching operation.
The control throttle is closed and switched by moving the spool of
The control throttle is stopped by the return of the spool at the end of the operation.
Delay valve to open the valve and feed to the hydraulic multi-disc clutch.
A pressure difference depending on the amount of oil is generated before and after, and the pressure difference
Corresponding to, buffering the return operation of the delay valve spool
A buffer throttle is provided, and an accumulator that is provided in parallel with the oil chamber and divides the flow rate of the gas introduced into the oil chamber to accumulate the pressure is provided.
【００１７】[0017]
【作用】本考案においては、制御スプールの一側の油室
に、制御絞りを経てライン圧が導入されると同時に、こ
の導入圧が前記油室に並設されたアキュムレータにも導
入され、該アキュムレータの蓄圧分流作用により制御ス
プールへの付勢力が緩和される結果、ライン圧の増加率
が、制御絞りの絞り面積と共にアキュムレータの容量に
よっても支配され、制御絞りの絞り面積を変更すること
なく、アキュムレータ側での設計変更による特性変更が
可能であり、また大なる絞り面積を有する制御絞りの採
用により、油中の異物の影響による動作不良の発生が回
避される。更に操作弁の切換え動作開始に伴う遅延弁の
スプールの移動により、制御絞りを閉止し、また切換え
動作終了に伴うスプールの復帰により制御絞りを開放す
ることとしたから、油圧多板クラッチの作動油流量によ
って絞り効果のタイミングが自動的に変化し、作動油流
量の変化の如何にかかわらず適正な絞りのタイミングが
得られることとなる。 In the present invention, the line pressure is introduced into the oil chamber on one side of the control spool through the control throttle, and at the same time, the introduced pressure is also introduced into the accumulators arranged in parallel in the oil chamber. As a result of the urging force on the control spool being relieved by the pressure-accumulation diversion action of the accumulator, the rate of increase in line pressure is governed by the capacity of the accumulator as well as the throttle area of the control throttle, without changing the throttle area of the control throttle. The characteristics can be changed by changing the design on the accumulator side, and the adoption of a control throttle having a large throttle area prevents the occurrence of malfunctions due to the influence of foreign matter in the oil. In addition, the delay valve
Control spool is closed and switched by moving the spool
The control throttle is opened by returning the spool at the end of operation.
Therefore, it depends on the hydraulic oil flow rate of the hydraulic multi-disc clutch.
Therefore, the timing of the throttling effect changes automatically,
Regardless of the amount change
Will be obtained.
【００１８】[0018]
【実施例】以下本考案をその実施例を示す図面に基づい
て詳述する。図１は本考案に係る調圧弁装置を用い、油
圧多板クラッチの動作油圧を発生すべく構成された油圧
回路の模式図である。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below in detail with reference to the drawings showing its embodiments. FIG. 1 is a schematic diagram of a hydraulic circuit configured to generate operating hydraulic pressure of a hydraulic multi-plate clutch using the pressure regulating valve device according to the present invention.
【００１９】この油圧回路は、ライン圧を調圧するため
の本考案に係る調圧弁装置１、図示しない油圧多板クラ
ッチへの動作油圧の送給，非送給の切換えを行うための
操作弁２、該操作弁２の切換え動作に後述の如く応動す
る遅延弁３、及び油圧発生源たる油圧ポンプ４を備えて
なる。図２は、調圧弁装置１、操作弁２及び遅延弁３を
共通のハウジング内に一体的に構成してある弁装置の断
面図を示すが、これらを別個に構成してもよいことは言
うまでもない。This hydraulic circuit includes a pressure regulating valve device 1 according to the present invention for regulating the line pressure, and an operating valve 2 for switching between feeding and non-feeding of operating hydraulic pressure to a hydraulic multi-plate clutch (not shown). A delay valve 3 that responds to the switching operation of the operation valve 2 as described later, and a hydraulic pump 4 that is a hydraulic pressure generation source. FIG. 2 shows a sectional view of a valve device in which the pressure regulating valve device 1, the operation valve 2 and the delay valve 3 are integrally formed in a common housing, but it goes without saying that these may be separately formed. Yes.
【００２０】本考案に係る調圧弁装置１は、共通のスプ
ール室17の内部に同軸上での摺動自在に配された排圧ス
プール10と制御スプール13とを備え、これらの対向面間
に、両者を離反する向きに付勢する第１ばね11を介装す
る一方、前記制御スプール13を、スプール室17内周の段
部との間に介装した第２ばね12により、第１ばね11と同
向きに付勢してなる。The pressure regulating valve device 1 according to the present invention is provided with an exhaust pressure spool 10 and a control spool 13 which are coaxially slidably arranged inside a common spool chamber 17, and between these facing surfaces. , A first spring 11 for urging the two in a direction to separate them from each other, and a second spring 12 for interposing the control spool 13 between the control spring 13 and a step portion on the inner circumference of the spool chamber 17 Biased in the same direction as 11.
【００２１】排圧スプール10の長手方向の略中央に周設
された環状溝は、スプール室17の内部において油圧ポン
プ４の吐出側に常時連通され、ライン圧が直接的に導入
されるようになしてあり、この導入油圧は、排圧スプー
ル10に穿設された導圧孔15を経てスプール室17一側の油
室14に導かれている。而して排圧スプール10は、油室14
に導入されるライン圧を面積ｓなるその一面に受圧し、
第１ばね11の付勢に抗して移動することになり、図１に
示す所定距離ａだけ移動したとき、前記環状溝を介して
ライン圧を排圧するリリーフ動作をなし、後述の如く油
圧多板クラッチに送給されるライン圧は、排圧スプール
10のリリーフ動作が生じる際の圧力を上限として調圧さ
れる。An annular groove provided around the center of the exhaust pressure spool 10 in the longitudinal direction is constantly communicated with the discharge side of the hydraulic pump 4 inside the spool chamber 17 so that the line pressure is directly introduced. This introduced hydraulic pressure is guided to the oil chamber 14 on one side of the spool chamber 17 via the pressure guiding hole 15 formed in the exhaust pressure spool 10. Thus, the exhaust pressure spool 10 has an oil chamber 14
Receives the line pressure introduced to the one side of the area s,
The first spring 11 moves against the urging force, and when it moves a predetermined distance a shown in FIG. 1, a relief operation for discharging the line pressure through the annular groove is performed. The line pressure sent to the plate clutch is the exhaust pressure spool.
The pressure is adjusted with the upper limit of the pressure when the relief operation of 10 occurs.
【００２２】一方、制御スプール13の面積Ｓなる受圧面
は、スプール室17他側の油室16に臨ませてあり、この油
室16は、制御絞り５及び遅延弁３を介して油圧ポンプ４
の吐出側に連通されている。而して、制御スプール13
は、制御絞り５を経て油室16に導入されるライン圧を受
圧し、第１ばね11及び第２ばね12の付勢に抗して図の右
方向に移動するが、この移動に応じて第１ばね11が縮短
する結果、該ばね11による排圧スプール10の付勢力は、
制御スプール13の移動に伴って強化される。即ち、排圧
スプール10への付勢力が制御スプール13の移動により抑
制されることになり、該排圧スプール10のリリーフ動作
により調圧されるライン圧は、制御スプール13が移動範
囲の左端にあるとき最低となり、右向きへの移動に伴っ
て増大する。なお制御スプール13を付勢する第２ばね12
には、組立ての段階において所定の与圧縮量ｂが与えら
れている。On the other hand, the pressure receiving surface having the area S of the control spool 13 faces the oil chamber 16 on the other side of the spool chamber 17, and this oil chamber 16 is provided with the hydraulic pump 4 via the control throttle 5 and the delay valve 3.
Is connected to the discharge side of. Thus, the control spool 13
Receives the line pressure introduced into the oil chamber 16 through the control throttle 5 and moves to the right in the figure against the bias of the first spring 11 and the second spring 12, but according to this movement. As a result of the contraction of the first spring 11, the urging force of the spring 11 by the spring 11 is
It is strengthened as the control spool 13 moves. That is, the urging force on the exhaust pressure spool 10 is suppressed by the movement of the control spool 13, and the line pressure adjusted by the relief operation of the exhaust pressure spool 10 is at the left end of the moving range of the control spool 13. It becomes the lowest at some time, and increases with the movement to the right. The second spring 12 that biases the control spool 13
Is given a predetermined compression amount b at the assembly stage.
【００２３】以上の構成は、図３に示す従来の調圧弁装
置１と同様であるが、本考案に係る調圧弁装置１は、更
に加えて、前記油室16への導入油を分流して蓄圧するア
キュムレータ７を備えている。このアキュムレータ７
は、図２に示す如く、スプール室17の一側に並設したシ
リンダ室18の内部に軸長方向への摺動自在に受圧ピスト
ン70を嵌挿し、これをシリンダ室18に内蔵された緩衝ば
ね71により付勢して、受圧ピストン70の他側に形成され
た油室72の内圧を、緩衝ばね71の縮短エネルギとして蓄
圧するばね式のアキュムレータである。アキュムレータ
７の油室72は、調圧弁装置１の油室16に連通されてお
り、該油室16への導入油圧が並行して導入されるように
なっている。The above construction is similar to that of the conventional pressure regulating valve apparatus 1 shown in FIG. 3, but the pressure regulating valve apparatus 1 according to the present invention additionally divides the introduced oil into the oil chamber 16. An accumulator 7 for accumulating pressure is provided. This accumulator 7
As shown in FIG. 2, a pressure receiving piston 70 is slidably inserted in a cylinder chamber 18 arranged side by side on one side of the spool chamber 17 so as to be slidable in the axial direction. It is a spring type accumulator that is biased by a spring 71 to store the internal pressure of an oil chamber 72 formed on the other side of the pressure receiving piston 70 as the shortening energy of the buffer spring 71. The oil chamber 72 of the accumulator 7 is communicated with the oil chamber 16 of the pressure regulating valve device 1, and the introduced hydraulic pressure to the oil chamber 16 is introduced in parallel.
【００２４】さて、前述の如く調圧されるライン圧は、
操作弁２を介して図示しない油圧多板クラッチに送給さ
れている。操作弁２は、図示の切換え位置（ニュートラ
ル位置）にあるときライン圧がブロックされるクローズ
ドセンター形の弁であり、図１の下位置又は上位置への
切換えにより、油圧多板クラッチの正転又は逆転用の作
動シリンダに連なる給油ポートＣ1 又はＣ2 にライン圧
が与えられるようになっている。この切換えは、例え
ば、切換レバ21の手動操作によりスプール20を移動させ
て行われる。The line pressure adjusted as described above is
It is fed to a hydraulic multi-plate clutch (not shown) via the operation valve 2. The operation valve 2 is a closed center type valve in which the line pressure is blocked when it is in the illustrated switching position (neutral position), and the normal rotation of the hydraulic multi-plate clutch is changed by switching to the lower position or the upper position in FIG. Alternatively, the line pressure is applied to the oil supply port C 1 or C 2 connected to the working cylinder for reverse rotation. This switching is performed, for example, by moving the spool 20 by manually operating the switching lever 21.
【００２５】一方、調圧弁装置１の前記油室16へのライ
ン圧の導入、遮断の切換え動作をなす前記遅延弁３は、
コイルばね31により付勢されたスプール30を有し、通常
は図示の切換え位置、即ち前記油室16にライン圧を導入
する切換え位置（導入位置）を保っている。操作弁２の
スプール20と遅延弁３のスプール30とは、図１に示す如
く関連させてあり、操作弁２の切換え操作が行われた場
合、これに伴うスプール20の移動によりスプール30が押
圧される結果、遅延弁３の切換え位置は一時的に他方
（遮断位置）に切り換わり、その後、コイルばね31のば
ね力により図示の切換え位置に復帰するようになしてあ
る。On the other hand, the delay valve 3 which performs the switching operation of introducing and shutting off the line pressure into the oil chamber 16 of the pressure regulating valve device 1,
It has a spool 30 biased by a coil spring 31, and normally maintains the illustrated switching position, that is, the switching position (introduction position) for introducing the line pressure into the oil chamber 16. The spool 20 of the operation valve 2 and the spool 30 of the delay valve 3 are associated with each other as shown in FIG. 1. When the switching operation of the operation valve 2 is performed, the spool 30 is pressed by the movement of the spool 20 accompanying this. As a result, the switching position of the delay valve 3 is temporarily switched to the other (cutoff position), and thereafter, the spring force of the coil spring 31 returns the switching position to the illustrated switching position.
【００２６】遅延弁３のスプール30にはまた、油圧ポン
プ４から操作弁２を経て油圧多板クラッチに至る送給ラ
インの中途に配した絞り34の前後に生じる圧力差が、前
記コイルばね31による付勢方向とは逆向きに作用させて
あり、操作弁２の切換え操作後におけるスプール30の復
帰動作は、前記圧力差によるスプール30への付与力がコ
イルばね31のばね力を上回っている間は生じないように
なしてある。The spool 30 of the delay valve 3 also has a pressure difference generated before and after the throttle 34 arranged in the middle of the feed line from the hydraulic pump 4 to the hydraulic multi-plate clutch via the operation valve 2 to the coil spring 31. In the return operation of the spool 30 after the switching operation of the operation valve 2, the force exerted on the spool 30 by the pressure difference exceeds the spring force of the coil spring 31. There is no gap.
【００２７】操作弁２及び遅延弁３の実際の構成、並び
に制御絞り５及び絞り34の配置は、例えば、図２に示す
如くである。操作弁２のスプール20は、軸心回りの回転
により前述した切換え動作をなす回転スプールであり、
外周面に各切換え位置に対応する凹所が形成されてい
る。一方、遅延弁３のスプール30は、中途部に油路切換
え用の環状溝 30a,30bを備え、軸長方向への移動により
前述した切換え動作をなす往復動スプールであり、該ス
プール30の基端は、先端側を付勢するコイルばね31のば
ね力により係合ボール32を介してスプール20に押付けら
れている。The actual configuration of the operation valve 2 and the delay valve 3 and the arrangement of the control throttle 5 and the throttle 34 are as shown in FIG. 2, for example. The spool 20 of the operation valve 2 is a rotary spool that performs the above-described switching operation by rotating about the axis,
Recesses corresponding to each switching position are formed on the outer peripheral surface. On the other hand, the spool 30 of the delay valve 3 is a reciprocating spool that is provided with annular grooves 30a and 30b for switching oil passages in the middle thereof and that performs the switching operation described above by moving in the axial direction. The end is pressed against the spool 20 via the engaging ball 32 by the spring force of the coil spring 31 that urges the tip side.
【００２８】而して、操作弁２のスプール20がいずれか
の切換え位置にある場合、該スプール20外周の凹所と前
記係合ボール32とが係合し、遅延弁３のスプール30は図
示の位置にあり、制御スプール13の一側に形成された油
室16は、環状溝 30aを介して制御絞り５を備えた油路に
連通され、該制御絞り５を介してライン圧Ｐが導入され
る。一方、操作弁２の切換え操作が行われている間に
は、前記スプール20の外周に係合ボール32が転接するよ
うになる結果、遅延弁３のスプール30は、コイルばね31
の付勢に抗して図示の位置よりも左方に移動し、制御絞
り５を備えた油路の開口端が環状溝 30a,30b間のランド
により閉止され、油室16へのライン圧Ｐの導入が断た
れ、前記油室16は環状溝 30bを介して低圧源に連通され
るようになり、更に、前記切換えのためのスプール20の
回転が終了した時点においては、再度生じる前記係合に
よりスプール30が左位置に復帰し、制御絞り５を備えた
油路の開口端が開放され、油室16へのライン圧Ｐの導入
が再開される。Thus, when the spool 20 of the operation valve 2 is in any of the switching positions, the recess on the outer periphery of the spool 20 and the engaging ball 32 are engaged with each other, and the spool 30 of the delay valve 3 is illustrated. The oil chamber 16 formed at one side of the control spool 13 is communicated with the oil passage provided with the control throttle 5 via the annular groove 30a, and the line pressure P is introduced via the control throttle 5. To be done. On the other hand, while the operation valve 2 is being switched, the engagement ball 32 comes into rolling contact with the outer periphery of the spool 20. As a result, the spool 30 of the delay valve 3 is coil spring 31.
It moves to the left of the position shown in the figure against the urging force of the valve, the opening end of the oil passage having the control throttle 5 is closed by the land between the annular grooves 30a and 30b, and the line pressure P to the oil chamber 16 is increased. Is cut off, the oil chamber 16 is communicated with the low pressure source through the annular groove 30b, and when the rotation of the spool 20 for the switching is completed, the engagement that occurs again occurs. The spool 30 is returned to the left position by the control aperture 5.
The open end of the oil passage is opened, and the introduction of the line pressure P into the oil chamber 16 is restarted.
【００２９】スプール30の先端には、ピストン板35が連
設されている。該ピストン板35の両側の油室は、油圧ポ
ンプ４の吐出側から操作弁２に至る間に、コイルばね31
による付勢側を下流側として組み込まれており、前記絞
り34は、図示の如く、ピストン板35を表裏に貫通する貫
通孔として構成されている。これにより絞り34の前後に
は、油圧ポンプ４から操作弁２に向かう油の流れ、換言
すれば、油圧多板クラッチへの送給油の流れの多少に応
じて高低となる圧力差が発生することになり、この圧力
差が、スプール30先端のピストン板35に、コイルばね31
による付勢方向と逆向き（図における左向き）の押圧力
を加え、該スプール30の前述した復帰を遅延させる作用
をなす。A piston plate 35 is connected to the tip of the spool 30. The oil chambers on both sides of the piston plate 35 have coil springs 31 between the discharge side of the hydraulic pump 4 and the operation valve 2.
The urging side is incorporated as the downstream side, and the diaphragm 34 is configured as a through hole that penetrates the piston plate 35 in the front and back as shown in the drawing. As a result, before and after the throttle 34, a pressure difference becomes high and low depending on the flow of oil from the hydraulic pump 4 toward the operation valve 2, that is, the flow of oil supplied to the hydraulic multi-plate clutch. This pressure difference causes the coil spring 31
A pressing force is applied in the direction opposite to the biasing direction (to the left in the figure) by the action of delaying the return of the spool 30 described above.
【００３０】さて、以上の如き調圧弁装置１を備えた油
圧回路において、操作弁２がニュートラル位置にある場
合、該操作弁２がクローズドセンター形であることから
所定のライン圧が生じており、このライン圧の受圧によ
り調圧弁装置１の排圧スプール10及び制御スプール13
は、夫々図１に示す位置にある。In the hydraulic circuit provided with the pressure regulating valve device 1 as described above, when the operation valve 2 is in the neutral position, a predetermined line pressure is generated because the operation valve 2 is a closed center type. By receiving this line pressure, the exhaust pressure spool 10 and the control spool 13 of the pressure regulating valve device 1
Are in the positions shown in FIG. 1, respectively.
【００３１】その後、油圧多板クラッチを正転又は逆転
動作させるべく操作弁２の切換え操作が行われた場合、
この操作に伴う遅延弁３の切換え位置の変化により油室
16の内圧が一旦失われ、制御スプール13が第２ばね12の
付勢により弁室17の左端にまで移動し、この移動に伴う
第１ばね11の伸長により該ばね11の付勢力が減じられる
結果、排圧スプール10が左方に移動し、ライン圧を低圧
源に排圧するリリーフ動作が行われ、操作弁２を経て油
圧多板クラッチに送給されるライン圧は低圧状態に保た
れる。After that, when the switching operation of the operation valve 2 is performed in order to rotate the hydraulic multi-plate clutch in the normal or reverse direction,
Due to the change in the switching position of the delay valve 3 accompanying this operation, the oil chamber
The internal pressure of 16 is once lost, the control spool 13 is moved to the left end of the valve chamber 17 by the urging of the second spring 12, and the urging force of the spring 11 is reduced by the extension of the first spring 11 accompanying this movement. As a result, the exhaust pressure spool 10 moves to the left, a relief operation for exhausting the line pressure to the low pressure source is performed, and the line pressure supplied to the hydraulic multi-plate clutch via the operation valve 2 is maintained at a low pressure state. .
【００３２】油圧の送給先である油圧多板クラッチの摩
擦板は、相互間に所定の初期隙間を有しており、操作弁
２の切換え操作によりライン圧の送給が開始された後、
摩擦板同士の係合により動力伝達が可能となるまでの間
には、前記初期隙間に相当する距離だけ摩擦板を移動さ
せるための油圧ピストンの変位が必要であり、この移動
の間には、油圧ポンプ４から操作弁２を経て油圧多板ク
ラッチへ至る給油路には作動油の流れが存在している。The friction plates of the hydraulic multi-plate clutch, which is the destination of the hydraulic pressure, have a predetermined initial gap between them, and after the line pressure is started to be fed by the switching operation of the operating valve 2,
Displacement of the hydraulic piston for moving the friction plates by a distance corresponding to the initial gap is required before power can be transmitted by engagement of the friction plates, and during this movement, A flow of hydraulic oil exists in the oil supply path from the hydraulic pump 4 to the hydraulic multi-plate clutch via the operation valve 2.
【００３３】一方、遅延弁３のスプール30の復帰動作
は、前述した如く、前記絞り34の前後に生じる圧力差に
よる力がコイルばね31の付勢力を上回っている間には生
じず、前記圧力差は、絞り34を経てピストン板35の一側
から他側に向かう油流、即ち、前記給油路内部における
送給油の流量の多少に応じて大小となる。従って、調圧
弁装置１の油室16へのライン圧の供給は、操作弁２の切
換え操作がなされた後、前記給油路を経て油圧多板クラ
ッチに送給される送給油の流速が所定値以下となった時
点において、換言すれば、操作弁２を経て送給される作
動油により油圧多板クラッチにおける摩擦板の初期隙間
が解消され、係合が始まる時点において開始されること
になる。On the other hand, the return operation of the spool 30 of the delay valve 3 does not occur while the force due to the pressure difference generated before and after the throttle 34 exceeds the biasing force of the coil spring 31, as described above. The difference becomes large or small according to the amount of oil flow from one side of the piston plate 35 to the other side through the throttle 34, that is, the flow rate of the oil supply inside the oil supply passage. Therefore, the line pressure is supplied to the oil chamber 16 of the pressure regulating valve device 1 after the switching operation of the operation valve 2 is performed, and the flow rate of the oil supplied to the hydraulic multi-plate clutch via the oil supply passage is a predetermined value. At the time point below, in other words, the hydraulic oil fed through the operation valve 2 eliminates the initial clearance of the friction plate in the hydraulic multi-plate clutch, and starts when the engagement starts.
【００３４】このように遅延弁３は、調圧弁装置１の後
述する動作の開始タイミングを、伝動容量、前記初期隙
間の大小、内部油温の高低等、ライン圧の送給先である
油圧多板クラッチ側での各種条件に応じて自動変更せし
める作用をなすから、本考案に係る調圧弁装置１は、種
々の油圧多板クラッチのみならず、作動油の送給から動
作開始までの間にタイムラグが存在する各種の負荷に対
して構成の変更を必要とせずに適用できる。As described above, the delay valve 3 determines the start timing of the operation of the pressure regulating valve device 1 which will be described later, such as the transmission capacity, the size of the initial clearance, the internal oil temperature, and the like. Since the plate clutch side has the function of automatically changing it according to various conditions, the pressure regulating valve device 1 according to the present invention can be used not only for various hydraulic multi-plate clutches, but also between the supply of hydraulic oil and the start of operation. It can be applied to various loads with a time lag without the need to change the configuration.
【００３５】さて以上の如き遅延弁３の復帰動作終了
後、調圧弁装置１の油室16へのライン圧の供給が再開さ
れ、該油室16の内圧を受圧する前記制御スプール13が右
方に移動し、この移動に伴う第１ばね11の縮短により排
圧スプール10への付勢力が高まる結果、該スプール10の
リリーフ動作により制限されるライン圧は、図４に示す
如く経過時間の２乗に比例して増加し、定常ライン圧Ｐ
0 に達して安定化する。なおこのようなライン圧の増加
特性は、前記（１），（２），（３）式を満たすように
調圧弁装置１各部の寸法を設定することにより得られ
る。After the return operation of the delay valve 3 is completed as described above, the supply of the line pressure to the oil chamber 16 of the pressure regulating valve device 1 is restarted, and the control spool 13 that receives the internal pressure of the oil chamber 16 is moved to the right. As a result of the shortening of the first spring 11 due to this movement, the urging force on the exhaust pressure spool 10 increases, and as a result, the line pressure limited by the relief operation of the spool 10 becomes 2 times the elapsed time as shown in FIG. It increases in proportion to the power, and the steady line pressure P
It reaches 0 and stabilizes. It should be noted that such an increase characteristic of the line pressure can be obtained by setting the size of each part of the pressure regulating valve device 1 so as to satisfy the expressions (1), (2) and (3).
【００３６】ところが、本考案に係る調圧弁装置１にお
いては、前記油室16へのライン圧の供給に並行してアキ
ュムレータ７の油室72にもライン圧が供給され、該アキ
ュムレータ７に前述した蓄圧動作が生じる。即ち、制御
絞り５を通過して油室16に導入される油の全量が直ちに
制御スプール13の移動に供されるのではなく、導入油の
一部はアキュムレータ７に同時並行的に吸収され、この
吸収により制御スプール13の移動速度が減じられる。こ
のことは、前記（２）式における定数Ｋ0 が、制御絞り
５の絞り面積ｓ0 のみの関数ではなく、前記アキュムレ
ータ７の蓄圧容量に関連する各部の寸法、例えば、受圧
ピストン70の受圧面積、並びに、緩衝ばね71のばね定数
及び与圧縮量等の関数であることを示しており、これら
の変更により制御絞り５の絞り面積ｓ0 を変更すること
なく特性の変更が可能となる。However, in the pressure regulating valve device 1 according to the present invention, the line pressure is also supplied to the oil chamber 72 of the accumulator 7 in parallel with the supply of the line pressure to the oil chamber 16, and the accumulator 7 is described above. Accumulation operation occurs. That is, the entire amount of the oil introduced into the oil chamber 16 through the control throttle 5 is not immediately supplied to the movement of the control spool 13, but a part of the introduced oil is absorbed by the accumulator 7 in parallel at the same time. This absorption reduces the moving speed of the control spool 13. This means that the constant K 0 in the equation (2) is not a function of only the throttle area s 0 of the control throttle 5, but the dimensions of each part related to the accumulator capacity of the accumulator 7, for example, the pressure receiving area of the pressure receiving piston 70. , And a function such as the spring constant and the amount of compression of the buffer spring 71. By changing these, the characteristics can be changed without changing the throttle area s 0 of the control throttle 5.
【００３７】また、アキュムレータ７の大容量化により
ライン圧の増加率βを小さくできることから、制御絞り
５に過剰な小面積化を強いることがなく、更には、緩衝
ばね71の与圧縮量を外部から変更可能に構成することに
より、制御絞り５の加工誤差に起因して生じる前記増加
率βの誤差を補正でき、送給先となる油圧多板クラッチ
での要求に正しく合致したライン圧の増加特性が得られ
る。Further, since the increase rate β of the line pressure can be reduced by increasing the capacity of the accumulator 7, the control throttle 5 is not forced to have an excessively small area, and further, the amount of compression of the buffer spring 71 is externally adjusted. Can be changed, the error of the increase rate β caused by the processing error of the control throttle 5 can be corrected, and the increase of the line pressure that exactly meets the requirement of the hydraulic multi-plate clutch as the destination. The characteristics are obtained.
【００３８】このことは、定常ライン圧Ｐ0 の送給によ
り油圧多板クラッチの伝達トルクが定常トルクに達する
までの間、負荷側の伝動系にショックが生じないことを
示しており、疲労破壊による伝動系の損傷を防止でき、
耐用年数が大幅に増すことになる。また油圧多板クラッ
チにおいても、単位時間，単位面積当たりの摩擦仕事が
定量化し易くなり、潤滑，冷却油量の決定、並びに摩擦
板のサイズ及び材質の選定等が容易になる。This means that no shock is generated in the transmission system on the load side until the transmission torque of the hydraulic multi-plate clutch reaches the steady torque by the delivery of the steady line pressure P 0 , and fatigue failure occurs. It is possible to prevent damage to the transmission system due to
The service life will be greatly increased. Also in the hydraulic multi-plate clutch, the friction work per unit time and unit area can be easily quantified, and the lubrication, the amount of cooling oil, the size and material of the friction plate, etc. can be easily selected.
【００３９】[0039]
【考案の効果】以上詳述した如く本考案に係る調圧弁装
置においては、制御絞りを経てライン圧が導入される制
御スプールの一側の油室にアキュムレータを並設し、該
アキュムレータの蓄圧動作により、ライン圧の導入によ
り生じる制御スプールの移動を緩和したから、油圧多板
クラッチに送給されるライン圧の増加特性を、制御絞り
の絞り面積の変更によらずにアキュムレータ側での調節
によっても変更でき、制御絞りの絞り面積を過度に小さ
くすることなく緩やかな増加率が得られ、油圧多板クラ
ッチ側での要求に確実に応え得ると共に、油中の異物の
影響による動作不良の発生の虞もない。 また、本考案に
係る調圧弁装置にあっては、操作弁の切換え動作開始に
伴う遅延弁のスプール変動により制御絞りを閉止し、切
換え動作終了に伴う同じくスプールの復帰により制御絞
りを開放させ、また油圧多板クラッチへの送給油量に応
じた圧力差をその前，後に発生し、この圧力差に対応し
て遅延弁のスプールの復帰動作を緩衝する絞りにて緩衝
させることとしたから、油圧多板クラッチに対する送給
油量の変化の如何にかかわず、絞り効果のタイミングが
自動的に変更されることとなる優れた効果を奏する。As described in detail above, in the pressure regulating valve device according to the present invention, the accumulator is installed in parallel in the oil chamber on one side of the control spool into which the line pressure is introduced via the control throttle, and the accumulator accumulates pressure. As a result, the movement of the control spool caused by the introduction of the line pressure is mitigated, so the increase characteristic of the line pressure fed to the hydraulic multi-plate clutch can be adjusted by adjusting the accumulator side without changing the throttle area of the control throttle. Can be changed, and a moderate increase rate can be obtained without excessively reducing the throttle area of the control throttle, which can reliably meet the demands on the hydraulic multi-plate clutch side, and malfunctions caused by foreign matter in the oil There is no fear of . In addition, the present invention
In such a pressure regulating valve device, the switching operation of the operating valve is started.
Due to the spool fluctuation of the delay valve, the control throttle is closed and turned off.
Similarly, when the replacement operation is completed
Release and adjust the amount of oil sent to the hydraulic multi-plate clutch.
The pressure difference generated before and after that will correspond to this pressure difference.
Buffering the delay valve spool return operation
Since it was decided to make it possible to feed to the hydraulic multi-plate clutch
Regardless of how the oil quantity changes, the timing of the throttling effect
It has an excellent effect that is automatically changed .
【図１】本考案に係る調圧弁装置を用いて油圧多板クラ
ッチの動作油圧を発生すべく構成した油圧回路の模式図
である。FIG. 1 is a schematic diagram of a hydraulic circuit configured to generate an operating hydraulic pressure of a hydraulic multi-plate clutch using a pressure regulating valve device according to the present invention.
【図２】本考案に係る調圧弁装置を遅延弁及び操作弁と
一体的に構成してなる弁装置の縦断面図である。FIG. 2 is a longitudinal sectional view of a valve device in which the pressure regulating valve device according to the present invention is integrally formed with a delay valve and an operation valve.
【図３】従来の調圧弁装置を用いて油圧多板クラッチの
動作油圧を発生すべく構成した油圧回路の模式図であ
る。FIG. 3 is a schematic diagram of a hydraulic circuit configured to generate operating hydraulic pressure of a hydraulic multi-plate clutch using a conventional pressure regulating valve device.
【図４】油圧多板クラッチへの送給油圧の望ましい変化
態様を示すグラフである。FIG. 4 is a graph showing a desirable variation of the hydraulic pressure supplied to the hydraulic multi-plate clutch.
１ 調圧弁装置 ２ 操作弁 ３ 遅延弁 ５ 制御絞り ７ アキュムレータ 10 排圧スプール 11 第１ばね 12 第２ばね 13 制御スプール 16 油室 30 スプール 34 絞り 70 受圧ピストン 71 緩衝ばね 72 油室 1 Pressure regulating valve device 2 Operation valve 3 Delay valve 5 Control throttle 7 Accumulator 10 Discharge pressure spool 11 1st spring 12 2nd spring 13 Control spool 16 Oil chamber 30 Spool 34 Throttling 70 Pressure receiving piston 71 Buffer spring 72 Oil chamber
Claims (1)
リリーフ動作をなす排圧スプールと、その一側の油室に
制御絞りを介して導入される前記ライン圧を受圧し、第
２ばねの付勢に抗して移動する制御スプールとの間に、
夫々の移動を制限する向きに付勢する第１ばねを介装し
てなり、前記制御スプールの移動に伴う第１ばねの縮短
により前記排圧スプールへの付勢力を抑制し、駆動源と
速度２乗比例トルク負荷とを係断する油圧多板クラッチ
に送給される前記ライン圧を調圧する調圧弁装置におい
て、前記油圧多板クラッチへの前記動作油圧の送給，非
送給の切換えを行う操作弁と、該操作弁の切換え動作開
始に伴うそのスプールの移動により、前記制御絞りを閉
止し、切換え動作終了に伴うそのスプールの復帰により
前記制御絞りを開放する遅延弁と、前記油圧多板クラッ
チへの送給油量に応じた圧力差をその前，後に発生し、
その圧力差に対応して前記遅延弁のスプールの復帰動作
を緩衝する緩衝絞りとを備えると共に、前記油室に並設
されて、該油室への導入流量を分流して蓄圧するアキュ
ムレータを具備することを特徴とする調圧弁装置。1. A line pressure of a hydraulic circuit is received and moved,
Between the relief pressure discharge spool and the control spool that receives the line pressure introduced into the oil chamber on one side through the control throttle and moves against the bias of the second spring,
A first spring that biases the respective movements in a direction to limit the movement is interposed, and the biasing force to the exhaust pressure spool is suppressed by the shortening of the first spring accompanying the movement of the control spool. In a pressure regulating valve device that regulates the line pressure supplied to a hydraulic multi-plate clutch that disconnects from a square proportional torque load , the operating hydraulic pressure is not supplied to the hydraulic multi-plate clutch.
Operation valve for switching feed and switching operation opening of the operation valve
The control throttle is closed by the movement of the spool at the beginning.
By stopping and returning the spool at the end of the switching operation
The delay valve for opening the control throttle and the hydraulic multi-plate clutch
A pressure difference according to the amount of oil sent to the
Return operation of the delay valve spool corresponding to the pressure difference
A pressure regulating valve device , comprising: a buffer throttle that buffers the oil pressure, and an accumulator that is installed in parallel in the oil chamber and divides the flow rate of the flow introduced into the oil chamber to accumulate the pressure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1992054522U JPH088356Y2 (en) | 1992-07-10 | 1992-07-10 | Regulator valve device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1992054522U JPH088356Y2 (en) | 1992-07-10 | 1992-07-10 | Regulator valve device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH068826U JPH068826U (en) | 1994-02-04 |
| JPH088356Y2 true JPH088356Y2 (en) | 1996-03-06 |
Family
ID=12972994
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1992054522U Expired - Fee Related JPH088356Y2 (en) | 1992-07-10 | 1992-07-10 | Regulator valve device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH088356Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110281566B (en) * | 2019-06-21 | 2024-04-12 | 江苏华宏科技股份有限公司 | Hydraulic packer |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6120334Y2 (en) * | 1980-09-13 | 1986-06-19 |
-
1992
- 1992-07-10 JP JP1992054522U patent/JPH088356Y2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH068826U (en) | 1994-02-04 |
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