JPS6230334B2 - - Google Patents
Info
- Publication number
- JPS6230334B2 JPS6230334B2 JP56077083A JP7708381A JPS6230334B2 JP S6230334 B2 JPS6230334 B2 JP S6230334B2 JP 56077083 A JP56077083 A JP 56077083A JP 7708381 A JP7708381 A JP 7708381A JP S6230334 B2 JPS6230334 B2 JP S6230334B2
- Authority
- JP
- Japan
- Prior art keywords
- oil
- pressure
- clutch
- oil passage
- chamber
- 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
Links
- 238000009825 accumulation Methods 0.000 claims description 25
- 238000011144 upstream manufacturing Methods 0.000 claims description 3
- 239000003921 oil Substances 0.000 description 96
- 239000010720 hydraulic oil Substances 0.000 description 16
- 230000035939 shock Effects 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001934 delay Effects 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/14—Fluid pressure control
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0203—Control by fluid pressure with an accumulator; Details thereof
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0209—Control by fluid pressure characterised by fluid valves having control pistons, e.g. spools
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Description
【発明の詳細な説明】
本発明はフオークリフトやその他の産業機械、
建設機械、農業機械、船舶等の油圧クラツチに併
設される油圧モジユレーシヨン装置に関する。[Detailed Description of the Invention] The present invention provides forklifts and other industrial machines,
This invention relates to hydraulic modulation devices attached to hydraulic clutches of construction machinery, agricultural machinery, ships, etc.
油圧モジユレーシヨン装置はクラツチ接続操作
時にクラツチ油圧を緩やかに上昇させ、それによ
り接続時のシヨツクを防止するためのもので、従
来からこの種の装置としてはピストンや絞りを備
えた蓄圧式のバルブが使用されている。ところが
従来品では接続時のシヨツクを確実に防止できる
程度にまで油圧を緩やかに上昇させようとする
と、バルブの蓄圧容量を極めて大きくしなければ
ならず、従つて装置が大型化して重量が増し、コ
スト増を招く。 Hydraulic modulation devices are designed to gently increase the clutch hydraulic pressure when the clutch is engaged, thereby preventing shock during engagement. Conventionally, this type of device uses an accumulator valve equipped with a piston or a restrictor. has been done. However, with conventional products, in order to gradually increase the oil pressure to a level that can reliably prevent shock during connection, the pressure accumulation capacity of the valve must be extremely large, which increases the size and weight of the device. This results in increased costs.
本発明は上記従来の不具合を解決するために、
蓄圧室やピストンによる昇圧動作と並行して作動
油の一部を排油油路により逃がし、それにより油
圧を緩やかに上昇させると共に、油圧が所定圧ま
で上昇するとピストンが排油油路を塞ぐようにし
たもので、図面により説明すると次の通りであ
る。 In order to solve the above-mentioned conventional problems, the present invention has the following features:
In parallel with the pressure raising operation by the pressure storage chamber and piston, a portion of the hydraulic oil is released through the drain oil passage, thereby gradually increasing the oil pressure, and when the oil pressure rises to a predetermined pressure, the piston closes the drain oil passage. The following is an explanation using the drawings.
断面略図である第１図において、１は油圧ポン
プ２から絞り３、手動切替バルブ４（切替弁）を
経て油圧クラツチ５に至る油路である。ポンプ２
は例えばフオークリフトの走行用エンジンにより
駆動されるようになつており、ポンプ２からの油
圧はエンジン回転数の増加に伴つて上昇する。油
路１のポンプ２と絞り３の間の部分はレギユレー
タバルブ３ａを有する分岐油路１ａを介して図示
されていないドレン系路又はトルクコンバータに
接続している。６はシリンダー７やピストン８を
有するモジユレーシヨンバルブで、シリンダー７
内にはピストン８を挾んで図中左側に蓄圧室１０
が形成され、図中右側に排油室１１が形成されて
いる。排油室１１に面したシリンダー端壁１２と
ピストン８との間には圧縮コイルばね１３が縮設
されている。ピストン８は中心部から他方のシリ
ンダー端壁１５側へ突出した突部１６と、ばね１
３の外周側を延びるスカート部１７を併え、蓄圧
室１０が加圧されていない図示の状態において、
突部１６は端壁１５に当接し、蓄圧室１０は突部
１６の周囲に環状に形成されている。シリンダー
７は上記環状の蓄圧室１０に連通する給油孔１９
と、端壁１２の近傍において排油室１１に連通す
る排油孔２０とを備えている。給油孔１９には前
記油路１の絞り３よりも下流側の部分Ａから分岐
した蓄圧油路２１が接続している。排油孔２０は
油路２２を介して排油タンク２３に接続してい
る。シリンダー７の端壁１２に近い内周面部分に
は環状段部等からなるストツパー２５が設けてあ
る。更にシリンダー７の周壁には油孔２６が設け
てある。孔２６は図示の位置にあるピストン８の
スカート部１７とストツパー２５の間において排
油室１１と連通しており、孔２６には油路２７の
出口が接続し、油路２７入口は蓄圧油路２１の途
中部分Ｂに接続している。油路２７又は孔２６に
は絞り（図示せず）が設けてある。 In FIG. 1, which is a schematic cross-sectional view, reference numeral 1 denotes an oil passage from a hydraulic pump 2 to a hydraulic clutch 5 via a throttle 3 and a manual switching valve 4 (switching valve). pump 2
The pump 2 is driven by, for example, a forklift engine, and the oil pressure from the pump 2 increases as the engine speed increases. A portion of the oil passage 1 between the pump 2 and the throttle 3 is connected to a drain line or a torque converter (not shown) via a branch oil passage 1a having a regulator valve 3a. 6 is a modulation valve having a cylinder 7 and a piston 8;
There is a pressure accumulator chamber 10 on the left side of the figure with a piston 8 in between.
is formed, and an oil drain chamber 11 is formed on the right side in the figure. A compression coil spring 13 is compressed between the cylinder end wall 12 facing the oil drain chamber 11 and the piston 8. The piston 8 has a protrusion 16 protruding from the center toward the other cylinder end wall 15, and a spring 1.
In the illustrated state in which the pressure accumulating chamber 10 is not pressurized,
The protrusion 16 abuts the end wall 15, and the pressure accumulator 10 is formed in an annular shape around the protrusion 16. The cylinder 7 has an oil supply hole 19 communicating with the annular pressure accumulation chamber 10.
and an oil drain hole 20 communicating with the oil drain chamber 11 near the end wall 12. A pressure accumulation oil passage 21 branched from a portion A of the oil passage 1 on the downstream side of the throttle 3 is connected to the oil supply hole 19 . The oil drain hole 20 is connected to a drain oil tank 23 via an oil passage 22. A stopper 25 consisting of an annular step or the like is provided on the inner peripheral surface of the cylinder 7 near the end wall 12. Further, an oil hole 26 is provided in the peripheral wall of the cylinder 7. The hole 26 communicates with the oil drain chamber 11 between the skirt portion 17 of the piston 8 and the stopper 25 in the illustrated position, the outlet of the oil passage 27 is connected to the hole 26, and the inlet of the oil passage 27 is connected to the oil drain chamber 11, and the inlet of the oil passage 27 is connected to the oil drain chamber 11. It is connected to part B in the middle of road 21. The oil passage 27 or the hole 26 is provided with a restriction (not shown).
次に作動を説明する。油圧ポンプ２から一定の
圧力Ｐn（第２図が）が供給されており、切替バ
ルブ４が図示の如くクラツチ遮断位置にある時、
油路１の部分Ａから油路２１を経て蓄圧室１０へ
圧力Ｐnが導入されており、ピストン８は圧力Ｐn
によりスカート部１７がストツパー２５に当接す
る位置まで移動して孔２６を塞いでいる。この状
態において、切替バルブ４をクラツチ接続方向
（前進クラツチＦ側又は後進クラツチＲ側）へ切
り替えると、油路１からクラツチ５へ作動油が供
給され始め、第２図中実線で示す如くクラツチ油
圧Ｐは低い所定圧P1まで短時間（Ｏ−T1）で上昇
し、クラツチ５は接続し始める。上記切り替えと
同時に部分Ａの油圧は一時的に大きく降下し、蓄
圧室１０の圧力も大幅に降下するので、ピストン
８はばね１３の弾力により図示の如く端壁１５に
当接する位置又はその近傍まで移動する。この移
動により蓄圧室１０から強制排出された作動油は
油路２１、油路１を通つてクラツチ５側へ流れ、
所定圧P1までの油圧上昇を促進する。ポンプ２か
ら吐出された作動油は引き続きクラツチ５へ流入
し、クラツチ油圧Ｐは上昇するが、その場合に作
動油の一部は部分Ａから蓄圧油路２１、孔１９を
経て蓄圧室１０へ流入し、蓄圧室１０内において
ピストン８を排油室１１側へばね１３の弾力に抗
して押す。又作動油の別の一部は部分Ｂから油路
２７へ流入し、油路２７の途中又は孔２６で絞ら
れながら排油室１１、孔２０、油路２２を経てタ
ンク２３へ排出される。このように作動油の一部
が蓄圧室１０の容積を押し広げながら蓄圧室１０
へ流入し、又別の一部がタンク２３へ排出される
ので、クラツチ油圧Ｐは接続開始時の油圧P1より
やや高圧の油圧P2まで緩やかに上昇する。 Next, the operation will be explained. When a constant pressure P n (as shown in FIG. 2) is supplied from the hydraulic pump 2 and the switching valve 4 is in the clutch cutoff position as shown in the figure,
A pressure P n is introduced from part A of the oil passage 1 to the pressure accumulation chamber 10 via the oil passage 21 , and the piston 8 receives the pressure P n
As a result, the skirt portion 17 moves to a position where it comes into contact with the stopper 25 and closes the hole 26. In this state, when the switching valve 4 is switched to the clutch connecting direction (forward clutch F side or reverse clutch R side), hydraulic oil starts to be supplied from the oil passage 1 to the clutch 5, and the clutch hydraulic pressure is increased as shown by the solid line in FIG. P rises in a short time (O-T 1 ) to a lower predetermined pressure P 1 and the clutch 5 begins to engage. Simultaneously with the above switching, the oil pressure in part A temporarily drops significantly, and the pressure in the pressure storage chamber 10 also drops significantly, so that the piston 8 moves to a position where it contacts the end wall 15 as shown in the figure or in the vicinity thereof due to the elasticity of the spring 13. Moving. Due to this movement, the hydraulic oil forcibly discharged from the pressure accumulation chamber 10 flows to the clutch 5 side through the oil passage 21 and the oil passage 1.
Promotes oil pressure rise to a predetermined pressure P1 . The hydraulic oil discharged from the pump 2 continues to flow into the clutch 5, and the clutch oil pressure P rises, but in this case, part of the hydraulic oil flows from part A through the pressure accumulation oil passage 21 and the hole 19 into the pressure accumulation chamber 10. Then, the piston 8 is pushed toward the oil drain chamber 11 in the pressure accumulation chamber 10 against the elasticity of the spring 13. Another part of the hydraulic oil flows into the oil passage 27 from part B, and is discharged to the tank 23 through the oil drain chamber 11, the hole 20, and the oil passage 22 while being throttled in the oil passage 27 or at the hole 26. . In this way, a part of the hydraulic fluid expands the volume of the pressure accumulation chamber 10 while expanding the volume of the pressure accumulation chamber 10.
, and another part is discharged to the tank 23, so the clutch oil pressure P gradually rises to oil pressure P2 , which is slightly higher than oil pressure P1 at the start of connection.
油圧Ｐが所定圧P2に達すると、蓄圧室１０内の
油圧によりピストン８はスカート部１７の先端が
孔２６を塞ぐ位置まで移動する。孔２６が塞がれ
ると、タンク２３への排油動作は停止するので、
油圧Ｐは所定圧P2から比較的急激に上昇する。 When the hydraulic pressure P reaches a predetermined pressure P 2 , the piston 8 moves to a position where the tip of the skirt portion 17 closes the hole 26 due to the hydraulic pressure in the pressure accumulating chamber 10 . When the hole 26 is blocked, the oil draining operation to the tank 23 will stop.
The oil pressure P rises relatively rapidly from the predetermined pressure P2 .
油圧Ｐが上昇して所定圧P3になると、ピストン
８のスカート部１７がストツパー２５に当接し、
ピストン８は停止する。従つて蓄圧室１０への作
動油に流入も停止し、クラツチ油圧は更に急激に
上昇して最高圧Ｐnに達する。 When the oil pressure P rises to a predetermined pressure P3 , the skirt portion 17 of the piston 8 comes into contact with the stopper 25,
Piston 8 stops. Therefore, the flow of hydraulic oil into the pressure storage chamber 10 is also stopped, and the clutch oil pressure further increases rapidly to reach the maximum pressure Pn .
又上記油圧P1〜Ｐnに対応してクラツチ５は次
のように作動する。前述の如く油圧P1で接続し始
めたクラツチ５は油圧P2まで半クラツチ状態を保
つ。その間（T1〜T2）の油圧上昇は緩やかに行わ
れるので、クラツチ５にシヤツクが生じることは
ない。油圧Ｐが所定圧P2となつてクラツチ５が完
全接続に近い状態となると、油圧Ｐは所定圧P3を
経て最高圧Ｐnまで速やかに上昇し、クラツチ５
は短時間で完全かつ確実に接続される。従つてク
ラツチ５の摩擦面に摩耗の原因となる無駄な滑り
が生じることはない。 Further, the clutch 5 operates as follows in response to the above-mentioned oil pressures P1 to Pn . As mentioned above, the clutch 5, which starts to be connected at oil pressure P1 , remains in a half-clutch state until oil pressure P2 . During this period (T 1 -T 2 ), the oil pressure increases slowly, so no shock occurs in the clutch 5. When the oil pressure P reaches the predetermined pressure P2 and the clutch 5 is close to fully connected, the oil pressure P quickly rises to the maximum pressure Pn through the predetermined pressure P3 , and the clutch 5
will be fully and reliably connected in a short time. Therefore, unnecessary slippage that causes wear does not occur on the friction surface of the clutch 5.
クラツチ遮断時には切替バルブ４を図示のニユ
ートラル位置へ戻す。そうするとクラツチ５内の
作動油は切替弁４のドレンを通つて排出され、ク
ラツチ５は速やかに遮断される。 When the clutch is disengaged, the switching valve 4 is returned to the neutral position shown. Then, the hydraulic oil in the clutch 5 is discharged through the drain of the switching valve 4, and the clutch 5 is immediately shut off.
以上説明したように本発明によると、クラツチ
接続動作時に切替バルブ４からクラツチ５へ送ら
れようとする作動油の一部を蓄圧油路２１を介し
て蓄圧室１０へ導入し、又別の一部を排油油路２
８（油路２７から油路２２までの部分）を介して
排油タンク２３へ排出するようにしたので、油圧
の立上り時間（T2−T1）を長くしてクラツチ５が
急激に接続することを防止し、接続時のシヨツク
を防ぐことができる。換言すれば排出系路を備え
ていない従来品により本発明の装置と同様の油圧
立上り特性を得ようとすると、蓄圧室の容量を非
常に大きくする必要があるが、本発明では排油油
路２８を備えているので蓄圧室１０の容量を小さ
くすることができ、従つて装置の軽量コンパクト
化がコストダウンを達成することができる。なお
第２図中２点実線は本発明の装置と同容量の蓄圧
室を有する従来品の特性を示しており、該従来品
では油圧P1から油圧P2までの立上り時間（T′2−
T1）が短いことがわかる。又本発明では排油油路
２８の途中部分を排油室１１や孔２６，２０で形
成し、油圧Ｐが所定圧P2まで上昇して半クラツチ
状態が終了した後は、ピストン８が孔２６を閉じ
て排油動作を停止させるようにしたので、クラツ
チ５が完全に接続した状態において充分に高い油
圧Ｐnを確実に得ることができ、作動油のロスや
クラツチ５の無駄な滑りを防ぐことができる。 As explained above, according to the present invention, a part of the hydraulic oil that is to be sent from the switching valve 4 to the clutch 5 during the clutch connection operation is introduced into the pressure accumulation chamber 10 via the pressure accumulation oil passage 21, and another part of the hydraulic oil is introduced into the pressure accumulation chamber 10 through the pressure accumulation oil passage 21. Drain oil passage 2
8 (portion from oil passage 27 to oil passage 22) to drain oil tank 23, the oil pressure rise time (T 2 - T 1 ) is lengthened and the clutch 5 is suddenly engaged. This can prevent shocks during connection. In other words, in order to obtain the same hydraulic rise characteristics as the device of the present invention using a conventional product that does not have a discharge system, it is necessary to make the capacity of the pressure accumulation chamber extremely large. 28, the capacity of the pressure accumulating chamber 10 can be reduced, and therefore the device can be made lighter and more compact, thereby reducing costs. The two-dot solid line in Fig. 2 shows the characteristics of a conventional product having a pressure accumulating chamber with the same capacity as the device of the present invention .
It can be seen that T 1 ) is short. In addition, in the present invention, the intermediate portion of the drain oil passage 28 is formed by the drain chamber 11 and the holes 26, 20, and after the oil pressure P rises to a predetermined pressure P2 and the half-clutch state ends, the piston 8 closes the hole. 26 is closed to stop the oil draining operation, a sufficiently high oil pressure P n can be reliably obtained when the clutch 5 is fully connected, and loss of hydraulic oil and unnecessary slipping of the clutch 5 can be avoided. It can be prevented.
更に本発明では、油路１の絞り３と切替弁４と
の間の部分から蓄圧油路２１を分岐させるととも
に、切替弁４を、クラツチ遮断位置において油路
１を閉鎖して該油路１の切替弁４よりも上流側の
部分を加圧状態に保つように構成している。 Furthermore, in the present invention, the pressure accumulation oil passage 21 is branched from a portion between the throttle 3 of the oil passage 1 and the switching valve 4, and the oil passage 1 is closed by closing the oil passage 1 with the switching valve 4 at the clutch cutoff position. The upstream side of the switching valve 4 is kept in a pressurized state.
従つて先に詳細に説明したように、クラツチ遮
断状態では蓄圧室１０を加圧してピストン８を第
１図で右方へ移動させ、蓄圧室１０に多量の作動
油を溜めることができる。そして次に切替弁４を
クラツチ接続位置に切り替えると、それと同時に
分岐部分Ａや蓄圧室１０の油圧は一時的に大きく
降下するので、ピストン８はばね１３に押されて
蓄圧室１０内の多量の作動油をクラツチ５側へ排
出する。従つて油圧は所定値Ｐ１まで速やかに上
昇する。 Therefore, as described in detail above, in the clutch disengaged state, the pressure accumulator 10 is pressurized, the piston 8 is moved to the right in FIG. 1, and a large amount of hydraulic fluid can be stored in the pressure accumulator 10. Then, when the switching valve 4 is switched to the clutch connection position, at the same time, the oil pressure in the branch part A and the pressure accumulation chamber 10 temporarily drops significantly, so the piston 8 is pushed by the spring 13 and a large amount of pressure in the pressure accumulation chamber 10 is released. Drain the hydraulic oil to the clutch 5 side. Therefore, the oil pressure quickly rises to the predetermined value P1.
なお、第１図の実施例では、切替弁４の接続位
置への切り替えとほぼ同時に排油油路２８からの
作動油排出が開始されるが、排油油路２８には絞
りが設けてあるので、排油油路２８から排出され
る作動油の量は僅かである。従つて、この排出動
作により上記所定値Ｐ１までの油圧上昇動作が大
幅に影響を受けることはなく、上述の如く油圧を
所定値Ｐ１まで速やかに上昇させることができ
る。 In the embodiment shown in FIG. 1, the discharge of hydraulic oil from the drain oil passage 28 is started almost simultaneously with switching the switching valve 4 to the connected position, but the drain oil passage 28 is provided with a restriction. Therefore, the amount of hydraulic oil discharged from the drain oil passage 28 is small. Therefore, this discharge operation does not significantly affect the operation of raising the oil pressure to the predetermined value P1, and the oil pressure can be quickly raised to the predetermined value P1 as described above.
上記動作をクラツチ５の実際の接続動作と関連
して説明すると、油圧が上記所定値Ｐ１まで上昇
する行程は、クラツチ５のピストンが空走して摩
擦板に接触し始めるまでの行程である。従つてこ
の行程ではクラツチ加圧室の容積が比較的大きく
増大し、そのために多量の作動油が要求される。
そして上記構成によると、ピストン８により蓄圧
室１０から多量の作動油を供給できる。従つてピ
ストンの空走時間を短縮し。クラツチ接続動作の
無駄な遅れを防止できる。 To explain the above operation in relation to the actual connecting operation of the clutch 5, the stroke in which the oil pressure rises to the predetermined value P1 is the stroke until the piston of the clutch 5 runs free and starts to come into contact with the friction plate. Therefore, in this stroke, the volume of the clutch pressurizing chamber increases relatively significantly, and a large amount of hydraulic fluid is therefore required.
According to the above configuration, a large amount of hydraulic oil can be supplied from the pressure accumulation chamber 10 by the piston 8. Therefore, the idle running time of the piston is shortened. Unnecessary delays in clutch connection operation can be prevented.
換言すれば、第１図の如く切替弁４の接続位置
への切り替えとほぼ同時に排油油路２８が開く場
合でも、本発明では、蓄圧室１０から多量の作動
油を排出できるので、ピストン空走時間を短縮で
きる。 In other words, even if the drain oil passage 28 opens almost simultaneously with switching the switching valve 4 to the connected position as shown in FIG. You can shorten running time.
なお、以下に説明する第３図の実施例では、油
圧が所定値Ｐ１以下の時、排油動作を停止又は規
制することができる。 In the embodiment shown in FIG. 3, which will be described below, when the oil pressure is below a predetermined value P1, the oil draining operation can be stopped or regulated.
第３図においてシリンダー７は更に別の孔２９
を備えている。孔２９は図示の状態、すなわち蓄
圧室１０の容積が最小の状態においてピストン８
により塞がれており、クラツチ油圧Ｐが所定圧P1
になると、ピストン８は孔２９を開くようになつ
ている。又油路２７の入口の孔２９に接続してお
り、従つて排油油路２８は蓄圧油路２１、孔１
９、蓄圧室１０、孔２９、油路２７，２６…油路
２２により形成されている。その他の構造は第１
図のものと同様である。この構造によると、油圧
Ｐが所定圧P1になるまでは排油油路２７（孔２９
又は孔２６）が閉鎖されるので、接続操作開始直
後は排油動作を停止してクラツチ５へ速やかに多
量の作動油を流入させることができ、従つて油圧
Ｐを第２図の破線（Ｏ〜T′間）の如く速やかに
所定圧P1まで上昇させ、切替バルブ４の操作から
クラツチ５の接続開始までの遅れ時間を可及的に
短くすることができる。 In FIG. 3, the cylinder 7 has a further hole 29
It is equipped with The hole 29 is inserted into the piston 8 in the illustrated state, that is, in the state where the volume of the pressure accumulation chamber 10 is at its minimum.
, and the clutch oil pressure P is the predetermined pressure P 1
At this point, the piston 8 opens the hole 29. Also, it is connected to the hole 29 at the entrance of the oil passage 27, and therefore the drain oil passage 28 is connected to the pressure accumulation oil passage 21 and the hole 1.
9, a pressure accumulation chamber 10, a hole 29, oil passages 27, 26, . . ., an oil passage 22. Other structures are first
It is similar to the one shown in the figure. According to this structure, until the oil pressure P reaches the predetermined pressure P1 , the drain oil passage 27 (hole 29
or hole 26) is closed, the oil draining operation is stopped immediately after the start of the connection operation, and a large amount of hydraulic oil can immediately flow into the clutch 5. Therefore, the oil pressure P can be adjusted to the dotted line (O to T'), and the delay time from the operation of the switching valve 4 to the start of engagement of the clutch 5 can be made as short as possible.
なお分岐部分Ａを切替弁４よりも下流側に設け
ることもできる。 Note that the branch portion A can also be provided downstream of the switching valve 4.
第１図は一実施例の断面略図、第２図は油圧特
性のグラフ、第３図は別の実施例の断面略図であ
る。１……油路、２……油圧ポンプ、３……絞
り、４……切替バルブ、５……油圧クラツチ、６
……モジユレーシヨンバルブ、８……ピストン、
１０……蓄圧室、１１……排油室、１３……ば
ね、２１……蓄圧油路、２６……孔、２７……排
油油路、Ａ……下流部分。
FIG. 1 is a schematic cross-sectional view of one embodiment, FIG. 2 is a graph of hydraulic characteristics, and FIG. 3 is a schematic cross-sectional view of another embodiment. 1... Oil path, 2... Hydraulic pump, 3... Throttle, 4... Switching valve, 5... Hydraulic clutch, 6
...Modulation valve, 8...Piston,
DESCRIPTION OF SYMBOLS 10... Pressure accumulation chamber, 11... Oil drain chamber, 13... Spring, 21... Pressure accumulation oil path, 26... Hole, 27... Oil drain oil path, A... Downstream part.
Claims (1)
チへ至る油路の絞りと切替弁との間の部分から蓄
圧油路と排油油路とを分岐させ、上記切替弁を、
クラツチ接続位置において上記油路を開放すると
ともに、クラツチ遮断位置において上記油路を閉
鎖して該油路の上記切替弁よりも上流側の部分を
加圧状態に保つように構成し、モジユレーシヨン
バルブにピストンを挾んで蓄圧室と排油室を設
け、上記バルブにピストンを蓄圧室側へ付勢する
ばねを設け、蓄圧油路を蓄圧室に接続し、上記バ
ルブの壁に排油室に連通する孔を設け、上記孔及
び排油室により排油通路の途中部分を形成し、排
油室よりも上流側の排油油路部分に絞りを設け、
蓄圧室の油圧が所定値まで上昇した時、上記孔が
ピストンにより閉鎖されるようにしたことを特徴
とするクラツチ油圧用モジユレーシヨン装置。1. A pressure accumulation oil passage and an oil drain oil passage are branched from a portion between the restriction and the switching valve of the oil passage leading from the pump to the hydraulic clutch via the throttle and the switching valve, and the switching valve is
The module is configured to open the oil passage at the clutch connection position and close the oil passage at the clutch cutoff position to maintain a pressurized portion of the oil passage upstream of the switching valve. A pressure accumulating chamber and an oil drain chamber are provided between the piston in the valve, a spring is provided in the valve to bias the piston toward the pressure accumulating chamber, a pressure accumulating oil passage is connected to the pressure accumulating chamber, and an oil drain chamber is provided in the wall of the valve. A hole communicating with is provided, the hole and the oil drain chamber form an intermediate portion of the oil drain passage, and a restriction is provided in a portion of the oil drain oil path upstream of the oil drain chamber,
1. A clutch hydraulic modulation device characterized in that the hole is closed by a piston when the hydraulic pressure in the pressure storage chamber rises to a predetermined value.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56077083A JPS57192628A (en) | 1981-05-20 | 1981-05-20 | Hydraulic modulator for clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56077083A JPS57192628A (en) | 1981-05-20 | 1981-05-20 | Hydraulic modulator for clutch |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS57192628A JPS57192628A (en) | 1982-11-26 |
| JPS6230334B2 true JPS6230334B2 (en) | 1987-07-01 |
Family
ID=13623880
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP56077083A Granted JPS57192628A (en) | 1981-05-20 | 1981-05-20 | Hydraulic modulator for clutch |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS57192628A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61157835A (en) * | 1984-12-28 | 1986-07-17 | Aisin Warner Ltd | Accumulator |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4820027U (en) * | 1971-07-16 | 1973-03-07 |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5840347Y2 (en) * | 1978-10-11 | 1983-09-10 | 株式会社小松製作所 | Power shift transmission hydraulic control device |
-
1981
- 1981-05-20 JP JP56077083A patent/JPS57192628A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4820027U (en) * | 1971-07-16 | 1973-03-07 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS57192628A (en) | 1982-11-26 |
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