JP3407565B2 - Spool valve - Google Patents
Spool valveInfo
- Publication number
- JP3407565B2 JP3407565B2 JP28483496A JP28483496A JP3407565B2 JP 3407565 B2 JP3407565 B2 JP 3407565B2 JP 28483496 A JP28483496 A JP 28483496A JP 28483496 A JP28483496 A JP 28483496A JP 3407565 B2 JP3407565 B2 JP 3407565B2
- Authority
- JP
- Japan
- Prior art keywords
- outflow
- spool
- valve chamber
- depression
- path
- 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
Landscapes
- Sliding Valves (AREA)
- Details Of Valves (AREA)
Description
【発明の詳細な説明】
【０００１】
【発明の属する技術分野】本発明は、各種の油圧制御回
路に使用されるスプール弁に関する。
【０００２】
【従来の技術】自動車用自動変速機の油圧制御回路に使
用されるスプール弁は、図１２に一部を示すように、本
体１にスプール孔２、流入路３と流出路４をそれぞれ形
成し、流入路３と流出路４をスプール孔２の軸芯方向に
少し離れた２個所に連通している。丸軸形状のスプール
５は、中央部に長方形断面の周溝の弁室６を軸対称に形
成している。スプール孔２には、スプール５を軸芯方向
に移動可能に嵌合している。スプール５は、軸芯方向の
所定の範囲内で移動可能である。
【０００３】弁室６と流出路４の連通部９の増減によっ
て流入路３または流出路４の圧力や流量を制御する場
合、流入路３は、スプール５の位置に拘らず、常に、弁
室６に連通している。
【０００４】スプール５が流入路３側に移動している
と、スプール孔２の流入路３連通部と流出路４連通部の
中間部７がスプール５の流出路４側のランド８で閉鎖さ
れ、弁室６と流出路４が遮断されている。
【０００５】スプール５を流出路４側に移動すると、図
１２に示すように、スプール孔２の流入路３連通部と流
出路４連通部の中間部７が開放され、弁室６と流出路４
が連通する。スプール５を流出路４側に移動するに従っ
て、弁室６と流出路４の連通部９即ち絞り部９の開度ｘ
が増加する。
【０００６】作動油のような流体が流入路３から弁室６
に流入し、弁室６から絞り部９を経て流出路４に流出す
ると、流体の流入時と流出時では圧力ないし運動量が異
なるので、その圧力ないし運動量の差に基づく軸芯方向
の力Ｆがスプール５に作用する。この力Ｆは、流体力と
呼ばれ、スプール５を軸芯方向に移動させる操作力に影
響を与える。
【０００７】
【発明が解決しようとする課題】上記のようなスプール
弁において、流入路３または流出路４の圧力や流量を制
御する精度が高いときには、流体力Ｆがスプール５の操
作力に与える影響が大きくなる。
【０００８】例えば、自動車用自動変速機の油圧制御回
路において、図１３に一部を示すように、スプール弁の
流入路３に、エンジンに直結したオイルポンプ１１と、
変速機構を操作するライン圧力の通路１２を接続し、流
出路４をドレンの通路１３にし、スプール５の一端にラ
イン圧力を作用させてライン圧力などでスプール５を移
動させ、スプール５の位置即ち絞り部９の開度ｘでライ
ン圧力を制御する場合、絞り部９の開度ｘを減少させる
向きに作用する流体力Ｆは、図２に従来例Ｆとして示す
ように、絞り部９の開度ｘによって、への字形状に大き
く変化する。
【０００９】従って、流体力Ｆは、絞り部９の開度ｘに
よる変化が大きいので、スプール５を所望の位置に移動
させ難く、ライン圧力が所望の通りに制御されない。変
速時の衝撃が大きくなったり、変速の遅れが大きくなる
ことがある。
【００１０】結局、スプール弁においては、流体力Ｆ
は、小さく、かつ、絞り部９の開度ｘによる変化が小さ
いことが望まれる。
【００１１】
【課題を解決するための研究】上記のようなスプール弁
において、図１２に示すように、密度ρの流体が流量Ｑ
で流入路３から弁室６に速度Ｖ1，流入角θ1で流入し、
弁室６から絞り部９を経て流出路４に速度Ｖ2，流出角
θ2で流出する場合、流体力Ｆは、絞り部９の開度ｘを
減らす向きを正にすると、運動量理論から次の通りにな
る。
【００１２】Ｆ＝ρＱ（Ｖ2cosθ2−Ｖ1cosθ1）
この式において、流体力Ｆは、流入角θ1を小さくし
て、流出角θ2を大きくすると、小さくなる。しかし、
流入角θ1は、弁室６の形状を変えても、あまり変化し
ないので、流出角θ2を大きくする弁室６の形状を考察
することにする。
【００１３】弁室６は、図１に例示するように、流出端
の端面を滑らかに湾曲して弓形状断面の窪み２１を軸対
称に形成し、窪み２１の流出端と流出路４側ランド８の
外周面の間の角度θを鋭角、好ましくは８０度以下にす
る。
【００１４】流体が弁室６の流出端の滑らかな窪み２１
に沿って流れれば、窪みがなくて上記の角度θが直角で
ある従来の場合より、流出角θ2が大きくなる。
【００１５】ところが、弁室６の流出端の端面に窪み２
１を形成すると、窪み２１が滑らかな弓形状断面であっ
ても、窪み２１に二次渦が発生することがある。窪み２
１に二次渦が発生すると、流れが窪み２１から剥離し易
く、流体が窪み２１に沿って流れ難い。
【００１６】そこで、流れの転向を抑制する二次渦の発
生を防止し、流体を窪み２１に沿って流すため、図１に
例示するように、窪み２１直前の円輪形状断面の流路２
３を、窪み２１に近付くに従って流速が徐々に増加する
増速流路にする。例えば、弁室６の流出端側部分２２
は、窪み２１に近付くに従って底を軸対称に徐々に浅く
する。実効流路断面を窪み２１に近付くに従って徐々に
減少させる。
【００１７】すると、流体が窪み２１直前の流路２３で
増速流れとなって窪み２１に流入し、窪み２１に二次渦
が発生し難く、流体が窪み２１から剥離し難く窪み２１
に沿って流れ易く、流出角θ2が大きくなって、流体力
Ｆが減少する。
【００１８】
【課題を解決するための手段】本発明は、流入路と流出
路をスプール孔の軸芯方向に離れた２個所に連通し、ス
プールの中央部に周溝の弁室を形成し、スプール孔にス
プールを軸芯方向に移動可能に嵌合し、流体が流入路か
ら弁室に流入して弁室と流出路の連通部を経て流出路に
流出し、弁室と流出路の連通部の開度によって流入路ま
たは流出路の圧力や流量を制御するスプール弁におい
て、弁室は、流出端の端面を湾曲して滑らかな窪みを形
成し、窪みの流出端と流出路側ランドの外周面との間の
角度を鋭角にし、窪み直前の流路は、窪みに近付くに従
って実効流路断面を徐々に減少させて増速流路にし、 流
体は、窪み直前の増速流路で徐々に増速して窪みに流入
し、窪みに沿って向きを変え、弁室と流出路の連通部を
通過する構成にしたことを特徴とする。
【００１９】窪みは、弓形状断面にして軸対称にするこ
とができる。
【００２０】窪みの流出端と流出路側ランドの外周面の
間の角度は、８０度以下にすることが好ましい。
【００２１】弁室の流出端側部分は、窪みに近付くに従
って底を軸対称に徐々に浅くすることができる。
【００２２】弁室の中央部分は、増速流路または等速流
路にすることが好ましい。
【００２３】
【発明の効果】本発明においては、弁室から流出路に流
出する流体の流出角が大きくなって、流体力が減少す
る。スプールを所望の位置に移動させ易く、流入路また
は流出路の圧力や流量を制御し易い。
【００２４】
【発明の実施の形態】
＜第１例（図１〜図９参照）＞本例のスプール弁は、ス
プール５の中央部に、従来とは断面形状が異なる周溝の
弁室６を軸対称に形成している。弁室６は、図１に一部
の縦断端面を示すように、流出端の端面を湾曲して滑ら
かな弓形状断面の窪み２１を軸対称に形成し、窪み２１
の流出端と流出路４側ランド８の外周面の間の角度θ、
即ち、窪み２１の流出端の角度θを８０度以下にしてい
る。
【００２５】弁室６の流出端側部分２２は、図１に示す
ように、窪み２１に近付くに従って底を軸対称に徐々に
浅くしている。窪み２１直前の円輪形状断面の流路２３
は、実効流路断面が窪み２１に近付くに従って徐々に減
少し、流速が窪み２１に近付くに従って徐々に増加する
増速流路にしている。弁室６の底面の流出端は、窪み２
１の流入端に滑らかに接続している。
【００２６】弁室６の流出端側部分２２を除く残りの部
分は、図１に示すように、窪み２１に近付くに従って底
を軸対称に徐々に深くしている。弁室６の中央部分は、
増速流路２４または等速流路にし、弁室６の流出端側部
分の増速流路２３に接続している。
【００２７】その他の構成は、図１２に示した従来例と
同様である。
【００２８】作動油のような流体は、図１に示すよう
に、流入路３から弁室６の流入端側部分に流入し、増速
流路２４または等速流路を経て増速流路２３に流入し、
増速流路２３で増速して窪み２１に流入し、滑らかな窪
み２１に沿って向きを変え、弁室６と流出路４の連通部
９即ち絞り部９を通過し、大きな流出角θ2で流出路４
に流出する。
【００２９】自動車用自動変速機の油圧制御回路におい
て、本例のスプール弁の流入路３に、エンジンに直結し
たオイルポンプと、変速機構を操作するライン圧力の通
路を接続し、流出路４をドレンの通路にし、スプール５
の一端にライン圧力を作用させてライン圧力などでスプ
ール５を移動させ、スプール５の位置即ち絞り部９の開
度ｘでライン圧力を制御する場合、絞り部９の開度ｘを
減少させる向きに作用する流体力Ｆは、図２に実施例Ａ
として示すように、絞り部９の開度ｘによってへの字形
状に変化するが、図１２に示した従来例Ｆに比較して、
絶対値が小さく、かつ、絞り部９の開度ｘによる変化が
小さい。
【００３０】なお、窪み２１の流出端の角度θは、本例
では７０度、従来例では９０度である。スプール５の径
Ｄは、共に、１２．５mmである。流体は、共に、温度７
０℃、密度０．８３４kgf/cm3、動粘度０．１５cm2/sで
ある。
【００３１】本例のスプール弁において、窪み２１の流
出端の角度θを７０度にした実施例Ａ、８０度にした実
施例Ｂと、図３に示すように、窪み２１をなくして弁室
６の流出端の角度θを９０度にした比較例Ｃについて、
同一条件で流体力Ｆを求め、流体力Ｆと流出端の角度θ
の関係を示すと、図４に示すようになる。この図から明
らかなように、流出端の角度θが８０度以下になると、
流体力Ｆが大幅に低下する。
【００３２】また、上記の実施例Ａ、実施例Ｂと比較例
Ｃ、及び、図５に示すような比較例Ｄ、図６に示すよう
な比較例Ｅ、更に、図１２に示した従来例Ｆについて、
同一条件で流体力Ｆを求めると、図７に示すように、流
体力Ｆは、実施例Ａと実施例Ｂでは小さいが、比較例
Ｃ、比較例Ｄと比較例Ｅ及び従来例Ｆでは大きい。その
理由は、比較例Ｃ、比較例Ｅと従来例Ｆでは窪みがない
ためであり、比較例Ｄでは、窪み２１直前の流路２３が
減速流路であって増速流路になっていないためであるも
のと認められる。
【００３３】実施例Ａ，Ｂと比較例Ｃ，Ｄ，Ｅ及び従来
例Ｆについて、同一条件の下での軸対称，非定常，非圧
縮，粘性流れの時間平均値の流線図を求めると、図８に
示すようになる。この図から明らかなように、実施例Ａ
と実施例Ｂでは、窪み２１での二次渦の発生が抑制され
て流出角θ2が大きくなっている。比較例Ｄでは、窪み
２１で二次渦が発生して流れの転向が抑制され、流出角
θ2が小さくなっている。比較例Ｃ、比較例Ｅと従来例
Ｆでは、流出角θ2が小さくなっている。
【００３４】図９に示すような比較例Ｇについて、流体
力Ｆは、図２に比較例Ｇとして示すように、従来例Ｆに
おけるよりは小さくなるが、実施例Ａにおけるより大き
くなる。実施例Ａにおいては、絞り部９の開度ｘが小さ
い範囲、即ち、流体力Ｆが大きくなる範囲で、流体力Ｆ
が大幅に低下する。
【００３５】＜第２例と第３例（図１０と図１１参照）
＞第２例のスプール弁は、図１０に示すように、弁室６
の流出端の端面に形成した窪み２１の流出端と流出路４
側ランド８の外周面の間に、そのランド８の外周面と直
交する狭い平坦部３１を軸対称に形成している。弁室６
の流入端側部分には、段状の凹部３２を軸対称に形成し
ている。
【００３６】その他の点は、第１例におけるのと同様で
ある。
【００３７】第３例のスプール弁は、図１１に示すよう
に、弁室６の流出端側部分を除く部分について、深さを
一定にしている。
【００３８】その他の点は、第１例におけるのと同様で
ある。
【００３９】なお、第１例〜第３例のスプール弁は、上
記の自動変速機用油圧制御回路以外の油圧制御回路にも
使用される。例えば、スプール弁のスプール５の一端に
作用する流体の圧力を、調整圧力を電気信号で制御する
比例式減圧弁で増減し、スプール弁の流入路３または流
出路４の圧力や流量を、比例式減圧弁に入力する電気信
号に比例して制御する油圧制御回路に使用される。する
と、流体力Ｆに基づく制御誤差が減少する。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a spool valve used for various hydraulic control circuits. 2. Description of the Related Art As shown in FIG. 12, a spool valve used in a hydraulic control circuit of an automobile automatic transmission has a main body 1 provided with a spool hole 2, an inflow passage 3 and an outflow passage 4. The inflow passage 3 and the outflow passage 4 are respectively communicated with two portions of the spool hole 2 slightly separated in the axial direction. The spool 5 having a round shaft shape has a valve chamber 6 having a circumferential groove with a rectangular cross section formed at the center in an axially symmetric manner. A spool 5 is fitted into the spool hole 2 so as to be movable in the axial direction. The spool 5 is movable within a predetermined range in the axial direction. When the pressure or flow rate of the inflow passage 3 or the outflow passage 4 is controlled by increasing or decreasing the communication portion 9 between the valve chamber 6 and the outflow passage 4, the inflow passage 3 is always in the valve chamber irrespective of the position of the spool 5. It communicates with 6. When the spool 5 is moving toward the inflow path 3, an intermediate portion 7 between the inflow path 3 and the outflow path 4 of the spool hole 2 is closed by a land 8 on the outflow path 4 of the spool 5. , The valve chamber 6 and the outflow passage 4 are shut off. When the spool 5 is moved to the outflow passage 4 side, as shown in FIG. 12, an intermediate portion 7 between the inflow passage 3 and the outflow passage 4 of the spool hole 2 is opened, and the valve chamber 6 and the outflow passage are opened. 4
Communicate. As the spool 5 is moved toward the outflow path 4, the opening x of the communication portion 9 between the valve chamber 6 and the outflow path 4, that is, the throttle portion 9 is set.
Increase. [0006] Fluid such as hydraulic oil flows from the inflow passage 3 through the valve chamber 6.
When the fluid flows out of the valve chamber 6 to the outflow passage 4 through the constricted portion 9, the pressure or momentum is different between the inflow and the outflow of the fluid. Therefore, the force F in the axial direction based on the difference between the pressure and the momentum is Acts on spool 5. This force F is called a fluid force and affects the operation force for moving the spool 5 in the axial direction. [0007] In the above-described spool valve, when the precision of controlling the pressure and flow rate of the inflow passage 3 or the outflow passage 4 is high, the fluid force F gives the operating force of the spool 5. The effect is greater. For example, in a hydraulic control circuit of an automatic transmission for an automobile, an oil pump 11 directly connected to an engine is provided in an inflow passage 3 of a spool valve as shown in FIG.
The line pressure passage 12 for operating the transmission mechanism is connected, the outflow passage 4 is changed to the drain passage 13, and the line pressure is applied to one end of the spool 5 to move the spool 5 by the line pressure or the like. When the line pressure is controlled by the opening degree x of the throttle section 9, the fluid force F acting in a direction to decrease the opening degree x of the throttle section 9 is increased as shown in FIG. Depending on the degree x, the shape changes greatly into a concave shape. Therefore, since the fluid force F greatly varies depending on the opening x of the throttle portion 9, it is difficult to move the spool 5 to a desired position, and the line pressure is not controlled as desired. The impact at the time of shifting may increase, or the delay of shifting may increase. After all, in the spool valve, the fluid force F
Is desired to be small and a change due to the opening x of the throttle unit 9 is small. In the above-described spool valve, as shown in FIG. 12, a fluid having a density ρ has a flow rate Q
Flows into the valve chamber 6 from the inflow passage 3 at a speed V 1 and an inflow angle θ 1 ,
When the fluid force F flows out of the valve chamber 6 to the outflow path 4 via the throttle portion 9 at the speed V 2 and the outlet angle θ 2 , the fluid force F becomes the following from the momentum theory if the direction in which the opening degree x of the throttle portion 9 is reduced is made positive. It becomes as follows. F = ρQ (V 2 cos θ 2 −V 1 cos θ 1 ) In this equation, the fluid force F decreases as the inflow angle θ 1 is reduced and the outflow angle θ 2 is increased. But,
The inflow angle θ 1 does not change much even when the shape of the valve chamber 6 is changed. Therefore, the shape of the valve chamber 6 that increases the outflow angle θ 2 will be considered. As shown in FIG. 1, the valve chamber 6 has an end face at the outflow end which is smoothly curved to form an indentation 21 having an arcuate cross-section in an axially symmetric manner. The angle θ between the outer peripheral surfaces of the outer peripheral surface 8 is an acute angle, preferably 80 degrees or less. Fluid flows into a smooth depression 21 at the outflow end of the valve chamber 6.
Flows out, the outflow angle θ 2 becomes larger than in the conventional case where the angle θ is a right angle without a depression. However, a recess 2 is formed in the end face of the outflow end of the valve chamber 6.
When 1 is formed, a secondary vortex may be generated in the depression 21 even if the depression 21 has a smooth bow-shaped cross section. Hollow 2
When a secondary vortex occurs in 1, the flow tends to separate from the depression 21, and the fluid does not easily flow along the depression 21. Therefore, in order to prevent the generation of the secondary vortex that suppresses the turning of the flow and to cause the fluid to flow along the depression 21, as shown in FIG.
3 is a speed increasing flow path in which the flow velocity gradually increases as approaching the depression 21. For example, the outflow end side portion 22 of the valve chamber 6
, The bottom is gradually reduced axially symmetrically as approaching the depression 21. Ru gradually reduced as approaching to the recess 21 the effective channel cross section. [0017] Then, flows into the recess 21 becomes Re accelerated flow in the flow path 23 of the 21 immediately preceding recesses fluid hardly secondary vortices in the recesses 21 occurs and easily separated from the fluid recess 21 recess 21
, The outflow angle θ 2 increases, and the fluid force F decreases. According to the present invention, an inflow passage and an outflow passage are communicated with each other at two locations separated in the axial direction of a spool hole, and a valve chamber having a circumferential groove is formed at the center of the spool. fitted movably spool in the axial direction in the spool bore, fluid or inlet channel
Flows into the valve chamber, passes through the communication between the valve chamber and the
In the spool valve that controls the pressure or flow rate of the inflow path or the outflow path by the opening degree of the communicating portion between the valve chamber and the outflow path , the valve chamber forms a smooth depression by bending the end face of the outflow end, the angle between the outer peripheral surface of the outlet end and the outlet roadside land of the recess is at an acute angle, the flow path just before the depression, and the accelerated flow path gradually reduces the effective channel cross section toward the recess, the flow
The body gradually accelerates in the speed increasing channel just before the dent and flows into the dent
And change the direction along the dent, and connect the communication between the valve chamber and the outflow passage.
It is characterized by passing through . The depression can be axially symmetrical with an arcuate cross section. It is preferable that the angle between the outflow end of the recess and the outer peripheral surface of the outflow path side land is 80 degrees or less. The bottom of the valve chamber at the outflow end can be gradually reduced axially symmetrically as it approaches the depression. It is preferable that the central portion of the valve chamber be a speed increasing flow path or a constant velocity flow path. According to the present invention, the outflow angle of the fluid flowing out of the valve chamber to the outflow path increases, and the fluid force decreases. It is easy to move the spool to a desired position, and it is easy to control the pressure and flow rate of the inflow path or the outflow path. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First Example (See FIGS. 1 to 9) The spool valve of the present example has a valve chamber 6 having a circumferential groove having a cross-sectional shape different from that of the related art at the center of the spool 5. Are formed axially symmetrically. As shown in FIG. 1, a part of the valve chamber 6 is curved at the outflow end so as to form a smooth bow-shaped cross section 21 axially symmetrically.
Θ between the outflow end of the lands and the outer peripheral surface of the outflow path 4 side land 8;
That is, the angle θ of the outflow end of the depression 21 is set to 80 degrees or less. As shown in FIG. 1, the outflow end portion 22 of the valve chamber 6 gradually becomes shallower axially symmetrically as it approaches the depression 21. Channel 23 having a ring-shaped cross section immediately before depression 21
Is a speed-increasing flow path that gradually decreases as the effective flow path cross section approaches the depression 21 and gradually increases as the flow velocity approaches the depression 21. The outflow end at the bottom of the valve chamber 6 is
1 is smoothly connected to the inflow end. As shown in FIG. 1, the remaining portion of the valve chamber 6 except for the outflow end side portion 22 gradually becomes deeper axially symmetrically as it approaches the depression 21. The central part of the valve chamber 6
The speed increasing channel 24 or the constant speed channel is connected to the speed increasing channel 23 on the outflow end side portion of the valve chamber 6. The other structure is the same as that of the conventional example shown in FIG. As shown in FIG. 1, a fluid such as hydraulic oil flows from the inflow passage 3 into the inflow end portion of the valve chamber 6 and passes through the speed increasing flow path 24 or the constant velocity flow path. Flows into 23,
The speed increases in the speed increasing flow path 23 and flows into the depression 21, changes its direction along the smooth depression 21, passes through the communication portion 9 between the valve chamber 6 and the outflow passage 4, that is, the throttle portion 9, and has a large outflow angle θ. Outflow channel 4 at 2
Leaked to In the hydraulic control circuit of the automatic transmission for an automobile, an oil pump directly connected to the engine and a line pressure passage for operating the transmission mechanism are connected to the inflow passage 3 of the spool valve of this embodiment, and the outflow passage 4 is connected to the outflow passage 4. In the drain passage, spool 5
When the line pressure is applied to one end to move the spool 5 by the line pressure or the like and the line pressure is controlled by the position of the spool 5, that is, the opening x of the throttle unit 9, the direction in which the opening x of the throttle unit 9 is decreased. FIG. 2 shows the fluid force F acting on
As shown in FIG. 12, the shape changes into a V-shape depending on the degree of opening x of the throttle unit 9, but as compared with the conventional example F shown in FIG.
The absolute value is small, and the change due to the opening x of the throttle unit 9 is small. The angle θ of the outflow end of the depression 21 is 70 degrees in the present embodiment and 90 degrees in the conventional example. The diameter D of each of the spools 5 is 12.5 mm. Both fluids have a temperature of 7
0 ° C., density 0.834 kgf / cm 3 , kinematic viscosity 0.15 cm 2 / s. In the spool valve of this embodiment, the embodiment A in which the angle θ of the outflow end of the recess 21 is 70 degrees, the embodiment B in which the angle θ is 80 degrees, and the valve chamber in which the recess 21 is eliminated as shown in FIG. In Comparative Example C in which the outflow end angle θ of No. 6 was 90 degrees,
The fluid force F is obtained under the same conditions, and the fluid force F and the angle θ between the outflow end are obtained.
FIG. 4 shows the relationship. As is clear from this figure, when the angle θ of the outflow end becomes 80 degrees or less,
The fluid force F is greatly reduced. Further, the above-mentioned Examples A, B and Comparative Examples C, Comparative Example D as shown in FIG. 5, Comparative Example E as shown in FIG. 6, and the conventional example shown in FIG. About F
When the fluid force F is obtained under the same conditions, as shown in FIG. 7, the fluid force F is small in Example A and Example B, but large in Comparative Example C, Comparative Example D, Comparative Example E, and Conventional Example F. . The reason is that there is no depression in Comparative Examples C, E and Conventional Example F, and in Comparative Example D, the flow path 23 immediately before the depression 21 is a deceleration flow path and not a speed-up flow path. It is recognized that it is. For each of Examples A and B, Comparative Examples C, D and E, and Conventional Example F, a flow diagram of time-average values of axially symmetric, unsteady, incompressible and viscous flows under the same conditions is obtained. , As shown in FIG. As is clear from this figure, Example A
In Example B, the generation of the secondary vortex in the depression 21 is suppressed, and the outflow angle θ 2 is increased. In Comparative Example D, a secondary vortex is generated in the depression 21 to suppress the turning of the flow, and the outflow angle θ 2 is reduced. In Comparative Example C, Comparative Example E and Conventional Example F, the outflow angle θ 2 is small. For Comparative Example G as shown in FIG. 9, the fluid force F is smaller than that of Conventional Example F but larger than that of Example A, as shown as Comparative Example G in FIG. In the embodiment A, in the range where the opening degree x of the throttle unit 9 is small, that is, in the range where the fluid force F is large, the fluid force F
Is greatly reduced. <Second and third examples (see FIGS. 10 and 11)
> The spool valve of the second example is, as shown in FIG.
Outflow end of recess 21 formed in the end face of outflow end and outflow path 4
A narrow flat portion 31 orthogonal to the outer peripheral surface of the land 8 is formed axially symmetrically between the outer peripheral surfaces of the side lands 8. Valve room 6
A stepped concave portion 32 is formed axially symmetrically at the inflow end side portion. The other points are the same as in the first example. In the spool valve of the third example, as shown in FIG. 11, the depth of the portion other than the outflow end side portion of the valve chamber 6 is made constant. The other points are the same as in the first example. The spool valves of the first to third examples are also used in hydraulic control circuits other than the automatic transmission hydraulic control circuit described above. For example, the pressure of the fluid acting on one end of the spool 5 of the spool valve is increased or decreased by a proportional pressure reducing valve that controls an adjustment pressure by an electric signal, and the pressure or flow rate of the inflow passage 3 or the outflow passage 4 of the spool valve is proportionally increased. It is used for a hydraulic control circuit that controls in proportion to the electric signal input to the pressure reducing valve. Then, the control error based on the fluid force F decreases.
【図面の簡単な説明】
【図１】本発明の実施形態の第１例のスプール弁の部分
縦断端面図。
【図２】スプール弁における流体力と絞り部の開度の関
係を示す線図。
【図３】比較例Ｃのスプール弁の部分縦断端面図。
【図４】スプール弁における流体力と流出端の角度の関
係を示す線図。
【図５】比較例Ｄのスプール弁の部分縦断端面図。
【図６】比較例Ｅのスプール弁の部分縦断端面図。
【図７】スプール弁における流体力と弁室の断面形状の
関係を示す線図。
【図８】スプール弁における流線図。
【図９】比較例Ｇのスプール弁の部分縦断端面図。
【図１０】本発明の実施形態の第２例のスプール弁の部
分縦断端面図。
【図１１】本発明の実施形態の第３例のスプール弁の部
分縦断端面図。
【図１２】従来例Ｆのスプール弁の部分縦断面図。
【図１３】従来例Ｆのスプール弁を使用した油圧制御回
路の部分図。
【符号の説明】
２ スプール孔
３ 流入路
４ 流出路
５ スプール
６ 弁室
９ 弁室と流出路の連通部，絞り部
２１ 窪み
２２ 弁室の流出端側部分
２３ 窪み直前の増速流路
θ 窪みの流出端と流出路側ランドの外周面の間の角度
ｘ 絞り部の開度BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a partial longitudinal sectional end view of a spool valve according to a first example of an embodiment of the present invention. FIG. 2 is a diagram showing a relationship between a fluid force in a spool valve and an opening degree of a throttle portion. FIG. 3 is a partial longitudinal sectional end view of a spool valve of Comparative Example C. FIG. 4 is a diagram showing the relationship between the fluid force and the angle of the outflow end in the spool valve. FIG. 5 is a partial longitudinal sectional end view of a spool valve of Comparative Example D. FIG. 6 is a partial longitudinal sectional end view of a spool valve of Comparative Example E. FIG. 7 is a diagram showing the relationship between the fluid force in the spool valve and the cross-sectional shape of the valve chamber. FIG. 8 is a streamline diagram of a spool valve. FIG. 9 is a partial longitudinal sectional end view of a spool valve of Comparative Example G. FIG. 10 is a partial longitudinal sectional end view of a spool valve according to a second example of the embodiment of the present invention. FIG. 11 is a partial longitudinal sectional end view of a spool valve according to a third example of the embodiment of the present invention. FIG. 12 is a partial longitudinal sectional view of a spool valve of a conventional example F. FIG. 13 is a partial view of a hydraulic control circuit using the spool valve of the conventional example F. [Description of Signs] 2 Spool hole 3 Inflow path 4 Outflow path 5 Spool 6 Valve chamber 9 Communication part between valve chamber and outflow path, constriction 21 Recess 22 Outflow end side portion of valve chamber 23 Speed-increase flow path θ immediately before depression Angle x between the outflow end of the depression and the outer peripheral surface of the outflow path side land x Opening of the throttle
───────────────────────────────────────────────────── フロントページの続き (72)発明者 山下 俊哉 愛知県豊田市トヨタ町１番地 トヨタ自 動車株式会社内 (56)参考文献 特開 昭60−125471（ＪＰ，Ａ) 特開 昭60−172784（ＪＰ，Ａ) 実開 昭62−126668（ＪＰ，Ｕ) 実開 昭57−163057（ＪＰ，Ｕ) 特公 昭63−668（ＪＰ，Ｂ２) 実公 昭59−12458（ＪＰ，Ｙ１) (58)調査した分野(Int.Cl.7，ＤＢ名) F16K 3/24 F16K 47/04 ──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Toshiya Yamashita 1 Toyota Town, Toyota City, Aichi Prefecture Inside Toyota Motor Corporation (56) References JP-A-60-125471 (JP, A) JP-A-60-172784 (JP, A) Japanese Utility Model Showa 62-126668 (JP, U) Japanese Utility Model Showa 57-163057 (JP, U) Japanese Patent Publication No. 63-668 (JP, B2) Japanese Utility Model Showa 59-12458 (JP, Y1) ( 58) Field surveyed (Int.Cl. 7 , DB name) F16K 3/24 F16K 47/04
Claims (1)
に離れた２個所に連通し、スプールの中央部に周溝の弁
室を形成し、スプール孔にスプールを軸芯方向に移動可
能に嵌合し、流体が流入路から弁室に流入して弁室と流
出路の連通部を経て流出路に流出し、弁室と流出路の連
通部の開度によって流入路または流出路の圧力や流量を
制御するスプール弁において、 弁室は、流出端の端面を湾曲して滑らかな窪みを形成
し、窪みの流出端と流出路側ランドの外周面との間の角
度を鋭角にし、 窪み直前の流路は、窪みに近付くに従って実効流路断面
を徐々に減少させて増速流路にし、 流体は、窪み直前の増速流路で徐々に増速して窪みに流
入し、窪みに沿って向きを変え 、弁室と流出路の連通部
を通過する構成にしたことを特徴とするスプール弁。(57) [Claim 1] An inflow passage and an outflow passage communicate with two locations separated in the axial direction of a spool hole, and a valve chamber having a circumferential groove is formed in a center portion of the spool. The spool is fitted in the hole so as to be movable in the axial direction, and the fluid flows into the valve chamber from the inflow path and flows into the valve chamber.
In the spool valve, which flows out to the outflow path through the outflow path and controls the pressure and flow rate of the inflow path or outflow path by the degree of opening of the communication section between the valve chamber and the outflow path, the valve chamber has a curved end face at the outflow end the effective flow path cross-section according to form a smooth depression, the angle between the outer peripheral surface of the outlet end and the outlet roadside land of the recess at an acute angle, the flow path just before the depression, to approach the recess
Is gradually reduced to form a speed increasing flow path, and the fluid gradually increases in speed in the speed increasing flow path immediately before the depression and flows into the depression.
A spool valve which is adapted to enter and change its direction along the depression so as to pass through a communicating portion between the valve chamber and the outflow passage.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28483496A JP3407565B2 (en) | 1996-10-28 | 1996-10-28 | Spool valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28483496A JP3407565B2 (en) | 1996-10-28 | 1996-10-28 | Spool valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH10132096A JPH10132096A (en) | 1998-05-22 |
| JP3407565B2 true JP3407565B2 (en) | 2003-05-19 |
Family
ID=17683624
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP28483496A Expired - Fee Related JP3407565B2 (en) | 1996-10-28 | 1996-10-28 | Spool valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3407565B2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7431043B2 (en) * | 2005-03-17 | 2008-10-07 | Borgwarner Inc. | Automatic transmission having a pressure regulator with flow force compensation |
| US7770597B2 (en) | 2005-08-17 | 2010-08-10 | Aisin Aw Co., Ltd. | Spool valve device |
| DE102013014671A1 (en) | 2013-09-03 | 2015-03-05 | Hydac Technology Gmbh | Ventilbaukomponenten |
| JP2015169212A (en) | 2014-03-04 | 2015-09-28 | 株式会社デンソー | fluid control valve |
| WO2018125321A1 (en) * | 2016-12-30 | 2018-07-05 | Parker-Hannifin Corporation | Valve with gradual flow area changes |
| KR102108161B1 (en) * | 2018-12-21 | 2020-05-07 | 주식회사 현대케피코 | Solenoid valve |
-
1996
- 1996-10-28 JP JP28483496A patent/JP3407565B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH10132096A (en) | 1998-05-22 |
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| LAPS | Cancellation because of no payment of annual fees |