JPH0335541B2 - - Google Patents
Info
- Publication number
- JPH0335541B2 JPH0335541B2 JP58094286A JP9428683A JPH0335541B2 JP H0335541 B2 JPH0335541 B2 JP H0335541B2 JP 58094286 A JP58094286 A JP 58094286A JP 9428683 A JP9428683 A JP 9428683A JP H0335541 B2 JPH0335541 B2 JP H0335541B2
- Authority
- JP
- Japan
- Prior art keywords
- orifice
- spring
- control
- pressure fluid
- spool
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 239000012530 fluid Substances 0.000 claims description 41
- 229910001285 shape-memory alloy Inorganic materials 0.000 claims description 4
- 238000006073 displacement reaction Methods 0.000 claims description 2
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 230000001846 repelling effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- KHYBPSFKEHXSLX-UHFFFAOYSA-N iminotitanium Chemical compound [Ti]=N KHYBPSFKEHXSLX-UHFFFAOYSA-N 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 229910001000 nickel titanium Inorganic materials 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000002940 repellent Effects 0.000 description 1
- 239000005871 repellent Substances 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Power Steering Mechanism (AREA)
- Temperature-Responsive Valves (AREA)
- Safety Valves (AREA)
Description
【発明の詳細な説明】
＜産業上の利用分野＞
本発明は、動力舵取装置用流量制御装置に関す
るものである。DETAILED DESCRIPTION OF THE INVENTION <Industrial Field of Application> The present invention relates to a flow control device for a power steering device.
＜従来技術＞
従来、上記機能を有する流量制御装置として、
ポンプ回転数の上昇による吐出流量の増加に基づ
いて制御絞り前後に圧力差を発生させ、この圧力
差によつて制御スプールをスプリングの撥力に抗
して変位させてオリフイスの開口面積を可変制御
し、第１図Ａに示すようにポンプ回転数Ｎが一定
の回転数になると吐出流量Ｑを降下させるように
して自転車の高速走行時のハンドル操作に安定を
与えるようにしたものがある。<Prior art> Conventionally, as a flow control device having the above functions,
A pressure difference is generated before and after the control throttle based on the increase in discharge flow rate due to an increase in pump rotation speed, and this pressure difference causes the control spool to be displaced against the repulsive force of the spring to variably control the opening area of the orifice. However, as shown in FIG. 1A, there is a device that lowers the discharge flow rate Q when the pump rotational speed N reaches a constant rotational speed, thereby stabilizing the steering wheel operation when the bicycle is running at high speed.
しかしながらかかる従来装置によると、低温時
では圧力流体の粘性が大きいので制御絞り前後の
差圧が大きくなり、その結果ポンプの回転数が十
分にあがらないうちに制御スプールが変位してオ
リフイスを絞つてしまい、第１図Ｂに示す流量特
性になる。このため圧力流体の低温時において
は、動力舵取装置へ供給させる圧力流体が不足す
る問題点があつた。 However, with such conventional devices, the viscosity of the pressure fluid is high at low temperatures, so the differential pressure across the control throttle becomes large, and as a result, the control spool displaces and throttles the orifice before the pump rotation speed increases sufficiently. As a result, the flow rate characteristic becomes as shown in FIG. 1B. Therefore, when the pressure fluid is at a low temperature, there is a problem that the pressure fluid supplied to the power steering device is insufficient.
＜発明の目的＞
本発明は従来のこのような問題を解決するため
になされたものであり、その目的とするところは
低温時における圧力流体の粘性変化にかかわら
ず、圧力流体の常温時における流量特性と同様の
流量特性が得られるようにし、動力舵取装置へ供
給される圧力流体が低温時でもダウンしないよう
にすることである。<Objective of the Invention> The present invention has been made to solve the above-mentioned conventional problems, and its purpose is to improve the flow rate of pressurized fluid at room temperature, regardless of the viscosity change of pressure fluid at low temperature. The objective is to obtain flow rate characteristics similar to the characteristics and to prevent the pressure fluid supplied to the power steering device from dropping down even when the temperature is low.
＜発明の構成＞
本発明は上記目的を達成するためになされたも
ので、前記制御スプールに対して撥力を付与する
スプリング、圧力流体の低温時では前記スプリン
グにより自由長が短くなるように変形し、常温時
では前記スプリングによる前記制御スプールを作
用する撥力を減少すべく自由長が長くなる形状を
記憶した形状記憶合金製のコイルスプリングを備
えたことを特徴とする動力舵取装置用流量制御装
置に関する。<Structure of the Invention> The present invention has been made to achieve the above object, and includes a spring that applies a repulsive force to the control spool, and a spring that deforms so that its free length becomes shorter when the pressure fluid is at a low temperature. A flow rate for a power steering device, characterized in that the coil spring is made of a shape memory alloy and has a shape in which the free length becomes longer in order to reduce the repulsive force exerted on the control spool by the spring at room temperature. Regarding a control device.
＜実施例＞
以下本発明の実施例を図面に基づいて説明す
る。第２図において１０はポンプハウジングで、
このポンプハウジング１０には、収納孔１１が貫
通して設けられていて、この収納孔１１の一端に
ユニオン２１が液密的に螺着されており、また収
納孔１１の他端に止め栓２５が液密的に嵌着され
ている。<Examples> Examples of the present invention will be described below based on the drawings. In Fig. 2, 10 is a pump housing;
This pump housing 10 is provided with a storage hole 11 passing through it, a union 21 is screwed into one end of the storage hole 11 in a fluid-tight manner, and a stopper 25 is attached to the other end of the storage hole 11. are fitted in a liquid-tight manner.
収納孔１１内にスプール弁２２が摺動可能に嵌
挿され、収納孔１１内に第１弁室３２と第２弁室
３３を形成している。また、スプール弁２２は第
２弁室３３内に介装したスプリング２６により付
勢され、スプール弁２２の進退は供給通路１２と
ポンプハウジング１０に設けたバイパス通路１３
を連通あるいは遮断させるようになつている。な
お、供給通路１２は流体ポンプの吐出室に連通さ
れ、バイパス通路１３は流体ポンプの吸入室に連
通されている。 A spool valve 22 is slidably inserted into the storage hole 11, and a first valve chamber 32 and a second valve chamber 33 are formed in the storage hole 11. Further, the spool valve 22 is biased by a spring 26 interposed in the second valve chamber 33, and the spool valve 22 moves forward and backward through the supply passage 12 and the bypass passage 10 provided in the pump housing 10.
It is designed to allow communication or interruption. Note that the supply passage 12 communicates with a discharge chamber of the fluid pump, and the bypass passage 13 communicates with a suction chamber of the fluid pump.
前記ユニオン２１の内孔内には制御スプール２
３がユニオン２１の内孔の外端側に嵌着したオリ
フイス形成部材２４と、ユニオン２１の内孔の内
端側段部２１ｂとの間において摺動可能に嵌挿さ
れている。この制御スプール２３には、第１弁室
３２と連通する流通孔２３ａが形成されており、
この流通孔２３ａは前記オリフイス形成部材２４
に形成された各オリフイス２４ａ，２４ｂを通し
て、ユニオン２１の送出口２１ａに連通してい
る。なお、ユニオン２１の送出口２１ａは動力舵
取装置に接続されている。 A control spool 2 is disposed within the inner hole of the union 21.
3 is slidably fitted between the orifice forming member 24 fitted into the outer end of the inner hole of the union 21 and the inner step 21b of the inner hole of the union 21. This control spool 23 is formed with a communication hole 23a that communicates with the first valve chamber 32.
This communication hole 23a is connected to the orifice forming member 24.
It communicates with the outlet 21a of the union 21 through orifices 24a, 24b formed in the union 21. Note that the outlet 21a of the union 21 is connected to a power steering device.
前記オリフイス形成部材２４には、制御ノズル
２４ｃを備えており、この制御ノズル２４ｃは各
オリフイス２４ａ，２４ｂの後流側を、ユニオン
２１およびポンプハウジング１０に設けた連通孔
２１ｄ，１４を通して第２弁室３３に連通させて
いる。これにより、各オリフイス２４ａ，２４ｂ
の後流側流体の一部が第２弁室３３内に導かれ、
スプール弁２２の両端に各オリフイス２４ａ，２
４ｂの前後の圧力が作用し、各オリフイス２４
ａ，２４ｂの前後の差圧に応じてスプール弁２２
が軸方向へ移動して、上記差圧を一定に保持すべ
くバイパス通路１３の開度を調整する。 The orifice forming member 24 is equipped with a control nozzle 24c, which connects the downstream side of each orifice 24a, 24b to the second valve through communication holes 21d, 14 provided in the union 21 and the pump housing 10. It communicates with room 33. As a result, each orifice 24a, 24b
A part of the downstream fluid is guided into the second valve chamber 33,
Each orifice 24a, 2 at both ends of the spool valve 22
4b is applied before and after each orifice 24.
spool valve 22 according to the differential pressure before and after a and 24b.
moves in the axial direction to adjust the opening degree of the bypass passage 13 in order to keep the differential pressure constant.
またユニオン２１に供給通路１２とユニオン２
１の内端側段部２１ｂとを連通する圧力導入孔２
１ｃが開口している。制御スプール２３とオリフ
イス形成部材２４間にはオリフイス形成部材２４
に撥力を付与する鉄系材質からなるスプリング２
７が介装され、ユニオン２１と制御スプール２３
間にはNi−Tiからなる形状記憶合金製のコイル
スプリング２８が介装されている。このコイルス
プリング２８は、圧力流体が常温時（０℃以上）
にはその自由長が長くなる形状を記憶しており、
スプリング２７と反対方向の撥力を制御スプール
２３に付与し、かつ圧力流体の低温時には撥力が
なくなり、スプリング２７によつて自由長が短く
なるように変形する。この結果、圧力流体の低温
時においては、制御スプール２３にスプリング２
７による撥力が作用し、圧力流体の常温時におい
ては、制御スプール２３にスプリング２７の撥力
からコイルスプリング２８の撥力を差し引いた押
圧力が作用する。 In addition, the supply passage 12 and the union 2 are connected to the union 21.
Pressure introduction hole 2 communicating with the inner end side step portion 21b of 1
1c is open. An orifice forming member 24 is provided between the control spool 23 and the orifice forming member 24.
Spring 2 made of iron-based material that provides repellency to
7 is interposed, the union 21 and the control spool 23
A coil spring 28 made of a shape memory alloy made of Ni-Ti is interposed between the two. This coil spring 28 operates when the pressure fluid is at room temperature (0°C or higher).
remembers the shape that increases its free length,
A repulsive force is applied to the control spool 23 in the opposite direction to that of the spring 27, and when the pressure fluid is at a low temperature, the repelling force disappears and the spring 27 deforms so that its free length becomes shorter. As a result, when the pressure fluid is at a low temperature, the spring 2 is attached to the control spool 23.
When the pressure fluid is at room temperature, a pressing force obtained by subtracting the repulsive force of the coil spring 28 from the repulsive force of the spring 27 acts on the control spool 23.
前記ユニオン２１の内端外周と前記収納孔１１
の内周面に制御絞り３１が形成されており、この
制御絞り３１を介して供給通路１２と第１弁室３
２とを連通するようになつている。この制御絞り
３１は、供給通路１２に供給される圧力流体の吐
出流量が多くなると、その流路抵抗により供給通
路１２と第１弁室３２間に圧力差が生じ、この圧
力差に応じて前記制御スプール２３がスプリング
２７に逆らつて軸方向に変位するようになつてい
る。供給通路１２と第１弁室３２間の圧力差が大
きいオリフイス形成部材２４の第１オリフイス２
４ａは制御スプール２３によつて閉じられ、第２
オリフイス２４ｂのみの流通経路に絞りこまれ
る。 The outer circumference of the inner end of the union 21 and the storage hole 11
A control throttle 31 is formed on the inner peripheral surface of the control throttle 31, and the supply passage 12 and the first valve chamber 3 are connected to each other via the control throttle 31.
It is designed to communicate with 2. When the discharge flow rate of the pressure fluid supplied to the supply passage 12 increases, a pressure difference is generated between the supply passage 12 and the first valve chamber 32 due to the flow passage resistance, and the control throttle 31 controls the Control spool 23 is adapted for axial displacement against spring 27. The first orifice 2 of the orifice forming member 24 has a large pressure difference between the supply passage 12 and the first valve chamber 32
4a is closed by the control spool 23 and the second
The distribution route is narrowed down to only the orifice 24b.
このように構成した流量制御装置においては、
車両エンジンにより流体ポンプが駆動されると、
圧力流体が流体ポンプの吐出室から供給通路１２
に供給され、流体ポンプの回転速度が低い場合に
は圧力流体の吐出流量が少ないため、スプール弁
２２はバイパス通路１３を閉じて圧力流体の全量
を各オリフイス２４ａ，２４ｂを経て動力舵取装
置へ給送させるが、流体ポンプの回転数の上昇に
応じて圧力流体の吐出流量が増大すると、スプー
ル弁２２はオリフイス２４ａ，２４ｂ前後の差圧
を一定にすべく摺動してバイパス通路１３を開
き、圧力流体の余剰流をバイパス通路１３を通し
て流体ポンプの吸入室へ還流させる。この結果、
動力舵取装置へ給送される圧力流体は、各オリフ
イス２４ａ，２４ｂにより決定される。 In the flow control device configured in this way,
When the fluid pump is driven by the vehicle engine,
Pressurized fluid is supplied from the discharge chamber of the fluid pump to the supply passage 12
When the rotational speed of the fluid pump is low, the discharge flow rate of pressure fluid is small, so the spool valve 22 closes the bypass passage 13 and directs the entire amount of pressure fluid to the power steering device via each orifice 24a, 24b. However, when the discharge flow rate of pressurized fluid increases as the rotational speed of the fluid pump increases, the spool valve 22 slides to keep the differential pressure across the orifices 24a, 24b constant and opens the bypass passage 13. , the excess flow of pressure fluid is returned through the bypass passage 13 to the suction chamber of the fluid pump. As a result,
The pressure fluid delivered to the power steering system is determined by each orifice 24a, 24b.
また、車両の高速走行への移行に伴い流体ポン
プの回転数がさらに上昇して、供給通路１２へ供
給される圧力流体の吐出流量が増大すると、制御
絞り３１における流路抵抗により供給通路１２内
の流体圧力が上昇し、供給通路１２と第１弁室３
２間に差圧が生じるとともに、供給通路１２の圧
力は圧力導入孔２１ｃを通して制御スプール２３
をスプリング２７に抗して摺動させる押圧力とし
て作用する。このため、圧力流体の吐出流量の増
大に応じて供給通路１２の圧力がスプリング２７
の付勢力に打勝つまで高まると、制御スプール２
３はスプリング２７に抗して漸次摺動し、最後に
第１オリフイス２４ａが完全に閉じられるため、
動力舵取装置へ給送される圧力流体の供給流量
は、第２オリフイス２４ｂで決定される。ところ
で、圧力流体が低温の場合は、流体の粘性が大き
いため制御スプール２３に流体の常温に比べて供
給通路１２と第１弁室３２間に大きな差圧が作用
するが、この常温時と低温時の差圧分だけ大きめ
のスプリング２７に用いたことにより、ポンプの
回転数が十分に上がつてから、第１オリフイス２
４ａを制御スプール２３によつて閉じるようにな
る。流体の常温の場合は、コイルスプリング２８
に撥力を持たせ、コイルスプリング２８によりス
プリング２７の撥力を減少させるようにすること
により低温の場合と同数のポンプの回転数により
第１オリフイス２４ａが制御スプール２３により
閉じるようになる。 Furthermore, when the rotational speed of the fluid pump further increases as the vehicle moves to high-speed running, and the discharge flow rate of the pressure fluid supplied to the supply passage 12 increases, the flow resistance in the control throttle 31 causes the inside of the supply passage 12 to increase. The fluid pressure of the supply passage 12 and the first valve chamber 3 increases.
A differential pressure is generated between the two, and the pressure in the supply passage 12 is transferred to the control spool 23 through the pressure introduction hole 21c.
acts as a pressing force that causes the spring 27 to slide against the spring 27. Therefore, the pressure in the supply passage 12 is increased by the spring 27 in response to an increase in the discharge flow rate of the pressure fluid.
When the force increases until it overcomes the biasing force of , the control spool 2
3 gradually slides against the spring 27, and finally the first orifice 24a is completely closed.
The supply flow rate of the pressure fluid fed to the power steering device is determined by the second orifice 24b. By the way, when the pressure fluid is at a low temperature, the viscosity of the fluid is high, so a large pressure difference acts on the control spool 23 between the supply passage 12 and the first valve chamber 32 compared to when the fluid is at room temperature. By using a spring 27 that is larger by the differential pressure at the time, the first orifice 2
4a is now closed by the control spool 23. If the fluid is at room temperature, the coil spring 28
By making the coil spring 28 have a repulsive force and reducing the repulsive force of the spring 27, the first orifice 24a can be closed by the control spool 23 at the same number of revolutions of the pump as in the case of low temperature.
＜発明の効果＞
以上述べたように本発明においては、オリフイ
ス側に設けられ制御スプールに対して撥力を付与
するスプリング、制御スプールに対してオリフイ
スと反対側に設けられ前記スプリングにより圧力
流体の低温時では自由長が短くなるように変形
し、常温時では前記スプリングによる前記制御ス
プールに作用する撥力を打ち消すべく自由長が長
くなる形状を記憶した形状記憶合金製のコイルス
プリングを備えたため低温時における圧力流体の
粘性変化にかかわらず、圧力流体の常温時におけ
る流量特性と同様の流量特性が得られ、動力舵取
装置へ供給される圧力流体が低温時でも所定の流
量が得られる利点がある。<Effects of the Invention> As described above, in the present invention, a spring is provided on the orifice side to apply a repelling force to the control spool, and a spring is provided on the opposite side of the control spool from the orifice to apply repellent force to the control spool. It is equipped with a coil spring made of a shape memory alloy that memorizes a shape that deforms so that its free length becomes short at low temperatures and becomes long at room temperature to cancel out the repulsive force exerted on the control spool by the spring. Regardless of changes in the viscosity of the pressure fluid over time, flow characteristics similar to those of the pressure fluid at room temperature can be obtained, and the advantage is that a predetermined flow rate can be obtained even when the pressure fluid supplied to the power steering device is at low temperature. be.
図面は本発明の実施例を示すもので、第１図は
ポンプ回転数に対する流量特性を示すグラフ、第
２図は本発明の流量制御装置を示す断面図であ
る。
１２……供給通路、１３……バイパス通路、２
２……スプール弁、２３……制御スプール、２４
ａ，２４ｂ……オリフイス、２７……スプリン
グ、２８……コイルスプリング、３１……制御絞
り。
The drawings show an embodiment of the present invention, and FIG. 1 is a graph showing flow rate characteristics with respect to pump rotation speed, and FIG. 2 is a sectional view showing a flow rate control device of the present invention. 12... Supply passage, 13... Bypass passage, 2
2... Spool valve, 23... Control spool, 24
a, 24b...orifice, 27...spring, 28...coil spring, 31...control aperture.
Claims (1)
して動力舵取装置に送出される圧力流体ならびに
その圧力流体の一部を余剰流としてポンプの吸入
側に還流すべくバイパス通路の開度を調整する流
量調整用スプール弁、前記供給通路内に設けられ
た制御絞り前後の圧力差に応じてオリフイス側に
設けられたスプリングを弾性変形させながら前記
オリフイスを絞り方向に変位して前記オリフイス
の開度を制御する制御スプール、制御スプールに
対し前記オリフイスと反対側に設けられ圧力流体
の低温時では前記スプリングにより自由長が短く
なるように変形し、常温時は前記制御スプールを
前記スプリングに抗してオリフイスを絞り方向に
変位させるべく自由長が長くなる形状を記憶した
形状記憶合金製のコイルスプリングを備えたこと
を特徴とする動力舵取装置用流量制御装置。1 Pressure fluid sent to the power steering device from the supply passage leading to the pump via the orifice, and flow rate adjustment that adjusts the opening degree of the bypass passage so that a portion of the pressure fluid flows back to the suction side of the pump as surplus flow. A spool valve for controlling the opening of the orifice is controlled by displacing the orifice in the throttle direction while elastically deforming a spring provided on the orifice side according to the pressure difference before and after the control throttle provided in the supply passage. A control spool is provided on the opposite side of the control spool from the orifice, and when the pressure fluid is at a low temperature, the spring deforms the free length to shorten it, and when the temperature is normal, the control spool is compressed by the orifice against the spring. 1. A flow control device for a power steering device, comprising a coil spring made of a shape memory alloy whose free length memorizes a shape in which the free length becomes longer in order to cause displacement in a direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58094286A JPS59220456A (en) | 1983-05-27 | 1983-05-27 | Flow volume control device for motor steering device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58094286A JPS59220456A (en) | 1983-05-27 | 1983-05-27 | Flow volume control device for motor steering device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59220456A JPS59220456A (en) | 1984-12-11 |
| JPH0335541B2 true JPH0335541B2 (en) | 1991-05-28 |
Family
ID=14106011
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP58094286A Granted JPS59220456A (en) | 1983-05-27 | 1983-05-27 | Flow volume control device for motor steering device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59220456A (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62103776U (en) * | 1985-12-21 | 1987-07-02 | ||
| JPH0191179U (en) * | 1987-12-09 | 1989-06-15 | ||
| CA3148837A1 (en) * | 2019-09-20 | 2021-03-25 | Parker-Hannifin Corporation | Pump system with over-temperature prevention |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5824692Y2 (en) * | 1979-10-11 | 1983-05-27 | エヌオーケー株式会社 | thermo valve |
| JPS56150680U (en) * | 1980-04-11 | 1981-11-12 | ||
| JPS56168474U (en) * | 1980-05-16 | 1981-12-12 | ||
| JPS6332783Y2 (en) * | 1980-11-19 | 1988-09-01 |
-
1983
- 1983-05-27 JP JP58094286A patent/JPS59220456A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS59220456A (en) | 1984-12-11 |
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