JPS6340365Y2 - - Google Patents
Info
- Publication number
- JPS6340365Y2 JPS6340365Y2 JP1980099811U JP9981180U JPS6340365Y2 JP S6340365 Y2 JPS6340365 Y2 JP S6340365Y2 JP 1980099811 U JP1980099811 U JP 1980099811U JP 9981180 U JP9981180 U JP 9981180U JP S6340365 Y2 JPS6340365 Y2 JP S6340365Y2
- Authority
- JP
- Japan
- Prior art keywords
- pump
- flow rate
- discharge
- bypass passage
- auxiliary
- 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
- 239000010720 hydraulic oil Substances 0.000 claims description 14
- 239000003921 oil Substances 0.000 claims description 13
- 230000001105 regulatory effect Effects 0.000 claims description 13
- 230000000694 effects Effects 0.000 description 7
- 238000010586 diagram Methods 0.000 description 4
- 241000234435 Lilium Species 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 239000000446 fuel Substances 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
Landscapes
- Details And Applications Of Rotary Liquid Pumps (AREA)
Description
【考案の詳細な説明】
〔産業上の利用分野〕
本考案は、動力舵取装置用ポンプ装置に係り、
特に、車両等の走行速度の上昇に伴ない舵取装置
への作動油の吐出流量を減少させるのに好適な動
力舵取装置用ポンプ装置に関する。[Detailed description of the invention] [Field of industrial application] The present invention relates to a pump device for a power steering device.
In particular, the present invention relates to a pump device for a power steering device suitable for reducing the discharge flow rate of hydraulic oil to a steering device as the traveling speed of a vehicle increases.
周知のように、動力舵取装置の操作力の軽減度
は、一般にポンプ装置からの作動油の供給量に比
例する。通常のポンプ装置の主軸はエンジン等の
駆動部に連結されているため、何らかの制御手段
を設けないと、高速走行時はポンプ回転数が高く
なり、作動油の吐出流量も多くなつて舵取装置が
異常に軽くなり、ハンドルの操作が不安定となる
危険がある。
As is well known, the degree of reduction in the operating force of the power steering device is generally proportional to the amount of hydraulic fluid supplied from the pump device. The main shaft of a normal pump device is connected to a driving part such as an engine, so unless some kind of control means is provided, the pump rotation speed will be high when driving at high speeds, and the discharge flow rate of hydraulic fluid will also increase, causing damage to the steering system. There is a risk that the handle will become abnormally light and the steering wheel will become unstable.
そこで従来は、基本的なポンプ装置として、舵
取装置に作動油を供給するポンプの吐出側と吸込
側とをバイパス通路を介して互に連通するととも
に、余剰吐出油を前記ポンプの吐出側から吸込側
に戻す流量調整弁をこのバイパス通路に設けたも
のが考えられた。これによると、設定吐出流量を
超える余剰油が流量調整弁によりポンプの吸込側
に戻されるので、第１図に流量特性曲線X1で示
すように、吐出流量はポンプ回転数の上昇に伴つ
て漸増後、ある一定値に留まる。つまり、高速走
行となつても、ハンドルの軽さは均一化する。 Therefore, conventionally, as a basic pump device, the discharge side and suction side of a pump that supplies hydraulic oil to the steering device are communicated with each other via a bypass passage, and the excess discharge oil is drained from the discharge side of the pump. It has been considered that a flow rate regulating valve that returns to the suction side is provided in this bypass passage. According to this, surplus oil exceeding the set discharge flow rate is returned to the suction side of the pump by the flow rate adjustment valve, so the discharge flow rate increases as the pump rotation speed increases, as shown by the flow rate characteristic curve X1 in Figure 1. After a gradual increase, it remains at a certain value. In other words, even when driving at high speeds, the steering wheel remains evenly light.
しかし、高速走行時には低速走行時よりもハン
ドル操作を重くするのが車両等の走行安全上望ま
しい。最近では、前記基本的なポンプ装置に補助
的な流量制御手段を加え、ポンプの高速回転時
は、逆に吐出流量を減少させることが考えられて
いる。例えば、流量制御弁の一部を利用してポン
プの吐出流量制御用絞り径を変化させる可変絞り
形のもの、または流量制御弁に付属するオリフイ
スよりもポンプ側の通路に設けたベンチユリによ
るベンチユリ効果を利用して流量制御弁を移動さ
せバイパス流路の開口面積を拡大するベンチユリ
形のものなどである。 However, when driving at high speeds, it is desirable to operate the steering wheel more heavily than when driving at low speeds in terms of driving safety. Recently, it has been considered to add an auxiliary flow rate control means to the basic pump device to reduce the discharge flow rate when the pump rotates at high speed. For example, a variable throttle type that uses a part of the flow control valve to change the orifice diameter for controlling the pump's discharge flow rate, or a vent lily effect created by a vent lily installed in the passage on the pump side of the orifice attached to the flow control valve. These include bench lily-shaped valves that use the flow rate control valve to expand the opening area of the bypass flow path.
ところが、これらの手段はいずれもポンプの吐
出側（高圧側）すなわち負荷側の不安定な流量に
基づいて吐出流量を制御するため、精度と信頼性
に問題がある。例えば、高速走行中ハンドルを切
つた時に流量が上昇して一瞬ハンドルが軽くなつ
たりすることがある。また、流量制御弁の一部を
利用したり、別にベンチユリを設けたりすること
は、限られたスペースに種々の機構を詰め込むこ
とになり、結局、構成が非常に複雑となる。
However, since all of these means control the discharge flow rate based on the unstable flow rate on the discharge side (high pressure side), that is, the load side of the pump, they have problems in accuracy and reliability. For example, when you turn the steering wheel while driving at high speed, the flow rate may increase and the steering wheel may become light for a moment. Furthermore, using a part of the flow control valve or providing a separate bench lily means cramming various mechanisms into a limited space, resulting in a very complicated configuration.
本考案の目的は、単純な構造で、高速走行時の
舵取装置への作動油の吐出流量を減少させること
が可能な動力舵取装置用ポンプ装置を提供するこ
とである。 An object of the present invention is to provide a pump device for a power steering device that has a simple structure and is capable of reducing the flow rate of hydraulic fluid discharged to the steering device during high-speed travel.
本考案は、上記目的を達成するために、舵取装
置に作動油を供給するポンプの吐出側と吸込側と
をバイパス通路を介して互いに連通するととも
に、余剰吐出油を前記ポンプの吐出側から吸込側
に戻す流量調整弁をこのバイパス通路に設けたも
のにおいて、前記ポンプの吐出側の流量調整弁よ
りも下流側部位と前記ポンプの吸込室部位とを補
助バイパス通路を介して互いに連通し、この補助
バイパス通路の途中に前記ポンプの吸込側を流れ
る作動油の油圧の大きさに応じて開閉し前記ポン
プの高速回転時のさらに余剰な吐出油を前記ポン
プの吐出側から吸込室に戻す補助流量調整弁を前
記流量調整弁とは別体設けた動力舵取装置用ポン
プ装置を提案するものである。
In order to achieve the above object, the present invention communicates the discharge side and suction side of a pump that supplies hydraulic oil to the steering device with each other via a bypass passage, and drains excess discharge oil from the discharge side of the pump. A flow regulating valve for returning the flow to the suction side is provided in the bypass passage, and a region downstream of the flow regulating valve on the discharge side of the pump and a suction chamber region of the pump are communicated with each other via an auxiliary bypass passage, This auxiliary bypass passage opens and closes in response to the hydraulic pressure of the hydraulic oil flowing on the suction side of the pump, and serves as an auxiliary bypass passage that returns excess discharge oil from the discharge side of the pump to the suction chamber when the pump rotates at high speed. The present invention proposes a pump device for a power steering device in which a flow rate adjustment valve is provided separately from the flow rate adjustment valve.
すなわち、ポンプの吸込側の圧力が負荷に直接
影響されないことを利用して、より安定した高速
回転時の吐出流量減少作用が行えるようにすると
ともに、比較的簡単な弁構成を実現した。また、
舵取装置への吐出流量の減少により配管抵抗が減
少するから、燃費の向上も図ることができる。 That is, by taking advantage of the fact that the pressure on the suction side of the pump is not directly affected by the load, a more stable discharge flow rate reduction effect during high-speed rotation can be performed, and a relatively simple valve configuration has been realized. Also,
Since piping resistance is reduced by reducing the discharge flow rate to the steering device, fuel efficiency can also be improved.
ポンプ装置内の作動油の状態を観察すると、第
２図に示すように、ポンプ吐出部１から吐出され
た作動油は高速走行時には、舵取装置のギヤボツ
クスヘの主流Ａと、流量調整弁２からバイパス通
路３を介してポンプ吸込室４へ分流Ｂとして戻る
余剰吐出油とに分かれる。この余剰吐出油は、タ
ンクからの吸込通路５を介する吸込油とバイパス
通路３内で合流し、吸込室４に流入する。この場
合、バイパス通路３の流量調整弁２側の部位(i)と
吸込室４側の部位(ii)とで圧力傾向を調べると、第
３図に示すように、(i)では負荷Ｐが、また(ii)で
は正圧Ｐが作用する（スーパーチヤージ効果と
いう）。吸込室部位(iii)ではさらに高い正圧Ｐが
作用する。つまり、ポンプの吸込側を流れる作動
油の油圧は各部で大きさが異なる。しかし、この
圧力差は吐出側と異なり、負荷の影響による変動
を生じることがなく、常時安定している。
Observing the state of the hydraulic oil in the pump device, as shown in Fig. 2, the hydraulic oil discharged from the pump discharge part 1 flows into the main stream A to the gearbox of the steering device and from the flow rate adjustment valve 2 when traveling at high speed. The excess discharged oil is separated into a branch flow B which returns to the pump suction chamber 4 via the bypass passage 3. This surplus discharged oil joins the suction oil from the tank via the suction passage 5 in the bypass passage 3 and flows into the suction chamber 4. In this case, when examining the pressure trends at the part (i) on the flow rate regulating valve 2 side of the bypass passage 3 and the part (ii) on the suction chamber 4 side, as shown in Fig. 3, in (i) the load P is , and in (ii), positive pressure P acts (referred to as supercharge effect). An even higher positive pressure P acts in the suction chamber portion (iii). In other words, the hydraulic pressure of the hydraulic oil flowing on the suction side of the pump differs in magnitude at each part. However, unlike on the discharge side, this pressure difference does not fluctuate due to the influence of load and is always stable.
本考案はこのような事情に着目してなされたも
ので、作動油の圧力状態が安定しているポンプ吸
込側の油圧の大きさに応じた弁操作を行うことに
より、ポンプが高速回転した場合に吐出流量を安
定状態で確実に減少させ、併せて燃費向上を向上
させることができる。 This invention was developed with a focus on this situation, and by operating the valve according to the amount of oil pressure on the pump suction side, where the pressure state of the hydraulic oil is stable, it is possible to prevent the pump from rotating at high speed. It is possible to reliably reduce the discharge flow rate in a stable state, and at the same time, improve fuel efficiency.
以下、本考案の一実施例を図面を参照して説明
する。
An embodiment of the present invention will be described below with reference to the drawings.
まず、第４図によりポンプ構成を説明する。ポ
ンプはベーン式のもので、ケーシング６の略中央
に設けたロータ７を、駆動軸８及びプーリ９を介
して、エンジンにより回転駆動する。ロータ７に
摺嵌したベーン１０の外周側の吸込室１１には、
タンク１２から吸込通路１３とバイパス通路１４
とを介して、作動油を供給する。また、ベーン１
０の側部には、吐出ポート１５を介して高圧室１
６が連通している。この高圧室１６からは吐出通
路１７を介して作動油を舵取装置のギヤボツクス
（図示せず）に供給する。 First, the pump configuration will be explained with reference to FIG. The pump is of a vane type, and a rotor 7 provided approximately in the center of a casing 6 is rotationally driven by an engine via a drive shaft 8 and a pulley 9. In the suction chamber 11 on the outer peripheral side of the vane 10 that is slidably fitted on the rotor 7,
From the tank 12 to the suction passage 13 and bypass passage 14
Hydraulic oil is supplied through. Also, vane 1
The high pressure chamber 1 is connected to the side of 0 through the discharge port 15.
6 are connected. Hydraulic oil is supplied from this high pressure chamber 16 via a discharge passage 17 to a gearbox (not shown) of the steering device.
次に、第４図および第５図により流量制御部の
構成を説明する。ポンプの吐出側すなわち吐出通
路１７と、吸込側すなわち吸込室１１とを互いに
連通させるバイパス通路１４に、流量調整弁１８
を設けてある。流量調整弁１８は調整スプリング
１９により、吐出通路１７側に規定圧力で付勢さ
れ、その吐出通路１７とバイパス通路１４とを通
じる弁孔２０を通常は閉じている。また、吐出通
路１７の流量調整弁１８よりも下流側のオリフイ
ス２１のさらに下流側に、吐出通路１７と吸込室
１１とを互いに連通する補助バイパス通路２２を
設け、補助バイパス通路２２の途中に、ポンプの
吸込側を流れる作動油の油圧に応じて通路２２を
開く補助流量調整弁２３を設けてある。補助バイ
パス通路２２は互いに略直角に交叉する一対の管
路すなわち吐出流路側管路２２Ａと吸込室側管路
２２Ｂとを有する。補助流量調整弁２３はピスト
ン状であり、軸線を吸込側管路２２Ｂの軸線と一
致させて各管路２２Ａ，２２Ｂの交叉部に配置し
てある。つまり、補助流量調整弁２３の周面で吐
出流路側管路２２Ａを、また一端面で吸込室側管
路２２Ｂを塞ぐようになつている。さらに、補助
流量制御弁２３の他端面は連絡管路２４を介して
バイパス通路１４の流量調整弁側の部位に臨ま
せ、この他端面部にはスーパーチヤージ効果によ
り負圧を作用させる一方、補助調整スプリング２
５により所定圧で一端側方向に押圧してある。 Next, the configuration of the flow rate control section will be explained with reference to FIGS. 4 and 5. A flow rate regulating valve 18 is provided in the bypass passage 14 that communicates the discharge side of the pump, that is, the discharge passage 17, and the suction side, that is, the suction chamber 11.
is provided. The flow rate adjustment valve 18 is biased toward the discharge passage 17 at a specified pressure by an adjustment spring 19, and normally closes a valve hole 20 that communicates with the discharge passage 17 and the bypass passage 14. Furthermore, an auxiliary bypass passage 22 that communicates the discharge passage 17 and the suction chamber 11 with each other is provided further downstream of the orifice 21 on the downstream side of the flow rate adjustment valve 18 of the discharge passage 17, and in the middle of the auxiliary bypass passage 22, An auxiliary flow regulating valve 23 is provided which opens the passage 22 in accordance with the hydraulic pressure of the hydraulic oil flowing on the suction side of the pump. The auxiliary bypass passage 22 has a pair of pipelines that intersect with each other at substantially right angles, that is, a discharge flow path side pipeline 22A and a suction chamber side pipeline 22B. The auxiliary flow rate regulating valve 23 has a piston shape and is arranged at the intersection of the respective pipes 22A and 22B with its axis aligned with the axis of the suction side pipe 22B. In other words, the circumferential surface of the auxiliary flow rate regulating valve 23 closes the discharge flow path side conduit 22A, and the one end surface closes the suction chamber side conduit 22B. Further, the other end surface of the auxiliary flow control valve 23 is made to face the portion of the bypass passage 14 on the flow rate adjustment valve side via the communication pipe 24, and negative pressure is applied to this other end surface due to the supercharge effect, while Auxiliary adjustment spring 2
5, it is pressed toward one end side with a predetermined pressure.
このような構成では、車両等の低速走行時、す
なわちポンプの低速回転時は吐出油が吐出通路１
７からオリフイス２１を介して駆動装置方向にの
み流れるが、速度が上がるにつれて、まず流量調
整弁１８が調整スプリング１９に抗して押圧さ
れ、弁孔２０を開くので、規定流量以上の余剰吐
出油は分流Ｃとなつてバイパス通路１４に流れ込
む。さらに高速になると、スーパーチヤージ効果
が大きくなり、補助流量調整弁２３の一端に作用
する吸込室１１側の正圧及び他端に作用するバイ
パス通路１４側の負圧がより大きくなり、補助流
量調整弁２３が補助調整スプリング２５に抗して
他端側方向（矢印イ）に吸引され、補助バイパス
通路すなわち管路２２Ａ，２２Ｂが連通状態にな
り、さらに余剰な吐出油がオリフイス２１の下流
側から補助バイパス通路２２を介して吸込室１１
側に流れ込む。第１図に流量特性曲線X2で示す
ように、ポンプが高速回転するにつれて吐出流量
が減少する。したがつて、車両等は高速走行時に
ハンドルが重くなり、走行安定性が増大する。な
お、補助調整スプリング２５による補助流量調整
弁２５のセツト圧力等を調整すると、例えば第１
図に流量特性曲線X3で示すように吐出流量の減
少するタイミングや設定流量等を種々変更でき
る。 In such a configuration, when the vehicle is running at low speed, that is, when the pump is rotating at low speed, the discharge oil flows through the discharge passage 1.
7 through the orifice 21, but as the speed increases, the flow rate adjustment valve 18 is first pressed against the adjustment spring 19 and opens the valve hole 20, so that excess discharged oil exceeding the specified flow rate becomes a branch flow C and flows into the bypass passage 14. As the speed increases further, the supercharge effect becomes larger, and the positive pressure on the suction chamber 11 side acting on one end of the auxiliary flow rate regulating valve 23 and the negative pressure on the bypass passage 14 side acting on the other end become larger, and the auxiliary flow rate increases. The regulating valve 23 is sucked in the direction of the other end (arrow A) against the auxiliary regulating spring 25, the auxiliary bypass passage, that is, the pipe lines 22A and 22B are brought into communication, and excess discharged oil is discharged to the downstream side of the orifice 21. from the suction chamber 11 via the auxiliary bypass passage 22
flows into the side. As shown by the flow rate characteristic curve X2 in FIG. 1, the discharge flow rate decreases as the pump rotates at high speed. Therefore, when a vehicle or the like is running at high speed, the steering wheel becomes heavy, and running stability is increased. Note that when the set pressure of the auxiliary flow rate adjustment valve 25 is adjusted by the auxiliary adjustment spring 25, for example, the first
As shown by the flow rate characteristic curve X3 in the figure, the timing at which the discharge flow rate decreases, the set flow rate, etc. can be changed in various ways.
本考案によれば、ポンプの吐出側と吸込室とを
連通する補助バイパス通路に、吸込側例えばバイ
パス通路を流れる作動油の油圧の大きさに応じて
開閉する補助流量調整弁を設けたので、高速回転
時の吐出流量がその補助バイパス通路を介する吸
込室へ流入により減ることは勿論であるが、補助
流量調整弁をポンプの吸込側の常に安定な圧力に
応じて動作させるから、負荷変動の影響のない安
定した流量制御作用が確実に得られる。したがつ
て、従来の吐出側のみで圧力を検出するものと異
なり、信頼性が大幅に向上する。また、この補助
流量調整弁は基本的な流量調整弁と別体に設けて
あるため、従来の一体的なもの等に比較して構成
が単純になる。さらに舵取装置へのポンプの流量
を減少させることにより、配管抵抗が減少し、消
費馬力が少なくなり、車両等の燃費向上にもな
る。
According to the present invention, the auxiliary bypass passage that communicates the discharge side of the pump with the suction chamber is provided with an auxiliary flow rate regulating valve that opens and closes depending on the magnitude of the hydraulic pressure of the hydraulic oil flowing through the suction side, for example, the bypass passage. Of course, the discharge flow rate during high-speed rotation is reduced by flowing into the suction chamber via the auxiliary bypass passage, but since the auxiliary flow rate adjustment valve is operated according to the always stable pressure on the suction side of the pump, load fluctuations are reduced. A stable flow rate control action without any influence can be reliably obtained. Therefore, unlike the conventional method in which pressure is detected only on the discharge side, reliability is significantly improved. Further, since this auxiliary flow rate adjustment valve is provided separately from the basic flow rate adjustment valve, the configuration is simpler than a conventional integrated valve. Furthermore, by reducing the flow rate of the pump to the steering device, piping resistance is reduced, horsepower consumption is reduced, and fuel efficiency of vehicles, etc. is improved.
第１図はポンプの流量特性を示す図、第２図は
ポンプ装置の一般的構成を示す図、第３図は第２
図ポンプの圧力特性を示す図、第４図は本考案に
よるポンプ装置の構成の一例を示す断面図、第５
図は第４図の−線で切つた流量制御部の構成
を示す断面図である。
１１……吸込室、１４……バイパス通路、１７
……吐出側（吐出通路）、１８……流量調整弁、
２２……補助バイパス通路、２３……補助流量調
整弁。
Figure 1 is a diagram showing the flow rate characteristics of the pump, Figure 2 is a diagram showing the general configuration of the pump device, and Figure 3 is a diagram showing the flow rate characteristics of the pump.
Figure 4 is a cross-sectional view showing an example of the configuration of the pump device according to the present invention; Figure 5 is a diagram showing the pressure characteristics of the pump;
This figure is a sectional view showing the configuration of the flow rate control section taken along the - line in FIG. 4. 11...Suction chamber, 14...Bypass passage, 17
...Discharge side (discharge passage), 18...Flow rate adjustment valve,
22...Auxiliary bypass passage, 23...Auxiliary flow rate adjustment valve.
Claims (1)
吸込側とをバイパス通路を介して互いに連通する
とともに、余剰吐出油を前記ポンプの吐出側から
吸込側に戻す流量調整弁を前記バイパス通路に設
けたものにおいて、 前記ポンプの吐出側の流量調整弁よりも下流側
部位と前記ポンプの吸込室部位とを補助バイパス
通路を介して互いに連通し、 当該補助バイパス通路の途中に前記ポンプの吸
込側を流れる作動油の油圧の大きさに応じて開閉
し前記ポンプの高速回転時のさらに余剰な吐出油
を前記ポンプの吐出側から吸込室に戻す補助流量
調整弁を前記流量調整弁とは別体に設けた ことを特徴とする動力舵取装置用ポンプ装置。[Claims for Utility Model Registration] The discharge side and suction side of a pump that supplies hydraulic oil to the steering device are communicated with each other via a bypass passage, and excess discharged oil is returned from the discharge side to the suction side of the pump. A flow rate adjustment valve is provided in the bypass passage, wherein a portion downstream of the flow rate adjustment valve on the discharge side of the pump and a suction chamber portion of the pump are communicated with each other via an auxiliary bypass passage; An auxiliary flow rate adjustment valve is provided in the middle of the process, which opens and closes depending on the hydraulic pressure of the hydraulic oil flowing through the suction side of the pump, and returns excess discharge oil from the discharge side of the pump to the suction chamber when the pump rotates at high speed. A pump device for a power steering device, characterized in that the pump device is provided separately from the flow rate regulating valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980099811U JPS6340365Y2 (en) | 1980-07-15 | 1980-07-15 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980099811U JPS6340365Y2 (en) | 1980-07-15 | 1980-07-15 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5722686U JPS5722686U (en) | 1982-02-05 |
| JPS6340365Y2 true JPS6340365Y2 (en) | 1988-10-21 |
Family
ID=29461442
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1980099811U Expired JPS6340365Y2 (en) | 1980-07-15 | 1980-07-15 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6340365Y2 (en) |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS598043Y2 (en) * | 1978-12-29 | 1984-03-12 | 自動車機器株式会社 | flow control valve |
-
1980
- 1980-07-15 JP JP1980099811U patent/JPS6340365Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5722686U (en) | 1982-02-05 |
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