JPS6361508B2 - - Google Patents
Info
- Publication number
- JPS6361508B2 JPS6361508B2 JP58084544A JP8454483A JPS6361508B2 JP S6361508 B2 JPS6361508 B2 JP S6361508B2 JP 58084544 A JP58084544 A JP 58084544A JP 8454483 A JP8454483 A JP 8454483A JP S6361508 B2 JPS6361508 B2 JP S6361508B2
- Authority
- JP
- Japan
- Prior art keywords
- fluid
- pulley
- pump
- pressure
- rotary pump
- 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
- 239000012530 fluid Substances 0.000 claims description 40
- 230000006835 compression Effects 0.000 claims description 5
- 238000007906 compression Methods 0.000 claims description 5
- 230000007423 decrease Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/08—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the rotational speed
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Power Steering Mechanism (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Description
【発明の詳細な説明】
本発明は動力舵取装置用ポンプの可変プーリ取
付装置に関し、その目的はポンプ変速システムの
コンパクト化を図り、ポンプ消費エネルギーを節
約することである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a variable pulley mounting device for a pump for a power steering device, and its purpose is to make the pump speed change system more compact and to save pump energy consumption.
一般に動力舵取装置用ポンプはエンジンの出力
軸に連結されて駆動されるため、エンジンの回転
数変化に比例して変化する。そしてエンジンの低
速回転時においてもポンプから所定の吐出流量が
得られるように回転比及びポンプの１回転当り吐
出量が設定されている。このためエンジン高速回
転時においては、ポンプ回転数も高くなり吐出流
量も増大して大量の余剰油を吐出し、必要以上の
動力を消費するばかりでなく、騒音、振動の発生
原因となつていた。 In general, the power steering device pump is connected to and driven by the output shaft of the engine, and therefore changes in proportion to changes in engine speed. The rotation ratio and the discharge amount per rotation of the pump are set so that a predetermined discharge flow rate can be obtained from the pump even when the engine is rotating at low speed. For this reason, when the engine rotates at high speed, the pump rotation speed increases and the discharge flow rate also increases, discharging a large amount of excess oil, which not only consumes more power than necessary, but also causes noise and vibration. .
この問題を解決するために、ポンプ駆動系に無
段変速機を介在する技術がある。一例として特公
昭48−26692号公報に記載された無段変速機はＶ
ベルトとプーリにて構成されているが、これの変
速比を調整するために、被動側のポンプとは別個
にポンプを設け、このポンプより供給される圧力
流体をポンプ軸と同軸に設けられたシリンダに導
入する回転軸軸端に流体分配手段を必要としてい
る。又このような構成要素は被動側のみならず駆
動側にも設けられている。このような構成では変
速制御用の流体供給手段を特別に設け、これを別
個に駆動しなければならず、装置が大形化し、設
置スペースが大となるため自動車に搭載するには
不向きである。 In order to solve this problem, there is a technique of interposing a continuously variable transmission in the pump drive system. As an example, the continuously variable transmission described in Japanese Patent Publication No. 48-26692 is V
It consists of a belt and a pulley, but in order to adjust its speed ratio, a pump is installed separately from the pump on the driven side, and the pressurized fluid supplied from this pump is installed coaxially with the pump shaft. A fluid distribution means is required at the end of the rotating shaft leading into the cylinder. Further, such components are provided not only on the driven side but also on the driving side. In such a configuration, a fluid supply means for speed change control must be specially provided and driven separately, resulting in a large device and a large installation space, making it unsuitable for installation in a car. .
本発明はこのような問題点に鑑みて提案された
ものであり、特にＶベルトプーリと同心的に設け
られかつ一体となつて回転する流体圧シリンダを
ポンプ駆動軸上に設け、この流体圧シリンダ室に
一端が開口しポンプハウジング内の環状溝に他端
が開口する流体通路を駆動軸内に形成し、この流
体通路の他端と対向する環状溝には、前記ロータ
リポンプ回転数の増大に応じた流体が流通する排
出孔に設けたオリフイスの背圧を導入する導入通
路を連通したものである。 The present invention has been proposed in view of these problems, and in particular, a fluid pressure cylinder that is provided concentrically with the V-belt pulley and rotates together with the V-belt pulley is provided on the pump drive shaft, and this fluid pressure cylinder A fluid passage is formed in the drive shaft, with one end opening in the chamber and the other end opening in an annular groove in the pump housing. An introduction passage for introducing back pressure from an orifice provided in a discharge hole through which a corresponding fluid flows is communicated.
以下本発明の実施例を図面に基づいて説明す
る。第１図において、１は図略のエンジンの出力
軸で、出力軸１に可変プーリ支持軸２が固着さ
れ、この支持軸２上に可変プーリ３が装着されて
いる。この実施例においては可変プーリ３はベル
ト係合用のＶ溝を形成する一対の可動滑車３ａ，
３ｂより構成され、この可動滑車３ａ，３ｂが支
持軸２上で回り止めされた状態でそれぞれが軸線
方向に摺動自在に支持されている。かかる可変プ
ーリ３の有効径は一対の可動滑車３ａ，３ｂの間
隔により決定されるもので、互いに近接すれば有
効径が増大し、離間すれば有効径が減少する。支
持軸２の基部に形成された鍔部と一方の可動滑車
３ａの間および支持軸２先端に固着された鍔部と
他方の可動滑車３ｂとの間には両可動滑車３ａ，
３ｂを互いに接近させて有効径を増大させる方向
に付勢するように圧縮バネすなわち弾性復元部材
４ａ，４ｂが介在されている。 Embodiments of the present invention will be described below based on the drawings. In FIG. 1, reference numeral 1 denotes an output shaft of an engine (not shown). A variable pulley support shaft 2 is fixed to the output shaft 1, and a variable pulley 3 is mounted on the support shaft 2. In this embodiment, the variable pulley 3 includes a pair of movable pulleys 3a forming a V-groove for belt engagement;
3b, and these movable pulleys 3a, 3b are supported on the support shaft 2 so as to be slidable in the axial direction in a state where they are prevented from rotating. The effective diameter of the variable pulley 3 is determined by the distance between the pair of movable pulleys 3a and 3b; if they are close to each other, the effective diameter increases, and if they are separated, the effective diameter decreases. Both movable pulleys 3a are located between the flange formed at the base of the support shaft 2 and one movable pulley 3a, and between the flange fixed to the tip of the support shaft 2 and the other movable pulley 3b.
Compression springs, that is, elastic restoring members 4a and 4b are interposed to urge the members 3b toward each other in a direction to increase the effective diameter.
第２図において、１０は図略の動力舵取装置の
アクチユエータに圧力流体を供給するロータリポ
ンプで、１１がロータ１２を回転させる駆動軸、
１３は流体タンク１４に連通したロータリポンプ
１０の吸入口、１５はロータリポンプ１０の吐出
口である。周知の如くこの吐出口からは駆動軸１
１の回転数に比例した圧力流体が吐出される。 In FIG. 2, 10 is a rotary pump that supplies pressure fluid to an actuator of a power steering device (not shown), 11 is a drive shaft that rotates a rotor 12;
13 is a suction port of the rotary pump 10 communicating with the fluid tank 14, and 15 is a discharge port of the rotary pump 10. As is well known, from this discharge port the drive shaft 1
A pressure fluid proportional to the rotation speed of 1 is discharged.
駆動軸１１上には可変プーリ１６が装着され、
この可変プーリ１６と前記エンジン出力軸１上の
可変プーリ３との間にＶベルト１７が巻掛けられ
ている。この可変プーリ１６も一対の可動滑車１
６ａ，１６ｂが駆動軸１１上で回り止めされた状
態でそれぞれ軸線方向に摺動自在に支持されてい
る。両可動滑車１６ａ，１６ｂ間には両者を有効
径減少方向に付勢するように圧縮バネすなわち弾
性復元部材１８が介在されている。 A variable pulley 16 is mounted on the drive shaft 11,
A V-belt 17 is wound between this variable pulley 16 and the variable pulley 3 on the engine output shaft 1. This variable pulley 16 is also a pair of movable pulleys 1
6a and 16b are supported on the drive shaft 11 so as to be slidable in the axial direction in a non-rotating state. A compression spring, ie, an elastic restoring member 18, is interposed between the two movable pulleys 16a, 16b so as to bias both in the direction of decreasing the effective diameter.
２０は可変プーリ１６の有効径を増大させる方
向に作用する流体圧シリンダで、この実施例にお
いては一方の可動滑車１６ｂに同心的に形成され
た流体圧シリンダ室２１に、他方の可動滑車１６
ａに取付けられたピストン２２が嵌装されてお
り、このシリンダ室２１に圧力流体が供給される
と両可動滑車１６ａ，１６ｂが互いに引き寄せら
れて有効径が増大する。 Reference numeral 20 denotes a fluid pressure cylinder that acts in a direction to increase the effective diameter of the variable pulley 16. In this embodiment, a fluid pressure cylinder chamber 21 formed concentrically with one movable pulley 16b is connected to the other movable pulley 16.
A piston 22 attached to a is fitted, and when pressure fluid is supplied to this cylinder chamber 21, both movable pulleys 16a and 16b are drawn toward each other and the effective diameter increases.
２５は動力舵取装置のアクチユエータに通じる
圧力流体送出口で、３０は吐出口１５から吐出さ
れてくる圧力流体の余剰流量を排出して送出口２
５に送出する圧力流体の最大流量を必要一定値に
制御する流量制御弁である。この実施例における
流量制御弁３０は例えば特許第577450号（特公昭
45−1381）の特許明細書に記載されたものと同一
で、スプール３１、オリフイス３２、スプリング
３３等から構成されており、吐出口１５から送ら
れてくる圧力流体の流量が設定値以上に増大する
とスプール３１を押動して排出孔３４が開かれ、
余剰流量は排出孔３４へと排出され、これにより
送出口２５へ送られる流量の最大値は常に上記設
定値に維持される。かかる排出孔３４は圧力室と
なつている。すなわち排出孔３４はオリフイス３
５を介してロータリポンプ１０の吸入口１３に連
通しており、排出孔３４に流入する余剰流は吸入
口１３へ戻れるが、吸入口１３内の圧力はほぼ大
気圧に維持されているため排出孔３４内の圧力は
流入される余剰流量に従つて変化する。 Reference numeral 25 is a pressure fluid delivery port leading to the actuator of the power steering device, and 30 is a pressure fluid delivery port for discharging the surplus flow rate of the pressure fluid discharged from the delivery port 15 to the delivery port 2.
This is a flow control valve that controls the maximum flow rate of the pressure fluid sent to the pressure fluid 5 to a necessary constant value. The flow rate control valve 30 in this embodiment is, for example, disclosed in Japanese Patent No. 577450 (Tokuko Showa).
45-1381), and is composed of a spool 31, an orifice 32, a spring 33, etc., and the flow rate of the pressure fluid sent from the discharge port 15 increases beyond the set value. Then, the spool 31 is pushed and the discharge hole 34 is opened.
The surplus flow rate is discharged to the discharge hole 34, so that the maximum value of the flow rate sent to the outlet port 25 is always maintained at the above-mentioned set value. This discharge hole 34 serves as a pressure chamber. That is, the discharge hole 34 is the orifice 3.
5, and the excess flow flowing into the discharge hole 34 can return to the suction port 13, but since the pressure inside the suction port 13 is maintained at approximately atmospheric pressure, it is not discharged. The pressure within the hole 34 changes according to the incoming surplus flow.
４０は圧力制御弁で、プラグ４１、スプール４
２、スプリング４３，４４等で構成されており、
プラグ４１の変位に比例した圧力の圧力流体が送
出口４５から取出される。この出力口４５は前記
駆動軸１１に開口された流路４６を介して前記流
体圧シリンダ２０のシリンダ室２１に連通されて
いる。入力口４７は前記流量制御弁３１の排出孔
すなわち圧力室３４に連通され、従つてプラグ４
１は圧力室３４内の圧力に比例して変位する。流
体供給口４８は前記ロータリポンプ１０の吐出口
１５に連通されておりロータリポンプ１０の吐出
流体が圧力制御弁４０の圧力媒体として使用され
る。排出口４９はロータリポンプ１０の吸入口１
３に連通されており排出流は吸入口１３へ戻され
る。 40 is a pressure control valve, a plug 41, a spool 4
2. Consists of springs 43, 44, etc.
Pressurized fluid with a pressure proportional to the displacement of the plug 41 is taken out from the outlet 45. This output port 45 is communicated with the cylinder chamber 21 of the fluid pressure cylinder 20 via a flow path 46 opened in the drive shaft 11 . The input port 47 communicates with the discharge hole of the flow control valve 31, that is, the pressure chamber 34, and therefore the plug 4
1 is displaced in proportion to the pressure within the pressure chamber 34. The fluid supply port 48 is connected to the discharge port 15 of the rotary pump 10, and the fluid discharged from the rotary pump 10 is used as a pressure medium for the pressure control valve 40. The discharge port 49 is the suction port 1 of the rotary pump 10.
3 and the exhaust flow is returned to the suction port 13.
次に、本発明装置の作用について説明する。ま
ずロータリポンプ１０の駆動軸１１の回転数Np
と吐出流口１５から吐出される吐出流量Qaおよ
び送出口２６から送出される送出流量Qbとの関
係を第４図に示す。吐出流量Qaは回転数Npに比
例して変化する。送出流量Qbは回転数Npが０か
らNp1の間は回転数Npに比例して変化するが、
回転数NpがNp1以上の領域では流量制御弁３０
の作用により回転数Npに係わりなく一定量に維
持される。従つて排出孔すなわち圧力室３４に排
出される流量（Qa−Qb）は回転数Npが０から
Np1の間は０であるが、回転数NpがNp1以上の
領域ではNpの変化に比例して変化する。 Next, the operation of the device of the present invention will be explained. First, the rotation speed Np of the drive shaft 11 of the rotary pump 10
FIG. 4 shows the relationship between the discharge flow rate Qa discharged from the discharge flow port 15 and the discharge flow rate Qb discharged from the discharge port 26. The discharge flow rate Qa changes in proportion to the rotation speed Np. The delivery flow rate Qb changes in proportion to the rotation speed Np between 0 and Np 1 , but
In the region where the rotational speed Np is Np 1 or more, the flow control valve 30
is maintained at a constant amount regardless of the rotational speed Np. Therefore, the flow rate (Qa - Qb) discharged to the discharge hole, that is, the pressure chamber 34, is the same as the rotation speed Np from 0 to
It is 0 between Np 1 , but changes in proportion to the change in Np in a region where the rotational speed Np is Np 1 or more.
従つて圧力室３４内の圧力は、回転数Npが０
からNp1の間は大気圧に維持されているが、Np1
以上の領域では回転数Npに従つて変化し、圧力
制御弁４０の出力口４５からは、ロータリポンプ
１０の吐出口１５から供給される圧力流体が圧力
室３４の圧力に比例した圧力に変換されて出力さ
れる。 Therefore, the pressure inside the pressure chamber 34 is such that the rotation speed Np is 0.
The atmospheric pressure is maintained between Np 1 and Np 1
In the above range, the pressure changes according to the rotation speed Np, and the pressure fluid supplied from the output port 45 of the pressure control valve 40 from the discharge port 15 of the rotary pump 10 is converted into a pressure proportional to the pressure in the pressure chamber 34. is output.
この圧力制御弁４０から出力される圧力流体が
流体圧シリンダ２０のシリンダ室２１に作用し、
弾性復元部材１８，４ａ，４ｂの撥力に抗して可
変プーリ１６の有効径を増大させるとともに可変
プーリ３の有効径を減少させる方向に流体圧シリ
ンダ２０を作動させる。可変プーリ１６の有効径
が増大し、可変プーリ３の有効径が減少すれば原
動機出力軸１の回転数Neに対するロータリポン
プ１０の駆動軸１１の回転数Npが低下する。従
つて回転数NpがNp1を越した領域では原動機出
力軸１の回転数Neに対する回転数Npの減速比が
回転数Npの変化に従つて、回転数Npが増大する
と減速比が増大する方向に、変化する。 The pressure fluid output from this pressure control valve 40 acts on the cylinder chamber 21 of the fluid pressure cylinder 20,
The fluid pressure cylinder 20 is operated in the direction of increasing the effective diameter of the variable pulley 16 and decreasing the effective diameter of the variable pulley 3 against the repulsive force of the elastic restoring members 18, 4a, 4b. If the effective diameter of the variable pulley 16 increases and the effective diameter of the variable pulley 3 decreases, the rotation speed Np of the drive shaft 11 of the rotary pump 10 with respect to the rotation speed Ne of the prime mover output shaft 1 decreases. Therefore, in the region where the rotational speed Np exceeds Np1 , the reduction ratio of the rotational speed Np to the rotational speed Ne of the prime mover output shaft 1 increases as the rotational speed Np increases. , change.
これを要約すれば、回転数Neが０からNe1の
間では、回転数Npは回転数Neに比例して０から
Np1の間で変化するとともに送出流量Qbも回転
数Neに比例して０からQb1の間で変化し、回転
数NeがNe1を越した領域では、回転数Npの変化
率は回転数Neの変化率に対して極めて小さくな
つて回転数Npの増加は小さく、また送出流量Qb
は回転数Neに係わりなく一定値Qb1に維持され
る。これらの関係を第５図に示す。当然Qb1は最
大必要流量に設定されている。 To summarize this, when the number of rotations Ne is between 0 and Ne 1 , the number of rotations Np increases from 0 to 1 in proportion to the number of rotations Ne.
At the same time, the delivery flow rate Qb also changes between 0 and Qb 1 in proportion to the rotational speed Ne, and in the region where the rotational speed Ne exceeds Ne 1 , the rate of change of the rotational speed Np is proportional to the rotational speed. The rate of change in Ne is extremely small, the increase in rotational speed Np is small, and the delivery flow rate Qb
is maintained at a constant value Qb 1 regardless of the rotational speed Ne. These relationships are shown in FIG. Naturally, Qb 1 is set to the maximum required flow rate.
以上説明したように、本発明は、ロータリポン
プの送出流量が最大必要流量に達した後は、ロー
タリポンプの回転数の上昇を押さえるとともに送
出流量を一定値に維持させるものであるから、不
必要なエネルギ消費を防止することができる。そ
して流体圧シリンダにてロータリポンプの回転数
制御用の可変プーリを操作せしめ、この流体圧シ
リンダにはロータリポンプより吐出されポンプ回
転数の増大に応じて圧力上昇する流体を導入し、
可変プーリの有効径を変化させかつ、被駆動側の
ポンプより吐出される油圧力によりプーリがベル
トを押圧するようになつているから、ロータリポ
ンプの回転数が正確に可変プーリの有効径に反映
され、必要以上の回転数増大がないため騒音、振
動の発生も少なくなるばかりでなく、負荷が増大
してもベルトスリツプは防止できる。更にポンプ
駆動軸と同心的に設けられた流体圧シリンダにポ
ンプ駆動軸を介して被動側ポンプ自体の吐出流体
を導入するようにしたから、プーリとともに回転
する流体圧シリンダの流体導入路形成が容易とな
り、特別な配管操作を不要とし、又別駆動のポン
プも必要としないため自動車搭載可能なコンパク
トな設計ができる。 As explained above, the present invention suppresses the increase in rotational speed of the rotary pump and maintains the delivery flow rate at a constant value after the delivery flow rate of the rotary pump reaches the maximum required flow rate. energy consumption can be prevented. Then, a variable pulley for controlling the rotation speed of the rotary pump is operated by a fluid pressure cylinder, and fluid discharged from the rotary pump and whose pressure increases as the pump rotation speed increases is introduced into the fluid pressure cylinder.
Since the effective diameter of the variable pulley is changed and the pulley presses the belt using the hydraulic pressure discharged from the pump on the driven side, the rotation speed of the rotary pump is accurately reflected in the effective diameter of the variable pulley. Since the rotational speed does not increase more than necessary, not only does noise and vibration occur less, but belt slip can be prevented even when the load increases. Furthermore, since the discharge fluid of the driven pump itself is introduced through the pump drive shaft into the fluid pressure cylinder provided concentrically with the pump drive shaft, it is easy to form a fluid introduction path for the fluid pressure cylinder that rotates with the pulley. This eliminates the need for special piping operations and also eliminates the need for a separately driven pump, allowing for a compact design that can be mounted on a car.
図面は本発明の一実施例を示すもので、第１図
は原動機出力軸側可変プーリの断面図、第２図は
ロータリポンプの縦断面図、第３図は第２図の
―断面図、第４図はロータリポンプの回転数と
ロータリポンプの送出流量との関係を表わす図、
第５図は原動機出力軸回転数とロータリポンプの
回転数および送出流量との関係を表わす図であ
る。
１……原動機出力軸、３……可変プーリ、４
ａ，４ｂ……弾性復元部材、１０……ロータリポ
ンプ、１１……ロータリポンプ駆動軸、１５……
吐出口、１６……可変プーリ、１７……Ｖベル
ト、２０……流体圧シリンダ、２５……送出口、
３０……流量制御弁、３４……圧力室、４０……
圧力制御弁。
The drawings show one embodiment of the present invention; FIG. 1 is a sectional view of the variable pulley on the motor output shaft side, FIG. 2 is a longitudinal sectional view of the rotary pump, and FIG. 3 is a sectional view of FIG. Figure 4 is a diagram showing the relationship between the rotation speed of the rotary pump and the delivery flow rate of the rotary pump.
FIG. 5 is a diagram showing the relationship between the rotational speed of the motor output shaft, the rotational speed of the rotary pump, and the delivery flow rate. 1...Motor output shaft, 3...Variable pulley, 4
a, 4b...Elastic restoring member, 10...Rotary pump, 11...Rotary pump drive shaft, 15...
Discharge port, 16... variable pulley, 17... V belt, 20... fluid pressure cylinder, 25... delivery port,
30...Flow control valve, 34...Pressure chamber, 40...
Pressure control valve.
Claims (1)
る方向に弾性復元部材にて付勢された第１可変プ
ーリを介して駆動される動力舵取装置用ロータリ
ポンプの可変プーリ取付装置であつて、ポンプハ
ウジングに軸承された駆動軸の突出部に被動側の
可変プーリを構成する一方の可動滑車を相対回転
を規制して挿着し、この一方の可動滑車に対し他
方の可動滑車を相対回転を規制し軸方向には相対
移動可能に同心的に保持し、両可動滑車間には両
者を互いに離間する方向に付勢する圧縮バネを介
挿し、この圧縮バネの押圧力に抗して両可動滑車
を互いに接近する方向に押圧する流体圧シリンダ
を前記可動滑車と同心的に設け、この流体圧シリ
ンダの圧縮バネ側のシリンダ室に一端が開口し、
ポンプハウジング内の環状溝に他端が開口する流
体通路を駆動軸内に形成し、この流体通路の他端
と対向する環状溝に前記ロータリポンプ回転数の
増大に応じた余剰流体が流通する排出孔に設けた
オリフイスの背圧を導入する導入通路を連通した
ことを特徴とする動力舵取装置用ロータリポンプ
の可変プーリ取付装置。1. A variable pulley mounting device for a rotary pump for a power steering device, which is driven via a first variable pulley that is inserted into the output shaft of an engine and is biased by an elastic restoring member in a direction in which the effective diameter increases. , one movable pulley that constitutes the variable pulley on the driven side is inserted into the protrusion of the drive shaft that is supported on the pump housing while restricting relative rotation, and the other movable pulley is rotated relative to this one movable pulley. A compression spring is inserted between both movable pulleys to urge them apart from each other, and both move against the pressing force of this compression spring. A fluid pressure cylinder that presses the movable pulleys in a direction toward each other is provided concentrically with the movable pulley, one end of which opens in a cylinder chamber on the compression spring side of the fluid pressure cylinder,
A fluid passage whose other end opens in an annular groove in the pump housing is formed in the drive shaft, and surplus fluid flows through the annular groove facing the other end of the fluid passage in response to an increase in the rotational speed of the rotary pump. A variable pulley mounting device for a rotary pump for a power steering device, characterized in that an introduction passage for introducing back pressure from an orifice provided in a hole is communicated.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58084544A JPS58214688A (en) | 1983-05-13 | 1983-05-13 | Driving device of rotary pump for power-driven steering device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58084544A JPS58214688A (en) | 1983-05-13 | 1983-05-13 | Driving device of rotary pump for power-driven steering device |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP50069910A Division JPS5854272B2 (en) | 1975-06-10 | 1975-06-10 | rotary pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58214688A JPS58214688A (en) | 1983-12-13 |
| JPS6361508B2 true JPS6361508B2 (en) | 1988-11-29 |
Family
ID=13833589
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP58084544A Granted JPS58214688A (en) | 1983-05-13 | 1983-05-13 | Driving device of rotary pump for power-driven steering device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58214688A (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5511959A (en) * | 1991-08-06 | 1996-04-30 | Hitachi, Ltd. | Scroll type fluid machine with parts of sintered ceramics |
| JPH1193860A (en) * | 1997-09-18 | 1999-04-06 | Jidosha Kiki Co Ltd | Variable-displacement pump |
| JPH1193862A (en) * | 1997-09-19 | 1999-04-06 | Jidosha Kiki Co Ltd | Variable-displacement pump |
| DE10104635A1 (en) * | 2001-02-02 | 2002-10-02 | Joma Hydromechanic Gmbh | Method for maintaining a constant output value, e.g. pressure, feed volume or capacity for vehicle oil pump, using rotational velocity transducer to adjust rotational speed of pump |
| US8403103B1 (en) | 2011-09-23 | 2013-03-26 | Trw Automotive U.S. Llc | Apparatus for use in turning steerable vehicle wheels |
-
1983
- 1983-05-13 JP JP58084544A patent/JPS58214688A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS58214688A (en) | 1983-12-13 |
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