JPH033077B2 - - Google Patents
Info
- Publication number
- JPH033077B2 JPH033077B2 JP974783A JP974783A JPH033077B2 JP H033077 B2 JPH033077 B2 JP H033077B2 JP 974783 A JP974783 A JP 974783A JP 974783 A JP974783 A JP 974783A JP H033077 B2 JPH033077 B2 JP H033077B2
- Authority
- JP
- Japan
- Prior art keywords
- movable ring
- spring
- pump
- fluid chamber
- outer periphery
- 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 21
- 238000003825 pressing Methods 0.000 claims description 9
- 238000006073 displacement reaction Methods 0.000 claims description 8
- 229910001285 shape-memory alloy Inorganic materials 0.000 claims description 7
- 230000002093 peripheral effect Effects 0.000 description 7
- 239000010720 hydraulic oil Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000003313 weakening effect Effects 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
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
- F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Description
【発明の詳細な説明】
〈産業上の利用分野〉
本発明はポンプハウジングの内孔内に径方向へ
移動可能な可動リングを有し、吐出容量を可変と
なした可変容量形ベーンポンプに関する。DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to a variable displacement vane pump having a movable ring movable in a radial direction within an inner hole of a pump housing, and having variable discharge displacement.
〈従来技術〉
この種の可変容量形ベーンポンプにおいては、
ポンプハウジングの内周壁と可動リングの外周間
に形成される流体室を２つに区画するとともに一
方の区画室に連通する吐出通路にオリフイスを形
成し、このオリフイスの後流側圧力を他方の区画
室に付与することによりオリフイス前後の差圧を
利用して可動リングの偏心量を変化させ、ロータ
の回転速度の変動に拘らず圧力流体の流体機器へ
の供給流量を一定に制御するようにしたものがあ
る。しかしながら、かかる可変容量形ベーンポン
プ作動油温度が著しく低下する寒冷地において
は、作動油の密度、粘度が非常に高くなり、低流
量でもオリフイス前後に所定の差圧が発生して可
動リングの偏心量が低吐出側に移動制御されてし
まい必要吐出流量の確保ができない問題があつ
た。<Prior art> In this type of variable displacement vane pump,
The fluid chamber formed between the inner peripheral wall of the pump housing and the outer periphery of the movable ring is divided into two, and an orifice is formed in the discharge passage communicating with one compartment, and the pressure on the downstream side of this orifice is transferred to the other compartment. By applying pressure to the chamber, the eccentricity of the movable ring is changed using the differential pressure before and after the orifice, and the flow rate of pressurized fluid supplied to the fluid equipment is controlled to be constant regardless of fluctuations in the rotational speed of the rotor. There is something. However, in cold regions where the temperature of the hydraulic oil of variable displacement vane pumps drops significantly, the density and viscosity of the hydraulic oil become extremely high, and even at low flow rates, a certain pressure difference occurs before and after the orifice, causing the amount of eccentricity of the movable ring. There was a problem in that the required discharge flow rate could not be secured because the flow rate was controlled to move to the low discharge side.
〈発明の目的〉
そこで本発明は低温時においてもポンプ吐出流
量を確保することを目的とする。<Objective of the Invention> Therefore, an object of the present invention is to ensure a pump discharge flow rate even at low temperatures.
〈発明の構成〉
本発明の特徴とする構成は、可動リングを最大
偏心位置に付勢するためにハウジングと可動リン
グ間に配置されたスプリングの初期設定圧を低温
時に伸び変形する形状記憶合金製のばね体により
高めるようにしたものである。<Configuration of the Invention> The characteristic configuration of the present invention is that the initial set pressure of the spring placed between the housing and the movable ring is made of a shape memory alloy that expands and deforms at low temperatures in order to urge the movable ring to the maximum eccentric position. The height is increased by a spring body.
〈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１図、第２図には本発明に係る可変容量形
ベーンポンプが示されている。このポンプのポン
プハウジング１０は、フロントハウジング１１
と、ガイドハウジング１２と、リヤハウジング１
３とにより構成されておりガイドハウジング１２
内に可動リング２１および多数のベーン２２を備
えたロータ２３を収容する内孔１２ａが形成され
ている。<Example> Hereinafter, an example of the present invention will be described based on the drawings. 1 and 2 show a variable displacement vane pump according to the present invention. The pump housing 10 of this pump includes a front housing 11
, guide housing 12, and rear housing 1
3 and a guide housing 12.
An inner hole 12a is formed in which a rotor 23 having a movable ring 21 and a number of vanes 22 is accommodated.
可動リング２１は、ガイドハウジング１２の内
孔１２ａの径より所定量小径の真円状のもので、
内孔１２ａ内に径方向へ移動可能に収容されてい
て、内孔１２ａの周壁と可動リング２１の外周間
に流体室Ｒを形成している。また、ロータ２３は
フロントハウジング１１に液密的かつ回転可能に
支持した回転軸２４上の一端にスプライン嵌合さ
れており、可動リング２１の内部に収容され可動
リング２１の内周とロータ２３の外周面にポンプ
室Ｐを形成している。この可動リング２１は、ガ
イドハウジング１２の第２図示右側に配設したね
じ部材３０と可動リング２１の外周間に介装され
た流量調整用のスプリング２５及び形状記憶合金
製の皿ばね３２により図示左方向に付勢されて、
ガイドハウジング１２の第２図示左側に配設した
最大偏心量規制用のネジ２６に当接している。こ
れにより、可動リング２１はロータ２３に対して
最大量偏心している。 The movable ring 21 has a perfect circular shape and has a diameter smaller than the inner hole 12a of the guide housing 12 by a predetermined amount.
It is accommodated in the inner hole 12a so as to be movable in the radial direction, and a fluid chamber R is formed between the peripheral wall of the inner hole 12a and the outer periphery of the movable ring 21. The rotor 23 is spline-fitted to one end of a rotating shaft 24 that is rotatably and liquid-tightly supported by the front housing 11. A pump chamber P is formed on the outer peripheral surface. The movable ring 21 is constructed by a screw member 30 disposed on the right side of the guide housing 12 in the second drawing, a spring 25 for adjusting flow rate interposed between the outer periphery of the movable ring 21, and a disc spring 32 made of a shape memory alloy. Forced to the left,
The guide housing 12 is in contact with a screw 26 for regulating the maximum eccentricity disposed on the second left side of the guide housing 12 in the drawing. As a result, the movable ring 21 is eccentric to the rotor 23 by the maximum amount.
一方、フロントハウジング１１の内側面には、
吸入ポート１１ａと吐出ポート１１ｂが形成され
ている。吸入ポート１１ａは、フロントハウジン
グ１１に設けた吸入通路１１ｃとポンプ室Ｐの吸
入域とに連通し、また吐出ポート１１ｂはポンプ
室Ｐの吐出域と流体室Ｒとに連通している。 On the other hand, on the inner surface of the front housing 11,
A suction port 11a and a discharge port 11b are formed. The suction port 11a communicates with a suction passage 11c provided in the front housing 11 and the suction area of the pump chamber P, and the discharge port 11b communicates with the discharge area of the pump chamber P and the fluid chamber R.
しかして、フロントハウジング１１の内側面に
設けた長穴１１ｄと圧力プレート１４の内側面に
設けた長穴１４ａには、軸方向にのびるシールピ
ン２７の両端が嵌合されている。このシールピン
２７は、ガイドハウジング１２の内孔１２ａの上
部周壁に液密的に密接している。また、可動リン
グ２１の外周のシールピン２７に対向する部位に
は、シールピン２７に嵌合可能な嵌合溝２１ａが
軸方向に形成されている。この可動リング２１
は、ポンプ室Ｐの流体圧により上方へ押上げられ
て嵌合溝２１ａをシールピン２７に嵌合させてい
る。これにより、シールピン２７は可動リング２
１を第２図示左右方向へ揺動可能に支持している
とともに、当該支持部にてガイドハウジング１２
の内孔周壁と可動リング２１の外周との間をシー
ルしている。また、ガイドハウジング１２の内孔
１２ａの下部周壁には、軸方向に延びる嵌合凹所
１２ｂが形成されていて、この嵌合凹所１２ｂに
間隙調整部材２８が嵌合固着されている。この間
隙調整部材２８は、流体室Ｒ内にわずかに突出し
ていて、その内側面２８ａと可動リング２１の外
周面との間にオリフイスＯを形成しており、かつ
シールピン２７とともに流体室Ｒを吐出ポート１
１ｂが開口する第１作用室r1と吐出孔１２ｃが開
口する第２作用室r2とに区画している。これら両
作用室r1，r2は、オリフイスＯを通して互いに連
通している。 Thus, both ends of a seal pin 27 extending in the axial direction are fitted into the elongated hole 11d provided on the inner surface of the front housing 11 and the elongated hole 14a provided on the inner surface of the pressure plate 14. This seal pin 27 is in fluid-tight contact with the upper peripheral wall of the inner hole 12a of the guide housing 12. Furthermore, a fitting groove 21a into which the seal pin 27 can be fitted is formed in the axial direction at a portion of the outer periphery of the movable ring 21 that faces the seal pin 27. This movable ring 21
is pushed upward by the fluid pressure in the pump chamber P, causing the fitting groove 21a to fit into the seal pin 27. As a result, the seal pin 27 is attached to the movable ring 2.
The guide housing 12 is supported so as to be swingable in the left and right directions shown in the second figure.
A seal is formed between the peripheral wall of the inner hole and the outer periphery of the movable ring 21. Further, a fitting recess 12b extending in the axial direction is formed in the lower peripheral wall of the inner hole 12a of the guide housing 12, and a gap adjustment member 28 is fitted and fixed in the fitting recess 12b. The gap adjustment member 28 slightly protrudes into the fluid chamber R, forms an orifice O between its inner surface 28a and the outer peripheral surface of the movable ring 21, and together with the seal pin 27 discharges the fluid chamber R. port 1
It is divided into a first working chamber r1 in which the opening 1b opens and a second working chamber r2 in which the discharge hole 12c opens. Both working chambers r 1 and r 2 communicate with each other through an orifice O.
前記形状記憶合金製の皿ばね３２は、低温時に
おいてばね高さＨが大きなものを常温からポンプ
運転時の作動油温度（約80℃前後）の範囲におい
てばね高さＨが小さくなるように変形したものを
利用する。これによつて常温以上における皿ばね
３２の高さＨは小さくスプリングの初期設定圧は
低くなつている。これに対し低温時には皿ばね３
２のばね高さＨは大きくなりスプリング２５の初
期設定圧を高くするようになつている。 The shape memory alloy disc spring 32 has a large spring height H at low temperatures, but is deformed so that the spring height H becomes small in the range from normal temperature to the hydraulic oil temperature during pump operation (approximately 80 degrees Celsius). Use what you have. As a result, the height H of the disc spring 32 at temperatures above room temperature is small, and the initial set pressure of the spring is low. On the other hand, at low temperatures, the disc spring 3
The spring height H of No. 2 is increased to increase the initial setting pressure of the spring 25.
このように構成したベーンポンプが常温以上の
温度範囲で作動する場合、スプリング２５の押圧
力は低い状態になつている。非駆動時可動リング
２１は第２図に示すように最大量偏心しており、
エンジンの駆動により回転軸２４およびこれと一
体のロータ２３が回転すると、吸入通路１１ｃお
よび吸入ポート１１ａを通してポンプ室Ｐに吸入
された流体は圧力流体として吐出ポート１１ｂを
通して第１作用室r1へ吐出され、さらにオリフイ
スＯを通して第２作用室r2へ流入して、吐出孔１
２ｃおよび図示しない吐出通路を通して適宜の流
体作動機器へ供給される。この間、回転軸２４お
よびロータ２３の回転速度（ポンプ回転速度）が
増大して第１作用室r1への圧力流体の吐出量が増
大すると、第１作用室r1と第２作用室r2間に生じ
た差圧により可動リング２１がスプリング２５に
抗して第２図示右方へ揺動される。この結果、ロ
ータ２３に対する可動リング２１の偏心量は差圧
の増大（ポンプ回転速度の増大５に応じて減少し
てポンプ１回転当りの吐出量を減少させ、ポンプ
回転速度の増大に拘らず作動機器へ供給する圧力
流体の供給量を一定に制御し、必要流量の吐出が
なされる。 When the vane pump configured in this manner operates in a temperature range above normal temperature, the pressing force of the spring 25 is in a low state. When not driven, the movable ring 21 is eccentric by the maximum amount as shown in FIG.
When the rotating shaft 24 and the rotor 23 integrated therewith rotate due to the drive of the engine, the fluid sucked into the pump chamber P through the suction passage 11c and the suction port 11a is discharged as pressurized fluid to the first working chamber r1 through the discharge port 11b . Further, it flows into the second working chamber r2 through the orifice O, and then flows into the discharge hole 1.
2c and a discharge passage (not shown) to an appropriate fluid operating device. During this time, when the rotational speed of the rotating shaft 24 and the rotor 23 (pump rotational speed) increases and the amount of pressure fluid discharged to the first working chamber r1 increases, the first working chamber r1 and the second working chamber r2 Due to the differential pressure generated between them, the movable ring 21 is swung to the right in the second figure against the spring 25. As a result, the eccentricity of the movable ring 21 with respect to the rotor 23 decreases in accordance with the increase in differential pressure (increase in pump rotational speed 5), reducing the discharge amount per pump rotation, and the pump operates regardless of the increase in pump rotational speed. The amount of pressure fluid supplied to the equipment is controlled to be constant, and the required flow rate is discharged.
これに対して低温時においては、皿ばね３２の
ばね高さが大きくなるように変形してスプリング
２５の初期設定圧が高められているので可動リン
グ２１の押圧力も強められている。このためロー
タ２３が回転し圧力流体の吐出によつてオリフイ
ス前後の差圧が前記常温以上の場合よりも高い差
圧とならないと可動リング２１の右方変位は生じ
ないことになるが、低温時においては粘度が高く
なつているため同じ流量でもオリフイス前後の差
圧は大きくなる傾向にあるため、スプリング２５
の押圧力を強めることにより、必要流量の確保が
可能となる。 On the other hand, at low temperatures, the spring height of the disc spring 32 is deformed to increase the initial setting pressure of the spring 25, so that the pressing force of the movable ring 21 is also increased. Therefore, the rightward displacement of the movable ring 21 will not occur unless the rotor 23 rotates and the differential pressure across the orifice becomes higher than that at room temperature or above due to the discharge of pressure fluid. Since the viscosity is higher in the orifice, the differential pressure before and after the orifice tends to increase even with the same flow rate, so the spring 25
By increasing the pressing force, it is possible to secure the required flow rate.
又、形状記憶合金製のスプリングをネジ２６側
に設け、低温時にはスプリング２５方向への押圧
力を弱め、高温時は押圧力を強めるようにしても
同様の効果が得られる。 Alternatively, a similar effect can be obtained by providing a spring made of a shape memory alloy on the screw 26 side, weakening the pressing force in the direction of the spring 25 when the temperature is low, and increasing the pressing force when the temperature is high.
〈発明の効果〉
以上述べたように本発明においては、低温時に
ばね高さが増大する形状記憶合金製のばねを設け
たものであるから、低温時におけるスプリングの
可動リング押圧力を高めることができ、低温時の
高粘度の作動流体でも必要吐出量を確保すること
ができる利点を有する。<Effects of the Invention> As described above, in the present invention, since the spring made of a shape memory alloy whose height increases at low temperatures is provided, it is possible to increase the pressing force of the movable ring of the spring at low temperatures. This has the advantage that the required discharge amount can be secured even with a high viscosity working fluid at low temperatures.
第１図は本発明の実施例であるベーンポンプの
縦断面図、第２図は第１図の−線に沿う縦断
面図である。
１０……ポンプハウジング、１１ａ……吸入ポ
ート、１１ｂ……吐出ポート、１２ａ……内孔、
１２ｃ……吐出孔、２１……可動リング、２３…
…ロータ、２５……スプリング、２７……シール
ピン、２８……間隙調整部材、２８ａ……内側
面、Ｏ……オリフイス、Ｐ……ポンプ室、Ｒ……
流体室、r1，r2……作用室、３２……形状記憶合
金製皿ばね。
FIG. 1 is a longitudinal sectional view of a vane pump according to an embodiment of the present invention, and FIG. 2 is a longitudinal sectional view taken along the line - in FIG. 10...Pump housing, 11a...Suction port, 11b...Discharge port, 12a...Inner hole,
12c...Discharge hole, 21...Movable ring, 23...
... Rotor, 25 ... Spring, 27 ... Seal pin, 28 ... Gap adjustment member, 28a ... Inner surface, O ... Orifice, P ... Pump chamber, R ...
Fluid chamber, r 1 , r 2 ... action chamber, 32 ... disk spring made of shape memory alloy.
Claims (1)
能に収容した可動リングの内部に多数のベーンを
備えたロータを収容し、可動リングの外周には偏
心量増大方向に可動リングを押圧するスプリング
を配置してなる可変容量形ベーンポンプにおい
て、前記可動リングの外周と前記ポンプハウジン
グの内周との間に密着するシール部を設け、前記
可動リングと前記ポンプハウジングとの間にオリ
フイスを形成する間隙調整部材を前記可動リング
に対向して配置し、前記間隙調整部材と前記シー
ル部により前記可動リングの外周の流体室を前記
スプリングの押圧力による可動リングの移動によ
り容積が拡大する流体室と縮小する流体室とに区
画し、前記可動リングの内周と前記ロータの外周
間に形成したポンプ室の吐出域に連通する吐出ポ
ートを前記容積が縮小する流体室に連通し、前記
容積が拡大する流体室を前記ポンプハウジング外
部に通じる吐出孔と連通し、前記スプリング押圧
力を低温時に高める形状記憶合金製のばね体を設
けたことを特徴とする可変容量形ベーンポンプ。1 A rotor equipped with a large number of vanes is housed inside a movable ring that is movable in the radial direction within the inner hole of the pump housing, and a spring that presses the movable ring in the direction of increasing eccentricity is arranged on the outer periphery of the movable ring. In the variable displacement vane pump, a gap adjustment member is provided that includes a seal portion that is in close contact between the outer periphery of the movable ring and the inner periphery of the pump housing, and that forms an orifice between the movable ring and the pump housing. is arranged opposite to the movable ring, and the gap adjustment member and the seal portion define a fluid chamber on the outer periphery of the movable ring, with a fluid chamber whose volume expands and a fluid chamber whose volume contracts due to the movement of the movable ring due to the pressing force of the spring. a fluid chamber whose volume is expanded, with a discharge port communicating with a discharge area of a pump chamber formed between an inner periphery of the movable ring and an outer periphery of the rotor communicating with the fluid chamber whose volume is reduced; A variable displacement vane pump characterized in that a spring body made of a shape memory alloy is provided which communicates with a discharge hole communicating with the outside of the pump housing and increases the spring pressing force at low temperatures.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP974783A JPS59136592A (en) | 1983-01-24 | 1983-01-24 | Variable capacity type vane pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP974783A JPS59136592A (en) | 1983-01-24 | 1983-01-24 | Variable capacity type vane pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59136592A JPS59136592A (en) | 1984-08-06 |
| JPH033077B2 true JPH033077B2 (en) | 1991-01-17 |
Family
ID=11728893
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP974783A Granted JPS59136592A (en) | 1983-01-24 | 1983-01-24 | Variable capacity type vane pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59136592A (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0382821U (en) * | 1989-12-12 | 1991-08-23 | ||
| DE4302610C2 (en) * | 1993-01-30 | 1996-08-08 | Daimler Benz Ag | Process for regulating the pump output of lubricant pumps and lubricant pump therefor |
| DE10223466B4 (en) * | 2001-05-31 | 2015-07-02 | Magna Powertrain Hückeswagen GmbH | pump |
| JP4787637B2 (en) * | 2006-03-14 | 2011-10-05 | 株式会社ショーワ | Variable displacement pump |
| DE102014117483A1 (en) * | 2014-04-14 | 2015-10-15 | Erich Netzsch Gmbh & Co. Holding Kg | Adjustable pump unit for a positive displacement pump |
-
1983
- 1983-01-24 JP JP974783A patent/JPS59136592A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS59136592A (en) | 1984-08-06 |
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