JPH0617672B2 - Positive displacement fluid machine - Google Patents
Positive displacement fluid machineInfo
- Publication number
- JPH0617672B2 JPH0617672B2 JP59108742A JP10874284A JPH0617672B2 JP H0617672 B2 JPH0617672 B2 JP H0617672B2 JP 59108742 A JP59108742 A JP 59108742A JP 10874284 A JP10874284 A JP 10874284A JP H0617672 B2 JPH0617672 B2 JP H0617672B2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- discharge flow
- flow rate
- control valve
- fluid machine
- 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
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
- F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は、それぞれ流入通路および流出通路をもつ２つ
の歯車流体機械すなわち２つの歯車ポンプまたは２つの
歯車モータから成り、これらの歯車流体機械に共通な１
つの液圧回路が付属し、これらの歯車流体機械の吐出流
量が、容積形流体機械のハウジング部材に設けられる制
御手段により変化可能である、容積形流体機械に関す
る。DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application] The present invention comprises two gear fluid machines each having an inflow passage and an outflow passage, that is, two gear pumps or two gear motors. Common 1
The present invention relates to a positive displacement fluid machine to which two hydraulic circuits are attached and the discharge flow rate of these gear fluid machines can be changed by a control means provided in a housing member of the positive displacement fluid machine.
このような容積形流体機械は公知であり（特開昭57-838
2号公報）、付加的に設けられる弁装置は、個々の歯車
流体機械の吐出流量の任意の和である複数の異なる大き
さの吐出流量を生ずるのを可能にする。しかしこれは費
用を要しかつかさばるので、容積形流体機械の外部に特
別な装置が必要になる。制御手段を流体機械のハウジン
グ部材に設けることも公知である（実開昭52-134101
号）。Such a positive displacement fluid machine is known (Japanese Patent Laid-Open No. 57-838).
No. 2), an additionally provided valve device makes it possible to produce a plurality of different magnitude discharge flow rates, which is an arbitrary sum of the discharge flow rates of the individual gear fluid machines. However, this is costly and requires special equipment external to the positive displacement fluid machine. It is also known to provide a control means on a housing member of a fluid machine (Act. No. 52-134101).
issue).
本発明の課題は、容積形流体機械の吐出流量がこの容積
形流体機械を構成する個々の歯車流体機械の吐出流量よ
り小さい吐出流量の値まで変化可能で、こじんまり構成
される容積形流体機械を提供することである。It is an object of the present invention to provide a compact displacement fluid machine in which the discharge flow rate of the positive displacement fluid machine can be changed to a value of a discharge flow rate smaller than the discharge flow rate of each gear fluid machine constituting the positive displacement fluid machine. Is to provide.
この課題を解決するため本発明によれば、制御手段が任
意に調節可能な４ポート３位置方向制御弁と任意に調節
可能な２ポート２位置方向制御弁とから成り、４ポート
３位置方向制御弁の２つの接続口が、両方の歯車流体機
械の流出通路にそれぞれ接続され、第３の接続口が一方
の歯車流体機械の流入通路に接続され、第４の接続口が
負荷接続口であり、負荷接続口と他方の歯車流体機械の
流入通路との間に、２ポート２位置方向制御弁が設けら
れており、４ポート３位置方向制御弁および２ポート２
位置方向制御弁の切換え位置を適宜変更することによっ
て、吐出流量を、一方の歯車流体機械の吐出流量、他方
の歯車流体機械の吐出流量、両方の歯車流体機械の吐出
流量の和、両方の歯車流体機械の吐出流量の差の各流量
に選択可能とされている。ここでハウジング部材とは、
２つの歯車流体機械のいずれか１つのハウジングまたは
両方の歯車流体機械の間にある中間板をも意味する。In order to solve this problem, according to the present invention, the control means comprises a 4-port 3-position directional control valve that can be arbitrarily adjusted and a 2-port 2-position directional control valve that can be arbitrarily adjusted. The two connection ports of the valve are respectively connected to the outflow passages of both gear fluid machines, the third connection port is connected to the inflow passage of one gear fluid machine, and the fourth connection port is a load connection port. , A 2-port 2-position directional control valve is provided between the load connection port and the inflow passage of the other gear fluid machine.
By appropriately changing the switching position of the position direction control valve, the discharge flow rate can be adjusted so that the discharge flow rate of one gear fluid machine, the discharge flow rate of the other gear fluid machine, the sum of the discharge flow rates of both gear fluid machines, both gears It is possible to select each flow rate of the difference in the discharge flow rate of the fluid machine. Here, the housing member is
It also means the intermediate plate between the housing of any one of the two gear fluid machines or both gear fluid machines.
こうして本発明によれば、４ポート３位置方向制御弁と
２ポート２位置方向制御弁とを適宜に切換えることによ
り、負荷へ至る容積形流体機械の吐出流量を負荷の需要
に合った異なる大きさの吐出流量に、容易に変化するこ
とができる。しかも制御手段は容積形流体機械のハウジ
ング部材例えばいずれかの歯車ポンプのハウジングまた
は２つの歯車ポンプの間に存在する中間板に設けられる
ので、容積形流体機械全体を非常にこじんまり構成する
ことができる。Thus, according to the present invention, by appropriately switching the 4-port 3-position directional control valve and the 2-port 2-position directional control valve, the discharge flow rate of the displacement type fluid machine to the load can be adjusted to different sizes according to the demand of the load. The discharge flow rate can be easily changed. Moreover, since the control means is provided on the housing member of the positive displacement fluid machine, for example, on the housing of one of the gear pumps or the intermediate plate existing between the two gear pumps, the entire positive displacement fluid machine can be made very compact. .
本発明の実施例が図面に示されており、以下にこれにつ
いて詳細に説明する。An embodiment of the invention is shown in the drawing and will be explained in more detail below.
容積形流体機械10は、ハウジング11,12をもつ２つの歯
車ポンプA,Bから成り、これらのハウジングの間に中間
板13がある。ハウジング11,12は、中間板13とは反対側
の端面ハウジング蓋14,15により閉鎖されている。ハウ
ジング蓋14はねじ16によりハウジング11に取付けられて
いる。ハウジング11は一貫した切欠き１７をもち、この
切欠き内に歯車ポンプＡの歯車18,18′が設けられてい
る。歯車ポンプＡの歯車18,18′のジャーナルは軸受体2
1,21′,22,22′に支持されている。ハウジング11には流
入通路23と流出通路24が形成されている。The positive displacement fluid machine 10 consists of two gear pumps A and B with housings 11 and 12, with an intermediate plate 13 between these housings. The housings 11 and 12 are closed by end face housing lids 14 and 15 on the side opposite to the intermediate plate 13. The housing lid 14 is attached to the housing 11 with screws 16. The housing 11 has a consistent notch 17 in which the gears 18, 18 'of the gear pump A are provided. The journal of the gear 18, 18 'of the gear pump A is the bearing body 2
It is supported by 1,21 ', 22,22'. An inflow passage 23 and an outflow passage 24 are formed in the housing 11.
歯車ポンプＢも歯車ポンプＡと全く同様に構成されてい
る。すなわちハウジング12も同様に一貫した切欠き25内
をもっている。歯車26,26′のジャーナルは、同様に切
欠き25に設けられた軸受体28,28′,29,29′に支持され
ている。歯車26は突起30をもち、この突起３０がハウジ
ング蓋15の穴を液体漏れなく外方へ貫通し、ポンプとし
て使用する場合、その駆動軸として役だつ。ハウジング
12内には流入通路31と流出通路32が形成されている。The gear pump B has the same structure as the gear pump A. That is, the housing 12 likewise has a consistent cutout 25. The journals of the gears 26, 26 'are supported on bearing bodies 28, 28', 29, 29 ', which are likewise provided in the cutout 25. The gear 26 has a protrusion 30 which penetrates the hole of the housing lid 15 outward without leaking liquid and serves as a drive shaft for the pump when used as a pump. housing
An inflow passage 31 and an outflow passage 32 are formed in the inside 12.
中間板13には、切換え位置I,II,IIIと一方の側にある接
続口a,bおよび他方の側にある接続口c,dをもつ４ポート
３位置方向制御弁34が設けられている。中間板13には吸
入接続通路35が通じて、流入通路23へ至る通路36、流入
通路31へ至る通路37および方向制御弁34の接続口aへ至
る通路38に分岐している。方向制御弁34の負荷接続口と
しての接続口ｂから、通路39が図示しない負荷へ通じて
いる。The intermediate plate 13 is provided with a 4-port 3-position directional control valve 34 having switching positions I, II, III and connection ports a, b on one side and connection ports c, d on the other side. . A suction connection passage 35 communicates with the intermediate plate 13, and is branched into a passage 36 leading to the inflow passage 23, a passage 37 reaching the inflow passage 31, and a passage 38 reaching the connection port a of the directional control valve 34. A passage 39 leads to a load (not shown) from a connection port b as a load connection port of the directional control valve 34.
通路36と通路39との間に、２ポート２位置方向制御弁61
を含む接続通路60が設けられている。この方向制御弁61
は接続口a,bと切換え位置I,IIをもち、切換え位置Ｉで
は方向制御弁61にある逆止弁62が２つの接続口ａとｂの
間にあり、通路36の方へ閉じている。通路36にはさらに
逆止弁63が組込まれて、流入通路23の方へ開いている。A 2-port 2-position directional control valve 61 is provided between the passage 36 and the passage 39.
A connection passage 60 including is provided. This directional control valve 61
Has connection ports a and b and switching positions I and II, and at switching position I a check valve 62 in the directional control valve 61 is located between the two connection ports a and b and is closed towards the passage 36. . A check valve 63 is further incorporated in the passage 36 and opens toward the inflow passage 23.
方向制御弁34と方向制御弁61の組合わせにより、４つの
異なる大きさの吐出流量が可能である。まず方向制御弁
34の切換え位置Ｉおよび方向制御弁61の切換え位置Ｉで
は、負荷への吐出流量Ｑは歯車ポンプＢの吐出流量Q1に
等しい。吐出流量Q2は戻り通路38へ達する。方向制御弁
34の切換え位置IIおよび方向制御弁61の切換え位置Ｉで
は、負荷への吐出流量Ｑは歯車ポンプＡおよびＢの吐出
流量の和Q1+Q2となる。方向制御弁61が切換え位置Ｉに
あり、方向制御弁34が切換え位置IIIにあると、負荷へ
の吐出流量Ｑは歯車ポンプＡの吐出流量Q2に等しい。吐
出流量Q1は戻り通路38へ達する。方向制御弁34の切換え
位置Ｉと方向制御弁61の切換え位置IIでは、負荷への吐
出流量Ｑは、両歯車ポンプの吐出流量Q1とQ2との差とな
る。方向制御弁61の切換え位置IIと方向制御弁34の切換
え位置IIとの組合わせは、吐出流量Ｑとして再び吐出流
量Q1を生ずる。方向制御弁34の切換え位置IIとさらに方
向制御弁６１の切換え位置IIでは、吐出流量Ｑは零とな
る。吐出流量Ｑが負荷へ送られないので、歯車ポンプＡ
およびＢは負荷をかけられない。吐出流量Q1は通路38へ
戻り、吐出流量Q2は通路36へ戻る。The combination of the directional control valve 34 and the directional control valve 61 enables four different discharge flow rates. First the directional control valve
At the switching position I of 34 and the switching position I of the directional control valve 61, the discharge flow rate Q to the load is equal to the discharge flow rate Q 1 of the gear pump B. The discharge flow rate Q 2 reaches the return passage 38. Directional control valve
At the switching position II of 34 and the switching position I of the directional control valve 61, the discharge flow rate Q to the load is the sum Q 1 + Q 2 of the discharge flow rates of the gear pumps A and B. When the directional control valve 61 is in the switching position I and the directional control valve 34 is in the switching position III, the discharge flow rate Q to the load is equal to the discharge flow rate Q 2 of the gear pump A. The discharge flow rate Q 1 reaches the return passage 38. At the switching position I of the directional control valve 34 and the switching position II of the directional control valve 61, the discharge flow rate Q to the load is the difference between the discharge flow rates Q 1 and Q 2 of both gear pumps. The combination of the switching position II of the directional control valve 61 and the switching position II of the directional control valve 34 produces the discharge flow rate Q 1 again as the discharge flow rate Q. At the switching position II of the directional control valve 34 and the switching position II of the directional control valve 61, the discharge flow rate Q becomes zero. Since the discharge flow rate Q cannot be sent to the load, the gear pump A
And B are not loaded. The discharge flow rate Q 1 returns to the passage 38, and the discharge flow rate Q 2 returns to the passage 36.
歯車ポンプA,Bへ通路39を介して圧力媒体が供給される
場合には、容積形流体機械10は液圧モータとして動作す
る。When the pressure medium is supplied to the gear pumps A and B through the passage 39, the positive displacement fluid machine 10 operates as a hydraulic motor.
なお方向制御弁34および61は、歯車ポンプＡまたはＢの
ハウジングに設けることも可能である。The direction control valves 34 and 61 can be provided in the housing of the gear pump A or B.
図は本発明による容積形流体機械の実施例の縦断面図で
ある。 10…容積形流体機械、11,12,13…ハウジング部材、23,3
1…流入通路、24,32…流出通路、34…４ポート３位置方
向制御弁、61…２ポート２位置方向制御弁、A,B…歯車
流体機械、a,b,c,d…接続口、Q,Q1,Q2…吐出流量。FIG. 1 is a vertical sectional view of an embodiment of a displacement type fluid machine according to the present invention. 10… Volumetric fluid machine, 11, 12, 13… Housing member, 23, 3
1 ... Inflow passage, 24, 32 ... Outflow passage, 34 ... 4-port 3-position directional control valve, 61 ... 2-port 2-position directional control valve, A, B ... Gear fluid machine, a, b, c, d ... Connection port , Q, Q 1 , Q 2 ... Discharge flow rate.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 ヴイリ・マ−ル ドイツ連邦共和国デイツツインゲン・レヒ ベルクシユトラ−セ35／１ (72)発明者 ジ−クフリ−ト・マイエル ドイツ連邦共和国フアイインゲン・テ−オ ド−ル−ホイス−シユトラ−セ24 (72)発明者 カルル−ハインツ・ミユレル ドイツ連邦共和国フアイインゲン・ゲ−ロ クシユトラ−セ６／２ (72)発明者 マンフレ−ト・ラスペル ドイツ連邦共和国レ−オンベルク４フンメ ルベルクヴエ−ク42 (56)参考文献 特開 昭57−8382（ＪＰ，Ａ) 実開 昭52−134101（ＪＰ，Ｕ) 実公 昭27−1664（ＪＰ，Ｙ１) ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Vuilie Mars Dates Twingen Lechberg Schuttraße 35/1 (72) Inventor Siegfried Meier Federal Republic of Germany Huijingen Te -Odor-Heus-Schütlersee 24 (72) Inventor Karl-Heinz Miurel Federal Republic of Germany Huijingen Gerlochschutlersee 6/2 (72) Inventor Manfred Rasper Federal Republic of Germany RAHONBERG 4 HUMMERBERK WEEK 42 (56) Reference JP-A-57-8382 (JP, A) Actually open 52-134101 (JP, U) Actual public 27-1664 (JP, Y1)
Claims (2)
31)および流出通路(24,32)をもつ２つの歯車流体機械
(A,B)すなわち２つの歯車ポンプまたは２つの歯車モー
タから成り、これらの歯車流体機械(A,B)に共通な１つ
の液圧回路が付属し、これらの歯車流体機械(A,B)の吐
出流量が、容積形流体機械のハウジング部材(11,12,13)
に設けられる制御手段により変化可能であるものにおい
て、制御手段が任意に調節可能な４ポート３位置方向制
御弁(34)と任意に調節可能な２ポート２位置方向制御弁
(61)とから成り、４ポート３位置方向制御弁(34)の２つ
の接続口(c,d)が、両方の歯車流体機械(A,B)の流出通路
(24,32)にそれぞれ接続され、第３の接続口（ａ）が一
方の歯車流体機械（Ｂ）の流入通路(31)に接続され、第
４の接続口（ｂ）が負荷接続口であり、負荷接続口
（ｂ）と他方の歯車流体機械（Ａ）の流入通路(23)との
間に、２ポート２位置方向制御弁(61)が設けられてお
り、４ポート３位置方向制御弁(34)および２ポート２位
置方向制御弁(61)の切換え位置を適宜変更することによ
つて、吐出流量を、一方の歯車流体機械（Ｂ）の吐出流
量(Q1)、他方の歯車流体機械（Ａ）の吐出流量(Q2)、両
方の歯車流体機械(A,B)の吐出流量の和(Q1+Q2)、両方の
歯車流体機械(A,B)の吐出流量の差(Q1-Q2またはQ2-Q1)
の各流量に選択可能としたことを特徴とする、容積形流
体機械。1. A positive displacement fluid machine is provided with inflow passages (23,
31) and two gear fluid machines with outflow passages (24, 32)
(A, B), that is, consisting of two gear pumps or two gear motors, one hydraulic circuit common to these gear fluid machines (A, B) is attached, and these gear fluid machines (A, B) The discharge flow rate of the positive displacement fluid machine housing member (11,12,13)
Which can be changed by the control means provided in the control means, the control means can arbitrarily adjust the 4-port 3-position directional control valve (34) and the 2-port 2-position directional control valve
(61) and the two connection ports (c, d) of the 4-port 3-position directional control valve (34) are connected to the outflow passages of both gear fluid machines (A, B).
(24, 32), the third connection port (a) is connected to the inflow passage (31) of one gear fluid machine (B), and the fourth connection port (b) is a load connection port. Yes, a 2-port 2-position directional control valve (61) is provided between the load connection port (b) and the inflow passage (23) of the other gear fluid machine (A). By appropriately changing the switching positions of the valve (34) and the 2-port 2-position directional control valve (61), the discharge flow rate can be set to the discharge flow rate (Q 1 ) of one gear fluid machine (B) and the other gear. Of the discharge flow rate (Q 2 ) of fluid machine (A), the sum of the discharge flow rates of both gear fluid machines (A, B) (Q 1 + Q 2 ), and the discharge flow rate of both gear fluid machines (A, B) Difference (Q 1 -Q 2 or Q 2 -Q 1 )
A displacement type fluid machine characterized by being selectable for each flow rate of.
の中間板(13)に設けられていることを特徴とする、特許
請求の範囲第１項に記載の容積形流体機械。2. Positive displacement fluid according to claim 1, characterized in that the control means are provided on the intermediate plate (13) between the two gear pumps (A, B). machine.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE8316310 | 1983-06-03 | ||
| DE83163107 | 1983-06-03 | ||
| DE34063498 | 1984-02-22 | ||
| DE3406349.8 | 1984-02-22 | ||
| DE8316310.7 | 1984-02-22 | ||
| DE19843406349 DE3406349A1 (en) | 1983-06-03 | 1984-02-22 | DISPLACEMENT MACHINE |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS603492A JPS603492A (en) | 1985-01-09 |
| JPH0617672B2 true JPH0617672B2 (en) | 1994-03-09 |
Family
ID=25818707
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59108742A Expired - Lifetime JPH0617672B2 (en) | 1983-06-03 | 1984-05-30 | Positive displacement fluid machine |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPH0617672B2 (en) |
| DE (1) | DE3406349A1 (en) |
| FR (1) | FR2546981B1 (en) |
| GB (1) | GB2140872B (en) |
| IT (1) | IT1178481B (en) |
Families Citing this family (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5071327A (en) * | 1990-10-31 | 1991-12-10 | Parker Hannifin Corporation | Two speed gerotor motor with centrally located valve and commutator |
| DE4111116C2 (en) * | 1991-04-03 | 1994-11-03 | Mannesmann Ag | Fluid operated rotary actuator |
| DE4302916A1 (en) * | 1993-02-03 | 1994-08-04 | Philipp Dipl Ing Breitling | Hydrostatic drive with variable speed |
| DE4310211A1 (en) * | 1993-03-29 | 1994-03-24 | Bosch Gmbh Robert | Hydraulic gear pump or motor with main gear pair (5) - has second compensation gear pair (5) with continuously meshing tooth pair(s) |
| DE19623169A1 (en) * | 1996-05-30 | 1997-12-04 | Luk Fahrzeug Hydraulik | Vane pump with rotor |
| EP1184573B1 (en) * | 2000-08-28 | 2014-04-09 | Eaton Corporation | Hydraulic motor having multiple speed ratio capability |
| GB2367095A (en) * | 2000-09-13 | 2002-03-27 | Sauer Danfoss | Valve arrangement in separating plate of multiple hydraulic pump and motor ass emblies |
| DE102011086429A1 (en) | 2011-11-16 | 2013-05-16 | Robert Bosch Gmbh | Internal gear pump |
| DE102011089609A1 (en) | 2011-12-22 | 2013-06-27 | Robert Bosch Gmbh | Internal gear pump |
| DE102012223905A1 (en) | 2012-12-20 | 2014-06-26 | Robert Bosch Gmbh | Rotary piston pump e.g. high pressure gear pump for conveying fluid e.g. petrol to internal combustion engine of motor car, has outlet channels opened in diverting workspace for discharging to-be-conveyed fluid from diverting workspace |
| DE102012223935A1 (en) | 2012-12-20 | 2014-06-26 | Robert Bosch Gmbh | Rotary piston pump e.g. high-pressure pump for conveying fluid e.g. fuel to internal combustion engine, has an actuator for variable control and/or regulation of bypass channel, to integrate routable volume flow of fluid into channel |
| DE102012223907B4 (en) | 2012-12-20 | 2022-12-01 | Robert Bosch Gmbh | Method for manufacturing at least one rotary piston pump and a high-pressure injection system |
| DE102012223920A1 (en) | 2012-12-20 | 2014-06-26 | Robert Bosch Gmbh | Rotary piston pump e.g. high-pressure pump for conveying fluid e.g. fuel to internal combustion engine, has an actuator for variable control and/or regulation of bypass channel, to integrate routable volume flow of fluid into channel |
| DE102012223892A1 (en) | 2012-12-20 | 2014-06-26 | Robert Bosch Gmbh | Rotary piston pump e.g. gear pump, for conveying e.g. petrol into combustion engine in motor car, has chamber arranged at wheel, where position of outflow and inflow channels at chamber is adjustable for controlling volumetric flow of fluid |
| DE102012223930A1 (en) | 2012-12-20 | 2014-06-26 | Robert Bosch Gmbh | Rotary piston pump i.e. gear pump, for conveying fluid in high pressure injection system for combustion engine for motor car, has bypass duct passed into channel, and regulating unit regulating control of volumetric flow of fluid by duct |
| DE102015213387A1 (en) | 2015-07-16 | 2017-01-19 | Robert Bosch Gmbh | Rotary piston pump |
| DE102016206062A1 (en) | 2016-04-12 | 2017-10-12 | Robert Bosch Gmbh | Rotary piston pump |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB237147A (en) * | 1924-11-11 | 1925-07-23 | Leroux Eugene | A compressed-air rotary engine |
| GB297860A (en) * | 1927-06-28 | 1928-09-28 | Sigismondo Diamant | Improvements in or relating to rotary gear pumps |
| FR933636A (en) * | 1945-10-25 | 1948-04-27 | Eaton Mfg Co | Improvements to multi-stage compound pumping systems |
| GB661875A (en) * | 1947-05-07 | 1951-11-28 | Borg Warner | Improvements in or relating to gear pump assemblies |
| FR1004798A (en) * | 1947-05-14 | 1952-04-02 | Snecma | Installation of pressurized fluid distribution at various flow rates |
| GB707904A (en) * | 1950-07-06 | 1954-04-28 | Cummins Engine Co Inc | Improvements in or relating to a fuel supply apparatus for an internal combustion engine |
| FR1080123A (en) * | 1952-05-24 | 1954-12-07 | Borg Warner | Improvements in hydraulic transmission systems |
| DE1004483B (en) * | 1955-09-17 | 1957-03-14 | Wolfram Sielemann | Switching arrangement of several displacement pumps for gradual regulation of the total delivery rate |
| GB985331A (en) * | 1960-06-15 | 1965-03-10 | Plessey Co Ltd | Improvements in or relating to hydraulic engine starters |
| US3361068A (en) * | 1966-08-18 | 1968-01-02 | Allis Chalmers Mfg Co | Double hydraulic pump with built-in unloading valve |
| US3601506A (en) * | 1969-11-28 | 1971-08-24 | Chandler Evans Inc | Wear equalized fuel delivery system |
| JPS52134101U (en) * | 1976-04-07 | 1977-10-12 | ||
| IT1119682B (en) * | 1979-03-07 | 1986-03-10 | Fiat Allis Macch Movi | AFLUID PUMP FOR HYDRAULIC CIRCUITS |
-
1984
- 1984-02-22 DE DE19843406349 patent/DE3406349A1/en not_active Withdrawn
- 1984-05-30 JP JP59108742A patent/JPH0617672B2/en not_active Expired - Lifetime
- 1984-05-31 GB GB08413921A patent/GB2140872B/en not_active Expired
- 1984-06-01 IT IT21210/84A patent/IT1178481B/en active
- 1984-06-01 FR FR8408678A patent/FR2546981B1/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| IT1178481B (en) | 1987-09-09 |
| GB8413921D0 (en) | 1984-07-04 |
| FR2546981B1 (en) | 1988-11-25 |
| IT8421210A0 (en) | 1984-06-01 |
| IT8421210A1 (en) | 1985-12-01 |
| JPS603492A (en) | 1985-01-09 |
| DE3406349A1 (en) | 1984-12-06 |
| FR2546981A1 (en) | 1984-12-07 |
| GB2140872B (en) | 1987-07-08 |
| GB2140872A (en) | 1984-12-05 |
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