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WO1980001098A1 - Orientable blades for hydraulic machines - Google Patents

Orientable blades for hydraulic machines Download PDF

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Publication number
WO1980001098A1
WO1980001098A1 PCT/DE1978/000034 DE7800034W WO8001098A1 WO 1980001098 A1 WO1980001098 A1 WO 1980001098A1 DE 7800034 W DE7800034 W DE 7800034W WO 8001098 A1 WO8001098 A1 WO 8001098A1
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WO
WIPO (PCT)
Prior art keywords
blades
profile
flow
fixed
rotatable
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.)
Ceased
Application number
PCT/DE1978/000034
Other languages
German (de)
French (fr)
Inventor
E Floegel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to PCT/DE1978/000034 priority Critical patent/WO1980001098A1/en
Priority to IT27266/79A priority patent/IT1165370B/en
Priority to JP14828679A priority patent/JPS55104508A/en
Publication of WO1980001098A1 publication Critical patent/WO1980001098A1/en
Priority to EP78900264A priority patent/EP0020331A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/48—Control of exclusively fluid gearing hydrodynamic
    • F16H61/50—Control of exclusively fluid gearing hydrodynamic controlled by changing the flow, force, or reaction of the liquid in the working circuit, while maintaining a completely filled working circuit
    • F16H61/52—Control of exclusively fluid gearing hydrodynamic controlled by changing the flow, force, or reaction of the liquid in the working circuit, while maintaining a completely filled working circuit by altering the position of blades
    • F16H61/56—Control of exclusively fluid gearing hydrodynamic controlled by changing the flow, force, or reaction of the liquid in the working circuit, while maintaining a completely filled working circuit by altering the position of blades to change the blade angle

Definitions

  • the invention relates to rotatable blades, the fixed guide blades or the fixed blades of a wheel of a turbomachine.
  • Hydrodynamic torque converters with such rotatably mounted blades are known (eg US Pat. No. 2,190,830).
  • this measure can advantageously be applied to the stator of a Trilok converter.
  • Each fixed vane of the stator is preceded by a rotatable, smaller vane, which is pressed in the region of greater change by the flowing working fluid against the underside of the fixed vane and forms a strongly curved profile with it.
  • the upstream blade rotates with the direction of flow and thus releases a gap between it and the downstream fixed blade, whereby the impact losses are reduced compared to the profile formed in the event of a major change.
  • the object of the invention is now to significantly reduce the impact losses of the stator in the clutch area compared to the prior art when using a profile of the rotatable blades that is optimal for the area of greater conversion.
  • each rotatable blade can be arranged so that the profile nose of the downstream fixed blade is covered by the rounded profile nose of the rotating blade, so that it lies in the "slipstream" of the rotating blade (Fig. 1). Thanks to this, impact losses are largely avoided on the downstream fixed blade and the two blades together form a profile that is almost ideal for the coupling area and the area of the smaller wall.
  • the impact losses of this stator are even lower than the impact losses of the fixed blades alone. That is, they are lower than the shock losses of the stator in the disassembled rotatable blades, which means a corresponding reduction in the shock losses compared to the prior art described above.
  • FIG. 2 the position of the rotatable blade 1 to the fixed blade 2 depending on the different flow directions 6 to 8 of the working medium.
  • the blade 1 is around
  • the position of the rotatable blade 1 in FIG. 2 results from the position in Pig. 1 by turning clockwise by 120 degrees.
  • Fig. 3 corresponds to Pig. 2, only the axis of rotation 11 is arranged differently here.
  • the position of the rotatable blade 1 for the flow directions 7 to 8 remains unchanged as in FIG. 1.
  • Fig. 4 shows a Trilok converter according to the invention in section.
  • Pig. 4 illustrates one embodiment of a hydrodynamic torque converter that best takes advantage of this invention.
  • the stator is located between the pump 3 and the turbine 4 connected to the output shaft 41, which is connected to the housing 5 via a one-way clutch 51.
  • a smaller vane 1 In front of each fixed vane 2 of the stator is a smaller vane 1, which is rotatably supported about the axis 11 by means of two bearings 12 in the inner and outer stator ring - 21 and 27.
  • the control of this rotatable blade 1 takes place via a lever arm 13 which carries a tooth-shaped cam 14 which engages in an annular groove 26 of an annular piston 22 which is displaceably mounted in the stator housing 21.
  • the cavity formed by the annular piston 22 and the stator housing 21 - the sealing strip 23 is used for sealing purposes - is connected to the control line 52 via the bore 25 and the annular groove 24.
  • the necessary overpressure or underpressure is generated in this cavity, which is necessary to move the annular piston 22 and fix it in the two possible end positions, and thus simultaneously adjust the rotatable blades 1 accordingly, whereby they Rotate about 120 degrees around axis 11.
  • the usual creep tendency of the automatic system can be greatly reduced with this construction, since the rotating blades are basically the same as in Pig. 1 can be set.
  • the type of control is not the subject of this invention.
  • the profiling of the stator blades and their arrangement corresponds to the representation in FIG. 1 with regard to the middle current filament.
  • This torque converter shown is designed so that it has a very low pressure in the coupling point. This is achieved here in that the radius of the stator outlet has been chosen larger than the radius of the turbine outlet. At the same time, this measure increases the maximum conversion.
  • This construction is known per se, only on a conventional stator would such high shock losses occur in the coupling area that the coupling point would be reached at a relatively low speed ratio of the turbine and pump.
  • the stator according to the invention leads to a sufficient reduction in shock losses and to a correspondingly high coupling point which, in conjunction with the low pressure, enables this converter to manage with two instead of the usual three downstream gear stages. It is not necessary to shift gears automatically because the high maximum conversion results in sufficient acceleration even in direct gear.
  • the converter according to the invention is instead combined with a conventional downstream 3-speed fully automatic system, the third gear can be designed as a fast or economy gear, which would result in a corresponding fuel saving. In the case of a fully automatic transmission, there would also be no need to increase the radius of the pump outlet.
  • the invention is not limited to the shownssensfor men, rather it can be used advantageously in all impellers and guide wheels or fixed guide devices of turbomachines as soon as the flow direction of the working medium in the various working areas of the machine differs greatly.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Fluid Gearings (AREA)

Abstract

Orientable blades (1) are juxtaposed to the fixed or main blades (2) of the wheel of a hydraulic machine. To cover a maximum of flow directions of the medium, these moving blades are orientated in certain working areas of the hydraulic machine so as to place their trailing edges in the flow axis (8). Thereby, an inversion of the curvature of the profile of the blades is provided with respect to the flowing axis (6). This blade wheel may be use particularly as a directional wheel in a Trilok-converter.

Description

Verstellbare Schaufeln für StrömungsmaschinenAdjustable blades for turbo machines

Die Erfindung bezieht sich auf drehbare- Schaufeln, die festen Leitschaufeln oder den festen Schaufeln eines Rades einer Strömungsmaschine vorgelagert sind.The invention relates to rotatable blades, the fixed guide blades or the fixed blades of a wheel of a turbomachine.

Bekannt sind hydrodynamische Drehmomentwandler mit derartigen drehbar gelagerten Schaufeln (z.B. US-Patent 2 190 830). Insbesondere kann diese Maßnahme beim Leitrad eines Trilok-Wandlers vorteilhaft angewandt werden. Dabei ist jeder festen Schaufel des Leitrades eine drehbare kleinere Schaufel vorgelagert, die im Bereich stärkerer Wandlung durch die strömende Arbeitsflüssigkeit an die Unterseite der festen Schaufel gedrückt wird und mit ihr zusammen ein stark gekrümmtes Profil bildet. Bei Annäherung an den Kupplungsbereich dreht sich die vorgelagerte Schaufel mit der Strömungsrichtung und gibt so einen Spalt zwischen sich und der nachgelagerten festen Schaufel frei, wodurch die Stoßverluste gegenüber dem bei stärkerer Wandlung gebildeten Profil verringert werden. Der Nachteil dieser Konstruktion besteht darin, daß die drehbaren Schaufeln der strömenden Arbeitsflüssigkeit im Kupplungsbereich immer noch einen Strömungswiderstand bieten, der sich zu den Stoßverlusten an den nachgelagerten festen Schaufeln hinzuaάdiert. Dieser Widerstand ist umso größer, .je stärker gekrümmt die drehbaren Schaufeln gestaltet sind. D.h. ein für den Wandlungsbereich optimales Profil der drehbaren Schaufeln - das notwendigerweise eine entsprechende Krümmung Kupplungsbereich in geringerem Maße vermindern.Hydrodynamic torque converters with such rotatably mounted blades are known (eg US Pat. No. 2,190,830). In particular, this measure can advantageously be applied to the stator of a Trilok converter. Each fixed vane of the stator is preceded by a rotatable, smaller vane, which is pressed in the region of greater change by the flowing working fluid against the underside of the fixed vane and forms a strongly curved profile with it. When the coupling area is approached, the upstream blade rotates with the direction of flow and thus releases a gap between it and the downstream fixed blade, whereby the impact losses are reduced compared to the profile formed in the event of a major change. The disadvantage of this construction is that the rotatable blades of the flowing working fluid in the coupling area still offer a flow resistance that adds to the shock losses on the downstream fixed blades. This resistance is greater, the more curved the rotating blades are designed. Ie an optimal profile of the rotating blades for the area of change - this necessarily requires a corresponding curvature Reduce the coupling area to a lesser extent.

Aufgabe der Erfindung ist es -nun, bei Verwendung eines für den Bereich stärkerer Wandlung optimalen Profiles der drehbaren Schaufeln die Stoßverluste des Leitrades im Kupplung bereich gegenüber dem Stand der Technik wesentlich zu vermindern.The object of the invention is now to significantly reduce the impact losses of the stator in the clutch area compared to the prior art when using a profile of the rotatable blades that is optimal for the area of greater conversion.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß die drehbaren Schaufeln für den Bereich geringerer Wandlung und dem Kupplungsbereich so weit gedreht werden, daß die Profil hinterkanten in die Strömungsrichtung zeigen (Pig. 1). Dadurch kehrt sich die Krümmung der drehbaren Schaufeln um, und es wird ein nahezu stoßfreier Eintritt der strömenden Arbeitsflüssigkeit erreicht. Zusätzlich kann die Achse jede drehbaren Schaufel so angeordnet werden, daß die Profilnase der nachgelagerten festen Schaufel durch die abgerundete Profilnase der drehbaren Schaufel abgedeckt wird, so daß sie im "Windschatten" der drehbaren Schaufel liegt (Fig. 1). Dadurc werden Stoßverluste - an der nachgelagerten festen Schaufel weitgehend vermieden und beide Schaufeln bilden zusammen ein für den Kupplungsbereich und den Bereich geringerer Wandlun nahezu ideales Profil. Das führt dazu, daß die Stoßverluste dieses Leitrades sogar noch niedriger sind, als die Stoßverluste der festen Schaufeln alleine. D.h., daß sie niedriger sind als die Stoßverluste des Leitrades bei demontierten drehbaren Schaufeln, was eine entsprechende Verringerung der Stoßverluste gegenüber dem oben beschriebenen Stand der Technik bedeutet.This object is achieved in that the rotatable blades for the area of lower conversion and the coupling area are rotated so far that the profile edges point in the direction of flow (Pig. 1). This reverses the curvature of the rotatable blades and the flowing working fluid is almost free of bumps. In addition, the axis of each rotatable blade can be arranged so that the profile nose of the downstream fixed blade is covered by the rounded profile nose of the rotating blade, so that it lies in the "slipstream" of the rotating blade (Fig. 1). Thanks to this, impact losses are largely avoided on the downstream fixed blade and the two blades together form a profile that is almost ideal for the coupling area and the area of the smaller wall. As a result, the impact losses of this stator are even lower than the impact losses of the fixed blades alone. That is, they are lower than the shock losses of the stator in the disassembled rotatable blades, which means a corresponding reduction in the shock losses compared to the prior art described above.

Die Erfindung wird nachstehend anhand der Zeichnungen noch näher veranschaulicht. Dabei zeigt in rein schematischer Weise:The invention is illustrated below with reference to the drawings. This shows in a purely schematic manner:

Fig. 1-2 die Stellung der drehbaren Schaufel 1 zur festen Schaufel 2 in Abhängigkeit von den verschiedenen Anströmrichtungen 6 bis 8 des Arbeitsmediums. Die Schaufel 1 ist um die Stellung der drehbaren Schaufel 1 in Fig. 2 ergibt sich aus der Stellung in Pig. 1 durch Rechtsdrehung um 120 Grad.Fig. 1-2, the position of the rotatable blade 1 to the fixed blade 2 depending on the different flow directions 6 to 8 of the working medium. The blade 1 is around The position of the rotatable blade 1 in FIG. 2 results from the position in Pig. 1 by turning clockwise by 120 degrees.

Fig. 3 entspricht Pig. 2, nur ist hier die Drehachse 11 anders angeordnet. Die Stellung der drehbaren Schaufel 1 für die Anströmrichtungen 7 bis 8 bleibt dabei unverändert wie in Fig. 1.Fig. 3 corresponds to Pig. 2, only the axis of rotation 11 is arranged differently here. The position of the rotatable blade 1 for the flow directions 7 to 8 remains unchanged as in FIG. 1.

Fig. 4 einen erfindungsgemäßen Trilok-Wandler im Schnitt.Fig. 4 shows a Trilok converter according to the invention in section.

Pig. 4 stellt ein Ausführungsbeispiel eines hydrodynamischen Drehmomentwandlers dar, an dem die Vorteile dieser Erfindung am besten zur Wirkung kommen. In der üblichen Trilok-Bauweise liegt hier -zwischen- der Pumpe 3 und der mit der Abtriebswelle 41 verbundenen Turbine 4 das Leitrad, welches über eine Freilaufkupplung 51 mit dem Gehäuse 5 verbunden ist. Vor jeder festen Schaufel 2 des Leitrades ist eine kleinere Schaufel 1 angeordnet, die um die Achse 11 mittels zweier Lager 12 im inneren und äußeren Leitradring - 21 und 27 - drehbar gelagert ist. Die Steuerung dieser drehbaren Schaufel 1 erfolgt über einen Hebelarm 13, der eine zahnförmige Nocke 14 trägt, die in eine Ringnut 26 eines im Leitradgehäuse 21 verschiebbar gelagerten Ringkolbens 22 eingreift. Der durch den Ringkolben 22 und dem Leitradgehäuse 21 gebildete Hohlraum - zur Abdichtung dient die Dichtleiste 23 - steht über die Bohrung 25 und die Ringnut 24 mit der Steuerleitung 52 in Verbindung. Über die Steuerleitung wird der notwendige Über- bzw. Unterdruck in diesem Hohlraum erzeugt, der notwendig ist, um den Ringkolben 22 zu verschieben und ihn in den beiden möglichen Endstellungen zu fixieren, und damit gleichzeitig die drehbaren Schaufeln 1 -entsprechend einzustellen, wobei sie um ca. 120 Grad um die Achse 11 gedreht v/erden. Außerdem kann mit dieser Konstruktion die übliche Kriechneigung der Automatik stark reduziert werden, indem bei Nullgas die drehbaren Schaufeln grundsätzlich so wie in Pig. 1 eingestellt werden. Die Art der Steuerung st jedoch n cht Gegenstand d eser Erfindung. Die Profilierung der Leitradschaufeln und ihre Anordnung entspricht bezüglich des mittleren Stromfadens der Darstellung in Fig. 1.Pig. 4 illustrates one embodiment of a hydrodynamic torque converter that best takes advantage of this invention. In the usual Trilok design, the stator is located between the pump 3 and the turbine 4 connected to the output shaft 41, which is connected to the housing 5 via a one-way clutch 51. In front of each fixed vane 2 of the stator is a smaller vane 1, which is rotatably supported about the axis 11 by means of two bearings 12 in the inner and outer stator ring - 21 and 27. The control of this rotatable blade 1 takes place via a lever arm 13 which carries a tooth-shaped cam 14 which engages in an annular groove 26 of an annular piston 22 which is displaceably mounted in the stator housing 21. The cavity formed by the annular piston 22 and the stator housing 21 - the sealing strip 23 is used for sealing purposes - is connected to the control line 52 via the bore 25 and the annular groove 24. About the control line, the necessary overpressure or underpressure is generated in this cavity, which is necessary to move the annular piston 22 and fix it in the two possible end positions, and thus simultaneously adjust the rotatable blades 1 accordingly, whereby they Rotate about 120 degrees around axis 11. In addition, the usual creep tendency of the automatic system can be greatly reduced with this construction, since the rotating blades are basically the same as in Pig. 1 can be set. However, the type of control is not the subject of this invention. The profiling of the stator blades and their arrangement corresponds to the representation in FIG. 1 with regard to the middle current filament.

Dieser dargestellte Drehmomentwandler ist so ausgelegt, daß er im Kupplungspunkt eine sehr niedrige Drückung aufweist. Das wird hier dadurch erreicht, daß der Radius des Leitradaustrittes größer gewählt wurde als der Radius des Turbinenaustrittes. Gleichzeitig erhöht diese Maßnahme die maximale Wandlung. Diese Konstruktion ist an sich bekannt, nur würden an einem herkömmlichen Leitrad, so hohe Stoßverluste im Kupplungsbereich auftreten, daß der Kupplungspunkt bereits bei einem verhältnismäßig niedrigen Drehzahlverhältnis von Turbine und Pumpe erreicht würde. Hier führt das erfindungsgemäße Leitrad zu einer ausreichenden Reduzierung der Stoßverluste und zu einem entsprechend hohen Kupplungspunkt der es in Verbindung mit der niedrigen Drückung ermöglicht, daß dieser Wandler mit zwei statt der üblichen drei nachgeschaltete Gangstufen auskommt. Sin automatisches Schalten der Gänge ist dabei nicht notwendig, da die hohe maximale Wandlung eine ausreichende Anfahrbeschleunigung auch im direkten Gang ergibt. Es würde also eine 2-Gang-Halbautomatik genügen. Wird der erfindungsgemäße Wandler stattdessen mit einer üblichen nachgeschalteten 3-Gang-Vollautomatik kombiniert, kann der dritte Gang als Schnell- bzw. Spar-Gang ausgelegt werden, was eine entsprechende Kraftstoffersparnis zur Polge hätte. Im Falle eines vollautomatischen Getriebes würde sich auch die Erhöhung des Radius des Pumpenaustrittes erübrigen.This torque converter shown is designed so that it has a very low pressure in the coupling point. This is achieved here in that the radius of the stator outlet has been chosen larger than the radius of the turbine outlet. At the same time, this measure increases the maximum conversion. This construction is known per se, only on a conventional stator would such high shock losses occur in the coupling area that the coupling point would be reached at a relatively low speed ratio of the turbine and pump. Here, the stator according to the invention leads to a sufficient reduction in shock losses and to a correspondingly high coupling point which, in conjunction with the low pressure, enables this converter to manage with two instead of the usual three downstream gear stages. It is not necessary to shift gears automatically because the high maximum conversion results in sufficient acceleration even in direct gear. So a 2-speed semi-automatic would suffice. If the converter according to the invention is instead combined with a conventional downstream 3-speed fully automatic system, the third gear can be designed as a fast or economy gear, which would result in a corresponding fuel saving. In the case of a fully automatic transmission, there would also be no need to increase the radius of the pump outlet.

Die Erfindung ist nicht auf die dargestellten Ausführungsfor men beschränkt, vielmehr kann sie bei allen Lauf- und Leiträdern bzw. festen Leitvorrichtungen von Strömungsmaschinen vorteilhaft eingesetzt werden, sobald die Anstromrichtung de Arbeitsmediums in den verschiedenen Arbeitsbereichen der Maschine stark differiert. The invention is not limited to the shown Ausführungsfor men, rather it can be used advantageously in all impellers and guide wheels or fixed guide devices of turbomachines as soon as the flow direction of the working medium in the various working areas of the machine differs greatly.

Claims

P A T E N T A N S P R Ü C HE PATENT CLAIMS 1. Strömungsmaschinen mit drehbaren Schaufeln, die festen Leitschaufeln oder den festen Schaufeln eines Rades vorgelagert sind, d a du r c h g e k e nn z e i c h n e t , daß die drehbaren Schaufeln (1) für bestimmte Arbeitsbereiche der Strömungsmaschine soweit gedreht werden, daß die Hinterkante ihres Profiles in die Strömungsrichtung (8) zeigt und sich damit die Krümmung ihres Profiles bezüglich der Strömungsrichtung umkehrt.1. Turbomachines with rotatable blades, the fixed guide blades or the fixed blades of a wheel are upstream, since you rchgeke nn draws that the rotatable blades (1) for certain working areas of the turbomachine are rotated so far that the trailing edge of their profile in the direction of flow ( 8) shows that the curvature of its profile is reversed with respect to the direction of flow. 2. Strömungsmaschinen nach Anspruch 1, bei denen die drehbaren Schaufeln (1) je einer festen Schaufel (2) vorgelagert sind und ein Profil mit abgerundeter Profilnase und scharf auslaufender Hinterkante aufweisen, d a d u r c h g e k e n n z e i c h n e t , daß die Drehachsen (11) der Schaufeln (1) so angeordnet sind, daß in der Stellung, in der die Hinterkante ihres Profiles in die Strömungsrichtung (8) zeigt, ihre abgerundete Profilnase genau vor der Profilnase der betreffenden nachgelagerten festen Schaufel (2) liegt, so daß sich die festen Schaufeln (2) bezüglich der Strömungsrichtung (8) im Windschatten der drehbaren Schaufeln (1) befinden. 2. Turbomachines according to claim 1, in which the rotatable blades (1) are each a fixed blade (2) upstream and have a profile with a rounded profile nose and tapering trailing edge, characterized in that the axes of rotation (11) of the blades (1) so are arranged that in the position in which the rear edge of their profile points in the direction of flow (8), their rounded profile nose is exactly in front of the profile nose of the downstream fixed blade (2) in question, so that the fixed blades (2) with respect to Flow direction (8) in the slipstream of the rotatable blades (1).
PCT/DE1978/000034 1978-11-15 1978-11-15 Orientable blades for hydraulic machines Ceased WO1980001098A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
PCT/DE1978/000034 WO1980001098A1 (en) 1978-11-15 1978-11-15 Orientable blades for hydraulic machines
IT27266/79A IT1165370B (en) 1978-11-15 1979-11-14 ADJUSTABLE PALETTE FOR DYNAMIC FLUID MACHINES
JP14828679A JPS55104508A (en) 1978-11-15 1979-11-15 Adjustable blade for flowwutilizing machine
EP78900264A EP0020331A1 (en) 1978-11-15 1980-06-03 Orientable blades for hydraulic machines

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
WODE78/00034 1978-11-15
PCT/DE1978/000034 WO1980001098A1 (en) 1978-11-15 1978-11-15 Orientable blades for hydraulic machines

Publications (1)

Publication Number Publication Date
WO1980001098A1 true WO1980001098A1 (en) 1980-05-29

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ID=6687346

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1978/000034 Ceased WO1980001098A1 (en) 1978-11-15 1978-11-15 Orientable blades for hydraulic machines

Country Status (4)

Country Link
EP (1) EP0020331A1 (en)
JP (1) JPS55104508A (en)
IT (1) IT1165370B (en)
WO (1) WO1980001098A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2507251A1 (en) * 1981-06-05 1982-12-10 Escher Wyss Sa TURBINE INTENDED TO BE MOVED ALTERNATIVELY IN ONE SENSE AND IN THE OTHER BY THE WORKING FLUID

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE275474C (en) *
US2187937A (en) * 1932-04-23 1940-01-23 Dimitri Sensaud De Lavaud Hydraulic device for transmitting movement
US2205794A (en) * 1935-02-23 1940-06-25 Jandasek Joseph Turbine torque converter and clutch
FR53410E (en) * 1942-11-27 1946-01-10 Maybach Motorenbau Gmbh Current hydraulic gear change mechanism
FR1136414A (en) * 1955-09-23 1957-05-14 Caillard Et Cie Sa Des Ets Hydraulic clutch
US2909034A (en) * 1957-05-13 1959-10-20 Ford Motor Co Hydrokinetic torque converter with adjustable reactor blades

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE275474C (en) *
US2187937A (en) * 1932-04-23 1940-01-23 Dimitri Sensaud De Lavaud Hydraulic device for transmitting movement
US2205794A (en) * 1935-02-23 1940-06-25 Jandasek Joseph Turbine torque converter and clutch
FR53410E (en) * 1942-11-27 1946-01-10 Maybach Motorenbau Gmbh Current hydraulic gear change mechanism
FR1136414A (en) * 1955-09-23 1957-05-14 Caillard Et Cie Sa Des Ets Hydraulic clutch
US2909034A (en) * 1957-05-13 1959-10-20 Ford Motor Co Hydrokinetic torque converter with adjustable reactor blades

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2507251A1 (en) * 1981-06-05 1982-12-10 Escher Wyss Sa TURBINE INTENDED TO BE MOVED ALTERNATIVELY IN ONE SENSE AND IN THE OTHER BY THE WORKING FLUID

Also Published As

Publication number Publication date
JPS55104508A (en) 1980-08-11
EP0020331A1 (en) 1981-01-07
IT7927266A0 (en) 1979-11-14
IT1165370B (en) 1987-04-22

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