DE1550756B1

DE1550756B1 - Hydrodynamic torque converter

Info

Publication number: DE1550756B1
Application number: DE1966F0049470
Authority: DE
Inventors: A Lysholm
Original assignee: A Friedrich Flender AG
Current assignee: A Friedrich Flender AG
Priority date: 1965-06-28
Filing date: 1966-06-15
Publication date: 1970-06-18
Also published as: NL146584B; CH492145A; BE683271A; GB1153873A; US3385061A; NL6608955A

Description

1 21 2

Die Erfindung betrifft einen hydrodynamischen gewünschten Dichtspalt bildet, wobei die den Pum-The invention relates to a hydrodynamically desired sealing gap, wherein the pumping

Drehmomentwandler, bei dem die Pumpenschaufeln penschaufeln zugekehrte innere Seitenkante desTorque converter with the pump blades facing the inner side edge of the

im radial nach außen durchströmten Kanalbereich Kernringes eine Kurvenform aufweist, die den Un-in the channel area of the core ring through which flow is radially outward, has a curve shape which

des nur teilweise beschaufelten und mit einem zen- dichtigkeitsstrom dem Ring entlang radial nach außenthe only partially bladed and with a central leakage flow along the ring radially outwards

tralen Kern versehenen Strömungskreislaufes und die 5 leitet.central core provided flow circuit and the 5 leads.

Turbinen — sowie die Leitschaufeln in radial ver- Endlich ist noch vorgesehen, daß die absatzartigeTurbines - as well as the guide vanes in radial direction. Finally it is still provided that the step-like

laufenden Bereichen des Kreislaufes angeordnet sind, Erweiterung des Strömungsquerschnittes an derrunning areas of the circuit are arranged, expansion of the flow cross-section at the

wobei sich der durchströmte Kreislaufquerschnitt Nabe des Pumpenschaufelrades ausgebildet ist.wherein the flow cross-section is formed by the hub of the pump impeller.

zwischen den Leitschaufeln und dem Pumpenrad in Zwei Ausführungsbeispiele der Erfindung sind inbetween the guide vanes and the impeller in two embodiments of the invention are shown in FIG

Strömungsrichtung verringert. io der Zeichnung dargestellt, und zwar zeigtDirection of flow reduced. io of the drawing shown, namely shows

Die der Erfindung zugrunde liegende Aufgabe be- F i g. 1 einen Längsschnitt durch die Hälfte einesThe object on which the invention is based relates to FIG. 1 is a longitudinal section through half of a

steht darin, die Strömungsverluste durch im Kreis- einstufigen Wandlers,it says the flow losses due to the single-stage converter in the circuit,

lauf zu vermindern und einen besonders günstigen F i g. 2 einen Längsschnitt durch die Hälfte einesto reduce running and a particularly favorable F i g. 2 is a longitudinal section through half of a

Wirkungsgrad bei Wandlern zu erreichen. Wandlers mit zwei Leitschaufelkränzen, von denenTo achieve efficiency in converters. Converter with two guide vane rings, one of which

Diese Aufgabe soll dadurch gelöst werden, daß 15 einer freilaufend ist.This object is to be achieved in that 15 one is free running.

a) die Verengung im letzten Drittel desKanalkrüm- Im einstufigen Wandler nach Fig. 1 ist mehr als mers vor dem Pumpeneinlaß beginnt und die die Hälfte des äußeren Umfangs der Arbeitskammer geringste Strömungsquerschnittsfläche in Strö- durch die innere Mantelfläche eines zweiteiligen Gemungsrichtung kurz^;vor dem Pumpenradeintritt häuses la, Ib begrenzt, das in nicht gezeigter Weise in einem radial bezüglich der Kanalbegrenzungs- 20 mit dem Gestell des Wandlers fest verbunden ist. Die flächen liegenden Schnitt erreicht ist; übrige äußere Begrenzungsfläche der Arbeitskammera) the narrowing in the last third of the channel bend is short in the single-stage converter according to Fig. 1 more than mers before the pump inlet and the half of the outer circumference of the working chamber smallest flow cross-sectional area in flow through the inner surface of a two-part Gemungsrichtung short ^; limited in front of the pump wheel inlet housing la, Ib , which is firmly connected in a manner not shown in a radial manner with respect to the channel limitation 20 with the frame of the converter. The surface lying cut is reached; remaining outer boundary surface of the working chamber

b) daß ein Dichtspalt zwischen dem inneren radia- ™^{rd dur}f ^di%^N*^be eines Pumpenrades 2 und durch len Abschluß des Pumpenkernringes und der ?^msa äußeren Seitenrmg 3 b eines Turbinenschaufelinneren Kernmantelfläche so ausgebildet ist, daß ^Kr?^f^esr ^{a %}%^Ü77. , ..„ . . . _T . . . , die unter Überdruck stehende Flüssigkeit im ²⁵ , Mit der Gehausehalfte 1α ist ein Leitschaufel-Kernraum an dieser Stelle in den Strömungs- *™ηζ4β fest verbunden, dessen inneres Ende an kreislauf eintritt und die Grenzschicht entlang einem Kernring 5 befestigt ist und von diesem getrader Innenseite der Pumpenschaufeln abbläst gen wird Der Kernrmg hat auf der den Leitschaufeln fCoandaeffektV abgekehrten Seite eine Aussparung 5 a, in der so-b) that a sealing gap between the inner radial ™ ^{rd dur} f ^di % ^N * ^{be of} a pump wheel 2 and through len closure of the pump core ring and the ? ^msa outer Seitenrmg 3 b of a turbine blade inner core jacket surface is designed so that ^Kr ? ^ f ^it r ^a ^{%% Ü} 77. , .. “. . . _T. . . , the pressurized liquid in ²⁵ , with the housing half 1α a guide vane core space is firmly connected at this point in the flow * ™ ηζ4β, the inner end of which enters the circuit and the boundary layer is attached along a core ring 5 and from this gear The core arm has a recess 5 a on the side facing away from the guide vanes, in the lower

x ,„,„.. .... , 30 wohl ein innerer Seitenring 3 c der Turbinenschaufelx, "," .. ...., 30 probably an inner side ring 3 c of the turbine blade

c) daß der Stromungsquerschnitt hinter dem eng- 3 _a _{alg auch ein} _bmBta. ^_{n 2 c} _{deg Schaufelkran}.c) that the flow cross-section behind the eng- 3 _a _{alg also a} _bmBta . ^ _{n 2 c} _{deg bucket crane} .

sten Flachenquerschnitt unmittelbar vor dem _{zeg 2 fl deg Pmnpenrades 2} ^ _passendem Anschluß Pumpeneinlaß eine geringe absatzartige Erwei- _aQ ^ äußeren Krümmungsradien des Kernrings 5 terung zur Erzeugung eines Carnotstoßes auf- _drehbar _aag!BOldaist _sind> The most flat cross-section directly in front of the _{zeg 2 fl deg Pmnpenrades 2} ^ _matching connection pump inlet a small step-like widening _aQ ^ the outer radii of curvature of the core ring to generate a Carnot impact can be _rotated _{aag! BOldaist} _>

^wels ' 35 Das Pumpenrad 2 ist mittels einer Vielnutverbin- ^wels ' 35 The pump wheel 2 is connected by means of a multi-groove

Es ist bereits bekannt, Querschnittsverengungen dung od. dgl. fest auf einer Hohlwelle 6 angebracht, in Strömungsrichtung bei Kreisläufen von Wandlern die in einem Kugellager 7 in der Gehäusehälfte 1 a vor dem Pumpengitter vorzunehmen, wobei diese und in einem Gleitlager 8 od. dgl. in einem Turbinen-Verengungen jedoch über größere Bereiche und rad 3 drehbar gelagert ist und den Momentwandler durchweg konstant verlaufen. 40 antreibt.It is already known, cross-sectional constrictions dung od. Like. Fixedly mounted on a hollow shaft 6, which make in the direction of flow in circuits of transformers in a ball bearing 7 in the housing half 1a prior to the pumping grid, od this and in a sliding bearing. 8 like. in a turbine constriction, however, is rotatably mounted over larger areas and wheel 3 and the torque converter is constant throughout. 40 drives.

Auch das Abblasen der Grenzschicht bei Schau- Die Pumpenschaufeln 2 α setzen dabei eine in derAlso the blowing off of the boundary layer in the case of show- The pump blades 2 α put one in the

fein von Turbomaschinen ist bekannt. Arbeitskammer unter Überdruck eingeschlossenefine of turbo machines is known. Working chamber enclosed under overpressure

Ferner ist es bekannt, die Pumpeneintrittsbreite Flüssigkeit in Umlauf, die durch den Turbinenschauetwas größer zu machen als die Leitradaustrittsbreite. felkranz 3 α strömt und das Turbinenrad 3 in Dre-Dies erfolgt bei Wandlern aus konstruktiven Grün- 45 hung versetzt. Die Turbinenwelle 3 d ist in einem den, die fertigungsmäßig bedingt und ohne besondere Kugellager 9 in der Gehäusehälfte 1 b gelagert und Auswirkung sind. bildet die Abtriebswelle des Momentwandlers.Furthermore, it is known to make the pump inlet width of the liquid in circulation, which, as viewed in the turbine, is somewhat larger than the stator outlet width. felkranz 3 α flows and the turbine wheel 3 in Dre-Dies takes place in converters for structural reasons 45 offset. The turbine shaft 3 d is in one of the production-related and stored without special ball bearings 9 in the housing half 1 b and effect. forms the output shaft of the torque converter.

Durch die Erfindung wird infolge der Verengung Die zusammengesetzte äußere BegrenzungsflächeThrough the invention, as a result of the constriction, the composite outer boundary surface

des schaufelfreien Kanals vor der Pumpe, durch den der Kreislaufkammer bildet zusammen mit dem Kern-Coandaeffekt. — Wegblasen eines Teiles der Grenz- 5° ring 5 und den Innenringen 2 c, 3 c der Schaufelschicht entlang der Innenseite der Pumpenschaufeln kränze 2 α bzw. 3 α einen Flüssigkeitskreislauf mit zur Verhinderung einer Ablösung und durch den un- einem radial nach außen durchströmten Kanal 10 mittelbar vor dem Pumpeneinlaß erfolgenden Carnot- und einem entsprechenden, nach innen durchströmstoß, durch dessen Wirbel vor dem Pumpeneinlaß ten Kanal 11, die durch einen äußeren und einen wieder eine normale Grenzschicht hergestellt wird, 55 inneren schaufelfreien Krümmer 12 bzw. 13 miteinein besonders günstiger Strömungskreislauf hervor- ander verbunden sind.the vane-free channel in front of the pump, through which the circulation chamber forms together with the core Coanda effect. - Blowing away part of the boundary 5 ° ring 5 and the inner rings 2 c, 3 c of the blade layer along the inside of the pump blades wreath 2 α and 3 α a liquid circuit with to prevent detachment and through which one flowed radially outward Channel 10 taking place indirectly before the pump inlet Carnot and a corresponding, inward flow, through the vortex before the pump inlet th channel 11, which is made by an outer and a normal boundary layer again, 55 inner vane-free elbow 12 and 13 miteinein especially favorable flow circuit are connected to each other.

gerufen, bei dem die Strömungsverluste auf ein ge- Die Pumpenschaufeln 2 α und die Turbinenschau-called, in which the flow losses are due to the pump blades 2 α and the turbine

ringes Maß vermindert werden. fein 3 α sind im nach außen durchströmten Kanalreduced to a small extent. fine 3 α are in the outward flow channel

In vorteilhafter Weiterbildung der Erfindung ist drehbar angeordnet, während die als Reaktionsorgane vorgesehen, daß der Strömungsquerschnitt zwischen 60 dienenden Leitschaufeln 4 a, welche die Flüssigkeit dem Einlaß der Krümmung und dem Anfang der in einer bestimmten Richtung ablenken, in dem nach Verengung konstant ist, wobei die Verengung minde- innen durchströmten Kanal 11 fest angebracht sind, stens 5 °/o des Querschnittes des nach innen durch- Die Anordnung der Turbinenschaufeln 3 α radial strömten Kanals beträgt. außerhalb und die Strömungsrichtung in unmittel-In an advantageous development of the invention it is rotatably arranged, while the reaction organs are provided that the flow cross-section between 60 serving guide vanes 4 a, which deflect the liquid to the inlet of the curvature and the beginning of the in a certain direction, in which after narrowing is constant, wherein the constriction at least internally throughflow channel 11 are firmly attached, at least 5% of the cross-section of the inwardly through- The arrangement of the turbine blades 3 α radially flowed channel is. outside and the direction of flow in the immediate

Ein weiteres Merkmal der Erfindung liegt darin, 65 barem Anschluß an die Pumpenschaufeln 2 a, ermögdaß die innere Mantelfläche des Kernringes am ge- licht eine wirksame Ausnutzung der verschiedenen samten Umfang einen Vorsprung hat, der zusammen Geschwindigkeitskomponenten vom Pumpenauslaß mit dem Kernrmg des Pumpenschaufelkranzes den für die Momentwandlung.Another feature of the invention is the 65 barem connection to the pump blades 2a, enables the inner circumferential surface of the core ring to make effective use of the various entire circumference the moment change.

Claims

3 43 4

In the embodiment of FIG. 1, the flow is shown in FIG. 2, the inner bend 13 of the ungsquerschnitr of the inward flow in the flow direction in the frame anal 11 is slightly larger than the cross-section of the longest constriction according to the invention, The inner flow channel 11 is in the curved connecting channel 12 has essentially 5 cross section by less than 8% larger than that after constant cross-section. channel 10 with external flow. Here, too, is one

Experiments have shown, however, that for the purpose of step-like enlargement 2 b of the flow cross-section of the outer diameter of the housing 1 a, cut shortly before the pump inlet at the hub b, a reduction in the flow cross-section of the pump wheel 2 is formed, from about 10 ⁰ Zo in the middle of the channel 12 without io Just as with the single-stage torque converter, detectable additional losses are possible. F i g. 1 are the pump blades 2 α and the tur-

The inner manifold channel 13 between the canister blades 3 α in the outward flow 11 and 10, on the other hand, inclines at its core wall of the channel 10 of the circuit. The storage of it sometimes easier to signs of separation. With a pump and the turbine and the connection of its lücksicht thereon, the inner manifold 13 ER 15 inner rings 2 c and 3 c to the outer periphery of the indungsgemäß a narrowing of at least 5 ° / o central core ring 5 are consistent with the entsprechenuf, wherein the maximum constriction in a radial corresponds to the ratios of the single-stage converter. In contrast, the inner lateral surface of the solid ■ section AA through the core ring 5 forms. At the section housing la, Ib of the working chamber only the Be tA ends the guide and the inner radius 20 boundary surface of the outer circumference of the outer recess 5 a, the beginning of the narrowing curvature 12 of the working chamber. The outer Bennerhalb an area is, which comprises two thirds of the boundary of the inwardly flown-through channel 11 ^ length of the bend 13. and the first quarter of the inner curve 13 in

In the embodiment according to FIG. 1 is the presence of the flow direction through the hub of the constriction ang set so that the length of the comparison 25 of two stators 24, 25 are formed, ■ ngten part in the present invention the slightest The stator 24 is fixed in the housing Ia, Ib appropriate

st, whereby the flow cross-section of the manifold arranges and carries a fixed guide vane ring 24 a, J> on approximately two thirds of the manifold length which is approximately on the same radius as which is almost constant. Pump blade ring 2 a. The guide vanes 24 a

If, as in the previous exemplary embodiment, the cross-section of the inward flow-through 30 is not connected to the channel 11 by more than 5% larger than the core ring 5 and carries the same. ier of the outward flow channel 10 is the stator 25, the blades 25 α of which is radial

Cross-section of the narrowest point smaller outside the guide vanes 24 α , on the other hand, is the cross-section of the pump inlet. For the purpose of the two-phase converters in per se known / to reduce detachment in the pump inlet, 35 is mounted via a freewheel 14, which the guide: ine step-like extension 2 b of the flow wheel 25, for example when starting in a directional section on the hub of the Pump wheel 2 is formed opposite to the direction of rotation of the pump. The sudden expansion 2 b causes wheel 2 and turbine wheel 3 prevents. At higher 3Üie detachment on the outer circumference and causes a speed ratio acts on the blades Zarnot shock and thereby a small current vortex 40 25 α an opposing force, so that the stator lervor, which can be taken along a thin 25 at the pump inlet and in the liquid Boundary layer produces. electricity runs freely. It is therefore particularly important that such an extension 2 b is not tied to the flow losses in this guide vane ring 25 a specified cross-sectional ratio of the channels 10 and by the favorable design of the guide vanes down-II, but can also be used with advantage at 45 visibly in terms of their curvature and thickness to diminish. Larger differences between the flow A the upper guide vanes 25 α cross -sections of these channels are made. binding inner ring 25 c is in this embodiment-Along the inner radius, a detachment is counteracted for example in a recess of the fixed core ring 5 m pump inlet that a is arranged and closes at the limiting sealing gap between the inner radial edge of the 50 surface of the ring 5 to match.

inner ring 2 c of the pump blade ring and the switching on and off of the upper guide vane interior, shoulder-shaped outer surface of the core ring 25 α in indirect dependence on the rotary ^ es 5 is designed so that the leakage flow ratio of the motor and the adaptation of the jinen Coanda effect, thus blowing away the limit torque converter to alternative transmission ratio ■ does not cause. For this purpose, in the case of a differential gear or the like connected downstream, the inner circumferential surface of the core ring 5 is not explained in more detail.

Perimeter a projection 5 b, which can be used together with the The system of the two-phase converter

The inner ring 2 c of the pump blade ring can also be used to advantage in the case of converters rotating in opposite directions. Sealing gap forms, the pump blades 2 a

'. reversed inner side edge of the inner ring 2 c 60 claims:

has a waveform that represents the leakage flow

.lern ring 2 c conducts along radially outward. The 1st hydrodynamic torque converter, at

Leakage flow reaches a high speed as the pump blades radially outwards

'^ e time and therefore contributes to the boundary layer of the only partially exposed canal area, through which there is thin flow.

to make ncr and to counteract a detachment along the inner 65 blades and stranding of the pump blades 2 α with a central core. See the flow circuit and the turbine Dic design according to the invention of the hydraulic and the guide vanes in the radially extending working chamber of a two-phase converter is arranged in areas of the circuit, wherein

the flow cross-section between the guide vanes and the pump wheel is in Reduced flow direction, characterized in that

a) the narrowing begins in the last third of the channel bend (13) before the pump inlet and the smallest flow cross-sectional area in the flow direction is reached shortly before the pump wheel inlet (2 a) in a section (AA) lying radially with respect to the channel boundary surfaces;

b) a sealing gap between the inner radial end of the pump core ring (2 c) and the inner core jacket surface is designed so that the pressurized liquid in the core space (5 a) enters the flow circuit at this point (5 b) and along the boundary layer the inside of the pump blades (2 a) _Thus, blowing off (Coandaeff ect);

c) the flow cross-section behind the narrowest surface cross-section (AA) directly from the pump inlet has a small step-like widening (2 b) for generating a Carnot shock.

2. Hydrodynamic torque converter according to claim 1, characterized in that the flow cross section between the inlet of the curve (13) and the beginning of the constriction (AA) is constant.

3. Hydrodynamic torque converter according to claims 1 and 2, characterized in that the constriction is at least 5 ° / o of the Cross section of the inward flow channel (11) is.

4. Hydrodynamic torque converter 'according to claim 1, characterized in that' the inner circumferential surface of the core ring (5) on the entire circumference has a projection (5 b) which forms the desired sealing gap together with the core ring (2 c) of the pump blade ring, wherein the inner side edge of the core ring (2 c) facing the pump blades (2 d) has a curve shape which guides the leakage flow along the ring (2 c) radially outward.

5. Hydrodynamic torque converter according to claim 1, characterized in that the step-like extension (2 b) of the flow cross-section is formed on the hub of the pump impeller.

1 sheet of drawings