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WO2006002450A1 - Hydraulic system for controlling two clutches of a transmission - Google Patents

Hydraulic system for controlling two clutches of a transmission Download PDF

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Publication number
WO2006002450A1
WO2006002450A1 PCT/AT2005/000245 AT2005000245W WO2006002450A1 WO 2006002450 A1 WO2006002450 A1 WO 2006002450A1 AT 2005000245 W AT2005000245 W AT 2005000245W WO 2006002450 A1 WO2006002450 A1 WO 2006002450A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
check valve
hydraulic system
connection
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.)
Ceased
Application number
PCT/AT2005/000245
Other languages
German (de)
French (fr)
Inventor
Franz Gratzer
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.)
Magna Drivetrain AG and Co KG
Original Assignee
Magna Drivetrain AG and Co KG
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 Magna Drivetrain AG and Co KG filed Critical Magna Drivetrain AG and Co KG
Priority to DE112005000814.2T priority Critical patent/DE112005000814B4/en
Publication of WO2006002450A1 publication Critical patent/WO2006002450A1/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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D48/0206—Control by fluid pressure in a system with a plurality of fluid-actuated clutches
    • 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
    • F16H61/0021—Generation or control of line pressure
    • F16H61/0025—Supply of control fluid; Pumps therefor
    • 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
    • F16H61/68—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 specially adapted for stepped gearings
    • F16H61/684—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 specially adapted for stepped gearings without interruption of drive
    • F16H61/688—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 specially adapted for stepped gearings without interruption of drive with two inputs, e.g. selection of one of two torque-flow paths by clutches
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0224—Details of conduits, connectors or the adaptors therefor specially adapted for clutch control
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0227—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices
    • F16D2048/0233—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices by rotary pump actuation
    • F16D2048/0236—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices by rotary pump actuation with multiple independent pumps, e.g. one per clutch, or for supplying fluid to different systems
    • F16D2048/0242—Two or more rotating pumps driven together by the same power source, e.g. connected by a shaft, or a single pump having two or more fluid outputs
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
    • F16D2048/0263—Passive valves between pressure source and actuating cylinder, e.g. check valves or throttle valves
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
    • F16D2048/0266—Actively controlled valves between pressure source and actuation cylinder
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
    • F16D2048/0281—Complex circuits with more than two valves in series or special arrangements thereof not provided for in previous groups
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/30—Signal inputs
    • F16D2500/302—Signal inputs from the actuator
    • F16D2500/3024—Pressure

Definitions

  • the invention relates to a hydraulic system for the control of two clutches of a transmission, wherein each of the two clutches has a Neh ⁇ merzylinder, and the hydraulic fluid from a controllable Pumpen ⁇ unit from a reservoir via a first pressure line of the first clutch and a second Pressure line of the second clutches is provided. It is intended to: dual-clutch transmission, Lastschaltge ⁇ transmission, gearbox for adjustable distribution of a drive force on two half-waves of an axle or for distributing a drive force on two ange ⁇ exaggerated axles and transfer case, possibly even with a switchable off-road gear.
  • the reversibility of the pump unit that is to say the reversal of the conveying direction, is used here to supply the pressure oil to one or the other coupling. This is made possible by the arrangement of the four non-return valves. This not only saves a whole pump with its drive, but also inherent security against the engagement of both clutches achieved.
  • the pump unit consists of a reversible displacement pump and a reversible electric motor.
  • the displacement pump has a rotating displacer, so that the conveying direction depends on the direction of rotation of the displacer. It can be, for example, a gear pump or a so-called gerotor pump.
  • the control of the pump unit then takes place only by regulation or shaping of the current which is supplied to the pump driving the electric motor, and thus over all four quadrants of the characteristic field.
  • the first pressure line has a fifth
  • a first quick-release valve is provided in the first pressure line and a second quick-release valve in the second pressure line, which immediately opens automatically when falling below a certain pressure in the respective pressure line, so that no controlled valve is required for this.
  • a safety valve can be arranged between the double-acting check valve and the pressure gauge, which opens when a fault occurs. Such a fault may be about a breakdown of the supply voltage.
  • the slave cylinder of the first clutch is denoted by 1, the second to 2.
  • the clutches themselves are not darge; they may be friction clutches of any type, with one or more wet or dry running wheels.
  • the pistons 3,4 generate the pressure with which the clutch discs are pressed against each other, this pressure is approximately proportional to the transmitted torque.
  • the pump unit 3 consists of a rotary displacement pump 4 and a forward and backward speed adjustable electric motor 5. Both are usually combined to form a closed unit with a speed sensor 6.
  • the pump 4 has a first port 7 and a second port 8, both of which are in communication with the displacement chamber in the interior of the pump branches, which branch into T-pieces 9.10.
  • a branch leads from the branch 9 via a first check valve 13 to the reservoir 17, which could also be an oil sump;
  • the other branch leads via a second check valve 14 and a first pressure line 21 to the first slave cylinder 1.
  • one branch leads to the reservoir 17 via a third check valve 15, and the other branch leads via a fourth check valve 16 and a second pressure line 21 to the second slave cylinder. 2
  • the check valves (first 13 and third 15) close when they find themselves on the pressure side of the pump. Open the check valves (second 14 and fourth 16) when they are on the pressure side of the pump. Since the pressure on the pressure side and the suction side change when the pump is reversed, the rotation of the pump without further intervention also unambiguously determines which of the two slave cylinders 1, 2 is acted upon. By controlling the rotational speed of the pump, the torque to be transmitted by the respective clutch is determined.
  • a quick release valve 23,24 vor ⁇ seen which opens automatically at a certain pressure in the pressure lines 21,22 and so, as in a arranged between two axes transfer case in the case of ABS braking, fast uncoupled.
  • the quick-release valve 23,24 shown only schematically may be of any type.
  • a single pressure sensor 25 is provided, which, thanks to the two check valves 26, 27 provided in the branch lines 23, 24, measures the pressure prevailing in the respectively pressurized pressure line. It sends via a line 29 a pressure signal to a control unit 30. This elaborates from the pressure signal of 29, optionally from the Drehieresig ⁇ signal from the speed sensor 6 and from the vor ⁇ given by a transmission control setpoint signal the control signal for the electric motor 5, of course Interposition of a corresponding power electronics.
  • a safety valve 31 is provided, which is connected between the double-acting check valve 26/27 and the manometer 25. It is supplied with power by the control unit 30, which keeps it closed. If, for example, the voltage breaks down, the safety valve 31 opens and the system becomes depressurized, so that both actuators 1, 2 open their respective clutches.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

Disclosed is a hydraulic system for controlling two clutches comprising one respective slave cylinder (1, 2), each of which is supplied with hydraulic oil by a controllable pump unit (3) via a first pressure conduit (21) and a second pressure conduit (22). The aim of the invention is to make said hydraulic system simple, inexpensive, compact, and intrinsically safe. Said aim is achieved by providing said hydraulic system with a single reversible pump unit (3) in which one or the other connection (7, 8) of the pump (4) is used as a suction connection while the other or the one connection (8, 7) is used as a delivery connection according to the conveying direction of the pump (4). The connections (7, 8) are joined to the reservoir (17) via check valves (3, 15) which close when the pressure is positive while being joined to the respective pressure conduit (21, 22) thereof via second check valves (14, 16) that open when the pressure is positive.

Description

HYDRAULIKSYSTEM FÜR DIE STEUERUNG ZWEIER KUPPLUNGEN EINES GETRIEBES HYDRAULIC SYSTEM FOR CONTROLLING TWO COUPLINGS OF A GEARBOX

Die Erfindung betrifft ein Hydrauliksystem für die Steuerung zweier Kupp¬ lungen eines Getriebes, wobei jede der beiden Kupplungen über einen Neh¬ merzylinder verfugt, und das Hydraulikfluid von einer steuerbaren Pumpen¬ einheit aus einem Reservoir über eine erste Druckleitung der ersten Kupplung und über eine zweite Druckleitung der zweiten Kupplungen zur Verfügung gestellt wird. Dabei ist gedacht an: Doppelkupplungsgetriebe, Lastschaltge¬ triebe, Getriebe zur einstellbaren Verteilung einer Antriebkraft auf zwei Halbwellen einer Achse oder zur Verteilung einer Antriebkraft auf zwei ange¬ triebene Achsen und Verteilergetriebe, gegebenenfalls noch zusätzlich mit einer schaltbaren Geländegangstufe.The invention relates to a hydraulic system for the control of two clutches of a transmission, wherein each of the two clutches has a Neh¬ merzylinder, and the hydraulic fluid from a controllable Pumpen¬ unit from a reservoir via a first pressure line of the first clutch and a second Pressure line of the second clutches is provided. It is intended to: dual-clutch transmission, Lastschaltge¬ transmission, gearbox for adjustable distribution of a drive force on two half-waves of an axle or for distributing a drive force on two ange¬ exaggerated axles and transfer case, possibly even with a switchable off-road gear.

Bei derartigen Getrieben wird üblicherweise eine starr angetriebene Pumpe eingesetzt und die Steuerung erfolgt über eine Anzahl Steuerventile. Anzahl und Schaltung der Steuerventile bedingen aus Gründen der Betriebssicherheit und Stellgenauigkeit einen erheblichen Aufwand. Es muss sichergestellt sein, dass nie beide Kupplungen gleichzeitig eingerückt sind, dass die Kupplungen (oder zumindest eine) bei Wegfall des Öldruckes öffhen(t), die Kupplungen müssen für Fahrzeuge mit ABS (elektronisch beeinflusster Bremseneingriff) auch sehr schnell ausrückbar sein. Aus der EP 1 236 918 Al ist ein Hydrauliksystem für die Betätigung zweier Kupplungen bekannt, bei dem zwei immer in derselben Richtung fördernde Pumpen vorhanden sind, eine für jede einzelne Kupplung, wobei die Einrück¬ kraft der Kupplung und damit das übertragene Drehmoment durch Änderung der Drehzahl des Antriebsmotors eingestellt wird. Dadurch sind zwar Steuer¬ ventile weitgehend überflüssig, aber es ist nicht zwangsläufig sichergestellt, dass immer nur eine der Kupplungen geschlossen ist. Der Aufwand für zwei Hydraulikpumpen und der Raumbedarf sind dabei erheblich.In such transmissions usually a rigidly driven pump is used and the control is carried out via a number of control valves. Number and circuit of the control valves require for reasons of reliability and positioning accuracy a considerable effort. It must be ensured that never both clutches are engaged simultaneously, that the clutches (or at least one) open when the oil pressure drops (t), the clutches must be disengaged for vehicles with ABS (electronically influenced brake intervention) very quickly. From EP 1 236 918 A1, a hydraulic system for the actuation of two clutches is known, in which two pumps always conveying in the same direction are present, one for each individual clutch, wherein the engagement force of the clutch and thus the torque transmitted by changing the Speed of the drive motor is set. Although this tax are largely unnecessary, but it is not necessarily ensured that only one of the clutches is closed. The cost of two hydraulic pumps and the space required are significant.

Es ist daher Ziel der Erfindung, ein einfaches, billiges, raumsparendes und ab¬ solut eigensicheres Hydrauliksystem für die Ansteuerung von zwei Kupplun¬ gen zu schaffen. Erfindungsgemäß wird das durch die kennzeichnenden Merkmale des ersten Anspruches erreicht. Die Umsteuerbarkeit der Pumpen¬ einheit, das heisst die Umkehr der Förderrichtung wird hier genutzt, um das Drucköl der einen oder anderen Kupplung zu liefern. Das wird durch die An¬ ordnung der vier Rückschlagventile möglich. Dadurch wird nicht nur eine ganze Pumpe mit ihrem Antrieb eingespart, sondern auch inhärente Sicherheit gegen das Einrücken von beiden Kupplungen erzielt.It is therefore an object of the invention to provide a simple, inexpensive, space-saving and absolutely intrinsically safe hydraulic system for the actuation of two clutches. According to the invention this is achieved by the characterizing features of the first claim. The reversibility of the pump unit, that is to say the reversal of the conveying direction, is used here to supply the pressure oil to one or the other coupling. This is made possible by the arrangement of the four non-return valves. This not only saves a whole pump with its drive, but also inherent security against the engagement of both clutches achieved.

Vorzugsweise besteht die Pumpeneinheit aus einer umkehrbaren Verdrän¬ gungspumpe und einem umsteuerbaren Elektromotor. Die Verdrängungspum¬ pe hat einen rotierenden Verdränger, sodass die Förderrichtung vom Drehsinn des Verdrängers abhängt. Sie kann zum Beispiel eine Zahnradpumpe oder eine sogenannte Gerotorpumpe sein. Die Steuerung der Pumpeneinheit erfolgt dann nur durch Regelung beziehungsweise Formung des Stromes, der dem die Pumpe treibenden Elektromotor zugeführt wird, und somit über alle vier Quadranten des Kennfeldes. In Weiterbildung der Erfindung steht die erste Druckleitung über ein fünftesPreferably, the pump unit consists of a reversible displacement pump and a reversible electric motor. The displacement pump has a rotating displacer, so that the conveying direction depends on the direction of rotation of the displacer. It can be, for example, a gear pump or a so-called gerotor pump. The control of the pump unit then takes place only by regulation or shaping of the current which is supplied to the pump driving the electric motor, and thus over all four quadrants of the characteristic field. In a further development of the invention, the first pressure line has a fifth

Rückschlagventil und die zweite Druckleitung über ein sechstes Rückschlag¬ ventil mit einem Manometer in Verbindung, die einer die Pumpeneinheit ver¬ stellenden Steuereinheit ein Drucksignal liefert. Somit wird auch nur ein ein¬ ziges Manometer benötigt und die Steuereinheit braucht den vorgegebenen Sollwert nur mit einem einzigen Regelsignal zu vergleichen. Eine weitere Vereinfachung wird dadurch erzielt, dass das fünfte und das sechste Rück¬ schlagventil zu einem doppeltwirkenden Rückschlagventil zusammengefasst sind.Check valve and the second pressure line via a sixth Rückschlag¬ valve with a pressure gauge in combination, which provides a pressure signal to a control unit ver¬ the control unit. Thus, only a single pressure gauge is needed and the control unit only needs to compare the given setpoint value with a single control signal. A further simplification is achieved in that the fifth and the sixth Rück¬ check valve are combined to form a double-acting check valve.

In Weiterverfolgung des Erfindungsgedankens ist in der ersten Druckleitung ein erstes Schnellablassventil und in der zweiten Druckleitung ein zweites Schnellablassventil vorgesehen, das bei Unterschreiten eines bestimmten Dru¬ ckes in der jeweiligen Druckleitung sofort von selbst öffnet, sodass auch dafür kein gesteuertes Ventil benötigt wird. Weiters kann zwischen dem doppelt- wirkenden Rückschlagventil und dem Manometer ein Sicherheitsventil ange¬ ordnet sein, das bei Auftreten einer Störung öffnet. Eine solche Störung kann etwa ein Zusammenbrechen der Versorgungsspannung sein. Durch Anspre¬ chen des Sicherheitsventiles werden die Druckleitungen drucklos und die Kupplungen öffnen.In a further pursuit of the inventive concept, a first quick-release valve is provided in the first pressure line and a second quick-release valve in the second pressure line, which immediately opens automatically when falling below a certain pressure in the respective pressure line, so that no controlled valve is required for this. Furthermore, a safety valve can be arranged between the double-acting check valve and the pressure gauge, which opens when a fault occurs. Such a fault may be about a breakdown of the supply voltage. By addressing the safety valve, the pressure lines are depressurized and the couplings open.

Im Folgenden wird die Erfindung anhand einer schematischen Abbildung be¬ schrieben und erläutert. Der Nehmerzylinder der ersten Kupplung ist mit 1 bezeichnet, der der zweiten mit 2. Die Kupplungen selbst sind nicht darge¬ stellt; sie können Reibungskupplungen beliebiger Bauart sein, mit einer oder mehreren nass oder trocken laufenden Scheiben. Die Kolben 3,4 erzeugen den Druck, mit dem die Kupplungsscheiben aneinandergepresst werden, diesem Druck ist das übertragene Drehmoment ungefähr proportional. Die Pumpeneinheit 3 besteht aus einer rotierenden Verdrängungspumpe 4 und einem vorwärts und rückwärts drehzahlregelbarem Elektromotor 5. Beide sind in der Regel zu einer geschlossenen Baueinheit mit einem Drehzahlsensor 6 zusammengefasst. Die Pumpe 4 hat einen ersten Anschluss 7 und einen zwei¬ ten Anschluss 8, beide sind mit dem Verdrängungsraum im Inneren der Pum- pe in Verbindung stehende Leitungen, die sich in T-Stücken 9,10 verzweigen. Ein Zweig führt von der Verzweigung 9 über ein erstes Rückschlagventil 13 zum Reservoir 17, das auch ein Ölsumpf sein könnte; der andere Zweig führt über ein zweites Rückschlagventil 14 und eine erste Druckleitung 21 zum ers¬ ten Nehmerzylinder 1. Ebenso führt von der Verzweigung 10 der eine Zweig über ein drittes Rückschlagventil 15 zum Reservoir 17, und der andere Zweig führt über ein viertes Rückschlagventil 16 und eine zweite Druckleitung 21 zum zweiten Nehmerzylinder 2.In the following, the invention will be described and explained with reference to a schematic illustration. The slave cylinder of the first clutch is denoted by 1, the second to 2. The clutches themselves are not darge; they may be friction clutches of any type, with one or more wet or dry running wheels. The pistons 3,4 generate the pressure with which the clutch discs are pressed against each other, this pressure is approximately proportional to the transmitted torque. The pump unit 3 consists of a rotary displacement pump 4 and a forward and backward speed adjustable electric motor 5. Both are usually combined to form a closed unit with a speed sensor 6. The pump 4 has a first port 7 and a second port 8, both of which are in communication with the displacement chamber in the interior of the pump branches, which branch into T-pieces 9.10. A branch leads from the branch 9 via a first check valve 13 to the reservoir 17, which could also be an oil sump; The other branch leads via a second check valve 14 and a first pressure line 21 to the first slave cylinder 1. Likewise, from the branch 10, one branch leads to the reservoir 17 via a third check valve 15, and the other branch leads via a fourth check valve 16 and a second pressure line 21 to the second slave cylinder. 2

Die Rückschlagventile (erstes 13 und drittes 15) schließen, wenn sie sich an der Druckseite der Pumpe finden. Die Rückschlagventile (zweites 14 und vier¬ tes 16) öffnen, wenn sie an der Druckseite der Pumpe sind. Da beim Umsteu¬ ern der Pumpe Druckseite und Saugseite Platz tauschen, wird mit dem Dreh¬ sinn der Pumpe ohne weitere Eingriffe auch eindeutig bestimmt, welcher der beiden Nehmerzylinder 1,2 beaufschlagt wird. Durch Steuerung der Drehzahl der Pumpe wird das von der jeweiligen Kupplung zu übertragende Drehmo¬ ment bestimmt.The check valves (first 13 and third 15) close when they find themselves on the pressure side of the pump. Open the check valves (second 14 and fourth 16) when they are on the pressure side of the pump. Since the pressure on the pressure side and the suction side change when the pump is reversed, the rotation of the pump without further intervention also unambiguously determines which of the two slave cylinders 1, 2 is acted upon. By controlling the rotational speed of the pump, the torque to be transmitted by the respective clutch is determined.

In jeder der beiden Druckleitungen 21,22 ist ein Schnellablassventil 23,24 vor¬ gesehen, das bei einem bestimmten Druck in den Druckleitungen 21,22 selbsttätig öffnet und so, etwa bei einem zwischen zwei Achsen angeordneten Verteilergetriebe im Falle einer ABS - Bremsung, schnell entkuppelt. Das nur schematisch gezeigte Schnellablassventil 23,24 kann von beliebiger Bauart sein. Weiters ist nur ein einziger Dracksensor 25 vorgesehen, der dank der beiden in den Zweigleitungen 23,24 vorgesehenen Rückschlagventile 26,27 den in der jeweils unter Druck stehenden Druckleitung herrschenden Druck misst. Er sendet über eine Leitung 29 ein Drucksignal zu einer Steuereinheit 30. Diese erarbeitet aus dem Drucksignal von 29, gegebenenfalls aus dem Drehzahlsig¬ nal von dem Drehzahlsensor 6 und aus dem von einer Getriebesteuerung vor¬ gegeben Sollsignal das Stellsignal für den Elektromotor 5, natürlich unter Zwischenschaltung einer entsprechenden Leistungselektronik.In each of the two pressure lines 21,22 a quick release valve 23,24 vor¬ seen, which opens automatically at a certain pressure in the pressure lines 21,22 and so, as in a arranged between two axes transfer case in the case of ABS braking, fast uncoupled. The quick-release valve 23,24 shown only schematically may be of any type. Furthermore, only a single pressure sensor 25 is provided, which, thanks to the two check valves 26, 27 provided in the branch lines 23, 24, measures the pressure prevailing in the respectively pressurized pressure line. It sends via a line 29 a pressure signal to a control unit 30. This elaborates from the pressure signal of 29, optionally from the Drehzahlsig¬ signal from the speed sensor 6 and from the vor¬ given by a transmission control setpoint signal the control signal for the electric motor 5, of course Interposition of a corresponding power electronics.

Weiters ist noch ein Sicherheitsventil 31 vorgesehen, das zwischen dem dop¬ peltwirkenden Rückschlagventil 26/27 und dem Manometer 25 angeschlossen ist. Es wird von der Steuereinheit 30 aus mit Strom versorgt, der es geschlos¬ sen hält. Wenn zum Beispiel die Spannung zusammenbricht, öffnet das Si¬ cherheitsventil 31 und das System wird drucklos, sodass beide Aktuatoren 1 ,2 ihre respektiven Kupplungen öffnen. Furthermore, a safety valve 31 is provided, which is connected between the double-acting check valve 26/27 and the manometer 25. It is supplied with power by the control unit 30, which keeps it closed. If, for example, the voltage breaks down, the safety valve 31 opens and the system becomes depressurized, so that both actuators 1, 2 open their respective clutches.

Claims

P a t e n t a n s p r ü c h e Patent claims 1. Hydrauliksystem für die Steuerung zweier Kupplungen eines Getriebes, wobei jede der beiden Kupplungen über einen Nehmerzylinder (1,2) verfugt, und das Hydraulikfluid von einer steuerbaren Pumpeneinheit (3) aus einem Reservoir (17) über eine erste Druckleitung (21) dem ersten Nehmerzylinder (1) und über eine zweite Druckleitung (22) den zweiten Nehmerzylinder (2) zur Verfügung gestellt wird, dadurch gekennzeichnet, dass1. Hydraulic system for controlling two clutches of a transmission, each of the two clutches via a slave cylinder (1,2) grooved, and the hydraulic fluid from a controllable pump unit (3) from a reservoir (17) via a first pressure line (21) first slave cylinder (1) and via a second pressure line (22) the second slave cylinder (2) is provided, characterized in that a) eine einzige umsteuerbare Pumpeneinheit (3) mit einem ersten und einem zweiten Anschluss vorgesehen ist, wobei je nach Förderrichtung der Pumpe (4) entweder der eine oder andere Anschluss (7,8) Sauganschluss und ent¬ weder der andere oder der eine Anschluss (8,7) Drackanschluss ist,a) a single reversible pump unit (3) is provided with a first and a second connection, wherein depending on the conveying direction of the pump (4) either one or the other port (7,8) suction port and ent¬ neither the other or the one port (8,7) Drack connection is, b) der erste Anschluss (7) über ein erstes bei positivem Druck schließendes Rückschlagventil (13) mit dem Reservoir (17) und über ein zweites bei po¬ sitivem Druck öffnendes Rückschlagventil (14) mit einer ersten Drucklei¬ tung (21) in Verbindung steht,b) the first connection (7) via a first positive pressure closing check valve (13) with the reservoir (17) and via a second at positive pressure opening check valve (14) with a first Drucklei¬ device (21) in connection stands, c) der zweite Anschluss(8) über ein drittes bei positivem Druck schließendes Rückschlagventil (15) mit dem Reservoir (17) und über ein viertes bei posi¬ tivem Druck öffnendes Rückschlagventil (16) mit einer zweiten Drucklei¬ tung (22) in Verbindung steht.c) the second connection (8) via a third positive pressure closing check valve (15) with the reservoir (17) and a fourth at positive tivem pressure opening check valve (16) with a second Drucklei¬ device (22) in connection stands. 2. Hydrauliksystem nach Anspruch 1, dadurch gekennzeichnet, dass die Pumpeneinheit (3) aus einer umkehrbaren Verdrängungspumpe(4) und einem umsteuerbaren Elektromotor (5) besteht. 2. Hydraulic system according to claim 1, characterized in that the pump unit (3) consists of a reversible displacement pump (4) and a reversible electric motor (5). 3. Hydrauliksystem nach Anspruch 1, dadurch gekennzeichnet, dass die erste Druckleitung (21) über ein fünftes Rückschlagventil (26) und die zweite Druckleitung (22) über ein sechstes Rückschlagventil (27) mit einem Mano¬ meter (25) in Verbindung steht, die einer die Pumpeneinheit (3) verstellenden Steuereinheit (30) ein Drucksignal liefert.3. Hydraulic system according to claim 1, characterized in that the first pressure line (21) via a fifth check valve (26) and the second pressure line (22) via a sixth check valve (27) with a Mano¬ meter (25) is in communication, the one of the pump unit (3) adjusting control unit (30) delivers a pressure signal. 4. Hydrauliksystem nach Anspruch 3, dadurch gekennzeichnet, dass das fünfte (26) und das sechste Rückschlagventil (27) zu einem doppeltwirkenden Rückschlagventil (26/27) zusammengefasst sind.4. Hydraulic system according to claim 3, characterized in that the fifth (26) and the sixth check valve (27) are combined to form a double-acting check valve (26/27). 5. Hydrauliksystem nach Anspruch 1, dadurch gekennzeichnet, dass in der ersten Druckleitung (21) ein erstes Schnellablassventil (23) und in der zweiten Druckleitung (22) ein zweites Schnellablassventil (24) vorgesehen ist.5. A hydraulic system according to claim 1, characterized in that in the first pressure line (21) a first quick-release valve (23) and in the second pressure line (22), a second quick-release valve (24) is provided. 6. Hydrauliksystem nach Anspruch 4, dadurch gekennzeichnet, dass zwi¬ schen dem doppeltwirkenden Rückschlagventil (26/27) und dem Manometer (25) ein Sicherheitsventil (31) angeordnet ist, das bei Auftreten einer Störung öffnet. 6. Hydraulic system according to claim 4, characterized in that between the double-acting check valve (26/27) and the pressure gauge (25) a safety valve (31) is arranged, which opens when a fault occurs.
PCT/AT2005/000245 2004-06-30 2005-06-30 Hydraulic system for controlling two clutches of a transmission Ceased WO2006002450A1 (en)

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ATGM456/2004 2004-06-30

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