DE3727633A1 - Cone pulley transmission with controlled quantity of pressure medium - Google Patents

Cone pulley transmission with controlled quantity of pressure medium

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Publication number
DE3727633A1
DE3727633A1 DE19873727633 DE3727633A DE3727633A1 DE 3727633 A1 DE3727633 A1 DE 3727633A1 DE 19873727633 DE19873727633 DE 19873727633 DE 3727633 A DE3727633 A DE 3727633A DE 3727633 A1 DE3727633 A1 DE 3727633A1
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Germany
Prior art keywords
pressure medium
belt transmission
pulley belt
conical pulley
transmission according
Prior art date
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Granted
Application number
DE19873727633
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German (de)
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DE3727633C2 (en
Inventor
Manfred Rattunde
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Individual
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Individual
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Priority to DE19873727633 priority Critical patent/DE3727633A1/en
Publication of DE3727633A1 publication Critical patent/DE3727633A1/en
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Publication of DE3727633C2 publication Critical patent/DE3727633C2/de
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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
    • F16H61/66—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 continuously variable gearings
    • F16H61/662—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 continuously variable gearings with endless flexible members
    • F16H61/66272—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 continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing
    • 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
    • F16H61/66—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 continuously variable gearings
    • F16H61/662—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 continuously variable gearings with endless flexible members
    • F16H2061/66286—Control for optimising pump efficiency
    • 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
    • F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Transmission Device (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

The invention relates to an infinitely adjustable cone pulley transmission, to which pressure medium is fed by one or more pumps by way of a hydraulic control unit in order to adjust the transmission ratio. These transmissions are generally driven by an internal combustion engine at rotational speeds of between 1000 ... 6000 min<-1>, resulting in a quantity of pressure medium proportional to the speed, which quantity is not sufficient for the functioning of the cone pulley transmission under widely varying operating conditions and considerably impairs the overall efficiency. By means of the invention, the quantity of pressure medium is controlled as required by means of sensors, an electronic processing unit and a solenoid valve according to the instantaneous operating states (engine speed, accelerator pedal position, etc).

Description

Die Erfindung bezieht sich auf ein Kegelscheibenumschlingungs­ getriebe gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a conical pulley belt Gearbox according to the preamble of claim 1.

Getriebe dieser Gattung sind heute allgemein unter dem Begriff Continuously Variable Transmission (CVT) bekannt und deren Pumpe wird in der Regel von dem Verbrennungsmotor drehzahlproportional angetrieben. Da die Druckmittelmenge bei niedrigen Drehzahlen für die Pumpengröße maßgebend ist, entsteht bei höheren Drehzahlen eine unnötige hohe Druckmittelmenge, die den Gesamtwirkungsgrad eines solchen Getriebes erheblich verschlechtert. Außerdem wer­ den bei zu hohen Druckmittelmengen infolge innerer Drosselwider­ stände die Anpreßkräfte zwischen Kegelreibscheiben und Umschlin­ gungsmittel sowie die Lagerkräfte unnötig hoch.Gearboxes of this type are generally known today Continuously known Variable Transmission (CVT) and its pump is usually proportional to the speed of the internal combustion engine driven. Since the pressure medium quantity at low speeds for the pump size is decisive, arises at higher speeds an unnecessarily high amount of pressure medium, the total efficiency of such a transmission deteriorated significantly. Besides, who the resistance to excessive amounts of pressure medium due to internal throttle the contact forces between the conical friction disks and Umschlin means as well as the storage forces unnecessarily high.

Es sind Lösungen bekannt, die die Druckmittelmenge über der Mo­ tordrehzahl annähernd konstant halten, z.B. Flügelzellenpumpe mit schwenkbarem Innengehäuse, wobei die Druckmittelmenge, also die Exzentrizität, nur von der Motordrehzahl bestimmt wird, oder 2 Zahnradpumpen, wobei die Überschußmenge bei hohen Drehzahlen über einen Bypaß abgeleitet wird.Solutions are known that the amount of pressure medium over the Mo Keep the door speed approximately constant, e.g. Vane pump with pivotable inner housing, the amount of pressure medium, ie the Eccentricity, determined only by engine speed, or 2 Gear pumps, the excess amount at high speeds over a bypass is derived.

Diese Lösungen genügen jedoch dem erforderlichen funktionellen Verhalten eines Kegelscheibenumschlingungsgetriebes bei den un­ terschiedlichsten Betriebsbedingungen nur sehr unvollkommen. Bei erhöhtem Druckbedarf, der bei erhöhtem zu übertragenden Drehmoment erforderlich ist, ferner bei sehr heißem Öl, reicht die Druckmit­ telmenge wegen der Leckverluste an den Öleinführungen und Zylinder­ dichtungen oft nicht aus, das Getriebe schnell genug zu verstellen bzw. die Anpreßkraft zwischen Kegelscheiben und Umschlingungs­ mittel erreicht nicht die erforderliche Höhe, d.h. Rutschen des Umschlingungsmittels führt zu Schäden und kann das Getriebe zer­ stören. Auch energetisch haben die bekannten Lösungen den Mangel, daß die hydraulische Leistung unnötig hoch ist, um das funktionel­ le Verhalten sicherzustellen.However, these solutions meet the functional requirements Behavior of a conical pulley belt transmission at the un very different imperfect operating conditions. At increased pressure requirement, the increased torque to be transmitted necessary, furthermore with very hot oil, the pressure is sufficient volume due to the leakage losses at the oil inlets and cylinders seals often fail to adjust the gearbox quickly enough  or the contact pressure between the conical pulley and the belt medium does not reach the required height, i.e. Sliding of the Belt means damage and can break the transmission to disturb. The known solutions are also lacking energetically, that the hydraulic power is unnecessarily high to make it functional ensure le behavior.

Es ist Aufgabe der Erfindung, ein Kegelscheibenumschlingungsge­ triebe gemäß dem Oberbegriff des Patentanspruchs 1 zu schaffen, bei dem die Druckmittelmenge entsprechend den jeweiligen Betriebs­ bedingungen optimal geregelt wird.It is an object of the invention to provide a conical pulley belt to create drives according to the preamble of claim 1, in which the pressure medium amount according to the respective operation conditions is optimally regulated.

Die Lösung dieser Aufgabe ergibt sich gemäß dem kennzeichnenden Teil des Patentanspruchs 1.The solution to this problem arises according to the characteristic Part of claim 1.

Dadurch, daß der jeweilige Betriebszustand mittels Sensoren lau­ fend erfaßt und der elektronischen Recheneinheit mitgeteilt wird, wie Motordrehzahl, Fahrpedalstellung, Antriebsdrehzahl, Tempera­ tur usw., bewirkt die Stellgröße für das Magnetventil eine den jeweiligen Erfordernissen entsprechende Druckmittelmenge.Because the respective operating state is lukewarm by means of sensors fend recorded and communicated to the electronic computing unit, such as engine speed, accelerator pedal position, drive speed, tempera tur etc., the manipulated variable for the solenoid valve causes a corresponding amount of pressure medium to the respective requirements.

Zweckmäßige Ausgestaltungen der Erfindung werden in den folgenden Ausführungsbeispielen dargestellt und näher erläutert.Advantageous embodiments of the invention are described in the following Exemplary embodiments shown and explained in more detail.

Fig. 1 zeigt ein Blockschaltbild des erfindungsgemäßen Kegel­ scheibenumschlingungsgetriebes mit einer Einrichtung für die Regelung einer bedarfsgerechten Druckmittelmenge. Fig. 1 shows a block diagram of the cone pulley belt transmission according to the invention with a device for controlling a need-based amount of pressure medium.

Fig. 2 zeigt ein Beispiel eines Volumen-Drehzahl-Diagramms, in dessen schraffierter Fläche sich die jeweils bedarfsge­ rechte, geregelte Druckmittelmenge einstellen läßt. Fig. 2 shows an example of a volume-speed diagram, in the hatched area, the respective right, regulated pressure medium amount can be set.

Fig. 3 zeigt ein Volumen-Fahrpedalstellung-Diagramm. Fig. 3 is a volume accelerator pedal position-diagram.

Fig. 4 zeigt ein Diagramm des Volumens in Abhängigkeit von der Änderungszeit der Fahrpedalstellung. FIG. 4 shows a diagram of the volume as a function of the change time of the accelerator pedal position.

Fig. 5 zeigt die Volumenabhängigkeit von der jeweiligen Über­ setzung des stufenlosen Getriebes. Fig. 5 shows the volume dependence on the respective translation of the continuously variable transmission.

Fig. 6 zeigt eine Ausführungsform des Förderstromregelventils Fig. 7 zeigt eine volumenregelbare Pumpe, z.B. Flügelzellen­ pumpe variabler Exzentrizität. Fig. 6 shows an embodiment of the flow control valve . Fig. 7 shows a volume-controllable pump, eg vane pump variable eccentricity.

Fig. 8 zeigt ein Volumen-Drehzahl-Diagramm der Pumpe nach Fig. 7. Es kann innerhalb der schraffierten Fläche der jeweils bedarfsgerechte Förderstrom geregelt werden. FIG. 8 shows a volume-speed diagram of the pump according to FIG. 7. It is possible to regulate the delivery flow in each case within the shaded area.

Weitere Einzelheiten des Erfindungsgegenstandes ergeben sich aus der nachfolgenden Beschreibung anhand der Zeichnungen. Das in Fig. 1 gezeichnete Kegelscheibenumschlingungsgetriebe mit den Zylinder-Kolben-Aggregaten 1 und 2 wird von der hydrau­ lischen Steuereinheit 3 mit Druckmittel versorgt, welches von den Pumpen 4 und 5 geliefert wird. Einer elektronischen Re­ cheneinheit 6 werden mittels Sensoren 7 laufend die momenta­ nen Betriebsgrößen wie Drehzahlen, Fahrpedalstellung, Pumpendruck usw. mitgeteilt. Hieraus errechnet die elektronische Rechenein­ heit laufend den erforderlichen Sollwert der Druckmittelmenge. Ferner übermittelt ein Mengenmesser 8 den Istwert der Druck­ mittelmenge V an die elektronische Recheneinheit. Aus dem Soll- Istwert-Vergleich ermittelt die elektronische Recheneinheit eine Regelgröße, die über ein Magnetventil 9 die überschüssige Druck­ mittelmenge der Pumpe 4 mehr oder weniger in die gemeinsame Saugleitung 10 zurückfließen läßt. Die Druckmittelmenge der Pumpe 5 fließt hierbei immer voll in die hydraulische Steuer­ einheit 3 was durch ein Rückschlagventil 11 gesichert ist. Der Mengenmesser 8 kann entfallen, wenn die Druckmittelmenge indirekt erfaßt wird, z.B. durch Verwendung eines hubgeregelten Magnetventils.Further details of the subject matter of the invention emerge from the following description with reference to the drawings. The drawn in Fig. 1 with the belt-driven conical cylinder-piston units 1 and 2 is powered by the hydrau intermetallic control unit 3 with pressure medium which is supplied from the pumps 4 and 5. An electronic Re computing unit 6 , the momentary NEN operating variables such as speeds, accelerator pedal position, pump pressure, etc. are continuously communicated by sensors 7 . From this, the electronic computing unit continuously calculates the required setpoint of the pressure medium quantity. Furthermore, a quantity meter 8 transmits the actual value of the pressure medium quantity V to the electronic computing unit. From the setpoint-actual value comparison, the electronic computing unit determines a controlled variable that allows the excess amount of pressure of the pump 4 to flow more or less back into the common suction line 10 via a solenoid valve 9 . The amount of pressure medium of the pump 5 always flows fully into the hydraulic control unit 3, which is secured by a check valve 11 . The flow meter 8 can be omitted if the amount of pressure medium is detected indirectly, for example by using a stroke-controlled solenoid valve.

Das beispielhafte Volumen-Drehzahl-Diagramm in Fig. 2 zeigt, daß mit der Einrichtung nach Fig. 1 abweichend von der drehzahlbe­ dingten Basismenge jede geregelte Druckmittelmenge innerhalb des schraffierten Feldes an die hydraulische Steuerung 3 geliefert werden kann.The exemplary volume-speed diagram in FIG. 2 shows that, with the device according to FIG. 1, any regulated pressure medium quantity within the hatched field can be supplied to the hydraulic control 3 in deviation from the speed-related basic quantity.

Die Fig. 3, 4 und 5 zeigen Diagramme, in denen die Abhängig­ keit der Druckmittelmenge V von den wichtigsten Einflußgrößen wie Fahrpedalstellung, Zeit der Änderung der Fahrpedalstellung und Getriebeübersetzung dargestellt ist. Dieser funktionelle Zusammenhang ist in der elektronischen Recheneinheit abgespeichert und dient zum Errechnen des jeweiligen Sollwerts der erforderli­ chen Druckmittelmenge mittels eines Programms. FIGS. 3, 4 and 5 show diagrams in which the dependency ness of the pressure medium quantity V from the main influencing parameters such as accelerator pedal position, time is shown the change in the accelerator pedal position and gear ratio. This functional relationship is stored in the electronic computing unit and is used to calculate the respective target value of the required amount of pressure medium by means of a program.

Das Fahrverhalten wird z.B. verbessert, wenn bei niedrigen Über­ setzungen ("kleine Gänge") eine schnellere Verstellung erfolgt als bei höheren Übersetzungen ("Overdrive"), d.h. größere Menge bei niedrigen Übersetzungen. Es ist ferner auf einfache Weise möglich, die Änderungszeit von einer Fahrpedalstellung zur anderen in das Programm aufzunehmen (Steigung zweier benachbarter Meß­ punkte).The driving behavior is e.g. improved when low over settings ("small gears") a quicker adjustment takes place than with higher translations ("overdrive"), i.e. bigger amount at low translations. It is also simple possible to change the time from one accelerator pedal position to another to be included in the program (slope of two neighboring measuring Points).

Nicht gezeichnet ist die Abhängigkeit der Druckmittelmenge von der Temperatur und vom Druck. Es versteht sich von selbst, daß bei höheren Temperaturen und/oder erhöhtem Druck des Druckmittels entsprechend höhere Leckagen auftreten, die durch eine erhöhte Druckmittelmenge per Programm kompensiert werden können.The dependence of the pressure medium quantity on is not shown the temperature and pressure. It goes without saying that at higher temperatures and / or increased pressure of the pressure medium accordingly higher leakages occur, which are caused by an increased Pressure medium quantity can be compensated by the program.

Fig. 6 zeigt eine Ausführungsform des in Fig. 1 erwähnten Magnet­ ventils 9 . Es wandelt den variablen Druck der Leitung 12 in Abhängigkeit von der Regelgröße 13 in einen geregelten Druck um, der in der Kammer 14 herrscht. Dadurch wird der Kolben 15 mehr oder weniger gegen die Feder 16 verschoben, und über die Öffnung 17 und Leitung 18 fließt die überschüssige Druckmit­ telmenge in die gemeinsame Saugleitung 10 zurück. Fig. 6 shows an embodiment of the solenoid valve 9 mentioned in Fig. 1st It converts the variable pressure of line 12 as a function of controlled variable 13 into a regulated pressure that prevails in chamber 14 . As a result, the piston 15 is displaced more or less against the spring 16 , and via the opening 17 and line 18 , the excess Druckmit tel quantity flows back into the common suction line 10 .

In Fig. 7 ist eine weitere Ausführungsform der Erfindung darge­ stellt. Bei einer Flügelzellenpumpe mit variabler Exzentrizität 19 ist bekanntlich der Förderstrom von Drehzahl und Exzentri­ zität abhängig. Das Magnetventil 20 , z.B. Proportionalventil mit Pulsweitenmodulation, wandelt den variablen Druck der Leitung 12 in Abhängigkeit der Regelgröße 13 in einen geregelten Druck um, der in der Kammer 14 wirkt. Dadurch wird die Exzen­ trizität der Flügelzellenpumpe geändert und damit auch die Druck­ mittelmenge. Diese Ausführung ist besonders günstig, da der Ist­ wert der Druckmittelmenge nicht gesondert erfaßt werden muß, sie kann von der elektronischen Recheneinheit selbst laufend aus Dreh­ zahl und Regelgröße, die ein Maß der Exzentrizität ist, per Pro­ gramm ermittelt werden. Ferner ist diese Ausführung auch energetisch besonders günstig, weil keine druckbehafteten Überschußmengen abfließen müssen.In Fig. 7 another embodiment of the invention is Darge. In a vane pump with variable eccentricity 19 , the flow rate is known to depend on speed and eccentricity. The solenoid valve 20 , for example a proportional valve with pulse width modulation, converts the variable pressure of the line 12 as a function of the controlled variable 13 into a regulated pressure which acts in the chamber 14 . This changes the eccentricity of the vane pump and thus the pressure medium quantity. This version is particularly cheap, since the actual value of the pressure medium quantity does not have to be recorded separately, it can be determined by the electronic computing unit itself from the speed and controlled variable, which is a measure of the eccentricity, per program. Furthermore, this design is also particularly economical in terms of energy because no excess amounts under pressure have to flow off.

Schließlich zeigt Fig. 8, daß mit dem Ausführungsbeispiel in Fig. 7 abweichend von der drehzahlbedingten Basismenge jede Druckmittelmenge innerhalb des schraffierten Feldes möglich ist.Finally, FIG. 8 shows that, with the exemplary embodiment in FIG. 7, any pressure medium quantity within the hatched field is possible, deviating from the speed-related basic quantity.

Zweckmäßigerweise sind die Stellorgane so konzipiert, daß bei Ausfall der elektronischen Recheneinheit der hydraulischen Steuereinheit des Kegelscheibenumschlingungsgetriebes immer die maximale Druckmittelmenge geliefert wird. Wird der Druck der Kammer 14 zu Null, so bewirkt die Feder 16 die maximale Druck­ mittelmenge sowohl bei 2 Zahnradpumpen nach Fig. 1 und 6 als auch bei der Flügelzellenpumpe nach Fig. 7.The actuators are expediently designed such that the maximum amount of pressure medium is always supplied in the event of failure of the electronic computing unit of the hydraulic control unit of the conical pulley belt transmission. If the pressure of the chamber 14 becomes zero, the spring 16 causes the maximum amount of pressure medium both with 2 gear pumps according to FIGS. 1 and 6 and with the vane pump according to FIG. 7.

Der Mehraufwand der erfindungsgemäßen Lösung ist sehr gering, da für die Regelung der Übersetzung des Kegelscheibenumschlingungs­ getriebes die wichtigsten Sensoren und eine elektronische Rechen­ einheit bereits vorhanden sind.The additional effort of the solution according to the invention is very low, as for the regulation of the translation of the conical pulley belt transmission the most important sensors and an electronic rake unit already exist.

Claims (7)

1. Stufenlos einstellbares Kegelscheibenumschlingungsgetriebe, bei dem die axial verschiebbaren Kegelscheiben zusammen mit einem wellenfesten Kolben je ein Zylinder-Kolben-Aggregat bilden, dem zur Einstellung und Aufrechterhaltung der Getrie­ beübersetzung von einer oder mehreren Pumpen bezogenes Druck­ mittel über eine hydraulische Steuereinheit zugeteilt wird, das von einem Motor größeren Drehzahlbereichs, insbesondere Verbrennungsmotor, angetrieben wird, dadurch gekennzeichnet, daß eine Einrichtung bestehend aus Sensoren (7), einer elek­ tronischen Recheneinheit (6) und einem Magnetventil (9) den Druckmittelmengenstrom bedarfsgerecht regelt.1.Finely adjustable conical pulley belt transmission, in which the axially displaceable conical pulleys together with a shaft-fixed piston each form a cylinder-piston unit, which is assigned to the setting and maintenance of the transmission ratio of one or more pumps via a hydraulic control unit, which is driven by a motor with a larger speed range, in particular an internal combustion engine, characterized in that a device consisting of sensors ( 7 ), an electronic computing unit ( 6 ) and a solenoid valve ( 9 ) regulates the pressure medium flow rate as required. 2. Kegelscheibenumschlingungsgetriebe nach Anspruch 1, dadurch gekennzeichnet, daß die Einrichtung Sensoren (7) enthält, die mindestens einen der folgenden Momentanwerte erfassen:
Motordrehzahl
Abtriebsdrehzahl
Fahrpedalstellung
Kick-down-Position
Pumpendruck
Temperatur des Druckmittels.2. Conical pulley belt transmission according to claim 1, characterized in that the device contains sensors ( 7 ) which detect at least one of the following instantaneous values:
Engine speed
Output speed
Accelerator pedal position
Kick down position
Pump pressure
Temperature of the pressure medium. 3. Kegelscheibenumschlingungsgetriebe nach Anspruch 1 und 2, dadurch gekennzeichnet, daß die Einrichtung die Druckmittel­ menge von 2 Zahnradpumpen (4) und (5) regelt, wobei die 2 Zahnradpumpen von derselben oder von verschiedenen Wellen an­ getrieben sein können. 3. Conical pulley belt transmission according to claim 1 and 2, characterized in that the device controls the pressure medium amount of 2 gear pumps ( 4 ) and ( 5 ), wherein the 2 gear pumps can be driven by the same or by different shafts. 4. Kegelscheibenumschlingungsgetriebe nach Anspruch 1 und 2, dadurch gekennzeichnet, daß die Einrichtung das Volumen je Umdrehung einer verstellbaren Flügelzellenpumpe (19) regelt.4. Conical pulley belt transmission according to claim 1 and 2, characterized in that the device controls the volume per revolution of an adjustable vane pump ( 19 ). 5. Kegelscheibenumschlingungsgetriebe nach Anspruch 1 bis 4, dadurch gekennzeichnet, daß bei Ausfall der elektronischen Recheneinheit (6) der hydraulischen Steuereinheit (3) mittels Feder (16) immer die maximale Druckmittelmenge geliefert wird.5. Conical pulley belt transmission according to claim 1 to 4, characterized in that in the event of failure of the electronic computing unit ( 6 ) of the hydraulic control unit ( 3 ) by means of spring ( 16 ) the maximum amount of pressure medium is always supplied. 6. Kegelscheibenumschlingungsgetriebe nach Anspruch 1 bis 5, dadurch gekennzeichnet, daß die Einrichtung eine drehzahlab­ hängige Basis-Druckmittelmenge sicherstellt (Fig. 2 und Fig. 8).6. Conical pulley belt transmission according to claim 1 to 5, characterized in that the device ensures a speed-dependent basic pressure medium quantity ( Fig. 2 and Fig. 8). 7. Kegelscheibenumschlingungsgetriebe nach Anspruch 1 bis 6, da­ durch gekennzeichnet, daß die Einrichtung ausgehend von der Basis-Druckmittelmenge eine Erhöhung der Druckmittelmenge bei wenigstens einer der folgenden momentanen Betriebsgrößen bewirkt:
Erhöhung der Fahrpedalstellung (Fig. 3)
Kick-down-Position
Abnahme der Änderungszeit der Fahrpedalstellung (Fig. 4)
Abnahme der Übersetzung, d.h. in Richtung "kleinere Gänge" (Fig. 5)
Zunahme des Druckmitteldruckes
Zunahme der Druckmitteltemperatur.7. Conical pulley belt transmission according to claim 1 to 6, characterized in that the device causes an increase in the pressure medium quantity in at least one of the following instantaneous operating variables, starting from the basic quantity of pressure medium:
Increasing the accelerator pedal position ( Fig. 3)
Kick down position
Decrease in change time of accelerator pedal position ( Fig. 4)
Decrease in gear ratio, ie in the direction of "smaller gears" ( Fig. 5)
Increase in fluid pressure
Increase in pressure medium temperature.
DE19873727633 1987-08-19 1987-08-19 Cone pulley transmission with controlled quantity of pressure medium Granted DE3727633A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE19873727633 DE3727633A1 (en) 1987-08-19 1987-08-19 Cone pulley transmission with controlled quantity of pressure medium

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Application Number Priority Date Filing Date Title
DE19873727633 DE3727633A1 (en) 1987-08-19 1987-08-19 Cone pulley transmission with controlled quantity of pressure medium

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DE3727633A1 true DE3727633A1 (en) 1989-03-02
DE3727633C2 DE3727633C2 (en) 1993-07-22

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Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0423536A1 (en) * 1989-10-16 1991-04-24 Ford-Werke Aktiengesellschaft Control system of a continuously variable transmission for a motor vehicle
FR2654789A1 (en) * 1989-11-21 1991-05-24 Luk Lamellen & Kupplungsbau SPEED VARIATOR WITH SEPARATE CIRCUITS FOR GENERATING PRESSURES AS A FUNCTION OF TORQUE AND TRANSMISSION RATIO.
DE4131931A1 (en) * 1990-09-26 1992-04-02 Zahnradfabrik Friedrichshafen Continuously variable cone and pulley gearbox - has hydraulic pulley adjustment with actuator requiring less operating work
US5137498A (en) * 1991-03-05 1992-08-11 Van Doorne's Transmissie B.V. Continuously variable transmission with a regulable pump
NL1003876C2 (en) * 1996-08-26 1998-03-03 Doornes Transmissie Bv Continuously variable transmission with at least two pumps in series / parallel connection.
WO1999032806A1 (en) * 1997-12-19 1999-07-01 Zf Friedrichshafen Ag Continuously variable automatic transmission
EP1048879A3 (en) * 1999-04-30 2001-01-17 Hydraulik-Ring GmbH Pressure fluid supply of a CVT
WO2001053724A1 (en) * 2000-01-20 2001-07-26 Eagle-Picher Industries, Inc. Dual gerotor pump for use with automatic transmission
DE10104635A1 (en) * 2001-02-02 2002-10-02 Joma Hydromechanic Gmbh Method for maintaining a constant output value, e.g. pressure, feed volume or capacity for vehicle oil pump, using rotational velocity transducer to adjust rotational speed of pump
EP1085241A3 (en) * 1999-09-20 2003-01-29 General Motors Corporation Hydraulic control for a continuously variable transmission
WO2003087627A1 (en) * 2002-04-10 2003-10-23 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulic system and automatic gearbox
WO2005088131A1 (en) * 2004-03-12 2005-09-22 Neg Micon A/S Variable capacity oil pump
NL1032577C2 (en) * 2006-09-26 2008-03-27 Bosch Gmbh Robert Continuously variable transmission with a hydraulic control system and method for controlling it.
EP2431635A1 (en) * 2009-05-13 2012-03-21 Toyota Jidosha Kabushiki Kaisha Hydraulic device for stepless transmission
WO2013097876A1 (en) * 2011-12-28 2013-07-04 Robert Bosch Gmbh Method for controlling a continuously variable transmission with an electro-hydraulic control system
CN103629094A (en) * 2012-08-24 2014-03-12 罗伯特·博世有限公司 Pump device

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19822039A1 (en) * 1998-05-16 1999-11-18 Bayerische Motoren Werke Ag Hydraulic supply device, particularly for stageless enfolding gear in road vehicle
DE19924855A1 (en) * 1999-04-30 2000-11-02 Hydraulik Ring Gmbh Pressure medium supply for a CVT transmission
DE19930356A1 (en) * 1999-07-01 2001-01-04 Zahnradfabrik Friedrichshafen Automatic transmission
DE102005050478A1 (en) * 2005-10-21 2007-04-26 Volkswagen Ag Hydraulic conveying system for automatic transmissions in vehicles comprises a short circuit line which opens into a return line and/or directly into the suction side of a conveying unit downstream of a hydraulic throttle

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3000544A1 (en) * 1980-01-09 1981-07-16 Robert Bosch Gmbh, 7000 Stuttgart Stepless transmission control system - has electronic unit with mini-computer delivering signals to pressure regulator for varying pulley dia.
EP0228817A2 (en) * 1985-11-29 1987-07-15 Kabushiki Kaisha Toyota Chuo Kenkyusho Hydraulic control apparatus for stepless transmission

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3000544A1 (en) * 1980-01-09 1981-07-16 Robert Bosch Gmbh, 7000 Stuttgart Stepless transmission control system - has electronic unit with mini-computer delivering signals to pressure regulator for varying pulley dia.
EP0228817A2 (en) * 1985-11-29 1987-07-15 Kabushiki Kaisha Toyota Chuo Kenkyusho Hydraulic control apparatus for stepless transmission

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3934506C1 (en) * 1989-10-16 1991-05-08 Ford-Werke Ag, 5000 Koeln, De
EP0423536A1 (en) * 1989-10-16 1991-04-24 Ford-Werke Aktiengesellschaft Control system of a continuously variable transmission for a motor vehicle
FR2654789A1 (en) * 1989-11-21 1991-05-24 Luk Lamellen & Kupplungsbau SPEED VARIATOR WITH SEPARATE CIRCUITS FOR GENERATING PRESSURES AS A FUNCTION OF TORQUE AND TRANSMISSION RATIO.
DE4131931C2 (en) * 1990-09-26 1998-10-01 Zahnradfabrik Friedrichshafen Adjustable belt transmission
DE4131931A1 (en) * 1990-09-26 1992-04-02 Zahnradfabrik Friedrichshafen Continuously variable cone and pulley gearbox - has hydraulic pulley adjustment with actuator requiring less operating work
US5137498A (en) * 1991-03-05 1992-08-11 Van Doorne's Transmissie B.V. Continuously variable transmission with a regulable pump
EP0502263A1 (en) * 1991-03-05 1992-09-09 Van Doorne's Transmissie B.V. Continuously variable transmission with an adjustable pump
NL1003876C2 (en) * 1996-08-26 1998-03-03 Doornes Transmissie Bv Continuously variable transmission with at least two pumps in series / parallel connection.
EP0826910A1 (en) 1996-08-26 1998-03-04 Van Doorne's Transmissie B.V. Continuously variable transmission with at least two pumps connected in series/parallel
US5941786A (en) * 1996-08-26 1999-08-24 Van Doorne's Transmissie B.V. Continuously variable transmission with at least two pumps connected in series/parallel
EP1803975A1 (en) * 1996-08-26 2007-07-04 Van Doorne's Transmissie B.V. Continuously variable transmission with at least two pumps conntected in series
WO1999032806A1 (en) * 1997-12-19 1999-07-01 Zf Friedrichshafen Ag Continuously variable automatic transmission
EP1048879A3 (en) * 1999-04-30 2001-01-17 Hydraulik-Ring GmbH Pressure fluid supply of a CVT
US6387000B1 (en) 1999-04-30 2002-05-14 Hydraulik-Ring Gmbh Pressure medium supply arrangement for a continuous variable transmission
EP1085241A3 (en) * 1999-09-20 2003-01-29 General Motors Corporation Hydraulic control for a continuously variable transmission
WO2001053724A1 (en) * 2000-01-20 2001-07-26 Eagle-Picher Industries, Inc. Dual gerotor pump for use with automatic transmission
US6386836B1 (en) 2000-01-20 2002-05-14 Eagle-Picher Industries, Inc. Dual gerotor pump for use with automatic transmission
WO2002084117A2 (en) * 2001-02-02 2002-10-24 Joma-Hydromechanic Gmbh Speed variable feed pump
WO2002084117A3 (en) * 2001-02-02 2003-01-09 Joma Hydromechanic Gmbh Speed variable feed pump
DE10104635A1 (en) * 2001-02-02 2002-10-02 Joma Hydromechanic Gmbh Method for maintaining a constant output value, e.g. pressure, feed volume or capacity for vehicle oil pump, using rotational velocity transducer to adjust rotational speed of pump
WO2003087627A1 (en) * 2002-04-10 2003-10-23 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulic system and automatic gearbox
US7389640B2 (en) 2002-04-10 2008-06-24 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulic system and automatic transmission
AU2004317282B2 (en) * 2004-03-12 2008-06-05 Vestas Wind Systems A/S A wind turbine with a fluid supply system and method
WO2005088131A1 (en) * 2004-03-12 2005-09-22 Neg Micon A/S Variable capacity oil pump
AU2004317282B8 (en) * 2004-03-12 2008-09-11 Vestas Wind Systems A/S A wind turbine with a fluid supply system and method
CN1926337B (en) * 2004-03-12 2012-09-05 维斯塔斯风力系统有限公司 Variable capacity oil pump
US8827660B2 (en) 2004-03-12 2014-09-09 Vestas Wind Systems A/S Variable capacity oil pump
WO2008037665A1 (en) * 2006-09-26 2008-04-03 Robert Bosch Gmbh Continuously variable transmission with a hydraulic control system and method for controlling said transmission
NL1032577C2 (en) * 2006-09-26 2008-03-27 Bosch Gmbh Robert Continuously variable transmission with a hydraulic control system and method for controlling it.
EP2431635A1 (en) * 2009-05-13 2012-03-21 Toyota Jidosha Kabushiki Kaisha Hydraulic device for stepless transmission
EP2431635A4 (en) * 2009-05-13 2013-02-13 Toyota Motor Co Ltd Hydraulic device for stepless transmission
WO2013097876A1 (en) * 2011-12-28 2013-07-04 Robert Bosch Gmbh Method for controlling a continuously variable transmission with an electro-hydraulic control system
CN103629094A (en) * 2012-08-24 2014-03-12 罗伯特·博世有限公司 Pump device

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