EP2454490B1 - Hydraulic system - Google Patents
Hydraulic system Download PDFInfo
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- EP2454490B1 EP2454490B1 EP10742405.3A EP10742405A EP2454490B1 EP 2454490 B1 EP2454490 B1 EP 2454490B1 EP 10742405 A EP10742405 A EP 10742405A EP 2454490 B1 EP2454490 B1 EP 2454490B1
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- European Patent Office
- Prior art keywords
- pressure
- valve
- hydraulic
- working
- hydraulic system
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/025—Pressure reducing valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing valve
Definitions
- the invention relates to a hydraulic system with a designed as a slide valve with positive overlap pressure reducing valve having a tank port, a system pressure port and a working pressure port which is connectable by the pressure reducing valve to the system pressure port or the tank port, wherein a valve spool of the pressure reducing valve via a control line with a working pressure is applied, which is provided via the working pressure port, and with a return.
- the object of the invention is to improve the response of a pressure reducing valve in a hydraulic system according to the preamble of claim 1 in critical situations.
- the object is in a hydraulic system with a valve designed as a positive overlap valve pressure reducing valve having a tank port, a system pressure port and a working pressure port, which is connectable by the pressure reducing valve to the system pressure port or the tank port, wherein a valve spool of the pressure reducing valve via a control line with a Working pressure is applied, which is provided via the working pressure port, and with a return, solved in that an additional volume flow is discharged via a hydraulic resistance from the working pressure port and another consumer is supplied to hold the valve spool in critical situations at a control edge.
- the further consumer is preferably a cooling device and / or a lubricating device and / or a pilot circuit of a hydraulic valve or the tank. If the additional volume flow is led to other consumers, so that they have to take correspondingly less volume flow directly from the system, the permanent flow through the hydraulic resistance is not considered to be additional leakage, since it does not remain unused.
- the object is further in a hydraulic system with a valve designed as a positive overlap valve pressure reducing valve having a tank port, a system pressure port and a working pressure port which is connectable by the pressure reducing valve to the system pressure port or the tank port, wherein a valve spool of the pressure reducing valve via a control line with a working pressure is provided, which is provided via the working pressure port, and with a return, achieved in that the return via an additional valve and a hydraulic resistance to the working pressure port is connectable to the valve spool in critical situations at or near a control edge hold.
- the pressure reducing valve is preferably designed as a 3/2-way valve with positive coverage or as a 3/3-way valve.
- the tank connection communicates with a tank containing a working medium, such as hydraulic oil, which is subjected to a tank pressure, preferably ambient pressure.
- a working medium such as hydraulic oil
- the consumer is, for example, a hydraulic cylinder, in particular an adjusting cylinder for a CVT transmission, a gear adjusting cylinder for an automated manual transmission or for a dual-clutch transmission or a clutch cylinder.
- the valve spool In a positive overlap zone, the valve spool can move away without changing the working pressure.
- the positive overlap is needed to prevent working fluid from constantly flowing through the pressure reducing valve during operation. If the working fluid is relatively cold, the positive coverage, for example, due to viscous friction of the valve spool, may adversely affect the responsiveness of the pressure reducing valve.
- the valve spool is held according to an essential aspect of the invention by a targeted volume flow at or in the vicinity of the control edge. This significantly improves the response in critical situations.
- a preferred embodiment of the hydraulic system is characterized in that in critical situations via the additional valve, the hydraulic resistance and the pressure reducing valve, an additional volume flow, in particular via the tank connection or the tank, is discharged.
- the additional volume flow is preferably removed only at low temperatures. At high temperatures, the additional volume flow is switched off.
- Another preferred embodiment of the hydraulic system is characterized in that the additional valve is designed as a check valve. About the check valve and the hydraulic resistance always passes working fluid to the working pressure port when the working pressure is less than the return pressure.
- the check valve comprises a valve spring.
- the valve spring is preferably biased so that the check valve opens only from a certain pressure difference.
- a further preferred embodiment of the hydraulic system is characterized in that the additional valve is designed as a 2/2-way valve, which connects the working pressure port in the critical situations with the tank.
- the tank can be used in the context of the present invention, a return tank or drain.
- the additional 2-way valve opens the additional volume flow.
- Another preferred embodiment of the hydraulic system is characterized in that the 2/2-way valve is connected via a control line to the return. When a threshold value is exceeded, working fluid flows from the working pressure port via the hydraulic resistance and the 2/2-way valve into the tank. The control of the 2/2-way valve via the return pressure.
- the hydraulic resistance is designed as a diaphragm.
- the hydraulic resistance may be designed as a throttle.
- the hydraulic resistance is matched to the temperature behavior of the working fluid.
- a further preferred embodiment of the hydraulic system is characterized in that the output of a pump is connected to the system pressure port, wherein the return from a branch between the output of the pump and the system pressure port emanates. Via the return, the output of the pump is connected to the inlet of the pump and / or to the tank.
- Another preferred embodiment of the hydraulic system is characterized in that a pressure limiting valve is arranged in the return.
- the pressure relief valve ensures that the output of the pump is connected to the input of the pump or the tank only after a certain pressure value.
- a further preferred embodiment of the hydraulic system is characterized in that a cooler and / or a filter are arranged in the return line / is.
- the cooler serves to cool the working medium returned via the return.
- the filter is used to filter the discharged via the return working medium.
- a hydraulic cylinder is connected to the working pressure port.
- the hydraulic cylinder is preferably an adjusting cylinder, such as a gear adjusting cylinder of an automatic gearbox or a dual-clutch gearbox or a clutch cylinder, which is controlled by a transmission control by means of the pressure reducing valve.
- FIGS. 1, 2 and 3 is a hydraulic system 1; 41 is shown with a hydraulic cylinder 2 in the form of a hydraulic circuit diagram according to two different embodiments.
- the hydraulic cylinder 2 is, for example, an adjusting cylinder of a continuously variable conical-pulley belt drive, a gear adjusting cylinder in a transmission or a clutch cylinder.
- the hydraulic cylinder 2 is supplied via a pump 4 from a tank 5 with a working fluid.
- the working medium is a hydraulic medium, in particular hydraulic oil. The working medium is sucked in from the tank 5 via a suction line 6.
- a pressure-reducing valve 8 is connected for the control of the same, which is designed as a proportional valve and electromagnetically or hydraulically actuated.
- the pressure reducing valve 8 is designed as a 3/2-way valve with a positive coverage or as a 3/3-way valve.
- a system pressure connection of the pressure reducing valve 8 is connected via a connecting line 11 to an outlet of the pump 4 in connection.
- a tank connection of the pressure reducing valve 8 is in communication with the tank 5.
- a working pressure connection of the pressure reducing valve 8 is connected via a working pressure line 12 with the hydraulic cylinder 2 in connection. From the working pressure line 12 is a control line 14, through which a valve spool of the valve designed as a slide valve pressure reducing valve 8 is acted upon by the working pressure.
- the control line 14 of the pressure reducing valve 8 is also referred to as pressure feedback.
- a return 15 From the connecting line 11 is a return 15, which connects the connecting line 11 with an input of the pump 4 and with the tank 5.
- a pressure control valve 16 is arranged, which connects the connecting line 11 and the output of the pump 4 in response to the pressure at the outlet of the pump 4 and the pressure in the connecting line 11 with the input of the pump 4 and the tank.
- a cooler 17 and a filter 18 is further arranged.
- the working pressure connection or the working pressure line 12 is connected to the system pressure connection or the connecting line 11 or the tank connection or the tank 5 via the pressure reducing valve 8, as required with any intermediate positions.
- a third position or coverage zone is arranged in which all three ports are closed by the valve spool. In this overlap zone or third position, the valve slide can travel away without the working pressure in the working pressure line 12 changing significantly.
- This third position or coverage zone which is also referred to as a positive overlap, is required so that in operation, hydraulic medium does not flow back continuously from the working pressure line 12 via the working pressure connection and the pressure reducing valve 8 into the tank 5.
- Clutch cylinder, gear adjusting cylinder or adjusting cylinder have the peculiarity that they are actually carried out tightly and only record or release volume flow when they travel paths, for example, to drive over a clearance. If, however, a Wet clutch is applied, it reacts quite stiff and the clutch cylinder hardly moves even with pressure changes. The same applies to adjusting cylinders, if a bevel gear ratio is to be kept at changing moment, for example in Stön company. This causes a pressure reducing valve 8 when used with a clutch cylinder, a gear adjusting cylinder or an adjusting cylinder as the hydraulic cylinder 2, when the pressure is to be kept constant, often work in the overlap. In the case of a subsequent change request, that is to say pressure build-up or pressure reduction in the hydraulic cylinder 2, the valve slide must then often be moved only within the overlap in order to reach the control edge of the pressure-reducing valve 8.
- a flat behavior of the pressure reducing valve 8 in the overlap with a sharp bend to steep characteristics and outside of the overlap can easily lead to an unstable behavior of the pressure regulator, since the damping of the hydraulic system 1 must be tuned to either the steep characteristic part or the flat behavior. If the steep part is sufficiently damped, then this can lead to unsatisfactory dynamics in the coverage.
- the valve spool of the pressure reducing valve 8 is held in the previously described critical situations, especially in the cold, by a targeted flow in the working pressure port or out of this on its control edge.
- the valve slide With an inlet into the hydraulic cylinder 2, the valve slide is preferably held at a tank edge.
- the valve spool is preferably held at a system pressure control edge.
- the return pressure is used, which reaches about 4 bar in normal operation, for example. In the cold, the return pressure can reach 20 bar and more.
- the return line 15 via an additional line 20 to the working pressure line 12 is connectable.
- the additional line 20 is based on a branch 21 of the return line 15, which is arranged between the pressure regulating valve 16 and the radiator 17.
- the additional line 20 opens at a further branch 22, which is provided between the pressure reducing valve 8 and the hydraulic cylinder 2, in the working pressure line 12th
- an additional valve 25 and a hydraulic resistor 28 are connected in series.
- the additional valve 25 is designed as a check valve.
- the hydraulic resistor 28 is designed as a diaphragm.
- the working pressure line 12 is connected via an additional line 60 to the tank.
- the additional line 60 starts from a branch 61, which is arranged in the working pressure line 12 between the pressure reducing valve 8 and the hydraulic cylinder 2.
- an additional valve 65 and a hydraulic resistance 68 are arranged in the additional line 60.
- the hydraulic resistor 68 is designed as a diaphragm and connected in series between the branch 61 and the additional valve 65.
- the additional valve 65 is designed as a 2/2-way valve, which is biased by a spring in the illustrated closed position.
- the additional valve 65 is acted upon via a control line 70 with the return pressure.
- the control line 70 starts from a branch 72, which is arranged in the return line 15 between the pressure relief valve 16 and the radiator 17.
- the additional valve 65 is actuated via the control line 70, that is to say in its in FIG. 2 not shown open position connected, in which the working pressure line 12 is connected via the additional line 60 and the aperture 68 with the tank 5 in connection.
- FIG. 2 It is optionally possible to use the discharged from the tank drain of the valve 65 hydraulic medium for other tasks in a transmission, such as CVT, automatic transmission or dual-clutch transmission.
- the use can consist for example in the lubrication and / or cooling of components.
- Another possibility of use can be done in the hydraulic control itself, for example by the feed into the pilot circuit of a valve, in particular the pressure reducing valve. 8
- the valve 65 for interrupting the flow of the hydraulic medium from the working pressure line 12 according to FIG. 2 may even be omitted.
- This embodiment of the invention is in FIG. 3 shown.
- the additional volume flow discharged from the working pressure line 12 is therefore supplied directly to a consumer 66, which may be a device for lubricating and / or cooling and / or a pilot circuit and / or a fluid tank.
- the embodiment according to FIG. 3 is then particularly preferable if the additional volume flow to other consumers 66 causes them to have to remove correspondingly less oil flow directly from the system. The permanent flow would then not be regarded as additional leakage.
- the other consumer 66 may be the pilot circuit of the pressure reducing valve 8.
Description
Die Erfindung betrifft ein Hydrauliksystem mit einem als Schieberventil mit positiver Überdeckung ausgeführten Druckminderventil, das einen Tankanschluss, einen Systemdruckanschluss und einen Arbeitsdruckanschluss aufweist, der durch das Druckminderventil mit dem Systemdruckanschluss oder dem Tankanschluss verbindbar ist, wobei ein Ventilschieber des Druckminderventils über eine Steuerleitung mit einem Arbeitsdruck beaufschlagt ist, der über den Arbeitsdruckanschluss bereitgestellt wird, und mit einem Rücklauf.The invention relates to a hydraulic system with a designed as a slide valve with positive overlap pressure reducing valve having a tank port, a system pressure port and a working pressure port which is connectable by the pressure reducing valve to the system pressure port or the tank port, wherein a valve spool of the pressure reducing valve via a control line with a working pressure is applied, which is provided via the working pressure port, and with a return.
Aus der internationalen Veröffentlichung
Aufgabe der Erfindung ist es, das Ansprechverhalten eines Druckminderventils in einem Hydrauliksystem gemäß dem Oberbegriff des Anspruchs 1 in kritischen Situationen zu verbessern.The object of the invention is to improve the response of a pressure reducing valve in a hydraulic system according to the preamble of
Die Aufgabe ist bei einem Hydrauliksystem mit einem als Schieberventil mit positiver Überdeckung ausgeführten Druckminderventil, das einen Tankanschluss, einen Systemdruckanschluss und einen Arbeitsdruckanschluss aufweist, der durch das Druckminderventil mit dem Systemdruckanschluss oder dem Tankanschluss verbindbar ist, wobei ein Ventilschieber des Druckminderventils über eine Steuerleitung mit einem Arbeitsdruck beaufschlagt ist, der über den Arbeitsdruckanschluss bereitgestellt wird, und mit einem Rücklauf, dadurch gelöst, dass ein zusätzlicher Volumenstrom über einen hydraulischen Widerstand aus dem Arbeitsdruckanschluss abgeführt und einem weiteren Verbraucher zugeführt wird, um den Ventilschieber in kritischen Situationen an einer Steuerkante zu halten. Der weitere Verbraucher ist Vorzugsweise eine Kühlvorrichtung und/oder eine Schmiervorrichtung und/oder ein Vorsteuerkreis eines Hydraulikventils oder der Tank. Wenn der zusätzliche Volumenstrom zu anderen Verbrauchern geführt wird, so dass diese dadurch entsprechend weniger Volumenstrom direkt aus dem System entnehmen müssen, ist der permanente Durchfluss durch den hydraulischen Widerstand nicht als zusätzliche Leckage zu betrachten, da er ja nicht ungenutzt bleibt.The object is in a hydraulic system with a valve designed as a positive overlap valve pressure reducing valve having a tank port, a system pressure port and a working pressure port, which is connectable by the pressure reducing valve to the system pressure port or the tank port, wherein a valve spool of the pressure reducing valve via a control line with a Working pressure is applied, which is provided via the working pressure port, and with a return, solved in that an additional volume flow is discharged via a hydraulic resistance from the working pressure port and another consumer is supplied to hold the valve spool in critical situations at a control edge. The further consumer is preferably a cooling device and / or a lubricating device and / or a pilot circuit of a hydraulic valve or the tank. If the additional volume flow is led to other consumers, so that they have to take correspondingly less volume flow directly from the system, the permanent flow through the hydraulic resistance is not considered to be additional leakage, since it does not remain unused.
Die Aufgabe ist weiterhin bei einem Hydrauliksystem mit einem als Schieberventil mit positiver Überdeckung ausgeführten Druckminderventil, das einen Tankanschluss, einen Systemdruckanschluss und einen Arbeitsdruckanschluss aufweist, der durch das Druckminderventil mit dem Systemdruckanschluss oder dem Tankanschluss verbindbar ist, wobei ein Ventilschieber des Druckminderventils über eine Steuerleitung mit einem Arbeitsdruck beaufschlagt ist, der über den Arbeitsdruckanschluss bereitgestellt wird, und mit einem Rücklauf, dadurch gelöst, dass der Rücklauf über ein Zusatzventil und einen hydraulischen Widerstand mit dem Arbeitsdruckanschluss verbindbar ist, um den Ventilschieber in kritischen Situationen an oder in der Nähe einer Steuerkante zu halten. Das Druckminderventil ist vorzugsweise als 3/2-Wegeventil mit positiver Überdeckung beziehungsweise als 3/3-Wegeventil ausgeführt. Der Tankanschluss steht mit einem Tank in Verbindung, der ein Arbeitsmedium, wie Hydrauliköl, enthält, das mit einem Tankdruck, vorzugsweise Umgebungsdruck, beaufschlagt ist. An den Arbeitsdruckanschluss ist mindestens ein Verbraucher angeschlossen. Bei dem Verbraucher handelt es sich zum Beispiel um einen Hydraulikzylinder, insbesondere einen Verstellzylinder für ein CVT-Getriebe, einen Gangstellzylinder für ein automatisiertes Schaltgetriebe oder für ein Doppelkupplungsgetriebe oder einen Kupplungszylinder. In einer Zone der positiven Überdeckung kann der Ventilschieber Weg verfahren, ohne dass der Arbeitsdruck sich verändert. Die positive Überdeckung wird benötigt, um zu verhindern, dass im Betrieb ständig Arbeitsmedium durch das Druckminderventil strömt. Wenn das Arbeitsmedium relativ kalt ist, kann sich die positive Überdeckung, zum Beispiel aufgrund von viskoser Reibung des Ventilschiebers, nachteilig auf das Ansprechverhalten des Druckminderventils auswirken. In solchen kritischen Situationen, also insbesondere bei tiefen Temperaturen, wird der Ventilschieber gemäß einem wesentlichen Aspekt der Erfindung durch einen gezielten Volumenstrom an oder in der Nähe der Steuerkante gehalten. Dadurch wird das Ansprechverhalten in den kritischen Situationen deutlich verbessert.The object is further in a hydraulic system with a valve designed as a positive overlap valve pressure reducing valve having a tank port, a system pressure port and a working pressure port which is connectable by the pressure reducing valve to the system pressure port or the tank port, wherein a valve spool of the pressure reducing valve via a control line with a working pressure is provided, which is provided via the working pressure port, and with a return, achieved in that the return via an additional valve and a hydraulic resistance to the working pressure port is connectable to the valve spool in critical situations at or near a control edge hold. The pressure reducing valve is preferably designed as a 3/2-way valve with positive coverage or as a 3/3-way valve. The tank connection communicates with a tank containing a working medium, such as hydraulic oil, which is subjected to a tank pressure, preferably ambient pressure. At least one consumer is connected to the working pressure connection. The consumer is, for example, a hydraulic cylinder, in particular an adjusting cylinder for a CVT transmission, a gear adjusting cylinder for an automated manual transmission or for a dual-clutch transmission or a clutch cylinder. In a positive overlap zone, the valve spool can move away without changing the working pressure. The positive overlap is needed to prevent working fluid from constantly flowing through the pressure reducing valve during operation. If the working fluid is relatively cold, the positive coverage, for example, due to viscous friction of the valve spool, may adversely affect the responsiveness of the pressure reducing valve. In such critical situations, ie in particular at low temperatures, the valve spool is held according to an essential aspect of the invention by a targeted volume flow at or in the vicinity of the control edge. This significantly improves the response in critical situations.
Ein bevorzugtes Ausführungsbeispiel des Hydrauliksystems ist dadurch gekennzeichnet, dass in kritischen Situationen über das Zusatzventil, den hydraulischen Widerstand und das Druckminderventil ein zusätzlicher Volumenstrom, insbesondere über den Tankanschluss beziehungsweise den Tank, abgeführt wird. Der zusätzliche Volumenstrom wird vorzugsweise nur bei niedrigen Temperaturen abgeführt. Bei hohen Temperaturen wird der zusätzliche Volumenstrom abgeschaltet.A preferred embodiment of the hydraulic system is characterized in that in critical situations via the additional valve, the hydraulic resistance and the pressure reducing valve, an additional volume flow, in particular via the tank connection or the tank, is discharged. The additional volume flow is preferably removed only at low temperatures. At high temperatures, the additional volume flow is switched off.
Ein weiteres bevorzugtes Ausführungsbeispiel des Hydrauliksystems ist dadurch gekennzeichnet, dass das Zusatzventil als Rückschlagventil ausgeführt ist. Über das Rückschlagventil und den hydraulischen Widerstand gelangt immer dann Arbeitsmedium zu dem Arbeitsdruckanschluss, wenn der Arbeitsdruck geringer als der Rücklaufdruck ist.Another preferred embodiment of the hydraulic system is characterized in that the additional valve is designed as a check valve. About the check valve and the hydraulic resistance always passes working fluid to the working pressure port when the working pressure is less than the return pressure.
Ein weiteres bevorzugtes Ausführungsbeispiel des Hydrauliksystems ist dadurch gekennzeichnet, dass das Rückschlagventil eine Ventilfeder umfasst. Die Ventilfeder ist vorzugsweise so vorgespannt, dass das Rückschlagventil erst ab einer gewissen Druckdifferenz öffnet.Another preferred embodiment of the hydraulic system is characterized in that the check valve comprises a valve spring. The valve spring is preferably biased so that the check valve opens only from a certain pressure difference.
Ein weiteres bevorzugtes Ausführungsbeispiel des Hydrauliksystems ist dadurch gekennzeichnet, dass das Zusatzventil als 2/2-Wegeventil ausgeführt ist, das den Arbeitsdruckanschluss in den kritischen Situationen mit dem Tank verbindet. Anstelle des Tanks kann im Rahmen der vorliegenden Erfindung auch ein Rücklaufbehälter oder Ablauf verwendet werden. Über das geöffnete 2/2-Wegeventil wird der zusätzliche Volumenstrom abgeführt.A further preferred embodiment of the hydraulic system is characterized in that the additional valve is designed as a 2/2-way valve, which connects the working pressure port in the critical situations with the tank. Instead of the tank can be used in the context of the present invention, a return tank or drain. The additional 2-way valve opens the additional volume flow.
Ein weiteres bevorzugtes Ausführungsbeispiel des Hydrauliksystems ist dadurch gekennzeichnet, dass das 2/2-Wegeventil über eine Steuerleitung mit dem Rücklauf verbunden ist. Bei Überschreiten eines Schwellenwertes strömt Arbeitsmedium von dem Arbeitsdruckanschluss über den hydraulischen Widerstand und das 2/2-Wegeventil in den Tank. Das Ansteuern des 2/2-Wegeventils erfolgt über den Rücklaufdruck.Another preferred embodiment of the hydraulic system is characterized in that the 2/2-way valve is connected via a control line to the return. When a threshold value is exceeded, working fluid flows from the working pressure port via the hydraulic resistance and the 2/2-way valve into the tank. The control of the 2/2-way valve via the return pressure.
Ein weiteres bevorzugtes Ausführungsbeispiel des Hydrauliksystems ist dadurch gekennzeichnet, dass der hydraulische Widerstand als Blende ausgeführt ist. Alternativ kann der hydraulische Widerstand als Drossel ausgeführt sein. Der hydraulische Widerstand ist auf das Temperaturverhalten des Arbeitsmediums abgestimmt.Another preferred embodiment of the hydraulic system is characterized in that the hydraulic resistance is designed as a diaphragm. Alternatively, the hydraulic resistance may be designed as a throttle. The hydraulic resistance is matched to the temperature behavior of the working fluid.
Ein weiteres bevorzugtes Ausführungsbeispiel des Hydrauliksystems ist dadurch gekennzeichnet, dass der Ausgang einer Pumpe an den Systemdruckanschluss angeschlossen ist, wobei der Rücklauf von einer Verzweigung zwischen dem Ausgang der Pumpe und dem Systemdruckanschluss ausgeht. Über den Rücklauf steht der Ausgang der Pumpe mit dem Eingang der Pumpe und/oder mit dem Tank in Verbindung.A further preferred embodiment of the hydraulic system is characterized in that the output of a pump is connected to the system pressure port, wherein the return from a branch between the output of the pump and the system pressure port emanates. Via the return, the output of the pump is connected to the inlet of the pump and / or to the tank.
Ein weiteres bevorzugtes Ausführungsbeispiel des Hydrauliksystems ist dadurch gekennzeichnet, dass ein Druckbegrenzungsventil in dem Rücklauf angeordnet ist. Das Druckbegrenzungsventil sorgt dafür, dass der Ausgang der Pumpe erst ab einem bestimmten Druckwert mit dem Eingang der Pumpe beziehungsweise dem Tank verbunden wird.Another preferred embodiment of the hydraulic system is characterized in that a pressure limiting valve is arranged in the return. The pressure relief valve ensures that the output of the pump is connected to the input of the pump or the tank only after a certain pressure value.
Ein weiteres bevorzugtes Ausführungsbeispiel des Hydrauliksystems ist dadurch gekennzeichnet, dass ein Kühler und/oder ein Filter in dem Rücklauf angeordnet sind/ist. Der Kühler dient dazu, das über den Rücklauf zurückgeführte Arbeitsmedium zu kühlen. Der Filter dient dazu, das über den Rücklauf abgeführte Arbeitsmedium zu filtern.A further preferred embodiment of the hydraulic system is characterized in that a cooler and / or a filter are arranged in the return line / is. The cooler serves to cool the working medium returned via the return. The filter is used to filter the discharged via the return working medium.
Ein weiteres bevorzugtes Ausführungsbeispiel des Hydrauliksystems ist dadurch gekennzeichnet, dass ein Hydraulikzylinder an den Arbeitsdruckanschluss angeschlossen ist. Bei dem Hydraulikzylinder handelt es sich vorzugsweise um einen Verstellzylinder, etwa einen Gangstellzylinder eines automatisierten Schaltgetriebes oder eines Doppelkupplungsgetriebes oder einen Kupplungszylinder, der durch eine Getriebesteuerung mit Hilfe des Druckminderventils gesteuert wird.Another preferred embodiment of the hydraulic system is characterized in that a hydraulic cylinder is connected to the working pressure port. The hydraulic cylinder is preferably an adjusting cylinder, such as a gear adjusting cylinder of an automatic gearbox or a dual-clutch gearbox or a clutch cylinder, which is controlled by a transmission control by means of the pressure reducing valve.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnung verschiedene Ausführungsbeispiele im Einzelnen beschrieben sind. Es zeigen:
Figur 1- einen Hydraulikschaltplan eines Hydrauliksystems gemäß einem ersten Ausführungsbeispiel mit einem Rückschlagventil,
Figur 2- ein ähnliches Hydrauliksystem wie in
mit einem 2/2-WegeventilFigur 1
und - Figur 3
- ein ähnliches Hydrauliksystem wie in
Fig. 1 ohne Zusatzventil.
- FIG. 1
- FIG. 2 shows a hydraulic circuit diagram of a hydraulic system according to a first exemplary embodiment with a check valve, FIG.
- FIG. 2
- a similar hydraulic system as in
FIG. 1 with a 2/2-way valve
and - FIG. 3
- a similar hydraulic system as in
Fig. 1 without additional valve.
In den
Zwischen die Pumpe 4 und den Hydraulikzylinder 2 ist zur Steuerung desselben ein Druckminderventil 8 geschaltet, das als Proportionalventil ausgeführt und elektromagnetisch beziehungsweise hydraulisch betätigbar ist. Das Druckminderventil 8 ist als 3/2-Wegeventil mit einer positiven Überdeckung beziehungsweise als 3/3-Wegeventil ausgeführt. Ein Systemdruckanschluss des Druckminderventils 8 steht über eine Verbindungsleitung 11 mit einem Ausgang der Pumpe 4 in Verbindung. Ein Tankanschluss des Druckminderventils 8 steht mit dem Tank 5 in Verbindung. Ein Arbeitsdruckanschluss des Druckminderventils 8 steht über eine Arbeitsdruckleitung 12 mit dem Hydraulikzylinder 2 in Verbindung. Von der Arbeitsdruckleitung 12 geht eine Steuerleitung 14 aus, durch die ein Ventilschieber des als Schieberventil ausgeführten Druckminderventils 8 mit dem Arbeitsdruck beaufschlagt ist. Die Steuerleitung 14 des Druckminderventils 8 wird auch als Druckrückführung bezeichnet.Between the
Von der Verbindungsleitung 11 geht ein Rücklauf 15 aus, der die Verbindungsleitung 11 mit einem Eingang der Pumpe 4 beziehungsweise mit dem Tank 5 verbindet. In dem Rücklauf 15 ist ein Druckregelventil 16 angeordnet, das die Verbindungsleitung 11 beziehungsweise den Ausgang der Pumpe 4 in Abhängigkeit von dem Druck an dem Ausgang der Pumpe 4 beziehungsweise dem Druck in der Verbindungsleitung 11 mit dem Eingang der Pumpe 4 beziehungsweise dem Tank verbindet. In dem Rücklauf 15 ist des Weiteren ein Kühler 17 und ein Filter 18 angeordnet.From the connecting
Über das Druckminderventil 8 wird der Arbeitsdruckanschluss beziehungsweise die Arbeitsdruckleitung 12, je nach Bedarf mit beliebigen Zwischenstellungen, mit dem Systemdruckanschluss beziehungsweise der Verbindungsleitung 11 oder dem Tankanschluss beziehungsweise dem Tank 5 verbunden. Zwischen der zum Tank geöffneten Stellung und der zum Systemdruck geöffneten Stellung ist eine dritte Stellung oder Überdeckungszone angeordnet, in der alle drei Anschlüsse durch den Ventilschieber verschlossen sind. In dieser Überdeckungszone beziehungsweise dritten Stellung kann der Ventilschieber Weg verfahren, ohne dass sich der Arbeitsdruck in der Arbeitsdruckleitung 12 wesentlich verändert. Diese dritte Stellung oder Überdeckungszone, die auch als positive Überdeckung bezeichnet wird, wird benötigt, damit im Betrieb nicht ständig Hydraulikmedium aus der Arbeitsdruckleitung 12 über den Arbeitsdruckanschluss und das Druckminderventil 8 in den Tank 5 zurückströmt.The working pressure connection or the working
Kupplungszylinder, Gangstellzylinder oder Verstellzylinder haben die Eigenart, dass sie eigentlich dicht ausgeführt werden und nur dann Volumenstrom aufnehmen oder abgeben, wenn sie Wege verfahren, zum Beispiel zum Überfahren eines Lüftspiels. Wenn dagegen eine Nasskupplung angelegt ist, reagiert sie recht steif und der Kupplungszylinder bewegt sich auch bei Druckänderungen kaum. Gleiches gilt für Verstellzylinder, wenn eine Kegelscheibengetriebe-Übersetzung bei wechselndem Moment, zum Beispiel bei Stützbedarf, gehalten werden soll. Das führt dazu, dass ein Druckminderventil 8 bei Verwendung mit einem Kupplungszylinder, einem Gangstellzylinder oder einem Verstellzylinder als Hydraulikzylinder 2, wenn der Druck konstant gehalten werden soll, oft im Bereich der Überdeckung arbeiten. Bei einem folgenden Änderungswunsch, das heißt Druckaufbau oder Druckabbau in dem Hydraulikzylinder 2, muss der Ventilschieber dann oft erst innerhalb der Überdeckung verfahren werden, um die Steuerkante des Druckminderventils 8 zu erreichen.Clutch cylinder, gear adjusting cylinder or adjusting cylinder have the peculiarity that they are actually carried out tightly and only record or release volume flow when they travel paths, for example, to drive over a clearance. If, however, a Wet clutch is applied, it reacts quite stiff and the clutch cylinder hardly moves even with pressure changes. The same applies to adjusting cylinders, if a bevel gear ratio is to be kept at changing moment, for example in Stützbedarf. This causes a
Bei normaler Betriebstemperatur stellt das Erreichen der Steuerkante kein Problem dar. Bei niedrigen Temperaturen, das heißt niedriger Hydraulikmediumtemperatur, kann die Überdeckung durch die viskose Reibung des Ventilschiebers und eine erhöhte Dämpfungswirkung der endlich langen Blenden in der Getriebesteuerung jedoch zu einer unerwünscht langen Antwortzeit und sogar zu Stabilitätsproblemen durch die Totzeit bis zum Ansprechen des Druckminderventils 8 führen.At normal operating temperature, reaching the control edge is not a problem. However, at low temperatures, ie, low hydraulic fluid temperature, the overlap due to the viscous friction of the valve spool and increased damping effect of the finite diaphragms in the transmission control may result in an undesirably long response time and even increase Stability problems due to the dead time to the response of the
Weiterhin kann ein flaches Verhalten des Druckminderventils 8 in der Überdeckung mit einem scharfen Knick zu steilen Kennlinien und außerhalb der Überdeckung leicht zu einem instabilen Verhalten des Druckreglers führen, da die Bedämpfung des Hydrauliksystems 1 entweder auf den steilen Kennlinienteil oder das flache Verhalten abgestimmt werden muss. Wenn der steile Teil ausreichend bedämpft ist, dann kann das zu einer unbefriedigenden Dynamik in der Überdeckung führen.Furthermore, a flat behavior of the
Durch die Erfindung wird das Ansprechverhalten des Druckminderventils 8, insbesondere bei Kälte, verbessert, ohne dass die Grundauslegung des Druckminderventils 8 verändert werden muss. Gemäß einem wesentlichen Aspekt der Erfindung wird der Ventilschieber des Druckminderventils 8 in den vorab beschriebenen kritischen Situationen, insbesondere bei Kälte, durch einen gezielten Volumenstrom in den Arbeitsdruckanschluss oder aus diesem hinaus an seiner Steuerkante gehalten. Bei einem Zulauf in den Hydraulikzylinder 2 wird der Ventilschieber vorzugsweise an einer Tankkante gehalten. Bei einem Ablauf aus dem Hydraulikzylinder 2 wird der Ventilschieber vorzugsweise an einer Systemdrucksteuerkante gehalten. Der zusätzliche Volumenstrom stellt zwar eine Zusatzleckage dar, die aber bei Kälte keine Rolle spielt, da die Steuerungsvolumetrie des Druckminderventils 8 vorzugsweise auf hohe Spaltleckagen bei Hitze abgestimmt ist.By the invention, the response of the
Als Eingangsgröße für das Bereitstellen des zusätzlichen Volumenstroms wird der Rücklaufdruck verwendet, der im Normalbetrieb zum Beispiel etwa 4 bar erreicht. Bei Kälte kann der Rücklaufdruck durchaus 20 bar und mehr erreichen.As an input variable for providing the additional volume flow, the return pressure is used, which reaches about 4 bar in normal operation, for example. In the cold, the return pressure can reach 20 bar and more.
Bei dem in
In der Zusatzleitung 20 sind, ausgehend von der Verzweigung 21, ein Zusatzventil 25 und ein hydraulischer Widerstand 28 in Reihe geschaltet. Das Zusatzventil 25 ist als Rückschlagventil ausgeführt. Der hydraulische Widerstand 28 ist als Blende ausgeführt. Über das Zusatzventil 25 und den hydraulischen Widerstand 28 wird immer dann Hydraulikmedium aus dem Rücklauf 15 in die Arbeitsdruckleitung 12 geleitet, wenn der Druck an der Verzweigung 22, der auch als Arbeitsdruck bezeichnet wird, geringer als der Druck an der Verzweigung 21 ist, der auch als Kühlerrücklaufdruck bezeichnet wird.In the
Bei dem in
Bei dem Ausführungsbeispiel nach
Das Ventil 65 zur Unterbrechung des Stroms des Hydraulikmediums aus der Arbeitsdruckleitung 12 gemäß
- 11
- Hydrauliksystemhydraulic system
- 22
- Hydraulikzylinderhydraulic cylinders
- 44
- Pumpepump
- 55
- Tanktank
- 66
- Saugleitungsuction
- 88th
- DruckminderventilPressure reducing valve
- 1111
- Verbindungsleitungconnecting line
- 1212
- ArbeitsdruckleitungWorking pressure line
- 1414
- Steuerleitungcontrol line
- 1515
- Rücklaufreturns
- 1616
- DruckregelventilPressure control valve
- 1717
- Kühlercooler
- 1818
- Filterfilter
- 2020
- Zusatzleitungadditional line
- 2121
- Verzweigungbranch
- 2222
- Verzweigungbranch
- 2525
- Zusatzventiladditional valve
- 2828
- hydraulischer Widerstandhydraulic resistance
- 4141
- Hydrauliksystemhydraulic system
- 6060
- Zusatzleitungadditional line
- 6161
- Verzweigungbranch
- 6565
- Zusatzventiladditional valve
- 6666
- Verbraucherconsumer
- 6868
- hydraulischer Widerstandhydraulic resistance
- 7070
- Steuerleitungcontrol line
- 7272
- Verzweigungbranch
Claims (10)
- Hydraulic system, with a pressure-reducing valve (8) designed as a slide valve with positive overlap, which hydraulic system has a tank connection, a system-pressure connection and a working-pressure connection which is connectable to the system-pressure connection or to the tank connection by means of the pressure-reducing valve (8), a valve slide of the pressure-reducing valve being acted upon via a control line (14) with a working pressure which is provided via the working-pressure connection, and with a return (15), characterized in that an additional volume flow is discharged out of the working-pressure connection via hydraulic resistance (68) and is delivered to a further consumer (66) in order to hold the valve slide at a control edge in critical situations.
- Hydraulic system, with a pressure-reducing valve (8) designed as a slide valve with positive overlap, which hydraulic system has a tank connection, a system-pressure connection and a working-pressure connection which is connectable to the system-pressure connection or to the tank connection by means of the pressure-reducing valve (8), a valve slide of the pressure-reducing valve being acted upon via a control line (14) with a working pressure which is provided via the working-pressure connection, and with a return (15), characterized in that the return (15) is connectable to the working-pressure connection via an additional valve (25; 65) and hydraulic resistance (28; 68) in order to hold the valve slide at a control edge in critical situations.
- Hydraulic system according to Claim 2, characterized in that an additional volume flow is discharged via the additional valve (25; 65), the hydraulic resistance (28; 68) and the pressure-reducing valve (8) in critical situations.
- Hydraulic system according to either one of Claims 2 and 3, characterized in that the additional valve (25) is designed as a non-return valve.
- Hydraulic system according to Claims 2 or 3, characterized in that the additional valve (65) is designed as a 2/2-way valve which connects the working-pressure connection to the tank (5) or to further consumers in the critical situations.
- Hydraulic system according to Claim 5, characterized in that the 2/2-way valve is connected to the return (15) via a control line (70).
- Hydraulic system according to one of the preceding claims, characterized in that the hydraulic resistance (28; 68) is designed as a diaphragm.
- Hydraulic system according to one of the preceding claims, characterized in that the outlet of a pump (4) is connected to the system-pressure connection, the return (15) emanating from a branch between the outlet of the pump (4) and the system-pressure connection.
- Hydraulic system according to one of the preceding claims, characterized in that a pressure-limiting valve (16) is arranged in the return.
- Hydraulic system according to one of the preceding claims, characterized in that a hydraulic cylinder (2) is connected to the working-pressure connection.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009033844 | 2009-07-16 | ||
DE102009034559 | 2009-07-23 | ||
PCT/DE2010/000728 WO2011006465A1 (en) | 2009-07-16 | 2010-06-24 | Hydraulic system |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2454490A1 EP2454490A1 (en) | 2012-05-23 |
EP2454490B1 true EP2454490B1 (en) | 2013-05-01 |
Family
ID=43027523
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10742405.3A Not-in-force EP2454490B1 (en) | 2009-07-16 | 2010-06-24 | Hydraulic system |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2454490B1 (en) |
CN (1) | CN102625882B (en) |
DE (2) | DE102010024923A1 (en) |
WO (1) | WO2011006465A1 (en) |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SE521188C2 (en) * | 2002-02-11 | 2003-10-07 | Kalmar Ind Sverige Ab | Hydraulic system for a vehicle, a vehicle comprising such a hydraulic system and an additional unit for such a vehicle |
DE10330869A1 (en) * | 2003-07-09 | 2005-02-17 | Hydac System Gmbh | Hydraulic system |
FR2864178B1 (en) * | 2003-12-23 | 2006-02-17 | Giat Ind Sa | CONTROL DEVICE IN POSITION OF A HYDRAULIC ACTUATOR AND SERVOVALVE INTERFACE PLATE USING SUCH A DEVICE |
EP1902227A1 (en) | 2005-07-01 | 2008-03-26 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Method and device for triggering a vehicle clutch |
DE102008058693A1 (en) * | 2007-12-07 | 2009-06-10 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Hydraulic system for controlling clutch of transmission of motor vehicle, has pressure regulating valve with system pressure connection that is subjected with higher pressure than another system pressure connection |
-
2010
- 2010-06-24 WO PCT/DE2010/000728 patent/WO2011006465A1/en active Application Filing
- 2010-06-24 DE DE102010024923A patent/DE102010024923A1/en not_active Withdrawn
- 2010-06-24 EP EP10742405.3A patent/EP2454490B1/en not_active Not-in-force
- 2010-06-24 CN CN201080031253.5A patent/CN102625882B/en not_active Expired - Fee Related
- 2010-06-24 DE DE112010002946T patent/DE112010002946A5/en not_active Withdrawn
Also Published As
Publication number | Publication date |
---|---|
CN102625882A (en) | 2012-08-01 |
WO2011006465A1 (en) | 2011-01-20 |
DE102010024923A1 (en) | 2011-01-27 |
DE112010002946A5 (en) | 2012-08-30 |
CN102625882B (en) | 2014-12-24 |
EP2454490A1 (en) | 2012-05-23 |
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