WO2011006465A1 - Système hydraulique - Google Patents

Système hydraulique Download PDF

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Publication number
WO2011006465A1
WO2011006465A1 PCT/DE2010/000728 DE2010000728W WO2011006465A1 WO 2011006465 A1 WO2011006465 A1 WO 2011006465A1 DE 2010000728 W DE2010000728 W DE 2010000728W WO 2011006465 A1 WO2011006465 A1 WO 2011006465A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure
hydraulic
port
working pressure
Prior art date
Application number
PCT/DE2010/000728
Other languages
German (de)
English (en)
Inventor
Reinhard Stehr
Original Assignee
Schaeffler Technologies Gmbh & 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 Schaeffler Technologies Gmbh & Co. Kg filed Critical Schaeffler Technologies Gmbh & Co. Kg
Priority to EP10742405.3A priority Critical patent/EP2454490B1/fr
Priority to CN201080031253.5A priority patent/CN102625882B/zh
Priority to DE112010002946T priority patent/DE112010002946A5/de
Publication of WO2011006465A1 publication Critical patent/WO2011006465A1/fr

Links

Classifications

    • 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
    • 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
    • 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 horran- connection and a working pressure port, which is connectable by the pressure reducing valve with 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.
  • pressure reducing valves which connect the working pressure either with the tank pressure or with the system pressure or occupy intermediate positions in order to steplessly modulate the working pressure.
  • 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.
  • the object is further in a hydraulic system with a 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 is supplied with a working pressure, 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 Hold control edge.
  • 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 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.
  • 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.
  • 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 kickback til and the hydraulic resistance always reaches working fluid to the working pressure connection when the working pressure is lower 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 Ultikan- conclusion in 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.
  • FIG. 1 shows a hydraulic circuit diagram of a hydraulic system according to a first embodiment with a check valve
  • Figure 2 is a similar hydraulic system as in Figure 1 with a 2/2-way valve and
  • Figure 3 is a similar hydraulic system as in Fig. 1 without additional valve.
  • 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 tight 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.
  • adjusting cylinder if a bevel gear ratio is to be kept at changing moment, for example in Stön partner. This causes a pressure reducing valve 8 when used with a clutch cylinder, a gear adjusting cylinder or an adjusting cylinder as a 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.
  • 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 additional volume flow is an additional leakage, but does not matter in the cold, since the control volume of the pressure reducing valve 8 is preferably tuned to high gap leakage in the heat.
  • 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 When a threshold value defined by the prestressed spring is exceeded, the additional valve 65 is actuated via the control line 70, that is, switched to its opening division, not shown in FIG. 2, in which the working pressure line 12 communicates with the tank 5 via the additional line 60 and the orifice 68 stands.
  • the discharged from the tank drain of the valve 65 hydraulic medium for other tasks in a transmission, such as CVT, automated manual 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 Figure 2 may even be omitted.
  • This embodiment of the invention is shown in FIG.
  • 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 particularly preferred when the additional volume flow to other consumers 66 results in the fact that they 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Transmission Device (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

Système hydraulique qui comporte une soupape de réduction de pression se présentant sous la forme d'une soupape à tiroir à recouvrement total et pourvue d'un raccord pour réservoir, d'un raccord pour pression de système et d'un raccord pour pression de travail qui peut être raccordé par l'intermédiaire de la soupape de réduction de pression au raccord pour pression de système ou au raccord pour réservoir, une soupape à tiroir de la soupape de réduction de pression étant soumise par l'intermédiaire d'une conduite de commande à une pression de travail acheminée via le raccord pour pression de travail, et une conduite de retour. L'invention se caractérise en ce qu'un débit volumétrique supplémentaire est évacué à partir du raccord pour pression de travail par l'intermédiaire d'une résistance hydraulique et acheminé vers un autre consommateur pour maintenir la soupape à tiroir à une arête de commande dans des situations critiques.
PCT/DE2010/000728 2009-07-16 2010-06-24 Système hydraulique WO2011006465A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP10742405.3A EP2454490B1 (fr) 2009-07-16 2010-06-24 Système hydraulique
CN201080031253.5A CN102625882B (zh) 2009-07-16 2010-06-24 液压系统
DE112010002946T DE112010002946A5 (de) 2009-07-16 2010-06-24 Hydrauliksystem

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102009033844.6 2009-07-16
DE102009033844 2009-07-16
DE102009034559 2009-07-23
DE102009034559.0 2009-07-23

Publications (1)

Publication Number Publication Date
WO2011006465A1 true WO2011006465A1 (fr) 2011-01-20

Family

ID=43027523

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2010/000728 WO2011006465A1 (fr) 2009-07-16 2010-06-24 Système hydraulique

Country Status (4)

Country Link
EP (1) EP2454490B1 (fr)
CN (1) CN102625882B (fr)
DE (2) DE102010024923A1 (fr)
WO (1) WO2011006465A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005005842A1 (fr) * 2003-07-09 2005-01-20 Hydac System Gmbh Systeme hydraulique
WO2007003151A1 (fr) 2005-07-01 2007-01-11 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Procede et dispositif de commande d'un embrayage de vehicule
DE102008058693A1 (de) * 2007-12-07 2009-06-10 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydrauliksystem mit einem Druckminderventil

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE521188C2 (sv) * 2002-02-11 2003-10-07 Kalmar Ind Sverige Ab Hydraulsystem för ett fordon, fordon innefattande ett sådant hydraulsystem samt en tilläggsenhet för ett sådant fordon
FR2864178B1 (fr) * 2003-12-23 2006-02-17 Giat Ind Sa Dispositif de commande en position d'un actionneur hydraulique et plaque interface de servovalve mettant en oeuvre un tel dispositif

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005005842A1 (fr) * 2003-07-09 2005-01-20 Hydac System Gmbh Systeme hydraulique
WO2007003151A1 (fr) 2005-07-01 2007-01-11 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Procede et dispositif de commande d'un embrayage de vehicule
DE102008058693A1 (de) * 2007-12-07 2009-06-10 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydrauliksystem mit einem Druckminderventil

Also Published As

Publication number Publication date
CN102625882B (zh) 2014-12-24
CN102625882A (zh) 2012-08-01
EP2454490B1 (fr) 2013-05-01
DE112010002946A5 (de) 2012-08-30
EP2454490A1 (fr) 2012-05-23
DE102010024923A1 (de) 2011-01-27

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