WO2012062259A1 - Hydraulische steuerung für ein automatisches getriebe - Google Patents
Hydraulische steuerung für ein automatisches getriebe Download PDFInfo
- Publication number
- WO2012062259A1 WO2012062259A1 PCT/DE2011/001790 DE2011001790W WO2012062259A1 WO 2012062259 A1 WO2012062259 A1 WO 2012062259A1 DE 2011001790 W DE2011001790 W DE 2011001790W WO 2012062259 A1 WO2012062259 A1 WO 2012062259A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- valve
- pressure
- system pressure
- cooling
- hydraulic control
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/34—Locking or disabling mechanisms
- F16H63/3416—Parking lock mechanisms or brakes in the transmission
- F16H63/3483—Parking lock mechanisms or brakes in the transmission with hydraulic actuating means
-
- 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
-
- 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
- F16H2061/1244—Keeping the current state
-
- 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
- F16H2061/1256—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures characterised by the parts or units where malfunctioning was assumed or detected
- F16H2061/1292—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures characterised by the parts or units where malfunctioning was assumed or detected the failing part is the power supply, e.g. the electric power supply
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
Definitions
- the invention relates to a hydraulic control for an automatic transmission, for example a dual-clutch transmission, a continuously variable transmission (CVT), an automated manual transmission or a stepped automatic transmission. More particularly, the invention relates to a hydraulic control system for a motor vehicle having an internal combustion engine and an automatic transmission, with a system pressure valve, a parking lock valve and a pilot valve.
- an automatic transmission for example a dual-clutch transmission, a continuously variable transmission (CVT), an automated manual transmission or a stepped automatic transmission.
- CVT continuously variable transmission
- the invention relates to a hydraulic control system for a motor vehicle having an internal combustion engine and an automatic transmission, with a system pressure valve, a parking lock valve and a pilot valve.
- the object of the present invention is to provide a hydraulic control which covers the required functions in the automatic or automated transmissions with as few valves and electromagnets as possible. Furthermore, the energy requirement of the hydraulic transmission control should be kept as low as possible at the lowest possible cost.
- a parking brake which is also referred to as "park-by-wire”, provided and constructed redundantly.
- the above objects are achieved with a hydraulic control with a permanently driven by an internal combustion engine pump.
- the transmission remains in its last switched position in case of power failure of the TCU until the engine is switched off. After that takes place in any case the insertion of a parking brake.
- the system holds both hydraulically and electrically in a designed position.
- the hydraulic control fulfills the mentioned functions in a dual-clutch transmission with only eleven identical magnets, so that high numbers of units and thus low valve costs are made possible.
- the inventive solution consists inter alia in the interconnection of the parking brake valve with the system pressure valves and the cooling oil minimum pressure valve with the two clutch cooling valves.
- a preferred embodiment of the hydraulic control for a motor vehicle with an internal combustion engine and an automatic transmission, with a system pressure valve, a parking lock valve and a pilot valve is characterized in that the system pressure valve, the parking lock valve and the pilot valve are interconnected so that the transmission at a Failure, especially power failure, an electronic transmission control remains in its last switched position until the engine is switched off.
- the electronic transmission control is also called Transmission Control Unit TCU. After the failure of the TCU, the parking lock is engaged.
- TCU Transmission Control Unit
- a further preferred embodiment of the hydraulic control is characterized in that the pilot valve is connected via a first control pressure line to the system pressure valve and via a second control pressure line to the parking lock valve.
- the parking lock valve is assigned to the parking lock.
- the two control pressure lines are preferably connected, for example via a common connection line, to a common connection of the pilot valve. From this connecting line is preferably a pressure feedback to one end of a pilot valve piston, which also acts on an actuating magnet for actuating the pilot valve.
- the other end of the pilot valve piston is biased, preferably by a spring force.
- a further preferred embodiment of the hydraulic control is characterized in that a first end of a system pressure valve piston is connected via the first control pressure line to a port of the pilot valve, wherein a second end of the system pressure valve piston is subjected to a system pressure.
- the system pressure is provided by a pump, which is preferably directly mechanically driven by the engine.
- a further preferred embodiment of the hydraulic control is characterized in that in the second control pressure line, a branch is provided, via which one end of a parking lock valve piston is acted upon by the pressure from the second control pressure line. At this end of the parking lock valve piston preferably also attacks an actuating magnet with which the parking lock valve is actuated. At the opposite end of the parking lock valve piston, preferably acts on a biasing force, which is provided for example by a spring.
- a further preferred embodiment of the hydraulic control is characterized in that the branch is arranged between two hydraulic resistors. The two hydraulic resistors are designed as diaphragms, for example. Due to the design of the two hydraulic resistors of the inlet and outlet flow in the control circuit can be designed so that the control pressure on the parking brake valve collapses when the system pressure valve is on tank, that is connected to a tank.
- the second control pressure line between the first control pressure line and the branching also have an infinitely large resistance, ie an interruption, so that there is no more direct connection between the system pressure valve and the parking lock valve.
- the interruption preferably comprises a biased by a spring piston with a superior check ball, via which a return passage to the parking lock valve can be opened and closed.
- the hydraulic control is characterized in that the pilot valve and the parking brake venti I run each as a 3/2-way valve and / or are driven electromagnetically.
- the pilot valve is preferably equipped with a system pressure port, a tank port and the common port for the two pilot pressure lines.
- the parking lock valve is preferably provided with a system pressure connection, a tank connection and a connection for the second control pressure line.
- the pilot valve and the parking lock valve are equipped with identical parts, in particular actuated with the same electromagnet.
- the system pressure valve is designed as a 3/3-way proportional valve.
- the system pressure valve is preferably equipped with a system pressure port, a connection line port, and a return line port.
- the connecting line is preferably used to connect a clutch cooling circuit to the system pressure valve.
- the return line port is preferably for connecting a return line connecting the system pressure valve to the input of the pump, which provides the system pressure.
- a further preferred embodiment of the hydraulic control is characterized in that the system pressure valve has a tank connection, a system pressure circuit and a clutch cooling connection, to which a clutch cooling is connected.
- the clutch cooling preferably includes two clutch cooling devices associated with two clutches of a dual clutch transmission.
- the clutch cooling comprises two cooling pressure regulators and a minimum cooling pressure valve which are connected, directly or indirectly, with the interposition of a cooling and / or filtering device, to the coupling cooling connection of the system pressure valve.
- the minimum cooling pressure valve is preferably designed as a 2/2-way proportional valve.
- a further preferred embodiment of the hydraulic control is characterized in that the cooling pressure regulator are each designed as a 2/2-way valve and / or are driven electromagnetically. Particularly advantageously, the cooling pressure regulator are equipped with the same actuating magnet as the pilot valve and the parking lock valve. As a result, the manufacturing costs of the hydraulic control can be significantly reduced.
- Figure 1 is a hydraulic circuit diagram of a first embodiment of a hydraulic control with a sub-circuit for a parking brake and a sub-circuit for a clutch cooling;
- Figure 1 A the sub-circuit for the parking brake of Figure 1;
- FIG. 2 shows a partial circuit for the parking brake according to a second embodiment.
- Cooling oil minimum pressure valve I VMD
- the parking lock unlocking valve VPbw is also referred to as a parking lock valve 13.
- the system pressure and parking lock self-sustaining pilot valve VpSys is also referred to as pilot valve 11.
- the system pressure regulating valve VSys is also referred to as system pressure valve 12.
- the clutch cooling oil pressure regulators VKU1, VKU2 are also referred to as cooling pressure regulators 41, 42.
- the cooling oil minimum pressure valve VMD is also referred to as minimum cooling pressure valve 40.
- FIGS. 1, 1A and 1B schematically illustrate a circuit diagram 1 of a hydraulic control system 1 according to the invention for an automatic transmission
- the hydraulic clutch and transmission control 30 is shown schematically in the part of the circuit diagram 1.
- the control 30 contains, for example, the hydraulic elements for actuating two clutches K1 and K2 and four shift forks GS1 to GS4 for six to seven forward gears and one reverse.
- connection line 14 Connected to the pilot valve 11 is a connection line 14, from which a pressure return line, in which a hydraulic resistance is arranged, is returned to one end of a valve piston of the pilot valve 11. At the same end of the valve piston, an electromagnet is indicated, which serves to actuate the pilot valve 11.
- the pilot valve 11 is designed as a 3/2-way valve and biased by a symbolically indicated spring in its illustrated position.
- a first control pressure line 15 extends to one end, in the figures to the right end of a valve piston of the system pressure valve 12. At the the same end of the valve piston of the system pressure valve 12 engages a spring, through which the system pressure valve 12 is biased in its illustrated position.
- the system pressure valve 12 is designed as a 3/3-way proportional valve.
- a second control pressure line 16 extends from the connection line 14 to a connecting line 200, which is connected to the parking brake valve 13.
- a branch 17 is arranged, via which one end, in the figures, the left end of a valve piston of the parking brake valve 13 is acted upon by the pressure from the second control pressure line 16.
- the end of the valve piston of the parking brake valve 13 engages an electromagnet, which serves to actuate the parking brake valve 13.
- an electromagnet which serves to actuate the parking brake valve 13.
- At the other end of the valve piston of the parking brake valve 13 engages a spring through which the park is detenventil 13 biased in its illustrated position.
- the branch 17 is arranged between two hydraulic resistors 18, 19 in the second control pressure line 16.
- the two hydraulic resistors 18, 19 are designed as diaphragms.
- a system pressure line From the output of the pump 2 is a system pressure line, which is acted upon by a system pressure, which is provided by the pump 2.
- system pressure line In the system pressure line three branches 21, 22, 23 are provided. From the branch 21, a connection line 24 extends to the system pressure connection of the pilot valve 11.
- a connecting line 25 extends to the system pressure port of the system pressure valve 12.
- a system pressure line 26 which also starts from the branch 22, and in which a hydraulic resistance is arranged, one end, in the figures, the left end of Valve piston of the system pressure valve 12 is supplied with the system pressure.
- connection lines 27, 28 are connected to two further connections of the system pressure valve 12.
- the function of the connection lines 27, 28 will be explained below.
- a connecting line 29 extends to the system pressure connection of the parking brake valve 13.
- the parking lock valve 13 connects the connection line 200 with the tank in its illustrated position. In its second, not shown position, the connection to the tank is interrupted, wherein the connecting lines 29 and 200 are connected to each other.
- the pilot valve 11 connects in its illustrated position, the connecting line 24 to the connecting line 14, so that the two control pressure lines 15 and 16 are acted upon by the branch 21 to the system pressure. In its second, not shown in the figures position, the pilot valve 11 connects the connecting line 14 to the tank, so that the two control pressure lines 15 and 16 are relieved in the tank.
- the cooling device 36 is followed by a filter device 38.
- the minimum cooling pressure valve 40 is designed as a 2/2-way proportional valve. By a spring, the valve 40 is biased in its illustrated closed position. At the first connection of the valve 40, the connecting line 34 is connected, via which the valve 40 is connectable to the pump inlet. Connected to the second connection of the valve 40 is a connecting line 46, which is connected via a branch 47 and a connecting line 48 to a connecting line 50.
- connection line 50 connects the output of the filter 38 to a connection of the cooling pressure regulator 41. From the connection line 50, there is another connection line 51, which is connected to a connection of the cooling pressure regulator 42. To the other terminals of the cooling pressure regulator 41, 42 are via connecting lines 53 and 54 the Coupling cooling means 43 and 44, preferably in the form of jet pumps, connected.
- the parking lock can be unlocked.
- the parking lock unlocking valve VPbw is energized.
- the system pressure also builds up behind the parking lock release valve Vpbw and the valve goes into hydraulic self-holding.
- the parking brake remains set. In this switching state, the energization of the Parksperrenentriegelungsventils VPbw could be withdrawn, the parking brake would still remain in latching.
- the magnet of the parking lock release valve VPbw must no longer be energized, and furthermore the system pressure control valve VpSys must be switched to tank, in this case fully energized.
- the supply and discharge flow rates in the control circuit can be designed so that the control pressure at the parking lock unlocking valve VPbw collapses when the system pressure regulating valve VpSys is in the tank.
- the sub-circuit 20 of the circuit diagram 1 shows a clutch cooling circuit. As soon as the system pressure regulating valve Vsys regulates the volume flow from the system pressure circuit, the clutch cooling circuit 20 is filled. As long as no cooling is switched on, the minimum pressure valve VMD sets a low pressure in the clutch cooling circuit.
- the magnet of the respective clutch cooling valve VKU1 or VKU2 is energized.
- the respective pressure control valve then opens and delivers on the low pressure level set by the minimum pressure valve VMD a flow into the channel to a corresponding jet pump (clutch cooling 1, clutch cooling 2).
- Both channels to the jet pumps are returned to the minimum pressure valve VMD.
- the thereby applied to the minimum pressure valve VMD oil pressure acts in the same direction as the spring force, which increases the bias of the slider in the minimum pressure valve VMD. This in turn has the consequence that the Abregeltik the minimum pressure valve VMD shifts to higher pressures.
- the pressure in the clutch cooling circuit 20 is raised so far that the volume flow of the clutch cooling valves VKU1 or VKU2 promotes at the respective jet pump as a propulsion jet an additional volume flow for the clutch cooling.
- FIG 2 an alternative solution for a "park-by-wire" circuit is illustrated only as a subcircuit 110.
- Like or similar parts are designated by the same reference numerals as in Figures 1 and 1A
- opening and closing of the return passage to parking lock unlocking valve VPbw is done by means of one kind Pressure relief valve 5 with piston, spring and superior ball.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Gear-Shifting Mechanisms (AREA)
- Control Of Transmission Device (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112011103688T DE112011103688A5 (de) | 2010-11-04 | 2011-10-04 | Hydraulische Steuerung für ein automatisches Getriebe |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102010050218 | 2010-11-04 | ||
DE102010050218.9 | 2010-11-04 | ||
DE102011105023.3 | 2011-06-20 | ||
DE102011105023 | 2011-06-20 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2012062259A1 true WO2012062259A1 (de) | 2012-05-18 |
Family
ID=45023462
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2011/001790 WO2012062259A1 (de) | 2010-11-04 | 2011-10-04 | Hydraulische steuerung für ein automatisches getriebe |
Country Status (2)
Country | Link |
---|---|
DE (2) | DE102011083963A1 (de) |
WO (1) | WO2012062259A1 (de) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10408347B2 (en) | 2017-10-20 | 2019-09-10 | Ford Global Technologies, Llc | Transmission park control system |
US10697541B2 (en) | 2017-10-20 | 2020-06-30 | Ford Global Technologies, Llc | Transmission park control system |
US11073207B2 (en) | 2016-04-19 | 2021-07-27 | Zf Friedrichshafen Ag | Method for operating a parking lock device by means of a hydraulic system |
US11585436B2 (en) * | 2017-04-18 | 2023-02-21 | Punch Powertrain Psa E-Transmissions Nv | Hydraulic system for a vehicle, a vehicle transmission, and method for operating a vehicle transmission |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013223613A1 (de) * | 2013-11-20 | 2015-05-21 | Zf Friedrichshafen Ag | Parksperrensystem für ein Kraftfahrzeuggetriebe |
EP3012488A1 (de) * | 2014-10-20 | 2016-04-27 | Transmisiones y Equipos Mecánicos, S.A. de C.V. | Getriebe mit Strahlpumpe |
DE102021213980A1 (de) | 2021-12-08 | 2023-06-15 | Zf Friedrichshafen Ag | Hydrauliksystem eines Automatikgetriebes, insbesondere eines Automatikgetriebes einer elektrischen Fahrzeugachse, Automatikgetriebe mit einem Hydrauliksystem und elektrische Fahrzeugachse |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10032680C1 (de) * | 2000-07-05 | 2001-10-25 | Daimler Chrysler Ag | Automatikgetriebe mit einer Steuervorrichtung zur Auswahl einer Getriebefahrstufe |
DE102004033362A1 (de) * | 2004-07-02 | 2006-01-26 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Hydraulikkreis für ein Doppelkupplungsgetriebe |
-
2011
- 2011-10-04 WO PCT/DE2011/001790 patent/WO2012062259A1/de active Application Filing
- 2011-10-04 DE DE201110083963 patent/DE102011083963A1/de not_active Withdrawn
- 2011-10-04 DE DE112011103688T patent/DE112011103688A5/de not_active Withdrawn
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10032680C1 (de) * | 2000-07-05 | 2001-10-25 | Daimler Chrysler Ag | Automatikgetriebe mit einer Steuervorrichtung zur Auswahl einer Getriebefahrstufe |
DE102004033362A1 (de) * | 2004-07-02 | 2006-01-26 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Hydraulikkreis für ein Doppelkupplungsgetriebe |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11073207B2 (en) | 2016-04-19 | 2021-07-27 | Zf Friedrichshafen Ag | Method for operating a parking lock device by means of a hydraulic system |
US11585436B2 (en) * | 2017-04-18 | 2023-02-21 | Punch Powertrain Psa E-Transmissions Nv | Hydraulic system for a vehicle, a vehicle transmission, and method for operating a vehicle transmission |
US10408347B2 (en) | 2017-10-20 | 2019-09-10 | Ford Global Technologies, Llc | Transmission park control system |
US10697541B2 (en) | 2017-10-20 | 2020-06-30 | Ford Global Technologies, Llc | Transmission park control system |
Also Published As
Publication number | Publication date |
---|---|
DE112011103688A5 (de) | 2013-08-01 |
DE102011083963A1 (de) | 2012-05-10 |
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