US20140169994A1 - Dual clutch transmission - Google Patents

Dual clutch transmission Download PDF

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Publication number
US20140169994A1
US20140169994A1 US14/115,721 US201214115721A US2014169994A1 US 20140169994 A1 US20140169994 A1 US 20140169994A1 US 201214115721 A US201214115721 A US 201214115721A US 2014169994 A1 US2014169994 A1 US 2014169994A1
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United States
Prior art keywords
switching position
valve
conduit
switching
control valve
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Abandoned
Application number
US14/115,721
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English (en)
Inventor
Dietmar Schuller
Stefan Ammler
Stephan Herold
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Audi AG
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Audi AG
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Assigned to AUDI AG reassignment AUDI AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AMMLER, STEFAN, HEROLD, STEPHAN, Schuller, Dietmar
Publication of US20140169994A1 publication Critical patent/US20140169994A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D48/0206—Control by fluid pressure in a system with a plurality of fluid-actuated clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
    • F16H57/0435—Pressure control for supplying lubricant; Circuits or valves therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • F16H61/0025—Supply of control fluid; Pumps therefore
    • F16H61/0031—Supply of control fluid; Pumps therefore using auxiliary pumps, e.g. pump driven by a different power source than the engine
    • 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
    • F16H61/02—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 characterised by the signals used
    • F16H61/0202—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 characterised by the signals used the signals being electric
    • F16H61/0204—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 characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
    • F16H61/0206—Layout of electro-hydraulic control circuits, e.g. arrangement of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/68—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings
    • F16H61/684—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive
    • F16H61/688—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive with two inputs, e.g. selection of one of two torque-flow paths by clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0227—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices
    • F16D2048/0233—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices by rotary pump actuation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
    • F16D2048/0278—Two valves in series arrangement for controlling supply to actuation cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
    • F16D2048/0287—Hydraulic circuits combining clutch actuation and other hydraulic systems
    • F16D2048/029—Hydraulic circuits combining clutch actuation with clutch lubrication or cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
    • F16D2048/0287—Hydraulic circuits combining clutch actuation and other hydraulic systems
    • F16D2048/0293—Hydraulic circuits combining clutch and transmission actuation
    • 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
    • F16H2061/0037—Generation or control of line pressure characterised by controlled fluid supply to lubrication circuits of the gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0473—Friction devices, e.g. clutches or brakes
    • 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
    • F16H61/02—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 characterised by the signals used
    • F16H61/0262—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 characterised by the signals used the signals being hydraulic
    • F16H61/0265—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 characterised by the signals used the signals being hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals
    • F16H61/0267—Layout of hydraulic control circuits, e.g. arrangement of valves

Definitions

  • the invention relates to a dual clutch transmission, in particular of a motor vehicle, in particular with a hydraulic circuit for cooling the dual clutch transmission, wherein the hydraulic circuit includes at least one pump for conveying a hydraulic medium flow, at least one cooler for cooling the hydraulic medium flow, and a volume control valve for adjusting the hydraulic medium flow for at least one cooling system associated with clutches of the dual clutch transmission.
  • Dual clutch transmissions are preferably used in passenger cars.
  • a dual clutch transmission generally includes two coaxially disposed transmission input shafts, which are each associated with a sub-transmission.
  • a respective clutch is associated with each of the transmission input shafts, via which the transmission input shaft of the respective sub-transmission can be frictionally coupled to the output of an engine, preferably an internal combustion engine of a motor vehicle.
  • a first of the two sub-transmissions typically includes the odd gears, whereas a second of the two sub-transmissions includes the even gears and the reverse gear.
  • one of the sub-transmissions is active while driving, which means that the transmission input shaft associated with this sub-transmission is coupled to the engine via its associated clutch.
  • a gear providing a current gear ratio is engaged in the active sub-transmission.
  • a controller determines whether the next higher or next lower gear is to be engaged depending on the driving situation. This gear which is probably used next is selected in the second, inactive sub-transmission.
  • the clutch of the inactive sub-transmission is engaged, while the clutch of the active portion is disengaged.
  • opening of the clutch of the active sub-transmission and closing the clutch of the inactive sub-transmission overlap so that the flow of force from the engine to the drive shaft of the motor vehicle is not at all or only briefly interrupted.
  • the gear expected to be used next can be engaged in the now inactive sub-transmission.
  • the gears are engaged and disengaged via elements, preferably via the shift rails that are actuated by hydraulic cylinders, i.e. the aforementioned switching cylinders, which have already been mentioned above.
  • the hydraulic cylinders are preferably formed as double-acting hydraulic cylinders, in particular synchronous cylinders or differential cylinders, so that preferably two gears may be associated with each switching cylinder. Alternatively, single-acting hydraulic cylinders may also be provided.
  • the hydraulic cylinders operating the elements, in particular the shift rails are also referred to as gear selector cylinders.
  • a gear selector cylinder designed as a synchronous cylinder to which in particular two gears are assigned, has preferably three switching positions, wherein in a first switching position a first defined gear is engaged, in a second switching position another defined gear is engaged, and in a third switching position none of the two above-mentioned gears is engaged.
  • the clutches associated with the two sub-transmissions are also hydraulically actuated, i.e. closed or opened.
  • the clutches each close when hydraulic pressure is applied, whereas they open when no hydraulic pressure is applied, i.e. when pressure is relieved in a hydraulic cylinder associated with the respective clutch which is also referred to as clutch cylinder, as mentioned above.
  • Cooling of the clutches is typically attained with a fixed displacement pump driven by an internal combustion engine. At least one control or control valve is used for adequately cooling the clutch. The accuracy of the flow rate used for cooling the clutch strongly depends on the employed control or control valve.
  • the hydraulic medium conveyed by the pump is cooled by a cooler and then supplied to a cooling system associated with the clutches, so that only a single volume flow rate of the cooling medium is provided to both clutches. The common cooling of the clutches thereby worsens the control performance of couplings.
  • EP 1637756 A1 discloses a system where a volume control valve is connected upstream of the clutches, which supplies in a first switching position a lubricant to one clutch and a coolant to the other clutch, and supplies in another switching position a lubricant to one clutch and a coolant to the other clutch.
  • supplying coolant to the clutches depends here always on the lubrication of couplings, so that neither the clutch cooling nor the lubrication can be optimized.
  • volume control valves must be calibrated to allow a control command to cause a corresponding state of the volume control valve or a desired distribution/release of one or more hydraulic medium flows.
  • the switching position especially of solenoid valves is determined by a current command, wherein the position and hence the quantity of hydraulic medium is adjusted depending on the magnitude of the current command.
  • the calibration of such volume control valves is complicated and correspondingly expensive.
  • the volume control valve is constructed as a switching valve having at least two switching position ranges, wherein the hydraulic medium flow is conveyed in a first switching position range with a constant flow cross-section to a cooling system associated with a first of the clutches and in a second switching position range with a constant flow cross-section to a second cooling system associated with a second of the clutches, wherein the total switching range of the switching valve or volume control valve is substantially formed by the switching position ranges and only a narrow transition region between neighboring shift position ranges is provided.
  • the switching position ranges with a constant flow cross-section refer to a respective actuation travel of the switching valve, within which the control valve can be actuated/adjusted without causing the volume flow or a set flow cross-section to change.
  • the switching valve can be switched into the respective switching position range without changing the switching state with respect to the set fluid connection.
  • the total switching position range represents here the range over which the control valve is overall adjustable.
  • the overall switching position range is divided into the switching position ranges and the respective transition region located between adjacent switching position ranges. According to the invention, the transition region is rather narrow, so that the switching position ranges form substantially the entire switching range, so that the available switching position ranges within which the flow of the hydraulic medium is not affected by actuation of the switching valve are as large as possible.
  • the wide switching position ranges ensure that the desired switching position of the switching valve can be attained even when setting a control signal having tolerances and when the switching valve has production-related tolerances.
  • the shifting position ranges are then guaranteed to be greater than the expected tolerances. Because the switching valve is unable to individually adjust the respective flow volume and instead is only intended to open and close a connection, so that there is ultimately a digital operation, a safe operation of the dual clutch transmission is thus guaranteed in a particularly simple and cost-effective manner even without prior calibration of the flow control valve.
  • the transition region is designed to be so narrow that an almost constant flow cross-section is attained over the entire switching position range of the switching valve. This prevents backpressure spikes in a switchover.
  • Adjustment or actuation of the switching valve always refers to actuating or displacing a movable valve element of the switching valve, which cooperates for example with one or more flow-through openings in a stationary housing to open one or more flow cross-sections.
  • a movable valve element of the switching valve which cooperates for example with one or more flow-through openings in a stationary housing to open one or more flow cross-sections.
  • a gate valve or rotary vane valve is actuating or displacing a movable valve element of the switching valve.
  • the switching valve is designed as a 4/3-way switching valve or as a 3/2-way switching valve.
  • the 3/2-way proportional valve has three ports and two switching position ranges with a narrow transition, wherein a first port is connected to the pressure side of the pump, a second port is connected to the first cooling system, and a third port is connected to the second cooling system.
  • the 4/3-way switching valve has at least one additional port, and an additional third switching position range, wherein the additional port is connected to a return conduit leading to a tank providing the hydraulic medium.
  • the switching valve embodied as a 4/3-way switching valve conveys the hydraulic medium flow in a third shifting position range to a tank providing the hydraulic medium.
  • the volume control valve is disposed downstream of the cooler, the hydraulic medium can be cooled and returned to the tank by switching the switching valve into its third shifting position range, thereby generating a small cooling circuit for cooling the hydraulic medium residing in the tank.
  • the volume control valve and the switching valve can be controlled by an electric motor and/or electromagnetically.
  • an electric motor and/or an electromagnetic actuator is advantageously associated with the volume control valve, which can then be brought quickly and accurately to the desired shifting position range. Due to the advantageous embodiment of the switching valve with shifting position ranges having a constant flow cross section, wide flow ranges are available within which the switching valve can be brought into the desired switching position. The wide distribution of the current ranges eliminates the need for calibration, since the flow ranges are for switching the positions or position ranges are greater than the expected tolerances.
  • the pump is operatively connected to an in particular variable-speed electric motor.
  • the design of the volume control valve as a switching valve initially eliminates the possibility to affect the quantity of the hydraulic medium flow.
  • the capacity of the pump and hence the flow volume and the resulting quantity of the conveyed hydraulic medium can be adjusted so that preferably the electric motor is controlled for influencing the quantity of the hydraulic medium flow, wherein in particular the speed of the electric motor is controlled or regulated accordingly.
  • a manually operable separation element is interposed between the pump and the electric motor.
  • the drive shaft of the pump is or can be operatively connected to an output shaft of the drive or of the electric motor by way of the separating element.
  • the separating element is preferably an actuatable clutch or an overrunning clutch. The pump can then be switched off by actuating the clutch or by changing the direction of rotation, so as to interrupt transport of the hydraulic medium.
  • the second switching position range may be located between the first switching position range and the third switching position range.
  • the switching position ranges assigned to the cooling systems are then adjacent to each other, so that the cooling systems can be supplied quasi simultaneously with hydraulic medium by pulsed control of the switching valve.
  • the third switching position range is located between the first switching position range and the second switching position range. This prevents hydraulic medium from flowing to the other cooling system during pulsed actuation of the switching valve for setting a desired hydraulic medium flow for only one of the clutches or cooling systems. Instead, during pulsed control, the hydraulic medium flow that is not conveyed to the respective cooling system is transported into the tank.
  • the quantity of the hydraulic medium conveyed to the first and/or second cooling system is preferably determined by a pulsed control of the switching valve and/or by adjusting the rotation speed of the electric motor.
  • FIG. 1 shows a hydraulic circuit 1 which is used to actuate, in particular to couple and engage and disengaging gears of a dual clutch transmission and to cool the transmission.
  • the hydraulic circuit 1 includes a tank 3 , serving in particular as a reservoir or sump for a hydraulic medium used for operation and cooling, in which the hydraulic medium is preferably stored without pressure.
  • An electric motor 5 driving a first pump 7 and a second pump 9 is provided.
  • the speed and rotation direction of the electric motor 5 can be controlled, preferably regulated.
  • the first pump 7 is fixedly connected to the electric motor 5 , i.e. without a separation element. In other words, the pump 7 is always driven when the electric motor 5 is running and the hydraulic medium is preferably conveyed in the same direction in the both rotation directions.
  • the pump 9 is preferably connected to the electric motor 5 by way of a separating element 11 . Accordingly, the pump 9 can be decoupled from the electric motor 5 , so that the pump 9 is not running when the electric motor 5 is running.
  • the separation element 11 is preferably formed as a clutch or an overrunning clutch, wherein in the second situation the direction of rotation of the electric motor 5 determines whether hydraulic medium is conveyed by the pump 9 or not.
  • the first pump 7 and the second pump 9 are each connected via a corresponding conduit 13 , 15 to a junction 17 into which an additional conduit 19 opens.
  • This additional conduit 19 connects the tank 3 to the junction 17 through a suction filter 21 .
  • inlets of the pump 7 , 9 are thus connected to the tank 3 via the conduits 13 , 15 , the junction 17 and the conduit 19 having the suction filter 21 .
  • the outlet of the first pump 7 is connected to a conduit 23 which leads to a junction 25 .
  • the junction 25 is connected to the tank 3 via a pressure relief valve 27 .
  • the pressure relief valve 27 can open under overpressure in the direction of the tank 3 .
  • a conduit 29 which leads via a pressure filter 31 to a port 33 of a switching valve 35 , originates from the junction 25 .
  • the pressure filter 31 may be bypassed by a bypass 37 , wherein a differential pressure valve 39 is arranged in the bypass 37 , which allows bypassing the filter 31 in the direction of the port 33 under overpressure.
  • the differential pressure valve 39 opens starting at a preset differential pressure across the pressure filter 31 .
  • the switching valve 35 is embodied as a 5/2-way valve, which has four additional ports 41 , 43 , 45 , 47 in addition to the port 33 .
  • the port 33 is connected to the port 41 , whereas the other ports 43 , 45 and 47 are connected blind, i.e. they are closed.
  • the port 41 opens into a conduit 49 in which a check valve is disposed 51 .
  • the conduit 49 leads to a pressure accumulator 53 , wherein a pressure sensing device 55 is hydraulically connected to the conduit 49 upstream of the pressure accumulator 53 .
  • a second switching state of the switching valve 35 illustrated in FIG. 1 the port 33 is connected to the port 43 which opens into a conduit 57 that leads to a hydraulic sub-circuit 59 which is used, in particular, to cool the clutches of the dual clutch transmission.
  • the port 41 is connected blind, and the port 45 is connected to the port 47 .
  • a conduit 61 opens into the port 45 which is subjected to the pressure of the hydraulic medium in the pressure accumulator 53 .
  • the port 47 opens into a conduit 63 which is hydraulically connected to a first valve face 65 of the switching valve 35 .
  • a second valve face 67 of the switching valve 35 is permanently subjected to the pressure of the pressure accumulator 53 via a conduit 69 .
  • a conduit 73 branches off from the conduit 49 at a junction 71 , from which the conduit 61 branches off at a junction 75 , and the conduit 69 branches off at a junction 77 .
  • the junction 71 is connected to the check valve 51 on the side facing away from the switching valve 35 .
  • the conduit 73 opens into a junction 79 , from which the conduits 81 , 83 and 85 originate.
  • the conduit 81 supplies a first sub-transmission in a sub-transmission circuit 87 .
  • the first sub-transmission has a clutch K 1 .
  • the conduit 81 opens into a port 89 of a switching valve 91 which is constructed as a 3/2-way valve and serves as a safety valve for the clutch K 1 .
  • the port 89 is hydraulically connected to a port 93 , while a port 95 of the switching valve 91 is switched blind.
  • the port 93 is connected to the port 95 and via the latter to the tank 3 , while the port 89 is connected blind.
  • the clutch K 1 is switched unpressurized in this second switching state.
  • the port 93 is connected to a conduit 97 and via the latter to a port 99 of a pressure control valve 101 .
  • the pressure control valve 101 is designed as 3/2-way proportional valve having a port 103 which is connected via a conduit 105 to the clutch K 1 .
  • the pressure control valve 101 additionally has a port 107 that is connected to the tank 3 .
  • the port 99 is connected to the port 103 , while the port 107 is connected blind.
  • the full pressure prevailing in the conduit 97 of the hydraulic medium is then applied to the clutch K 1 .
  • the port 103 is connected to the port 107 so that the clutch K 1 is unpressurized.
  • the pressure control valve 101 regulates the pressure prevailing in the clutch K 1 in a conventional manner through proportional variation between these extreme states.
  • a conduit 109 leads from the clutch K 1 via a check valve 111 back to the conduit 97 . If the pressure in the clutch K 1 rises due to the pressure in the conduit 97 , the check valve 111 opens, thereby opening a hydraulic connection between the clutch K 1 to the conduit 97 via the conduit 109 .
  • a conduit 115 branches off from the conduit 109 at a junction 113 which returns the pressure in the clutch K 1 as a control variable to the pressure control valve 101 .
  • the conduit 105 includes a junction 117 for hydraulically operatively connecting a pressure detecting device 119 .
  • the pressure prevailing in the clutch K 1 is thereby detected by the pressure detecting device 119 .
  • the switching valve 91 is controlled by a pilot valve 121 which is actuated by an electric actuator 123 . It is formed as a 3/2-way valve and includes the ports 125 , 127 and 129 .
  • the port 125 is connected via a conduit 131 to a junction 133 provided in the conduit 81 .
  • the port 127 is connected by a conduit 135 to a valve face 137 of the switching valve 91 .
  • the port 125 is switched blind while the port 127 is connected to the port 129 and via the latter to the tank 3 , whereby the valve face 137 of the switching valve 91 is switched unpressurized via conduit 135 .
  • the pilot valve 121 assumes this switching state when no electric control signal is applied to the actuator 123 .
  • the port 125 is connected to the port 127 while the port 129 is connected blind.
  • the pressure in the conduit 81 operates on the valve face 137 of the switching valve 91 via the junction 133 , the conduit 131 and the conduit 135 , causing the switching valve 91 to switch against a biasing force into its second switching state where the port 93 is hydraulically connected to the port 95 , so that the clutch K 1 is unpressurized.
  • the switching valve 91 can preferably be operated by way of electrical control of the pilot valve 121 , so that the clutch K 1 is unpressurized and hence open.
  • the conduit 83 originating at the junction 79 is used to supply a clutch K 2 of a hydraulic sub-circuit 139 of a second sub-transmission.
  • Control of the clutch K 2 also includes a switching valve 91 ′, a pilot valve 121 ′, and a pressure control valve 101 ′.
  • the operation is identical to the operation already described in conjunction with the first clutch K 1 . Reference is therefore made to the corresponding description of the sub-transmission circuit 87 .
  • the hydraulic actuation of the clutch K 2 corresponds to that of the clutch K 1 .
  • the conduit 85 originating at the junction 79 is connected to a pressure control valve 141 , via which the pressure of the hydraulic medium in a conduit 143 can be controlled.
  • the operation of the pressure control valve 141 preferably corresponds to the operation of the pressure control valves 101 , 101 ′, thus making repeating the description unnecessary.
  • the conduit 143 is connected to a junction 145 , from which a conduit 147 and a conduit 149 originate.
  • a junction 151 at which a conduit 153 originates is provided in the conduit 149 , via which the pressure prevailing in the conduit 149 and thus also in the conduit 143 is returned to the pressure control valve 141 as a control variable, It is apparent that the junction 151 may also be provided in the conduits 151 or 147 .
  • the conduit 147 is used to supply gear actuator cylinders 155 and 157 in the sub-transmission circuit 87 , which are constructed as two double-acting cylinders, i.e. synchronizing cylinders.
  • a volume control valve 159 is provided for hydraulic actuation of the gear actuating cylinder 155 , which is designed as a 4/3-way proportional valve. It has four ports 161 , 163 , 165 and 167 .
  • the first port 161 is connected to the conduit 147
  • the second port 163 is connected to a first chamber 169 of the gear actuating cylinder 155
  • the third port 165 is connected to a second chamber 171 of the gear actuating cylinder 155
  • the fourth port 167 is connected to the tank 3 .
  • the first port 161 is connected to the second port 163
  • the third port 165 is connected to the fourth port 167 .
  • the hydraulic medium can then flow from the conduit 147 into the first chamber 169 of the gear actuating cylinder 155 , while the second chamber 171 is connected via the ports 165 , 167 to the tank 3 without an applied pressure.
  • a piston 173 of the gear actuating cylinder 155 is then moved in a first direction, for example for disengaging a specific gear of the dual clutch transmission or for engaging another specific gear.
  • both the port 163 and the port 165 are connected to the port 167 , while the port 161 is connected blind, In this way, both chambers 169 , 171 of the gear actuating cylinder 155 are connected to the tank 3 and unpressurized.
  • the piston 173 of the gear actuating cylinder 155 then remains in its current position due to the absence of forces.
  • the port 161 is connected to the port 165 and the port 163 is connected to the port 167 .
  • Hydraulic medium then flows from the conduit 147 into the second chamber 171 of the gear actuating cylinder 155 , and the first cylinder chamber 169 is unpressurized in relation to the tank 3 via port 163 and the port 167 .
  • the hydraulic medium then exerts a force on the piston 173 of the gear actuating cylinder 155 such that the piston 173 is displaced in a second direction opposite to the first direction. In this way, the aforementioned specified other gear can be disengaged, or the aforementioned specified gear can be engaged.
  • the volume control valve 159 is designed as a proportional valve.
  • the hydraulic medium flow coming from the conduit 147 is divided into the chambers 169 , 171 by varying the valve states between the three extreme states, so that a defined speed for engaging or disengaging a gear can be specified by controlling/regulating the volume flow.
  • a conduit 177 which opens into a volume control valve 179 used to control the gear actuating cylinder 157 branches off from the conduit 147 at a junction 175 .
  • the operation of the hydraulic control of the gear actuating cylinder 157 is then identical to that described in conjunction with the gear actuating cylinder 155 , making a renewed description unnecessary.
  • the conduit 149 is used to supply gear actuating cylinders 155 ′ and 157 ′ of the second sub-transmission in the sub-transmission circuit 139 , which are also controlled by volume control valves 159 ′ and 179 ′.
  • the sub-transmission circuits 87 and 139 for controlling the gear actuating cylinders 155 , 155 ′ and 157 , 157 ′, respectively, are constructed identically, so reference is made to the preceding description.
  • the outlet of the pump 9 is connected to a conduit 181 which leads to the hydraulic sub-circuit 59 which is preferably used in particular for cooling the clutches K 1 , K 2 .
  • the conduit 181 runs via a cooler 183 to a volume control valve 185 .
  • a junction 187 is arranged in the conduit 181 downstream of the outlet of the pump 9 and upstream of the cooler 183 , from which a conduit 189 branches off, with the conduit 189 leading to the tank 3 via a pressure relief valve 191 opening toward the tank 3 .
  • a junction 193 into which the conduit 57 opens is arranged downstream of the junction 187 and upstream of the cooler 193 , with the conduit 57 coming from the switching valve 35 and being connected to its port 43 .
  • the hydraulic sub-circuit 59 can be supplied via the conduit 57 with hydraulic medium conveyed by the pump 7 , when the switching valve 35 is in its second switching state. Furthermore, a bypass 195 branches off from the junction 193 which has a differential pressure valve 197 and arranged parallel to the cooler 183 . The differential pressure valve 197 opens the bypass in the direction of the volume control valve 185 under overpressure. The cooler 183 can thus be bypassed.
  • the volume control valve 185 is designed as 4/3-way switching valve having ports 199 , 201 , 203 , 205 and 207 .
  • the port 199 is connected to the conduit 181 via the cooler 183 and the differential pressure valve 197 , respectively, as is the port 201 which is connected to the conduit 181 via a conduit 209 and a junction 211 .
  • the ports 199 and 201 thus form a common port of the flow control valve 185 because they are both connected to the conduit 181 downstream of the cooler 183 .
  • Two ports 199 , 201 are shown only for sake of clarity; in actuality, only a single port, for example 199 or 201 , is provided for the conduit 181 on the volume control valve 185 , wherein according to an alternative embodiment, the volume control valve 185 may in fact be formed as 5/3-way switching valve with the two separate ports 199 , 201 .
  • the port 203 is connected to a conduit 213 which leads via a pressure filter 215 to the tank 3 .
  • the pressure filter 215 can be bypassed by a bypass 217 with a differential pressure valve 219 that opens in the direction of the tank 3 .
  • the port 205 of the volume control valve 185 is connected to a cooling system 221 particularly for the first clutch K 1 .
  • the port 207 is connected to a second cooling system 223 particularly for the second clutch K 2 .
  • the ports of the switching valve are constructed so as to form a plurality of switching position ranges within which the respective unobstructed flow cross section does not change.
  • a constant flow cross-section therefore exists in each of the switching position ranges, so that no change occurs at the ports 199 , 201 , 203 , 205 and 207 when the switching valve is actuated in the respective switching position range.
  • the transitions between adjacent switching position ranges are narrow, in particular compared to the width of the switching position ranges, so that the largest possible switching position ranges are formed in relation to the total switching range of the switching valve.
  • the flow cross-section is preferably nearly constant over the entire switching control range.
  • the port 201 is connected to the port 203 while the ports 199 , 205 and 207 are connected blind.
  • the total hydraulic medium flow flowing in the hydraulic conduit 181 and through the cooler 183 , respectively, is hence conveyed via the port 201 , 203 into conduit 213 and thus into the tank 3 via the pressure filter 215 .
  • the ports 199 and 205 are connected to each other, while the ports 201 , 203 and 207 are connected blind.
  • the entire hydraulic medium flow arriving at the volume control valve 185 is supplied to the first cooling system 221 .
  • a third switching position range of the volume control valve 185 In a third switching position range of the volume control valve 185 , the ports 199 and 207 connected together. The ports 201 , 203 and 205 are connected blind. In this state or in every switching position of the volume control valve 185 within the third switching position range, the entire hydraulic medium flow flowing in the conduit 181 is then supplied to the second cooling system 223 .
  • the volume control valve 185 is designed as a switching valve, so that no intermediate states can be set which would enable control of the volume flow to the cooling systems 221 , 223 or to the pressure filter 215 .
  • the volume control valve 185 may be operated in pulsed mode by fast switching back and forth, i.e. a pulsed operation of the volume control valve 185 , wherein at least one switching position within one of the three switching position ranges can be assumed for a short time.
  • the time-averaged volume flow is then also controlled or regulated in this mode of operation, which is supplied to the cooling systems 221 , 223 or the pressure filter 215 and hence to the tank 3 .
  • FIG. 1 shows that additionally a hydraulic medium flow of the conduit 57 may replace the hydraulic medium flow in the conduit 181 and be supplied to the hydraulic sub-circuit 59 .
  • the conduit 57 may convey hydraulic medium.
  • the proportional valves 101 , 101 ′, 141 , 159 , 159 ′, 179 , 179 ′ are each electrically proportionally adjustable particularly against a spring force.
  • the conduit 57 opens into the hydraulic sub-circuit 59 , more precisely into the conduit 181 downstream of the pump 9 .
  • the conduit 57 opens into the conduit 181 preferably downstream of the cooler 183 .
  • the total flow rate through the cooler 183 is reduced by supplying the hydraulic medium from the high pressure circuit into the hydraulic sub-circuit 59 according to the alternative embodiment.
  • the pressure drop across the cooler 183 is reduced due to the reduced volume flow, thereby also reducing the necessary drive power for the pumps 7 and/or 9 .
  • the drive energy required for driving the electric motor 5 is likewise reduced by reducing the backpressures.
  • the pump 9 can be connected directly to the electric motor 5 with a sufficiently large reduction of the backpressures or of the pressure level—irrespective of how this reduction is achieved—, i.e. the clutch 11 can be eliminated.
  • the pressure filter 215 is arranged in the conduit 213 not between the volume control valve 185 and the tank 3 , but preferably in the conduit 181 , in particular between the cooler 183 and the volume control valve 185 .
  • the conduit 57 opens into conduit 181 downstream of the pressure filter 215 .
  • the switching position ranges are interchanged such that in the first switching position range the ports 199 and/or 201 are connected to the port 205 or 207 while the other ports of the volume control valve 185 are connected blind, in the second switching position range the connections 201 and/or 199 are connected to the port 3 while the other ports are connected blind, and in the third switching position range the ports 199 and/or 201 are connected to the port 207 or 205 while the remaining ports are connected blind.
  • Interchanging the switching positions prevents, when using pulsed control for the volume control valve 185 for setting a desired hydraulic medium flow for one of the cooling systems 221 and 223 , respectively, the hydraulic medium from flowing also to the other cooling system 223 or 221 . Instead, the volume flow that is not conveyed to the respective cooling system 221 or 223 under pulsed operation is directed into the tank 3 .
  • the ports 199 and 201 are always to be understood as a common or sole port for the conduit 181 to the volume control valve 185 , so that in fact only one of the two ports 199 , 201 is provided on the volume control valve 185 .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Transmission Device (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
US14/115,721 2011-05-06 2012-04-30 Dual clutch transmission Abandoned US20140169994A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102011100849A DE102011100849A1 (de) 2011-05-06 2011-05-06 Doppelkupplungsgetriebe
DE102011100849.0 2011-05-06
PCT/EP2012/001851 WO2012152397A1 (fr) 2011-05-06 2012-04-30 Boîte de vitesses à double embrayage

Publications (1)

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US20140169994A1 true US20140169994A1 (en) 2014-06-19

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ID=46052703

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US14/115,721 Abandoned US20140169994A1 (en) 2011-05-06 2012-04-30 Dual clutch transmission

Country Status (5)

Country Link
US (1) US20140169994A1 (fr)
EP (1) EP2705277B1 (fr)
CN (1) CN103518081B (fr)
DE (1) DE102011100849A1 (fr)
WO (1) WO2012152397A1 (fr)

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US20160123456A1 (en) * 2014-10-31 2016-05-05 Airbus Helicopters Triple circuit lubrication device with increased reliability for a main power transmission gearbox of an aircraft
CN108626366A (zh) * 2017-03-24 2018-10-09 博格华纳公司 用于自动变速器的包括三通电磁致动阀的冷却和润滑系统
US10184561B2 (en) 2014-04-25 2019-01-22 Zf Friedrichshafen Ag Transmission device having a hydraulic system
WO2019129367A1 (fr) * 2017-12-29 2019-07-04 Volvo Truck Corporation Circuit de fluide et procédé de commande d'un flux de fluide fourni à au moins un équipement
US10815866B2 (en) 2016-03-03 2020-10-27 Audi Ag Method for ascertaining behavior of a valve installed in a vehicle, and vehicle
US11255423B2 (en) * 2017-03-29 2022-02-22 Great Wall Motor Company Limited Dual-clutch automatic transmission cooling and lubrication hydraulic control system and vehicle
US11401981B2 (en) * 2017-05-11 2022-08-02 Schaeffler Technologies AG & Co. KG Switching unit for cooling oil, and hybrid module having a switching unit

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DE102012220742A1 (de) * 2012-11-14 2014-05-15 Zf Friedrichshafen Ag Anordnung zum Antrieb von Ölpumpen
DE102013222988A1 (de) * 2013-11-12 2015-05-13 Zf Friedrichshafen Ag Getriebevorrichtung mit mehreren Übersetzungen
US10047840B2 (en) * 2014-02-17 2018-08-14 Engineering Center Steyr Gmbh & Co Kg Dual-clutch transmission that can be shifted under full load
DE102014003083A1 (de) * 2014-03-01 2015-09-03 Audi Ag Verfahren zum Betreiben eines Hydrauliksystems eines Automatikgetriebes
DE102014207806B4 (de) 2014-04-25 2023-05-25 Zf Friedrichshafen Ag Hydraulische Betätigungsvorrichtung für ein Getriebe
WO2016131594A1 (fr) * 2015-02-19 2016-08-25 Audi Ag Boîte de vitesses à double embrayage pour véhicule à moteur
DE102015204816A1 (de) * 2015-03-17 2016-09-22 Zf Friedrichshafen Ag Getriebevorrichtung mit wenigstens einem fluidisch betätigbaren Schaltelement
WO2018055204A1 (fr) 2016-09-26 2018-03-29 Hofer Mechatronik Gmbh Circuit hydraulique d'une transmission à embrayage double, en particulier comprenant une commande d'embrayage, et procédé de réaction d'urgence
CN107435733B (zh) * 2017-05-24 2022-10-28 捷孚传动科技有限公司 换档液压控制系统及变速箱
DE102018007461A1 (de) * 2018-09-21 2020-03-26 Fte Automotive Gmbh Hydraulische Vorrichtung zum Kühlen von wenigstens zwei nasslaufenden Kupplungen in einem Kraftfahrzeug

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US20160123456A1 (en) * 2014-10-31 2016-05-05 Airbus Helicopters Triple circuit lubrication device with increased reliability for a main power transmission gearbox of an aircraft
US9829088B2 (en) * 2014-10-31 2017-11-28 Airbus Helicopters Triple circuit lubrication device with increased reliability for a main power transmission gearbox of an aircraft
US10815866B2 (en) 2016-03-03 2020-10-27 Audi Ag Method for ascertaining behavior of a valve installed in a vehicle, and vehicle
CN108626366A (zh) * 2017-03-24 2018-10-09 博格华纳公司 用于自动变速器的包括三通电磁致动阀的冷却和润滑系统
US10443707B2 (en) * 2017-03-24 2019-10-15 Borgwarner Inc. Cooling and lubrication system including 3-way solenoid-actuated valve for automatic transmission
US11255423B2 (en) * 2017-03-29 2022-02-22 Great Wall Motor Company Limited Dual-clutch automatic transmission cooling and lubrication hydraulic control system and vehicle
US11401981B2 (en) * 2017-05-11 2022-08-02 Schaeffler Technologies AG & Co. KG Switching unit for cooling oil, and hybrid module having a switching unit
WO2019129367A1 (fr) * 2017-12-29 2019-07-04 Volvo Truck Corporation Circuit de fluide et procédé de commande d'un flux de fluide fourni à au moins un équipement
CN111448371A (zh) * 2017-12-29 2020-07-24 沃尔沃卡车集团 流体回路和用于控制供应到至少一个设备的流体流的方法
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US11598230B2 (en) * 2017-12-29 2023-03-07 Volvo Truck Corporation Fluid circuit and a process for controlling a flow of fluid supplied to at least one equipment

Also Published As

Publication number Publication date
DE102011100849A8 (de) 2012-12-20
WO2012152397A1 (fr) 2012-11-15
CN103518081B (zh) 2016-03-16
EP2705277A1 (fr) 2014-03-12
CN103518081A (zh) 2014-01-15
DE102011100849A1 (de) 2012-11-08
EP2705277B1 (fr) 2015-09-16

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