WO2018046145A1 - Elektrohydraulisches system für die betätigung von kupplung(en) und gangsteller(n) von schaltgetrieben mit einer kolben-zylinder-einheit mit doppelhubkolben - Google Patents
Elektrohydraulisches system für die betätigung von kupplung(en) und gangsteller(n) von schaltgetrieben mit einer kolben-zylinder-einheit mit doppelhubkolben Download PDFInfo
- Publication number
- WO2018046145A1 WO2018046145A1 PCT/EP2017/054642 EP2017054642W WO2018046145A1 WO 2018046145 A1 WO2018046145 A1 WO 2018046145A1 EP 2017054642 W EP2017054642 W EP 2017054642W WO 2018046145 A1 WO2018046145 A1 WO 2018046145A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- hydraulic
- pressure
- clutch
- gearbox
- Prior art date
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Classifications
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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
- F16D48/00—External control of clutches
- F16D48/06—Control by electric or electronic means, e.g. of fluid pressure
- F16D48/066—Control of fluid pressure, e.g. using an accumulator
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- 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
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
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- 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
- F04B5/00—Machines or pumps with differential-surface pistons
- F04B5/02—Machines or pumps with differential-surface pistons with double-acting pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/20—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors controlling several interacting or sequentially-operating members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/14—Energy-recuperation means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
- F15B7/003—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors with multiple outputs
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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
- F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
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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
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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
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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
- F16D25/14—Fluid pressure control
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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
- F16D48/00—External control of clutches
- F16D48/06—Control by electric or electronic means, e.g. of fluid pressure
- F16D48/062—Control by electric or electronic means, e.g. of fluid pressure of a clutch system with a plurality of fluid actuated clutches
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
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- 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
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/2807—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted using electric control signals for shift actuators, e.g. electro-hydraulic control therefor
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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
- 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
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20507—Type of prime mover
- F15B2211/20515—Electric motor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20538—Type of pump constant capacity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/275—Control of the prime mover, e.g. hydraulic control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6306—Electronic controllers using input signals representing a pressure
- F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/633—Electronic controllers using input signals representing a state of the prime mover, e.g. torque or rotational speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/665—Methods of control using electronic components
- F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/665—Methods of control using electronic components
- F15B2211/6653—Pressure control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/88—Control measures for saving energy
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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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/104—Clutch
- F16D2500/10443—Clutch type
- F16D2500/1045—Friction clutch
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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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/11—Application
- F16D2500/1107—Vehicles
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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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/302—Signal inputs from the actuator
- F16D2500/3026—Stroke
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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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/70—Details about the implementation of the control system
- F16D2500/704—Output parameters from the control unit; Target parameters to be controlled
- F16D2500/70402—Actuator parameters
- F16D2500/70406—Pressure
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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
- 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
- F16H2061/1208—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures with diagnostic check cycles; Monitoring of failures
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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
- 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
- F16H2061/126—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 controller
- F16H2061/1264—Hydraulic parts of the controller, e.g. a sticking valve or clogged channel
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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
- 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
- F16H2063/025—Final output mechanisms for double clutch transmissions
Definitions
- Electrohydraulic system for the actuation of clutch (s) and gear (s) of manual transmissions with a piston-cylinder unit with Doppelhubkolben
- the present invention relates to a transmission, a control unit and at least one electromotive driven piston-cylinder unit having a piston which is connected via hydraulic lines with several Wegge- transmission units of the gearbox and this adjusted, wherein the transmission units comprise at least two coupling units.
- DE 10 2006 038 446 AI a manual transmission with an electric motor driven piston-cylinder unit is described in which actuate one or two piston-cylinder units four gear actuator and two clutches.
- the piston-cylinder unit generates the pressure needed to adjust the gear actuators and clutches, with a pressure sensor measuring the pressure generated.
- DE 10 2006 038 446 A1 describes two possible embodiments for this purpose.
- clutches and gear shifter are adjusted over for actuation of so-called multiplex valves by means of the piston-cylinder unit.
- the pressure build-up and the pressure reduction via the piston-cylinder unit can take place.
- additional exhaust valves are provided, via which the pressure in the individual consumers can be lowered regulated.
- the object of the invention is to improve the known from DE 10 2006 038 446 AI manual transmission on.
- the two piston surfaces can either have the same size, so that the same volume is promoted at the same displacement of the piston during the forward stroke and the return stroke.
- the piston surfaces are formed differently large, z. B. in the ratio 1.5-2: 1, so that 1.5 to 2 times the volume is promoted during the return stroke as the return stroke, so that in the forward stroke of faster volume can be promoted in terms of rapid pressure build-up and thus rapid actuation of Clutch or a quick gear operation.
- the volume ratio 2: 1 can be used in such a sense, in which a volume balance between two working spaces of a Doppelhubkolbens can be achieved via a switching valve and thus the Axialkraftbelastung is reduced to the transmission, as in the forward stroke and in the return stroke only half the area on the gear unit acts.
- This makes sense, especially at high pressures, since the axial force reduces the gear load and thus enables the use of a cost-effective plastic trapezoid spindle drive.
- the advantage of Doppelhubkolbens over a continuously running pump is that the pressure generating unit must be operated only during a switching operation.
- the displacement control of the piston which corresponds to a volume control
- the displacement or volume control in a simple way, at least one manual transmission unit can have more than two switching positions without complex pressure control, because due to the incompressibility of the hydraulic medium via a predetermined volume delivered, the respective transmission unit can be selectively adjusted to one of the possible positions .
- the components of the transmission units, in particular gear and clutch plates can also be adjusted accurately and faster than with proportional valves, because due to prior knowledge of the displacement volume, an additional control variable is used.
- proportional valves can use this advantage only to a limited extent since their control quantity relates to the valve current and this in turn depends on the hydraulic fluid state and its viscosity.
- proportional valves due to the known volumetric balance and the conception without leaks in the reservoir, even small leakages to the outside and leakage of vents can be accurately diagnosed.
- At least one pressure sensor or a position sensor can be advantageously provided for some gearboxes, a pressure control or position control for pressure build-up and also to reduce pressure, so that by means of the piston-cylinder unit both a way or. Volume control and a pressure control takes place.
- the pressure is controlled via targeted piston stroke control or via targeted energization of the electric motor.
- pressure control the non-linear relationship between pressure and Kolbenverstellweg is detected and stored in a map. This map is used in the pressure control such that a certain distance is approached via the piston, which corresponds to a certain pressure. If the map changes due to temperature or air bubbles, it is recalibrated or recorded.
- a torque can be controlled via the current of the electric motor.
- the torque constant kt (relationship between torque of the electric motor and phase current) of the electric motor can be used.
- the torque constant can be determined in electric motors in production, initial commissioning and is characterized in that kt changes slightly over time and essentially changes only temperature influences linearly.
- the supply current of the electric romotors are used.
- a pressure estimation can be accomplished by means of a model.
- a model can consist of a motor with a gear that, for example, presses or optionally pulls on a single-acting or double-acting hydraulic piston.
- the parameters in the subunits (motor torque constant kt, gearbox efficiency and hydraulic piston cross-sectional area, friction due to seals) must either be subject to minor influences or the parameter variations adjusted at regular intervals.
- An exact model can be realized in such a way, by the o. Parameter changes of the model are detected during operation, which affect the pressure estimation or pressure control. For example, pressure sensors that are only active in partial operation or an indirect pressure calculation can be used.
- a method for indirectly measuring the pressure across the electric motor current can be calculated by the position of the clutch piston in the slave cylinder and the acting cross-sectional area of the master cylinder piston, with knowledge of the clutch release spring and the diameter of the clutch slave cylinder.
- a system can completely dispense with a pressure transducer, which leads to significant cost savings, as pressure transmitters are primary cost drivers of hydraulic systems.
- a pressure transducer is about 4 times more expensive than a switching valve and comparably expensive like a proportional valve. If a system architecture of a transmission actuator is now used, which is operated with a motor with hydraulic piston, this does not necessarily have to be provided with a pressure sensor.
- Various pressures in the system can be sufficiently estimated via models as described above.
- the information about pressure at a gear position may be beneficial. If a gear actuator is actuated, the force can be calculated on the shift fork. This means, one knows the position in the gear regulator, where the synchronization begins and therefore does not need separate algorithms, the learn the synchronization points in all gear actuators.
- Already known systems, such as the described transmission actuator in DE 101 34 115 B4, have no pressure sensors, but only position sensors in the gear positions.
- the synchronization point is then evaluated as the speed in the transmission line or in the sub-transmission line changes. Due to the high inertia of the gear trains, the speed changes significantly slower than the pressure in the gear selector and must, therefore, in order to keep the dynamics high, to use experience from previous circuits or learning procedures.
- wet clutches can advantageously be used, wherein the fluid for the cooling of the wet clutches are used either by means of the drives for the Doppelhubkolben or separate drives.
- an additional double-stroke piston can be coupled or rigidly connected to the first double-stroke piston, which is used for displacing the cooling fluid.
- the first Doppelhubkolbens When adjusting the first Doppelhubkolbens then also the cooling fluid is promoted. If no clutch or gear plate must be adjusted, the first Doppelhubkolben by means of suitable valves, the fluid only from the reservoir and out directly into this promote.
- the manual transmission according to the invention may be formed with only two clutch plates, i. E. without gear plate, as is the case in particular in 2-speed transmissions for electric vehicles with two clutches and is shown and described in Figure 3.
- Fig. La Manual transmission with a piston-cylinder unit with Doppelhubkolben with eight valves and two dry-running clutch actuators and four gear actuators in the closed hydraulic circuit;
- Fig. Lb manual transmission with a piston-cylinder unit with Doppelhubkolben with twelve valves and two dry-running clutches and four gear actuators in the closed hydraulic circuit
- Fig. Lc manual transmission with a piston-cylinder unit with double-stroke piston with intelligent control for clutch actuation with potential for downsizing the engine-transmission-piston unit due to the use of energy stored in a clutch;
- FIG. 1 d use of the stored energy in a clutch during the changeover operation between two clutches
- Pressure control via piston control and exhaust valves to reduce power consumption
- FIG. 2a gearbox with a piston-cylinder unit with Doppelhubkol- ben with two wet-running clutches and four gear actuators in the closed hydraulic circuit with additional pump;
- Fig. 2b Manual transmission with a piston-cylinder unit with Doppelhubkolben with two wet-running clutches and four gear actuators in the closed hydraulic circuit with driven via the drive of the piston-cylinder unit Doppelhubkolben (DHK pump);
- Fig. 4 extended transmission with additional piston-cylinder unit. 2a shows a first possible embodiment of the transmission according to the invention in the form of a dual-clutch transmission with a piston-cylinder unit 19 with Doppelhubkolben 19c for moving the hydraulic medium in the clutch actuator 25 / C1, 28 / C2.
- the piston-cylinder unit 19 is driven by the drive 1 via the transmission 2.
- the Doppelhubkolben 19c separates the two working spaces 19a and 19b from each other, wherein the piston surface 19e, which limits the working space 19b, is greater than the effective piston area 19d, which limits the working space 19a is.
- the working space 19a is connected via the hydraulic main line HL2.
- the working space 19b is connected to the hydraulic main line HL1.
- the hydraulic supply lines HL25, HL28, HL30a, HL30b, HL33a, HL33b, HL35a, HL35b, HL38a and HL38 are derived, which contain the hydraulic main lines HL1, HL2 with the couplings 25 / C1, 28 / C2 and the gear actuators 30, 33, 35 and 38.
- the hydraulic supply lines HL25, HL28, HL30a, HL30b In the hydraulic supply lines HL25, HL28, HL30a, HL30b,
- HL33a, HL33b, HL35a, HL35b, HL38a and HL38 are each arranged switchable valves 24, 27, 32, 33, 37, 40 and 41 for selectively shutting off or opening the supply lines.
- the two working spaces 19a and 19b are each connected via hydraulic lines HL19a and HL19b to a reservoir 6, whereby switchable 2/2 way valves 20, 22 are arranged in the hydraulic lines HL19a and HL19b.
- Parallel to each 2/2-way valve 20, 22 a check valve 21, 23 is arranged in each case.
- the manual transmission according to Figure la with two clutch plates and four gear actuators requires only eight switchable 2/2-way valves.
- the gear plates 30, each have two working spaces 30a, 30b, 33a, 33b, 35a, 35b and 38a, 38b which are sealed and separated from each other by pistons. It is important in this arrangement that the first working spaces 30a, 33a, 35a, and 38a are connected to the first hydraulic main line HL1 and thus to the working space 19b, and that the second working spaces 30b, 33b, 35b, and 38b are connected via the second hydraulic main line HL2 are connected to the working space 19 a of the piston-cylinder unit 19.
- a gear change can be implemented as follows: For a gear change from the first to the second gear, the second gear must first be engaged, with the clutch Cl (25) being pressed in this initial state and thus also closed , However, so that the volume or the pressure from the clutch Cl does not escape, the clutch actuator valve 24 must be closed. To initiate the gear change the gear actuator valve 1 (35) is opened, the exhaust valve 1 and the clutch actuator valve 2 is closed. Subsequently, the Doppelhubkolben 19 c can be moved to the left with the engine and gear unit 1 and 2, whereby volume in the gear tray 2/4 (33) is moved specifically into the chamber 33 b.
- valve 35 If the valve 35 is not opened in this process to allow the shift actuator 33 to move, the system would be hydraulically locked. If gear 2 in gear selector 2/4 (33) in the sub-transmission is synchronized with, for example, the crankshaft, the gear can finally be engaged. Gear control valve 35 is closed again, clutch actuator valve 27 is opened and exhaust valve 20 remains closed and the clutch actuation in clutch C2 (28) can be started. In order to switch frictional interruption free, a continuous load change of the two clutches Cl (25) and C2 (28) must take place. The closing of the clutch C2 is undertaken by means of the pressure build-up in the double-stroke piston 19, which in turn moves to the left.
- the simultaneous opening of the clutch Cl (25) is possible with a stufweiser or stepless control of the clutch actuator valve 24 that discharges the fluid controlled via the corresponding outlet valve 22.
- the gear 1/3 (30) can either be set to neutral (mid-position of the shift fork 30c) or the next gear can be preselected.
- the clutch actuator valves 24, 27, the exhaust valve 22 are closed and the gear actuator valve 32 is opened.
- the Doppelhubkolben 19 displaces the volume from chamber 19b and thus shifts the gear plate 30 to the right, according to the displaced volume.
- the gear position from 1 to 2 is finally completed.
- the piston 19c is located before starting the journey in a middle position, since it can not be predicted whether at the start of the vehicle first gear or reverse gear is engaged. Thus, for both maneuvers corresponding volume for actuating a gear actuator and a clutch is present. Alternatively, the piston would have to be moved with the valves 20 and 22 open in the correct position.
- the control of the clutches either via possible position sensors 26, 29 or pressure sensors.
- a pressure or position sensor is used in current transmissions.
- Dry couplings are usually carried out with position sensors and wet couplings with pressure sensors.
- the controlled discharge of the couplings can be done either with the valves 24 and 27 or with the valves 20 and 22 either gradually or steplessly, depending on which valve types are used.
- a position sensor 31, 34, 36, 39 is provided in each gear plate 30, 33, 35, 38, so that possible leaks in the valves 32, 37, 40, 41 are not can lead to mechanical destruction.
- the valves 20, 22, 24 and 27 must be carried out in normally open position, so that in case of system failure both clutches 25, 28 are opened immediately, without further needing a supply.
- Figure lb shows an embodiment in which pressure can be locked in the gear actuators 30, 33, 35, 38 by means of switching valves 32 and 52, 41 and 53, 37 and 54, 40 and 55.
- the clutch Cl or C2 can be actuated, which is also operated with so-called micro-slip and is controlled by the Doppelhubkolben 19.
- Micro-slip is used to dampen unwanted speed fluctuations on the crankshaft to a certain extent and to better estimate the opening position of the clutches. The effect of damping depends on the size of the operated slip on the corresponding coupling. If a gear change is to be completed, it often takes several hundred milliseconds, since the synchronization of the unloaded subtransmission takes up a large part of the total shift time.
- a Doppelhubkol- bens 19 which is operated with a trapezoidal spindle or a ball screw 2, a gear change can be initiated briefly.
- the last under load clutch 25 or 28 is locked in the corresponding partial transmission with the clutch actuator valve 24 or 27 and it can now be fluid with the valves 24 or 22 and also 27 or 21 are drained.
- a micro-slip control is not or only partially possible in this short time, but the clutch still continues to slip.
- the desired gear actuator is actuated and moved only to the synchronization point, whereby the pressure in the gear regulator can be calculated from the motor current. If the synchronization is initiated, the hydraulic pressure can be locked with switching valves in the corresponding gear selector and the Doppelhubkolben 19 can after a short time interruption, the micro-slip control on the loaded clutch 25 or 28 resume.
- the pressure level in Doppelhubkoben 19 must approach the loaded clutch and then open the clutch actuator valve 27 or 24 again pressure-differential. If the synchronization is completed in the unloaded partial transmission, the final gear change can be initiated and the load change is completed.
- FIG. 1c shows a variant for controlling the two clutches 25 / C1 and 28 / C2. It is an intelligent modification of the engine 1 for driving the hydraulic piston 19, which is driven by a spindle 2, to reduce and thus to save power, weight and space. If, for example, a gear change from the partial transmission 1 with the clutch Cl / 25 to the partial transmission 2 with the clutch C2 / 28 is carried out, the stored potential energy of the clutch Cl / 25 can be used for the pressure buildup in clutch C2 / 28.
- a schematic representation of the sequence is shown in the figures ld and le.
- FIG. 1 d shows possible pressure curves in the clutches in this modification and FIG le a simplified representation of the reduced power consumption of the electric motor. 1
- the pressure stored in the clutch C2 / 28 can be used analogously to assist the adjustment of the piston 19c. This reduces the maximum required power of the motor from P max _Th to P max , as shown in FIG.
- the motor 1 can thus be dimensioned smaller.
- the outlet valves 20 and 22 can provide suitable volume balances and discharge possible liquid excess via the lines HL19a, HL19b into the reservoir 6.
- the load change between the clutches the maximum power of the engine 1. This means that the engine 1 with comprehensive intelligent control (engine 1 and valves 20, 22, 24, 27) can generally be made smaller.
- FIG. 2a describes the design of a dual-clutch transmission with wet-running clutches C1 and C2 and a separate cooling circuit HLP with independent pump 44 with drive motor 43. The functioning and execution of a gear change functions identically as described in FIG.
- clutches C1 and C2 become C2 via the pressure sensors 41, 42 and not via position sensors 26, 29 regulated.
- the position sensors can therefore be omitted. Due to higher transmitted torque and the possible use of multi-plate clutches, the pump 44 is supplied with a separate cooling circuit HLP cooled with its own medium from the container 46.
- FIG. 2 b describes a system architecture of a double-stroke piston with wet-running clutches and separate cooling circuits HLK 1 and HLK 2 with simultaneously running double-stroke piston pump 50 which is connected to the piston passage of the engine / transmission piston unit 1, 2, 19.
- a pumping function can be taken over by means of a separate double-stroke piston 50. So an additional pump with motor can be saved.
- the cooling circuits HLKL, HLK2 run with separate medium whereby contamination can not get into the actual Doppelhubaktuator 19.
- the additional Doppelhubkolben 50d must be much larger than the actual actuator with Doppelhubkolben 19c, since some liters of fluid must be promoted for cooling per minute.
- cooling liquid can continue to be conveyed out of the container 47 and via the check valves 48 and 49 by opening valves 20 and 22.
- the piston 50d can be moved back and forth by means of the drive 1 as a function of the required delivery rate - high frequency with strong cooling, low frequency with low cooling - without the clutches C1 and C2 and the gear adjuster being adjusted. This is achieved by closing the associated valves 24, 27, 32, 37, 40 and 41 and opening the valves 20 and 22.
- the valve 31 shown in FIG. 1c can be arranged, which in the opened state can hydrate the two working spaces 19a, 19b.
- FIG. 4 shows the extension of a previously described system.
- the original system consists of the valve circuits in the partial transmission 1 and partial transmission 2 with the respective valves 24, 27, 32, 37, 40 and 41 for the actuation of the clutches 25, 28 and the gear plate 30, 33, 35, 38.
- the Hydrau - likaktuator 19, which is driven by the engine 1 via the gearbox 2 and has a Doppelhubkolben 19c is connected to its working spaces 19a, 19b via the two valves 20, 22 to the container or reservoir 6.
- the extension of the gearbox is that the pressure modulator 19 ' , which is driven by the engine 1 ' via the gear 2 ' , for actuating the clutches Cl and C2 is usable.
- the working chamber 19a ' is for this purpose via the hydraulic lines HL19a' -25 and HL19a '-28 lung actuators with the couplings 25, 29 connected, wherein a respective switching valve 32a, 32b in the respective hydraulic lines HL19a' -25 and HL19a '-28 to their Barrier or opening is arranged. This allows a continuous micro-slip control of the respective clutch in the traction.
- valves 32a, 32b which connect the pressure modulator 19a ' to the clutch actuators 25, 28 can be designed to be both normally open and normally closed.
- the functional properties of the circuit are explained in more detail below.
- Situation 1 Micro-slip control on clutch plate 25 with simultaneous gearshift in partial transmission 2.
- the pressure modulator 19a ' assumes the continuous micro-slip control of the clutch actuator 25 by the pressure modulation valve 32b is opened to the clutch actuator and the pressure modulation valve 32b to the other clutch actuator 28 and the clutch valve 24 is closed. Depending on the clutch travel sensor 26, the pressure modulator 19a ' controls the micro-slip on the clutch 25. If a gear position in the partial transmission 2 is now required in parallel, this can be taken over by the hydraulic actuator 19.
- the position of the clutch a is not controlled by an analogue controlled valve 24 or 30a, but via the pressure modulator 19a ' .
- the valves 24, 27, 30a, 30b are simplified towards pure digital switching valves.
- valves 24 and 27 are now opened.
- the valves 30a, 30b, 32, 37, 40 and 41 and the pressure modulation valve 32b between the clutch actuator 28 and the pressure modulator 19a ' are closed unless this is already the case anyway.
- the Doppelhubkolben 19c now the pressure build-up and the position is controlled to clutch plate 19c.
- the Doppelhubkolben 19c moves to the left.
- the right-hand chamber of the double-stroke piston thus simultaneously sucks over 24 Volume from the clutch plate 25 from.
- the pressure modulator 19a ' takes over the regulation of the pressure or the position of the clutch plate 25.
- the main volume flow is displaced in the situation by the double-stroke piston 19c.
- the pressure modulator 19a ' only corrects the volume for the clutch actuator 28 according to the requirements. After the partial transmission 2 is activated and the partial transmission 1 is deactivated, the coupling valves 24 and 27 are closed and the pressure modulator 19a ' separated by the pressure modulation valve 32a from the clutch actuator 25 and connected by the other pressure modulation valve 32b with the clutch actuator 28. Now the pressure modulator 19a ' assumes the micro-slip control on the clutch actuator 28.
- the advantage of this circuit is that the pressure modulator 19a ' comes out with a much lower volume budget than the Doppelhubkolben 19c.
- the volume flow requirements to the pressure modulator 19a ' are well below the volume flow from the Doppelhubkolben 19c. Added to this is the fact that the system works completely without analogue valves and works purely with lower-cost, digitally switching valves.
- the coupling position and gear position take over so must due to the low volume budget on the Outlet valves 30a and / or 30b in between volume nachge felicitt in the pressure modulator 33.
- the pressure modulator 33 fails, the function can be maintained via the hydraulic actuator 19, except for small interruptions in the micro-slip control. Basically, the extension of the original circuit is only necessary if short interruptions in the micro-slip control during gearshifts can not be accepted.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Control Of Transmission Device (AREA)
- Gear-Shifting Mechanisms (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Actuator (AREA)
- Electric Propulsion And Braking For Vehicles (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
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CN201780055111.4A CN109690144A (zh) | 2016-09-07 | 2017-02-28 | 用于操纵换挡变速器的离合器和挡位选择器的具有带有双冲程活塞的活塞缸单元的电动液压系统 |
DE112017004481.2T DE112017004481A5 (de) | 2016-09-07 | 2017-02-28 | Elektrohydraulisches System für die Betätigung von Kupplung (en) und Gangsteller (n) von Schaltgetrieben mit einer Kolben-Zylinder-Einheit mit Doppelhubkolben |
KR1020197009899A KR20190057322A (ko) | 2016-09-07 | 2017-02-28 | 이중 작용 왕복 피스톤을 갖는 피스톤 실린더 유닛을 구비하는 변속 기어박스들의 기어 선택기(들) 및 클러치(들)를 작동시키기 위한 전자 유압 시스템 |
US16/331,357 US20190195350A1 (en) | 2016-09-07 | 2017-02-28 | Electro-hydraulic system for the actuation of multiple clutches and gear selectors with high-precision control of several shift gearbox units simultaneously |
JP2019533281A JP2019532237A (ja) | 2016-09-07 | 2017-02-28 | ダブルアクションピストンを有するピストン−シリンダ−ユニットを備える変速伝動機構の単数または複数のクラッチおよびギヤ作動装置の操作用の電気液圧式のシステム |
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DE102016116778.9 | 2016-09-07 | ||
DE102016116778 | 2016-09-07 | ||
DE102016118423.3A DE102016118423A1 (de) | 2016-09-07 | 2016-09-29 | Elektrohydraulisches System für die Betätigung von Kupplung(en) und Gangsteller(n) von Schaltgetrieben |
DE102016118423.3 | 2016-09-29 |
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PCT/EP2017/054641 WO2018046144A1 (de) | 2016-09-07 | 2017-02-28 | Elektrohydraulisches system für die betätigung von mehrfachkupplungen und gangstellern mit hochgenauer regelung von mehreren schaltgetriebeeinheiten gleichzeitig |
PCT/EP2017/054642 WO2018046145A1 (de) | 2016-09-07 | 2017-02-28 | Elektrohydraulisches system für die betätigung von kupplung(en) und gangsteller(n) von schaltgetrieben mit einer kolben-zylinder-einheit mit doppelhubkolben |
PCT/EP2017/054643 WO2018046146A1 (de) | 2016-09-07 | 2017-02-28 | Elektrohydraulisches system für die betätigung von kupplung(en) und gangsteller(n) von schaltgetrieben |
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PCT/EP2017/054641 WO2018046144A1 (de) | 2016-09-07 | 2017-02-28 | Elektrohydraulisches system für die betätigung von mehrfachkupplungen und gangstellern mit hochgenauer regelung von mehreren schaltgetriebeeinheiten gleichzeitig |
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US (3) | US20190195350A1 (de) |
JP (3) | JP2019532237A (de) |
KR (2) | KR20190057321A (de) |
CN (3) | CN109715990A (de) |
DE (4) | DE102016118423A1 (de) |
WO (3) | WO2018046144A1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102018115365A1 (de) | 2018-06-26 | 2020-01-02 | Lsp Innovative Automotive Systems Gmbh | Vorrichtung zur Ansteuerung von mehreren Stellgliedern mit einem gemeinsamen getakteten Auslassventil zum Druckabbau |
WO2020002077A1 (de) | 2018-06-26 | 2020-01-02 | Lsp Innovative Automotive Systems Gmbh | Vorrichtung zur ansteuerung von mehreren stellgliedern |
DE102020111492A1 (de) | 2020-04-28 | 2021-10-28 | Schaeffler Technologies AG & Co. KG | Hydraulikanordnung |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017130920B4 (de) * | 2017-12-21 | 2020-02-06 | Getrag Ford Transmissions Gmbh | Aktuatoranordnung für einen Kraftfahrzeugantriebsstrang und Verfahren zu dessen Betreiben |
CN111237445B (zh) * | 2020-01-10 | 2021-12-07 | 一汽解放汽车有限公司 | 一种基于pwm阀的同步器换挡气动控制方法 |
KR102401403B1 (ko) * | 2021-07-16 | 2022-05-24 | 곽태영 | 근력 운동을 위한 중량 발생 장치 |
CN114838122B (zh) * | 2022-03-29 | 2023-10-27 | 中国人民解放军陆军装甲兵学院 | 一种变速箱换挡液压系统在环的故障检测系统及其方法 |
CN115467907B (zh) * | 2022-11-15 | 2023-03-03 | 西南石油大学 | 钻井液排量控制的钻柱扭矩传递与分离装置及其方法 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006014280A1 (de) * | 2006-01-26 | 2007-08-02 | Continental Teves Ag & Co. Ohg | Hydraulische Schaltungsanordnung |
DE102006038446A1 (de) | 2006-08-16 | 2008-02-21 | Lsp Innovative Automotive Systems Gmbh | Elektromotorischer Kolbenantrieb |
DE10134115B4 (de) | 2001-07-13 | 2014-05-28 | Volkswagen Ag | Doppelkupplungsgetriebe eines Kraftfahrzeuges mit einem Hydraulikkreis und Verfahren zur hydraulischen Steuerung eines Doppelkupplungsgetriebes |
WO2015036623A2 (de) * | 2013-09-16 | 2015-03-19 | Ipgate Ag | Elektrisch angetriebene druckregel- und volumenfördereinheit |
Family Cites Families (26)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS58184323A (ja) * | 1982-04-23 | 1983-10-27 | Toyota Motor Corp | 歯車変速装置に於ける同期装置の駆動装置 |
JPS6213204U (de) * | 1985-07-10 | 1987-01-27 | ||
DE4320353A1 (de) * | 1992-06-27 | 1994-01-05 | Teves Gmbh Alfred | Hydraulische Getriebeansteuerung |
DE4413999B4 (de) * | 1994-04-22 | 2006-03-09 | Zf Sachs Ag | Stellantrieb für eine Kraftfahrzeug-Reibungskupplung |
NL1014476C2 (nl) * | 2000-02-23 | 2001-08-24 | Applied Power Inc | Hydraulische bedieningsinrichting voor een afdekkapsamenstel van een voeruig. |
DE10163404B4 (de) * | 2001-12-21 | 2009-06-04 | Zf Sachs Ag | Verfahren zur Steuerung eines Kupplungssystem mit wenigstens einer Lamellen-Kupplungsanordnung |
DE10391573D2 (de) * | 2002-04-10 | 2005-02-24 | Luk Lamellen & Kupplungsbau | Verfahren zur Erkennung einer Leckage eines hydraulischen Ausrücksystems einer Doppelkupplung eines Parallelschaltgetriebes |
DE102004018962B3 (de) * | 2004-04-14 | 2005-10-06 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Hydraulikkreis und Verfahren zum Steuern desselben |
DE112011100496T5 (de) * | 2010-02-10 | 2013-01-03 | Honda Motor Co., Ltd. | Hydraulische Steuervorrichtung für Automatikgetriebe |
WO2012075983A1 (de) * | 2010-12-09 | 2012-06-14 | Schaeffler Technologies AG & Co. KG | Hydrauliksystem für ein doppelkupplungsgetriebe |
KR101305157B1 (ko) * | 2011-07-29 | 2013-09-12 | 현대 파워텍 주식회사 | 듀얼 클러치 장치 |
BR112014004712A2 (pt) * | 2011-08-30 | 2017-03-28 | Toyota Motor Co Ltd | dispositivo de vedação para circuito hidráulico |
DE102013008701B3 (de) * | 2013-05-22 | 2014-10-09 | Audi Ag | Verfahren zum Betreiben einer Getriebeeinrichtung sowie entsprechende Getriebeeinrichtung |
WO2015067259A1 (de) * | 2013-11-08 | 2015-05-14 | Schaeffler Technologies AG & Co. KG | Fluidanordnung |
CN204114098U (zh) * | 2014-05-12 | 2015-01-21 | 天津市松正电动汽车技术股份有限公司 | 一种变速器换挡执行器及变速器 |
CN105626844A (zh) * | 2014-10-28 | 2016-06-01 | 上海汽车集团股份有限公司 | 湿式双离合器变速箱的液压控制系统 |
JP6384761B2 (ja) * | 2014-12-11 | 2018-09-05 | いすゞ自動車株式会社 | デュアルクラッチ装置 |
WO2016134795A1 (de) * | 2015-02-27 | 2016-09-01 | Engineering Center Steyr Gmbh & Co Kg | Hydraulikkreis zur betätigung eines hybridgetriebes |
WO2016146222A2 (de) | 2015-03-16 | 2016-09-22 | Ipgate Ag | Bremsanlage mit schwimmkolben-hauptbremszylindereinheit mit neuartiger mux-regelung (mux 2.0) mit mindestens einem auslassventil und verfahren zur druckregelung |
WO2016146692A1 (de) | 2015-03-16 | 2016-09-22 | Ipgate Ag | Druckerzeugungseinrichtung und betätigungsverfahren mit elektrisch angetriebenem doppelhubkolben |
CN104948729B (zh) * | 2015-05-11 | 2017-05-31 | 合肥工业大学 | 一种7速对置式双离合器变速器用电液控制系统 |
DE102015218784A1 (de) * | 2015-09-29 | 2017-03-30 | Schaeffler Technologies AG & Co. KG | Fluidanordnung zum fluidischen Betätigen von Kraftfahrzeugkomponenten |
CN105299219B (zh) * | 2015-10-29 | 2017-11-14 | 吉林大学 | 带常合离合器的电动车辆双挡变速器 |
DE102016214375B3 (de) * | 2016-08-03 | 2017-11-16 | Audi Ag | Hydrauliksystem für ein Automatikgetriebe eines Kraftfahrzeugs |
DE102016223741A1 (de) * | 2016-11-30 | 2018-05-30 | Schaeffler Technologies AG & Co. KG | Fluidanordnung |
DE102017130297A1 (de) * | 2017-12-18 | 2019-06-19 | Schaeffler Technologies AG & Co. KG | Aktuatoreinrichtung |
-
2016
- 2016-09-29 DE DE102016118423.3A patent/DE102016118423A1/de not_active Withdrawn
-
2017
- 2017-02-28 JP JP2019533281A patent/JP2019532237A/ja not_active Withdrawn
- 2017-02-28 US US16/331,357 patent/US20190195350A1/en not_active Abandoned
- 2017-02-28 WO PCT/EP2017/054641 patent/WO2018046144A1/de active Application Filing
- 2017-02-28 DE DE112017004503.7T patent/DE112017004503A5/de active Pending
- 2017-02-28 WO PCT/EP2017/054642 patent/WO2018046145A1/de active Application Filing
- 2017-02-28 JP JP2019533282A patent/JP2019529842A/ja not_active Withdrawn
- 2017-02-28 DE DE112017004481.2T patent/DE112017004481A5/de active Pending
- 2017-02-28 JP JP2019533280A patent/JP2019526767A/ja not_active Withdrawn
- 2017-02-28 DE DE112017004501.0T patent/DE112017004501A5/de not_active Withdrawn
- 2017-02-28 WO PCT/EP2017/054643 patent/WO2018046146A1/de active Application Filing
- 2017-02-28 KR KR1020197009897A patent/KR20190057321A/ko unknown
- 2017-02-28 CN CN201780055119.0A patent/CN109715990A/zh active Pending
- 2017-02-28 US US16/331,219 patent/US20190242445A1/en not_active Abandoned
- 2017-02-28 CN CN201780055077.0A patent/CN109690143A/zh active Pending
- 2017-02-28 US US16/331,195 patent/US20190219154A1/en not_active Abandoned
- 2017-02-28 CN CN201780055111.4A patent/CN109690144A/zh active Pending
- 2017-02-28 KR KR1020197009899A patent/KR20190057322A/ko unknown
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10134115B4 (de) | 2001-07-13 | 2014-05-28 | Volkswagen Ag | Doppelkupplungsgetriebe eines Kraftfahrzeuges mit einem Hydraulikkreis und Verfahren zur hydraulischen Steuerung eines Doppelkupplungsgetriebes |
DE102006014280A1 (de) * | 2006-01-26 | 2007-08-02 | Continental Teves Ag & Co. Ohg | Hydraulische Schaltungsanordnung |
DE102006038446A1 (de) | 2006-08-16 | 2008-02-21 | Lsp Innovative Automotive Systems Gmbh | Elektromotorischer Kolbenantrieb |
WO2015036623A2 (de) * | 2013-09-16 | 2015-03-19 | Ipgate Ag | Elektrisch angetriebene druckregel- und volumenfördereinheit |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102018115365A1 (de) | 2018-06-26 | 2020-01-02 | Lsp Innovative Automotive Systems Gmbh | Vorrichtung zur Ansteuerung von mehreren Stellgliedern mit einem gemeinsamen getakteten Auslassventil zum Druckabbau |
WO2020002077A1 (de) | 2018-06-26 | 2020-01-02 | Lsp Innovative Automotive Systems Gmbh | Vorrichtung zur ansteuerung von mehreren stellgliedern |
DE102018115364A1 (de) | 2018-06-26 | 2020-01-02 | Lsp Innovative Automotive Systems Gmbh | Vorrichtung zur Ansteuerung von mehreren Stellgliedern |
DE102020111492A1 (de) | 2020-04-28 | 2021-10-28 | Schaeffler Technologies AG & Co. KG | Hydraulikanordnung |
Also Published As
Publication number | Publication date |
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US20190219154A1 (en) | 2019-07-18 |
WO2018046144A1 (de) | 2018-03-15 |
CN109690144A (zh) | 2019-04-26 |
DE112017004501A5 (de) | 2019-09-05 |
KR20190057322A (ko) | 2019-05-28 |
DE102016118423A1 (de) | 2018-03-08 |
KR20190057321A (ko) | 2019-05-28 |
JP2019532237A (ja) | 2019-11-07 |
JP2019526767A (ja) | 2019-09-19 |
US20190242445A1 (en) | 2019-08-08 |
CN109690143A (zh) | 2019-04-26 |
CN109715990A (zh) | 2019-05-03 |
DE112017004503A5 (de) | 2019-08-01 |
WO2018046146A1 (de) | 2018-03-15 |
JP2019529842A (ja) | 2019-10-17 |
US20190195350A1 (en) | 2019-06-27 |
DE112017004481A5 (de) | 2019-06-13 |
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