RU2213017C2 - Change-over device - Google Patents

Change-over device Download PDF

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Publication number
RU2213017C2
RU2213017C2 RU97109351/28A RU97109351A RU2213017C2 RU 2213017 C2 RU2213017 C2 RU 2213017C2 RU 97109351/28 A RU97109351/28 A RU 97109351/28A RU 97109351 A RU97109351 A RU 97109351A RU 2213017 C2 RU2213017 C2 RU 2213017C2
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RU
Russia
Prior art keywords
force
output
paragraphs
energy accumulator
spatial geometric
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Application number
RU97109351/28A
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Russian (ru)
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RU97109351A (en
Inventor
Пауль Маухер
Original Assignee
Лук Гетрибе-Зюстеме ГмбХ
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Priority to DE19622643 priority Critical
Priority to DE19622641.4 priority
Priority to DE19622643.0 priority
Priority to DE19622641 priority
Application filed by Лук Гетрибе-Зюстеме ГмбХ filed Critical Лук Гетрибе-Зюстеме ГмбХ
Publication of RU97109351A publication Critical patent/RU97109351A/en
Application granted granted Critical
Publication of RU2213017C2 publication Critical patent/RU2213017C2/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control 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
    • F16H61/26Generation or transmission of movements for final actuating mechanisms
    • F16H61/28Generation 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
    • F16H61/32Electric motors actuators or related electrical control means therefor
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B60VEHICLES IN GENERAL
    • B60TVEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/74Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive
    • B60T13/745Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive acting on a hydraulic system, e.g. a master cylinder
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B60VEHICLES IN GENERAL
    • B60WCONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00Conjoint control of vehicle sub-units of different type or different function
    • B60W10/02Conjoint control of vehicle sub-units of different type or different function including control of driveline clutches
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B60VEHICLES IN GENERAL
    • B60WCONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00Conjoint control of vehicle sub-units of different type or different function
    • B60W10/10Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B60VEHICLES IN GENERAL
    • B60WCONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W30/00Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units, or advanced driver assistance systems for ensuring comfort, stability and safety or drive control systems for propelling or retarding the vehicle
    • B60W30/18Propelling the vehicle
    • B60W30/1819Propulsion control with control means using analogue circuits, relays or mechanical links
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D28/00Electrically-actuated clutches
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D29/00Clutches and systems of clutches involving both fluid and magnetic actuation
    • F16D29/005Clutches and systems of clutches involving both fluid and magnetic actuation with a fluid pressure piston driven by an electric motor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00External control of clutches
    • F16D48/06Control by electric or electronic means, e.g. of fluid pressure
    • F16D48/066Control of fluid pressure, e.g. using an accumulator
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control 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
    • F16H61/26Generation or transmission of movements for final actuating mechanisms
    • F16H61/28Generation 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
    • F16H61/2807Generation 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
    • HELECTRICITY
    • H02GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02PCONTROL OR REGULATION OF ELECTRIC MOTORS, ELECTRIC GENERATORS OR DYNAMO-ELECTRIC CONVERTERS; CONTROLLING TRANSFORMERS, REACTORS OR CHOKE COILS
    • H02P7/00Arrangements for regulating or controlling the speed or torque of electric DC motors
    • H02P7/06Arrangements for regulating or controlling the speed or torque of electric DC motors for regulating or controlling an individual dc dynamo-electric motor by varying field or armature current
    • H02P7/18Arrangements for regulating or controlling the speed or torque of electric DC motors for regulating or controlling an individual dc dynamo-electric motor by varying field or armature current by master control with auxiliary power
    • H02P7/24Arrangements for regulating or controlling the speed or torque of electric DC motors for regulating or controlling an individual dc dynamo-electric motor by varying field or armature current by master control with auxiliary power using discharge tubes or semiconductor devices
    • H02P7/28Arrangements for regulating or controlling the speed or torque of electric DC motors for regulating or controlling an individual dc dynamo-electric motor by varying field or armature current by master control with auxiliary power using discharge tubes or semiconductor devices using semiconductor devices
    • H02P7/285Arrangements for regulating or controlling the speed or torque of electric DC motors for regulating or controlling an individual dc dynamo-electric motor by varying field or armature current by master control with auxiliary power using discharge tubes or semiconductor devices using semiconductor devices controlling armature supply only
    • H02P7/29Arrangements for regulating or controlling the speed or torque of electric DC motors for regulating or controlling an individual dc dynamo-electric motor by varying field or armature current by master control with auxiliary power using discharge tubes or semiconductor devices using semiconductor devices controlling armature supply only using pulse modulation
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00External control of clutches by electric or electronic means
    • F16D2500/10System to be controlled
    • F16D2500/102Actuator
    • F16D2500/1021Electrical type
    • F16D2500/1023Electric motor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00External control of clutches by electric or electronic means
    • F16D2500/10System to be controlled
    • F16D2500/108Gear
    • F16D2500/1081Actuation type
    • F16D2500/1085Automatic transmission
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00External control of clutches by electric or electronic means
    • F16D2500/30Signal inputs
    • F16D2500/302Signal inputs from the actuator
    • F16D2500/3021Angle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00External control of clutches by electric or electronic means
    • F16D2500/30Signal inputs
    • F16D2500/302Signal inputs from the actuator
    • F16D2500/3022Current
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00External control of clutches by electric or electronic means
    • F16D2500/30Signal inputs
    • F16D2500/302Signal inputs from the actuator
    • F16D2500/3023Force
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00External control of clutches by electric or electronic means
    • F16D2500/30Signal inputs
    • F16D2500/302Signal inputs from the actuator
    • F16D2500/3026Stroke
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00External control of clutches by electric or electronic means
    • F16D2500/30Signal inputs
    • F16D2500/302Signal inputs from the actuator
    • F16D2500/3028Voltage
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00External control of clutches by electric or electronic means
    • F16D2500/30Signal inputs
    • F16D2500/306Signal inputs from the engine
    • F16D2500/3067Speed of the engine
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00External control of clutches by electric or electronic means
    • F16D2500/30Signal inputs
    • F16D2500/306Signal inputs from the engine
    • F16D2500/3067Speed of the engine
    • F16D2500/3068Speed change of rate of the engine
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00External control of clutches by electric or electronic means
    • F16D2500/30Signal inputs
    • F16D2500/314Signal inputs from the user
    • F16D2500/31493Switches on the dashboard
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00External control of clutches by electric or electronic means
    • F16D2500/30Signal inputs
    • F16D2500/316Other signal inputs not covered by the groups above
    • F16D2500/3168Temperature detection of any component of the control system
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00External control of clutches by electric or electronic means
    • F16D2500/70Details about the implementation of the control system
    • F16D2500/71Actions
    • F16D2500/7107Others
    • F16D2500/7109Pulsed signal; Generating or processing pulsed signals; PWM, width modulation, frequency or amplitude modulation
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H59/00Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/68Inputs being a function of gearing status
    • F16H2059/6807Status of gear-change operation, e.g. clutch fully engaged
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control 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
    • F16H61/26Generation or transmission of movements for final actuating mechanisms
    • F16H61/28Generation 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
    • F16H2061/2823Controlling actuator force way characteristic, i.e. controlling force or movement depending on the actuator position, e.g. for adapting force to synchronisation and engagement of gear clutch
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H63/00Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30Constructional features of the final output mechanisms
    • F16H2063/3089Spring assisted shift, e.g. springs for accumulating energy of shift movement and release it when clutch teeth are aligned
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H63/00Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30Constructional features of the final output mechanisms
    • F16H63/304Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H63/00Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/40Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism comprising signals other than signals for actuating the final output mechanisms
    • F16H63/46Signals to a clutch outside the gearbox
    • HELECTRICITY
    • H02GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02HEMERGENCY PROTECTIVE CIRCUIT ARRANGEMENTS
    • H02H7/00Emergency protective circuit arrangements specially adapted for specific types of electric machines or apparatus or for sectionalised protection of cable or line systems, and effecting automatic switching in the event of an undesired change from normal working conditions
    • H02H7/08Emergency protective circuit arrangements specially adapted for specific types of electric machines or apparatus or for sectionalised protection of cable or line systems, and effecting automatic switching in the event of an undesired change from normal working conditions for dynamo-electric motors
    • H02H7/085Emergency protective circuit arrangements specially adapted for specific types of electric machines or apparatus or for sectionalised protection of cable or line systems, and effecting automatic switching in the event of an undesired change from normal working conditions for dynamo-electric motors against excessive load
    • H02H7/0852Emergency protective circuit arrangements specially adapted for specific types of electric machines or apparatus or for sectionalised protection of cable or line systems, and effecting automatic switching in the event of an undesired change from normal working conditions for dynamo-electric motors against excessive load directly responsive to abnormal temperature by using a temperature sensor
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02TCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00Road transport of goods or passengers
    • Y02T10/60Other road transportation technologies with climate change mitigation effect
    • Y02T10/72Electric energy management in electromobility

Abstract

FIELD: automotive industry. SUBSTANCE: device is designed for automatic change-over and (or) selection of reduction gear ratio and (or) automatically setting into action torque- transmitting system in automobile drive. Proposed device includes drive unit and, if necessary, reduction gear and output member for setting member in operation with at least one energy accumulator acting onto output member. Member with spatial geometric outline, for instance, with curvilinear profile or with curvilinear disk or cam taking up is functionally connected with drive. Force action of at least one energy accumulator is transmitted to output member through said spatial geometric outline member. EFFECT: provision of accurate and reliable automatic gear-shifting of automobile. 38 cl, 27 dwg

Description

 The invention relates to a device for actuating a controllable element, for example, a gearbox or a torque transmission system in a vehicle’s drive circuit, with a drive unit and an output element operably connected to it by means of a drive connection and with at least one energy accumulator, by means of which a direct or indirect force on the output element.

 Such actuating devices are known from DE-OS 19504847. In these devices for torque transmission systems, a structure is proposed in which an energy accumulator is provided for power support, made according to the principle of linear impact, and therefore there is a linear relationship between the movement of the device for actuation and force.

 The objective of the invention under consideration is to create the aforementioned actuating device, which provides a modulated (for example, along the way) nature of the change in the force acting on the output element and creating power support of the drive motor in at least one working direction. In addition, the basis of the invention is to create the aforementioned device, which can be performed in a more advantageous manner in terms of dimensions, cost and consumption of materials. The objective of the invention is also to provide a device with improved functionality.

 According to the invention, this is achieved in the aforementioned actuating devices by the fact that a force-sensing element with a spatial geometric contour, for example with a curved profile or with a curved disk or with a cam, is connected to the drive connection, and a power element is transmitted to the output element through the spatial geometric contour exposure to at least one energy storage device.

 Further, according to the invention, in a device for actuating a controlled element, for example for switching or selecting a gear ratio of a gearbox or for actuating a torque transmission system in a drive circuit of a vehicle comprising a drive unit, if necessary, the gearbox, as well as functionally the output element connected to them by means of a drive connection with at least one energy accumulator acting on the output element is expedient in the drive connection m Between the drive unit and the output element, install a force-sensing element with a spatial geometric contour, for example, with a curved disk, curved profile and (or) cam, and the force effect of at least one energy accumulator is transmitted to the output element through the spatial geometric contour.

 It is further advisable to provide that the force-sensing element with a spatial geometric contour, for example with a curved disk, a curved profile or with a cam, is affected by at least one energy accumulator in the area of the spatial geometric contour, as a result of which the power is transmitted from the energy accumulator to the output element through the spatial geometric contour.

 In another embodiment of the invention, it is expediently provided that the force-sensing element with a spatial geometric contour, for example with a curved disk, curved profile or cam, is an element that, when exposed to an actuated control element, starts to move.

 In the device for actuation, it is advisable to provide that when a force is applied to the force-sensing circuit and when an element with a force-sensing circuit moves, the force of the energy accumulator acting on the output element is modulated.

 It is further advisable to provide that the element with a force-sensing circuit when exposed to a control element moves in at least one direction.

 In the same way, it is advisable to provide that the element with the force-sensing contour moves rectilinearly and (or) in the axial, and (or) in the radial direction, and (or) in the circumferential direction.

 According to another embodiment of the invention, it is advisable to provide that the spatial geometric force-sensing contour of the element is oriented rectilinearly and (or) in the axial, and (or) in the radial direction, and (or) in the circumferential direction.

 According to another embodiment of the invention, it is advisable to provide that the force from at least one energy accumulator on the spatial geometric force-sensing contour of the element is oriented mainly rectilinearly and (or) in the axial, and (or) in the radial direction, and (or) in the circumferential direction.

 Further, it is advisable to provide that the modulation of the force-sensing spatial geometric contour of the element is oriented mainly linearly and (or) in the axial, and (or) in the radial direction, and (or) in the circumferential direction.

 It is advisable to provide that when a force is applied to the circuit, for example by at least one energy accumulator, the force acts at least mainly in the direction of the output element or in the opposite direction.

 Further, it is advisable to provide that when a force is applied to the circuit, for example by at least one energy accumulator, the force action is separated at least mainly in the direction of movement of the actuation of the output element and (or) in the direction perpendicular to the movement of actuation.

 It is also advisable to provide that a gearbox is integrated in the drive connection between the drive unit and the output element.

 It is advisable to design in which a spatial geometric element with a force-sensing circuit is in functional connection with the drive unit, the drive connection element and the output element.

 Further suitable is the embodiment in which an element with a spatial geometric force-sensing contour has a rotating curved disk, a curved surface or cam of a one-dimensional or two-dimensional shape. Further suitable is a design in which an element with a spatial geometric force-sensing contour has a curvilinear disk, a curved surface, or a cam of a one-dimensional or two-dimensional shape that can be moved rectilinearly or axially.

 According to the invention, it is expedient to design in which an element with a spatial geometric force-sensing contour has a curved disk, a curved profile or a cam of a three-dimensional shape.

 It is also advisable to design in which at least one energy accumulator that exerts a force effect on the spatial geometric contour has a support shoe, a roller and (or) a rolling bearing through which the energy accumulator rests on this contour.

 It is further advisable to carry out the invention in such a way that at least one energy accumulator acts on a certain element, for example, a lever, which is mounted movably in one section and has a support shoe, roller or rolling bearing in the second section, acting on the contour of the spatial geometric element.

 Further suitable is the design in which at least one energy accumulator acts on an element that is supported in straight guides and has a contour of a spatial geometric element.

 Moreover, it is further advisable to perform in which at least one energy accumulator acts on the tick-shaped element, which is mounted movably in one section and acts on the contour of the spatial geometric element.

 It is advisable to design in which at least one energy accumulator acts on an element with a spatial geometric contour, for example, on a reference section in the form of an eccentrically located journal, wherein the output element rests on a section of the spatial geometric contour.

 It is also advisable to design in which at least one energy accumulator acts on an element with a spatial geometric contour, for example, on a reference section in the form of an eccentrically arranged pin, and the element acting on the output element relies on a section of the spatial geometric contour.

 Further, it is advisable to perform in which the bearing on the spatial geometric contour and (or) the impact on the spatial geometric contour occurs by sliding, rolling or through a roller.

 According to the invention, it is advisable to make the drive unit in the form of an electric motor, electromagnetic or electromechanical device.

 It is also advisable to make the drive unit in the form of a device driven by a pressure medium, for example in the form of a hydraulic, hydropneumatic or pneumatic device.

 Further, it is advisable that the output element of the device for actuating as a result of the movement of the spatial geometric circuit and the application of force to this circuit, the force effect on the output element is modulated as a function of the path to actuate the output element.

 It is also advisable execution, in which power support occurs at least on a part of the path of actuating the output element.

 In another embodiment of the invention, it is advisable to provide that during the movement to activate the force support, if necessary, change the sign of its direction.

 According to another embodiment of the invention, in a device for actuating a controlled element, for example, for switching and (or) selecting a gear ratio of a gearbox and (or) for actuating a torque transmission system in a drive circuit of a vehicle, which includes a drive unit and if necessary, the gearbox, as well as the output element for actuating, with at least one energy acting on the output element, operatively connected to them by means of a drive connection a battery, it is advisable to provide that the output element exerts a force of at least one energy storage, wherein at least one energy store is configured as a spring with a departure from the dead point.

 In this case, it is especially advisable to design in which one against the other two energy accumulators are installed that act on the output element in the form of springs with departure from the dead center.

 It is also advisable to provide that at least one energy accumulator is made in the form of a spring with a departure from the dead point so that the first end section is pivotally connected to the output element, and the second end section is pivotally connected, for example, to the housing.

 In another embodiment of the invention, it is advisable to provide that for controlling the actuated control element, for example, for switching and (or) selecting the gear ratio of the gearbox and (or) for actuating the transmission system of the torque in the drive circuit of the vehicle, which includes the drive unit and if necessary, the gearbox, as well as the output element operably connected to them through the drive connection for driving, with at least two acting on the output electric element with energy accumulators, at least two energy accumulators acted on the output element so that they are installed in a row one after another.

 It is further advisable to provide that at least one energy accumulator has a preliminary tension.

 It is further advisable to provide that at least one energy storage device is a spring, for example a compression spring, a leaf spring, a loop spring or an elastic element made of metal, rubber material or plastic.

 It is also advisable to perform an element with a spatial shape contour of metal or plastic.

 It is also advisable to perform an element with a spatial geometric contour in one piece with the gear part.

 It is also advisable to perform an element with a spatial geometric contour in one piece with the output element.

 In an embodiment of the invention, it is advisable to perform an element with a spatial shape contour in one piece with the element of the functional connection between the drive unit and the output element.

 Further, it is advisable to connect the element with the spatial shape contour to the connecting link element between the drive unit and the output element.

Examples of the invention are explained in more detail below using the drawings. In particular, shown:
figure 1 - device for actuating,
figure 2 - device for actuating,
figure 3 - device for actuating,
figure 4 - compensation device,
on figa - compensation device,
on fig.4b - compensation device,
on figa - compensation device,
Fig.5b - compensation device
on figa - compensation device,
Fig.6b - compensation device,
on figs - compensation device,
on figa - compensation device,
Fig.7b - compensation device,
on figa - compensation device,
on fig.8b - compensation device,
figure 9 is a device for actuating,
figure 10 - curved disk
figure 11 is a curved disk,
Fig.12 is a graph,
Fig.13 is a graph,
on Fig - part of the device for actuating,
on figa - the location of the energy accumulators,
on fig.14b - the location of the energy accumulators,
on figa - the location of the energy accumulators,
on figb - the location of the energy accumulators,
on Fig - a device for actuating,
on Fig - a device for actuating.

 Figure 1 shows a device 1 for automatically driving, for example, a torque transmission system 2 and (or) for automatically switching a gear ratio of a gearbox in a drive chain of a car with a drive motor, a torque transmission system and a gearbox. Using this device, it is possible to automatically turn the torque transmission system on or off using the control unit or to purposefully control the torque transmitted by the torque transmission system. The gearbox can have manual or automatic switching, and in an automatically switched gearbox, this device can be used to purposefully enter, change or output gear stages of the gearbox. Depending on the kinematics of the device, the gear stages can be controlled in a cycle of gradual increase or decrease in any sequence.

 The device 1 for the automated actuation of the torque transmission system and (or) the gearbox has a drive unit 3, which can be made, for example, in the form of an electric motor. The drive unit of the device for actuation can also be made in the form of an electromagnetic device or a device driven by a pressure medium, such as a hydraulic or pneumatic device.

 In the embodiment of FIG. 1, a housing 4 of a drive device 1 is shown in which an electric motor 3 is inserted, the output shaft 5 being supported in bearings 6, 6a and 7. The electric motor 3 can also be mounted externally on the housing 4, moreover, In this case, the output shaft 5 enters the housing through an opening in the housing 4. The pole stator 3a of the electric motor 3 is connected to the housing 4 of the device, for example by means of screws, rivets or plug-in mounting. In this case, the output shaft enters, for example, the housing, forming a drive connection.

 A gearbox can be installed behind the output shaft of the engine, with which you can convert the movement of the drive, for example, the rotation of the output shaft of the electric motor, into another form of movement. In the example embodiment of FIG. 1, a worm gear installed behind the shaft is shown, as well as a crank mechanism located after it.

 In the area between the two bearings 6 and 7 on the output shaft 5, it is advisable to plant a worm, which is at least mainly connected to the shaft 5 motionless. In figure 1, this worm is not shown, but forms part of the worm gear. The worm is engaged with the worm wheel 8.

 Instead of a worm gear, other types of gears can also be used, for example, planetary, spur gears, bevel gears, spindle gears, etc.

 The worm drives the worm wheel 8, which rotates around axis 9. Next, a connecting rod 11 is connected to the worm wheel via a pin 10, which acts on the piston 12 of the driving cylinder of the driving device.

 The connecting rod 11 can be in a drive connection with the piston 12 of the master cylinder operating under pressure, in this case the hydraulic cylinder 13, and by axial movement of the piston 12, control the axial position of the piston 14 of the master cylinder working under the action of the pressure medium, in this case the master cylinder 15. The pressure line 12, 13, 14 can be made in the form of a hydraulic or pneumatic line of action.

 The connection between the connecting rod 11 and the piston 12 of the master cylinder can be made using the connecting link 16, which is a kind of ball joint or universal joint and made in such a way that during assembly the docking is facilitated by a latch.

 The output part 17 of the receiving hydraulic cylinder serves as the output part of the considered device for actuation, and in this embodiment, it acts on the clutch release fork 18, as a result of which the clutch release clutch bearing 19 can be adjusted or actuated to purposefully turn the clutch on or off, or to set a preset transmitted torque.

 The torque transmission system 2 is depicted in the form of a friction clutch with a pressure plate 20, a clutch plate 21 and a disk (diaphragm) spring 22, which is mounted on a flywheel 23; the cover of the clutch is indicated by the number 24. The clutch release bearing 19 during axial movement moves the cup spring 22, as a result of which the clutch engages or disengages. The friction clutch may be a self-adjusting, wear-compensating clutch. In addition, the torque transmission system may be a plate clutch, a torque converter lockup clutch, and the like. The friction clutch may be in the form of a dry clutch or a clutch operating in oil.

 The car reducer can be made with manual or with automatic switching. As an automatic gearbox, a step-by-step gearbox or a stepless gearbox, for example a stepless gearbox with bevel disks, can be used.

 The drive device in question can be used to turn on and / or turn off the torque transmission system or to change the gear ratio of one of the aforementioned gearboxes.

 The actuation of the clutch using the clutch release fork 18 is against the action of the force of the Belleville spring 22 as an energy accumulator. The means of switching off may be, for example, the central switching lever.

 At least one energy accumulator 25 is located inside the actuator 1, which at one end rests on the part 26, which in turn rests on the housing part 27, while the other end of the energy accumulator rests on the part 28, which is axially secured by a safety rings 29 on the connecting rod 11. Due to this embodiment of the energy storage device, power support of the connecting rod driven by the drive unit by the energy storage device can be achieved. The force generated by the energy accumulator 25 acts against the energy accumulator of the clutch or in the same direction as he. The direction of the force action of the energy accumulator 25 to the connecting rod or to the output element can be modulated along the path of actuation.

 The power accumulator 25 is located mainly coaxially with the connecting rod 11 and supports the movement of the connecting rod 11 in the direction of turning off and / or turning on the torque transmission system. By properly selecting the preliminary tension of the energy accumulator 25, for example, a compression screw spring, it can be achieved that this energy accumulator generates a force on the part of the path of movement of the part 11 that facilitates the shutdown process, and on the rest of the axial displacement, creates a force that counteracts the shutdown process. Thus, it is possible to provide a change in the direction of the force on the connecting rod.

 Further, the actuating device 1 comprises a spatial geometric element 40 having or bearing a curved profile and connected for transmitting rotation with the worm wheel 8. The connection of the element 30 with the worm wheel 8 can be accomplished by pressing in to transmit the torque, or using screws or rivets. You can also run the element 30 in one piece with the worm wheel 8. It is advisable to make the worm wheel by injection molding from plastic, performing the element 30 with its curved profile in one piece by pressure treatment or pressing it to the worm wheel. However, this part can also be made of metal.

 A force is applied to the element 30 carrying the curved profile in order to transmit it through the curved profile to the output element of the device for actuation. By modulating a curved profile, force can be modulated as a function of the path or movement during actuation. The energy accumulator 50 exerts a force effect on the curved profile directly or indirectly, for example, through a lever with a roller.

 A curved profile divides the force acting on it into a component in the direction of motion and a component in a direction perpendicular to the direction of motion, and the component in the direction of motion creates force support or force compensation.

 In FIG. 2 shows a device 100 for driving with a drive unit 101, for example an electric motor, with an output shaft 102 and with a gear located behind the shaft, for example a worm gear, the worm of which in FIG. 2 not shown. The worm is engaged with the worm wheel 103, which moves the output member 105 through the connecting rod 104. The connecting rod 104 is supported in the bearing in section 106, and the worm wheel is supported in the bearing in section 107. The motor shaft 102 rests in bearings 110 and 111.

 A spatial geometric element 120 is connected to the worm wheel 103 for transmitting rotation, having a contour 121 in the form of, for example, a curved profile or a curved disk. In the section 122, the lever element 123 is rotatably seated, and in the section 124 of the element 123 there is a rotating roller 125. The energy accumulator 126 loads the lever element 123 so that the roller 125 presses on the contour or profile 121 of the element 120. The energy accumulator relies on the protruding elements 130 and 131 in such a way that it cannot slip out of them, and they are made in such a way that they go into the central axial holes of the energy accumulator, in this case compression springs. Thanks to this installation, the energy accumulator is installed mainly reliably in order to avoid displacement and loss.

 The force produced by the energy accumulator 126 and transmitted through the lever 123 and the roller 125 to the circuit 121 is divided at the point of contact according to the usual parallelogram of forces into a component that acts in the radial direction and a component that acts in the circumferential direction. The power component in the radial direction acts centrally on the axis 107. The power component in the circumferential direction causes a force action on the connecting rod 104 and thereby on the output element 105. The force support or force compensation of the actuation force acting on the output element 105, achieved by this, can modulate as a function of the movement of the curved profile 121 of the spatial element 120, for example a curved disk or cam.

 Power components in the radial and circumferential directions correspond to the impact on a rotating curved disk. In the general case, the force acting on a curvilinear profile is divided into a component that is mainly parallel to the direction of movement or actuation, and a component that acts mainly perpendicular to the direction of motion or actuation.

 By controlling the force action or compensation of the compensation spring by means of a curve of the line, it is possible to obtain basically the desired nature of the change in the compensation force or the compensation moment, depending mainly on the particular application.

 In the example shown in FIG. 2, a spring 126 is fixed in the housing, which directly or indirectly through the lever 123 acts on the curved profile 121 on the worm wheel 103. When the distance from the point of contact of the spring with the curved profile to the axis of rotation 107 of the worm wheel changes, the moment changes in the circumferential direction. The curvilinear profile can be made such that this effective moment counteracts the moment caused by the force of driving the output element 105 or supports it. Using a compensation spring controlled by a curved line, it is possible, by modulating the profile of the curve, to limit, if necessary, the compensation effect to individual sections of the adjustable travel path, and this can be done so that when the curved profile 121 is rotated, the radius of this profile is changed only by part of the angle of rotation. In other parts of the rotation angle, a constant radius can be provided.

 The shape of the curved profile can provide targeted modulation of the force that acts or is applied in the direction of movement for actuation. In this case, the force action can, for example, be adjusted so that it acts in one direction along the entire actuation path or changes its sign at least once, i.e. direction. You can also modulate the value of the acting force as a function of the actuation path.

 By a spatial geometric contour, for example with a curved disk or curved profile, or with a modulated surface connected to a curved disk or cam, for example, we can mean surface 121 according to FIG. This surface has components in the axial direction and in the circumferential direction, and the surface or curved profile is modulated by modulating the radius as a function of the angle of rotation. The force is applied mainly in the radial direction and is divided into circumferential and radial components. The circumferential component of the impact force of the energy accumulator on the surface causes expedient power support of the drive. Equally expedient is the embodiment of FIG. 6a and 6b, when the surface has components in the circumferential and radial direction and creates axial modulation as a function of the angle of rotation, due to which the force acting in the axial direction as a result of separation into components has a component in the circumferential and axial directions, and the circumferential component serves to drive support. The above is appropriate for actuators with elements that make a circular motion. In devices with a rectilinear movement of elements, for example, in the device according to FIGS. 4-5b, it is advisable to provide that a surface with a spatial geometric contour, for example with a curved profile or with a curved disk or cam, has components in the radial and axial directions, and the modulation The surface is designed so that the distance or radius from the axis of motion is modulated as a function of the component in the axial direction. Due to this, a force effect is obtained, for example, on the system of rods and levers in the direction of movement, and the separation of force into components occurs under the action of the surface of a curved profile.

 In FIG. 3 shows an example embodiment according to FIG. 2, wherein the energy accumulator 200 is made in the form of a leaf spring fixed to the housing 202 by means of fixing means 201. A rotating roller 205 is mounted on the shelf 203 of the energy accumulator 200 in the bearing 204, and the energy accumulator 200 presses the roller 205 against the curved profile 206 spatial geometric element 207. A curved path or curved profile of the contour 206 of the element 207 is modulated in the radial direction as a function of the rotation of the element 207 in the circumferential direction. Due to this, it is possible to achieve power modulation, which leads to power support or to power compensation of the output element 210.

 Figure 4 shows a part of the power compensation device in the device for actuation, in which the force is transmitted from the energy accumulator through a curved profile to the output element. The force compensation device may cause force compensation or force support of the output element depending on the direction of the applied force.

 The power compensation device has an axially movable element 300, which is driven by a drive unit 301, such as an electric motor and gearbox. The axially movable element 300 has a contour or curvilinear profile 303 in the portion 302, which in the axial direction has a modulated surface, radius or distance. Further, the element 304 is connected to the actuated element, and the power support of the element 302 serves as power support for the actuated element. The force on the modulated section 303 is effected in such a way that the first angular lever 305 is supported for swinging in the section 311, and the second lever 306 in the same section 311, and an energy accumulator 307 is installed between the receiving sections 305a and 306a, which loads the receiving sections 305a and 306a compression.

 A rotating roller 308 is mounted on a portion 306a. Another rotating roller 309 is mounted on an end portion of a lever 305 on a bearing portion 310. When the power accumulator 307 is applied to sections 305a and 306a by force, the rollers 308 and 309 are pressed against the modulated surface 303 of element 302, so that the energy accumulator produces a supporting effect on the element 302 or 304. Through a curved surface or modulation of the section 302, 303, support or compensation of the force necessary to actuate the actuator is achieved.

 Fig. 4a shows a schematic diagram of a drive 301 that moves, for example, an element 300 through a gearbox. The element 300 has a section 302 provided with a curved surface or a curved profile 303. A roller 308, 309 acts on the curved profile, which is mounted to rotate in front of the support shoe 320, 321. The power accumulators 322, 323 are adjacent at one end to the support shoes, and rest at the other end in the housing. The support shoes 320, 321 are mounted with the possibility of sliding in the guides 324, 325. Through the rollers 308, 309, the force is transmitted from the energy accumulators to the curved profile 303, as a result of which the force acts on the element 302 and the output part 330 of the element 300. By modulating the curved profile 303 as a function of the axial extent of the element 300, a path-dependent force on the element 303 is achieved.

 In FIG. 4b shows another embodiment in which the actuator 303, for example, drives an element 300, which is provided with a curved profile 303 in section 302, then the element 300 has a section 330 on the output side, which acts on the element that controls the transmission system torque or gear. The impact on the curved profile 303 of the element 302 is made through the lever 335, mounted with the possibility of swinging on the plot 336, which is fixedly mounted in the housing. An energy accumulator 337 acts on the lever 335, which at one end 337a adjoins the lever, and is attached to the housing with the second end 337b. As a result of the force action, the roller 308 mounted for rotation on section 340 is pressed against the curved profile 303, as a result of which the force action is transmitted from the energy accumulator through the lever and the roller to the curved profile and output element 330.

 In FIG. 5a shows an element 350 that moves axially, and in a portion 351 it is controlled and driven by a drive unit. An element 352 is connected to the element 350, made with it in one piece or fixed on it. Element 352 has a modulated contact surface 353a, 353b. On the axis of rotation section 354, levers 355 and 356 are mounted to swing or rotate, which have sections 355a and 356a for installing an energy accumulator 357 therein, which pushes the elements 355 and 356 apart. In sections 360 and 361, rollers 362 and 363 are mounted, between which there is an element 352. The rollers 362 and 363 are rolled along the contour 353a, 353b, and under the action of the energy accumulator, pushing the levers, the rollers press the contour 353a, 353b, thereby acting on the element 352 As a result, the force action is transmitted from the energy accumulator 357 via levers and rollers to the curved surface 353a, 353b, and from it to the element 352 and further to the element 350.

 In FIG. 5 shows the embodiment of FIG. 5a in the form of arrow 370 in FIG. 5a. An element 350 is visible, on the portion 351 of which the drive acts and which, on the portion 371, acts on the actuated element. The sections 326a, 355a, as well as the levers 355 and 356 are shown. Next, the rollers 360 acting on the surface 353 and the element 352 are visible.

 In FIG. 6a shows part of a device for driving a torque transmission system or gearbox (400), the device having an element 402 that can rotate around an axis 401 under the action of the drive. The element 402 can be, for example, a worm wheel 8 of FIG. 1 or another a driven element, for example a gear wheel. An element 403 is connected to the driven element 402, which carries a curved profile 404, which is also connected directly to the element 402. The curved profile 404 of the element 403 is modulated in the axial direction, for which the axial coordinate of the modulated surface 404 varies in the circumferential direction.

 The energy accumulator 405 is fixed at one end 405a in the housing, for which the pin 405c is inserted into the opening of the energy accumulator, holding the spring in place. The end of the energy accumulator 405b is connected to the lever 406 by the portion 405d, so that the force of the energy accumulator 405 is transmitted through the lever 406 and the roller 407 to the curved surface or curved disk 404, and from there to the output element 402. The lever 406 rests on the section 406a in the bearing, and on the section 406b, the roller 407 is rotatably mounted. The force of the energy accumulator 405 is transmitted through the lever 406 and the roller 407 to the curved profile 404 mainly in the axial direction, and the force action on the element 402 occurs in circuitous direction. Thus, the embodiment of FIG. 6a creates a supporting force that acts in the circumferential direction relative to axis 401.

 In FIG. 6b further shows a unit 410 for power support or power compensation in a device for actuating a torque transmission system or gearbox, the element 412 being mounted rotatably about an axis 411 and can be set in motion and rotated using, for example, a drive unit. The element 412 can be made, for example, in the form of a worm wheel, as shown for example in Fig. 1, where it is indicated by the number 8. The element 413 is connected to the element 412 or is made integrally with it, and the element 413 is a generally cylindrical part, which has a curved profile at its outer periphery, for example an axially modulated protrusion. The curved profile 414 can be integral with the cylindrical element 413. The energy accumulator 416 is fixed at one end 416a to the fixing pin 416b of the housing 419, and its other end 416c is mounted on the lever with the fixing pin 416d. The lever 417 is supported on the swinging portion 417a, and a roller 418 is planted on the portion 417b, which, in the portion of the curved surface 415 of the curved profile 414, is supported in the axial direction, transferring the force of the energy accumulator to the element 402. The force of the energy accumulator 416 is in the axial direction, and with the help of a curved profile is converted to the impact in the circumferential direction of the element 412.

 In FIG. 6c shows an element of power compensation or force reduction or force support in a device for actuating a torque transmission system or gearbox, wherein element 432 is mounted on axis 431 and rotated by a drive unit. The cylindrical main body 433 is connected to the element 432 or is integral with it and carries a curvilinear profile 434. The energy accumulator 435 is connected by means of a fixing rod 439 with its end 435a to the body and acts on the plunger 436b, which moves linearly along the guides 438a and 438b. The pusher 436 has a roller or a sliding portion at its outer axial end that contacts the curved surface 434 of the element 433 to transfer power support from the energy accumulator 435 to the element 432. The guides 438a and 438b can be made sliding or on rolling bearings.

 FIG. 7a shows an element 500 that is mounted rotatably about an axis 501 and can be driven by a shaft 502 from a drive element or an intermediate gear. The peripheral section 503 of the element 500 is modulated in the radial direction, so that this section in the form of a curved disk can carry out modulated control. A trunnion 504 with an axis 505 is attached to the element 500, and during rotation of the element 500, the trunnion 504 moves along a circular path 506. The energy accumulator 507 is attached by means of a fixing rod 508 to the housing, and the fixing rod 508 is inserted into the hole at the end portion 507a, preventing shear or bulging power accumulator. At the end portion 507b, the energy accumulator is held by a fixing rod 509 having tabs 510a and 510b that allow the locking element 509 to swing relative to the journal 504. When mounting the energy accumulator in such a way that a tensile and shear load can act on it and it can also create such a load , it is possible to transmit power support to the element 500 through the pin, performing a force action with a change in the direction of the force and with the modulation of the force value. The output element 511 is made in the form of a pusher, which has a rotating roller 512 at its end portion 511a that abuts against the periphery 503 of the element 500. By depending on the angle of rotation of the modulation, the force of the energy accumulator acting on the element 500 and depending on the angle of rotation of the radius modulation of the element 500 can be used to obtain compensation or modulation of the force effect on the element 511.

In the embodiment according to figa, 7b shows a variant controlled by a curved contour of the compensation spring and the spring with the departure from the dead point or through the dead point on the pusher. In this embodiment, it is provided that, firstly, a spring is eccentrically fixed on the rotating disk, which, due to the initial tension, can create a moment relative to the axis of rotation of the disk, and in addition, it can actuate the coupling by contact with a curved profile on the disk. In this case, it is possible, having given the curvilinear profile the proper shape, to optimally coordinate the nature of the change in the clutch disengaging force with the nature of the change in the force of the compensation spring. The compensation force can, over a wide area of influence, have such a character of change that very closely corresponds to the nature of the change in clutch disengaging force. The shutdown force creates a moment acting on a curved disk. The relationship between these two quantities can be neglected for simplicity by friction, described as follows:

Figure 00000002

where M Last is the moment created by the power off,
r is the distance from the point of application of force to the curved disk to the pusher to actuate the clutch, and φ is the angle of rotation of the curved disk. The change in distance r corresponds to changes in the driving path
Figure 00000003

If an opposing force arises when the clutch is actuated, energy is released from the compensation spring on the rotating disk. In the event of a reverse action, i.e., when the pusher moves in the direction of the force, the energy released from the clutch spring can be reintroduced into the spring, which can lead to unloading of the drive element, for example, an electric motor.

 As a further improvement on the periphery of the curved disk, it is also possible to provide sections 520 for latching when the pusher roller enters such a section 520, which makes it necessary to apply increased force to exit this section.

 In FIG. 8a shows a power compensation or support unit in a device for actuating a torque transmission system and / or a gearbox, the element 600 being mainly disk-shaped mounted for rotation about an axis 601. The element 600 is rotationally driven by a drive shaft, for example, a connecting link 602, which causes the targeted rotation of the element 600. The periphery of the element 600 is made in the form of a radially modulated curved disk, which is within the first angular portion ka 604 and the second corner portion 605 has a radius that varies depending on the angle of rotation, and within this case, the corner portion 606 has a constant radius.

 A roller 607 mounted in a bearing 608 on a portion of the pusher abuts against a peripheral 603 having the shape of a curved disk, and the pusher 609 is driven from the element 602 through the element 600 and the roller 607. As a result of the rotation of the element 600 and the modulation of the radius, the axial movement of the element 609 to actuate the torque transmission system and / or to select or switch the gearbox.

 For power support, the energy accumulator in the form of a loop spring is mounted in such a way that the end 610a of the spring is fixed in the housing, for example by entering into the fixing portion of the housing 611. The other end of the spring 610b is connected to the element 600 by means of a geometric closure. The geometric closure is made in such a way that occurs in each position or rotation of the element 600, or that there is a free-wheeling angle in which there is no effect on the energy accumulator when the element 600 is rotated. Section 612, shown in Fig.8b, plays the role of such a section of free play, that is, the recess 612, which includes the end 610b of the spring 610, exerts a force on the spring only after passing a certain free angle. This corner portion 613 corresponds, for example, to that corner portion during which there is no radius modulation, i.e., the angle 613 corresponds in FIG. 8b to the corner portion 606.

The device according to FIG. 8a and 8b can be used, for example, for power compensation by means of a compensation spring to actuate the clutch using a curved disk, which is driven by, for example, an electric actuator. This is advisable when automating the process of switching the clutch and actuating the gearbox with two electric motor actuators. In this case, one actuator performs partial functions of coupling and switching, and the second - a partial selection function. Other types of separation of the functions of the clutch, gearshift and gearbox selection can also be carried out, and the process of selecting the method of putting the gearbox in action occurs between
switching zones, and the switching process is inside these zones. To conveniently turn off and turn on the torque transmission system, it is desirable to be able to quickly open the automated coupling and purposefully close it so that the coupling can be opened faster or slower depending on the operating condition, and closing is also faster or slower depending on the working state vehicle or operational parameters.

 The load on the actuator when the clutch is opened is usually the greatest, since when closed, the energy stored in the clutch release spring is released. The clutch release spring, for example, in a clutch with a disk (diaphragm) spring, is a disk (diaphragm). Since the actuation time increases with increasing load on the actuator, it is advisable to provide actuator support through an additional energy accumulator when the clutch is opened.

 By means of an electric motor actuator, for example for the clutch and shift functions, it is possible, for example, to drive a curved disk divided into three sections by means of a self-braking gearbox.

 In the first section, for example in the corner section 605, the clutch is open, in the second (for example 606) it continues to be open, and in the third (for example 604) the clutch closes again. For a curved disk with a linearly increasing or decreasing stroke or with increasing or decreasing stroke in accordance with another purposefully selected function of the rotation angle or path, a drive torque proportional to the coupling characteristic is required. In combination with a linearly acting compensation spring, the load moment when the clutch opens is initially negative. Such a linearly acting compensation spring for controlling the torque transmission system is shown, for example, in Fig. 1, where it is indicated by the number 25. Due to the presence of a self-braking actuator gearbox, the spring cannot accelerate this mechanism sufficiently, as a result of which the actuator in this case can work without load or mostly no load. In the second section of the curved disk, under the action of which the actuator performs switching, the clutch remains open. In this case, the compensation spring passes its free-wheeling section without loading. In the third section, within which the clutch is closed, the energy stored in the clutch release spring is released, as a result of which the load moment is negative at first. Due to the self-braking of the actuator or its gearbox, the actuator in this case acts mainly without load. Over approximately 2/3 of the shutdown path, the driving force is close to zero. In this area, the clutch often works to control the transmitted moment, which occurs for example in various operating states, in particular when switching on or off, or after switching processes or in situations with "torque tracking" control.

 In this case, “moment tracking” refers to the control of the torque transmission system provided by the drive motor, minus the moment consumed by other systems, such as a condensing system.

 Since actuation in such a section takes place almost without the application of force, the actuator can transmit torque to the clutch with low energy consumption. However, using the curved profile 603 on the disc 600, other actuation characteristics can also be realized. Until the clutch closes completely, the actuator must work against the compensation spring until it is tensioned again. A curved disk can also be made with a curved profile at the periphery or at the end of the cylinder. Instead of a curved disk, you can also apply any type of gear to obtain uneven movement with the phases of locking and movement. The compensation spring can be fixed in the housing with emphasis in a curved disk, but also on a curved disk with emphasis in the housing.

 The use of a torsion spring, for example a loop spring, which, when the coupling is opened and closed, interacts with a curved disk, is an appropriate embodiment of the invention. When the clutch closes, the compensation spring is charged, and the energy stored in the switch-off spring is converted to the pre-tension of the compensation spring. When the clutch opens, the compensation spring must compress or act on the actuator - the clutch release spring. In that section of the angle of rotation of the curved disk, on which the actuator performs switching or, for example, carries out the selection process, the clutch remains open, the compensation spring is relaxed and does not apply force to the driven link.

 Fig. 9 schematically shows an actuator 701 in which a drive unit 702, for example an electric motor, is mounted or flanged externally. The output shaft 703 of the engine is connected by the worm 704 to the worm wheel 705 to drive the output element 706, such as a pusher or connecting rod. For power compensation, a curved disk 707 with a modulated surface 708 is attached to the worm wheel, with at least one energy storage device 709, 710 acting on the disk 707. By modulating the curved disk or surface 708, a modulation of the force with which the energy storage acts on the output element 706 is achieved.

 10, the same content is illustrated more clearly, with a circular contour 750 depicting the outer surface of the worm wheel 705. Contour 751 corresponds to the contour of a curved disk 708.

Arrow 752 shows the force impact of the energy accumulator acting on the curved disk 751. Radius r 753 characterizes the distance from the center of the worm wheel 750, angle φ 754 characterizes the angle of rotation. The arrow 755 corresponds to the driving force acting on the output element, and the radius R 756 corresponds to the distance from the point of application of the driving force to the axis of rotation 757. Therefore, the compensation action of the compensation spring, which acts along the arrow 752 on the curved disk, is expressed by the formula:
M komp = dr / dφ * F feder .

 As an embodiment, the energy accumulator applying a force of 752 can be made in the form of a bending spring, leaf spring, or acting through a spring lever.

In FIG. 11 shows a design of a curved disk 800 used in an actuator for the combined actuation of a coupling and a gearbox. When turning 360 o there is a process of disengagement, the switching process and the process of turning on the coupling. Starting at point 801, at which the clutch is closed, the curved disk is automatically actuated in the direction of arrow 802 to achieve modulation of the force as a function of the path or the angle of actuation. To the beginning of the actuation when the clutch is closed, the energy accumulator 803 enters with the roller 804 in the area 801 and acts on the curved disk.

 At the corner section 805, the clutch is switched off, the switching process takes place at the corner section 806, the gear stage is displayed in the first half of the corner section, a neutral position is reached at point 807, and another gear stage is entered in the second half of the corner section 806 before at the corner section 808 the clutch will be engaged again. The recess 809 and 810 can be used to fix the neutral section or closed coupling.

On Fig shows the modulation of the radius R as a function of the angle of the curved radius according to 11. At an angle of 0 o, the radius is maximum or mostly maximum, and according to curve 900 and 901, a maximum or minimum takes place depending on the fixation. In the region from the angle 0 ° to the angle 90 °, the modulation of the radius can occur according to curves 902a, 902b or 902c, and at 90 ° a minimum is reached. In the region from 90 ° to 180 ° , the radius modulation increases again, and the transition in the region of 180 ° can pass through the minimum fixing position 903 or through a maximum of 904 before the minimum is reached in the corner section of 270 ° . In the area from 270 o to 360 o the modulation of the radius increases again. In the range from 0 o to 90 o the process of exposure to the coupling takes place, moreover, at 0 o the coupling is closed, and at mainly 90 o the coupling is open. In the range from 90 ° to 180 ° , a switching process occurs, and at 180 ° , a neutral position is reached, and in the section from 180 ° to 270 ° , a switching process occurs before the coupling closes again in the section from 270 ° to 360 ° .

On Fig shows the effect of compensation on the forces and moments on the clutch and the switching force. Curve 950 corresponds in the first section φ1 to the characteristic of the shutdown force, in the section from φ1 to φ2 to the characteristic of removing the gear stage in accordance with curve 950a, in the corner section from φ2 to φ3 in accordance with curve 950b to the process of introducing the gear stage, and in the corner section from φ3 to φ4 in accordance with curve 950c - the switching process. Curve 951 corresponds to the force or the moment of compensation, and in section 951a the compensation is negative, when φ1 the direction of the force changes to positive, in the section from φ1 to φ2 in accordance with curve 951 the compensation is positive, in the section from φ2 to φ3 in accordance with curve 951b it is negative, and at φ3 the direction changes again, as in the section from φ3 to φ4 in accordance with curve 951c, where the compensation is positive. The solid line 952 shows the resulting line or the resulting moment, as the sum of the forces 950 on the coupling and the switching forces and the compensation forces 951. You can see a generally noticeable decrease in the maximum values compared to the net forces on the coupling and the switching forces according to curve 950. On the corner section from 0 o to φ1 there is a reduced force on the coupling, in the region from φ1 to φ2, an increase in the forces on the coupling is visible, while in the region from φ2 to φ3, the switching forces decrease. A maximum of 954 occurs due to synchronization and unlocking processes, a maximum of 955 arises from the process of putting the teeth into gear when shifting, and a maximum force of 956 arises from running into the stop in the gearbox. In the region from φ3 to φ4, the characteristic of the switching force decreases in value from 950 s to 952 s. In general, a reduction in coupling forces and switching forces is achieved.

 Fig. 14 shows a part of the actuator according to Fig. 1 with a worm wheel 1001, a connecting rod 1002, and an energy accumulator 1003. The energy accumulator 1003, in contrast to the energy accumulator 25 in Fig. 1, is composed of two energy accumulators 1004 and 1005 arranged one after the other, and a two-stage characteristic is achieved due to the fact that the energy accumulator 1004 is made in the form of a softer spring than the energy accumulator 1005. The element 1006 serves as a stop for pre-tensioning. Thanks to the use of energy accumulators of different stiffness, it is possible to obtain a multi-stage characteristic of the effect of the compensation force.

 In FIG. 14a and 14b show exemplary embodiments with two energy accumulators, and the use of more than two energy accumulators may be appropriate to obtain a multi-stage force characteristic. The power accumulator 1050 is inserted into the holder 1051, where it can be subjected to pre-tensioning. The energy accumulator 1052 acts through the element 1053 on the pre-tensioned energy accumulator 1050, and when axially acting on the element 1054, the energy accumulator 1052 first perceives and deforms the force until the pre-tension force is overcome, after which the energy accumulator 1050 begins to compress.

 In FIG. 14b shows an embodiment in which the element 1055 between the energy accumulators 1050 and 1052 has a cup-shaped shape, whereby the axial structural space can be better used if the actuation path is sufficiently small and allows such a structural form. In the case of a relatively large axial path of actuation, the embodiment according to figa is advisable. Element 1051 has a cup shape and element 1055 has at least a cup cross section.

 The pre-tensioned springs of FIGS. 14a and 14b may have less rigidity than springs not subjected to pre-tension.

 Fig. 15 shows an example of a compensation spring assembly in a device for actuating a torque transmission system and / or gearbox, where at least one spring assembly 1101a, 1101b is mounted in the housing 1001, which is connected to a support 1102, 1103 with the housing is stationary, but with the possibility of swinging, and in addition, by means of connection 1104, 1105 is swingably connected to the driven element 1106. The element 1106 in the section 1106a is connected to the drive so that axial movement can occur, and on the output side section 1106 acts on the output element to actuate it. When the element 1106 is axially moved, the hinge sections 1104 and 1105 move in the axial direction, while the hinge sections 1102 and 1103 remain in place, resulting in a relative movement of the elements acting on the energy accumulators 1110 and 1111, which exert a force on the element 1106. The energy accumulators 1110 and 1111 are arranged in such a way that they in at least one (for example, final) position exert a force action in only one direction perpendicular to the axis of motion of element 1106. However, with eschenii element 1106 is one component of the force feedback element on the spring 1106 acts in the direction of movement of the element. The force can act in the opposite direction, creating a component in the direction of the axis of motion. This is schematically illustrated in FIG. 15b, where the element 1120 is mounted movably, and the energy accumulators 1121 and 1122 are connected to both the housing and the element 1120, for example, in the final position, the springs 1120 and 1121 according to the image are pre-tensioned. During the axial movement of the element 1120, the suspension point 1123 moves in the same direction to the point 1124, as a result of which the force action of the energy accumulators 1121 and 1122 also appears in the axial direction. Energy accumulators can be made in such a way that a dead point is reached in the final position, so that they do not act as springs with a transition beyond the dead point. However, it may also be appropriate for the energy accumulators to act as springs with a transition through a dead point, and then an axial force acts at the end point of actuation. This axial force is absent when the springs are at a dead point at the end of the actuation path.

 On Fig shows a device 1200 for actuating with the drive unit 1201 in the form of an electric motor. The electric motor 1201 rotates the shaft 1202, which in section 1203 rests and axially abuts the element 1204. In addition, shaft 1202 in section 1203 is inserted into the hole or guide 1205 in the wall of the housing 1206. A worm 1207 is connected to the shaft 1202 for transmitting rotation. The worm 1207 engages with the worm wheel 1208. which is mounted in the bearing 1209. To the worm wheel 1208 is attached or made with it for one whole gear wheel 1210. The gear wheel 1210 is engaged with the gear rack 1211, which controls the piston 1213 traveling cylinder 1214 operated by pressure medium, for example the leading cylinder. The gear rack 1211 is supported by a roller 1212 or a bearing in the radial direction of the gear wheel 1210. The worm wheel 1208 or a wheel connected thereto, for example a gear wheel 1210, has a curved profile, which is directly or indirectly affected by the energy accumulator 1219. The energy accumulator 1219 is installed between the supporting section of the housing 1206 and a support section of the lever 1217, which is mounted with the possibility of swinging in the bearing 1218. On the lever there is a roller 1216 mounted in the bearing 1222. The roller rolls along the contour of the curved profile 1215, ozdeystvuya on it and thus forming a device on the output element due to the form of the power profile, depending on the path and position. In the housing 1206, a support portion 1220 is provided, and in the arm 1217, a support portion 1221, which are included in the end sections of the energy accumulator, in this case a compression screw spring, to basically give the energy accumulator the desired position and to ensure that it cannot be lost.

 In FIG. 17 shows another expedient design of the proposed device 1300 for actuation. The device 1300 has a drive unit 1301, which can be made in the form of an electric motor. An electric motor rotates a shaft 1302, which is supported on a portion 1303 in a sliding or rolling bearing. A worm 1304, which is meshed with the worm wheel 1305, is planted on the shaft 1302 for transmitting rotation to it. The worm wheel 1305 has a contour or curved profile 1306 against which a sliding or rotating element, such as a roller 1307 or a support shoe, abuts. The roller 1307 is mounted on a lever or on a connecting rod 1308, which acts on the piston 1309 of the driving cylinder 1310, driven by a pressure medium, such as a hydraulic cylinder. A roller 1307 is rotatably seated in a bearing 1311. A lever 1312 pivotally suspended on the other side in a section 1313 is pivotally suspended on a portion of a bearing 1311. A lever 1312 directs the movement of the connecting rod 1308 under the action of the rotating circuit 1306 when the gear wheel 1305 is rotated. Modulation can be achieved. the piston of the driving cylinder as a function of the path of rotation of the worm wheel or, in general, as a function of the driving movement.

 In the embodiments according to FIGS. 16 and 17, embodiments are shown in which preferably the axis of the engine, in particular the shaft, is parallel to the axis of the connecting rod or pusher of the output element. In addition, the worm wheel can form one plane with the motor shaft, and the connecting rod or pusher can be located in this plane or outside it.

 The subject invention also relates to the previously filed DE 19622641, the contents of which are fully within the scope of the disclosure of the subject invention.

 The claims indicated in this application are proposals not prejudging the receipt of further patent protection. The applicant reserves the right to claim priority for other features that have so far been disclosed only in the description and (or) drawings.

 The references contained in the additional claims indicate a new execution of the subject matter of the main paragraph, characterized by the features of this additional paragraph, they should not be understood as a refusal to obtain an independent patent protection for the signs of the additional referenced paragraphs.

 The objects of these additional claims form independent inventions that have a form independent of the objects of the previous additional claims.

 The invention is also not limited to the performance example (s) given in the description. On the contrary, in the framework of the present invention, numerous varieties and modifications are possible, in particular such variants, elements and combinations and (or) materials, which, for example, due to the combination or variation of individual features, elements and steps of the methods described in the general description and in the forms of execution or claims that are contained in the drawings have inventive novelty and, due to combinable features, lead to a new subject or to new steps of the methods or sequences of steps of the methods, in t m including if they relate to methods of manufacturing, testing and operation.

Claims (38)

 1. A device for automatically switching, and (or) selecting a gear ratio of a gearbox, and (or) for automatically actuating a torque transmission system in a drive circuit of a vehicle, which includes a drive unit and, if necessary, a gearbox, as well as functionally connected with them by means of a drive connection, an output element for driving it, with at least one energy accumulator acting on the output element, characterized in that with the drive connection a force-sensing element is connected to a spatial geometric contour, for example, with a curved profile, or with a curved disk, or with a cam, and the force of at least one energy accumulator is transmitted to the output element through the spatial geometric contour of the element.
 2. A device for automatically switching, or selecting a gear ratio of a gearbox, or for automatically actuating a torque transmission system in a drive circuit of a vehicle, which includes a drive unit and, if necessary, a gearbox, as well as an output functionally connected to them by means of a drive connection an element with at least one energy accumulator acting on the output element, characterized in that in the drive connection between the drive unit and the output element There is a force-sensing element with a spatial geometric contour, for example with a curved disk, a curved profile and (or) with a cam, and the force effect of at least one energy accumulator is transmitted to the output element through the said spatial geometric contour.
 3. The device according to one of the preceding paragraphs, characterized in that the force-sensing element with a spatial geometric contour, for example with a curved disk, curved profile or with a cam, is configured to be exposed to at least one energy accumulator in the area of the spatial contour, s transferring force to the output element from the energy accumulator through said spatial geometric contour.
 4. The device according to one of paragraphs. 1-3, characterized in that the force-sensing element with a spatial geometric contour, for example a curved disk, curved profile, curved surface or cam, is driven by the actuation of the controlled element.
 5. The device according to one of paragraphs. 1-4, characterized in that when a force is applied to the force-sensing circuit and when an element with a force-sensing circuit moves, the force action of the energy accumulator on the output element is modulated.
 6. The device according to one of paragraphs. 1-5, characterized in that the element with a force-sensing circuit when actuating the control element is configured to move in at least one direction.
 7. The device according to p. 6, characterized in that the element with a force-sensing circuit is configured to move in a straight line and (or) rotate, and (or) in the axial, and (or) in the radial direction, and (or) in the circumferential direction .
 8. The device according to one of the preceding paragraphs, characterized in that the force-sensing spatial geometric contour of the element is oriented rectilinearly, and (or) in the axial, and (or) in the radial direction, and (or) in the circumferential direction.
 9. The device according to one of paragraphs. 1-8, characterized in that the force of at least one energy accumulator on the force-sensing spatial geometric contour of the element is oriented mainly in a straight line, and (or) in the axial, and (or) in the radial direction, and (or) in the circumferential direction.
 10. The device according to one of paragraphs. 1-9, characterized in that the modulation of the force-sensing spatial geometric contour of the element is mainly oriented rectilinearly, and (or) in the axial, and (or) in the radial direction, and (or) in the circumferential direction.
 11. The device according to one of paragraphs. 6-10, characterized in that when a force is applied to the circuit, for example by at least one energy accumulator, the force acts at least mainly in the direction of the output element or in the opposite direction.
 12. The device according to one of paragraphs. 1-11, characterized in that when a force is applied to the circuit, for example, by at least one energy accumulator, the force is separated, at least mainly in the direction of movement of the actuation of the output element and (or) in the direction perpendicular to actuation movement.
 13. The device according to one of paragraphs. 1-12, characterized in that a gearbox is integrated in the drive connection between the drive unit and the output element.
 14. The device according to one of paragraphs. 1-13, characterized in that the spatial geometric element with a force-sensing circuit is in functional connection with the drive unit, the drive connection element or with the output element.
 15. The device according to one of paragraphs. 1-14, characterized in that the element with a spatial geometric force-sensing circuit has a rotatably mounted curved disk, a curved surface and / or at least one cam.
 16. The device according to one of paragraphs. 1-15, characterized in that at least one energy accumulator that exerts a force on the spatial geometric contour has a shoe, a roller and (or) a rolling bearing, which the energy accumulator relies on this circuit.
 17. The device according to one of paragraphs. 1-16, characterized in that at least one energy accumulator is configured to act on an element, for example a lever, which is mounted movably in one section and has a support shoe, roller or rolling bearing in the second section, acting on the spatial geometric contour item.
 18. The device according to one of paragraphs. 1-17, characterized in that at least one energy accumulator is configured to act on an element that rests in straight guides and has a contour of a spatial geometric element.
 19. The device according to one of paragraphs. 1-18, characterized in that at least one energy accumulator is configured to act on the tick-shaped element, which in one section is mounted movably and acts on the contour of the spatial geometric element.
 20. The device according to one of paragraphs. 1-19, characterized in that at least one energy accumulator is configured to act on an element with a spatial geometric contour, for example, on a reference section in the form of an eccentrically arranged pin, and the output element is based on a section of the spatial geometric contour.
 21. The device according to one of paragraphs. 1-20, characterized in that at least one energy accumulator is configured to act on an element with a spatial geometric contour, for example, on a reference section in the form of an eccentrically arranged pin, and the element acting on the output element is supported by a spatial geometric section contour.
 22. The device according to one of paragraphs. 1-21, characterized in that the bearing on the spatial geometric contour and (or) the impact on the spatial geometric contour occurs by sliding, rolling or through a roller.
 23. The device according to one of paragraphs. 1-22, characterized in that the drive unit is an electric motor, electromagnetic or electromechanical device.
 24. The device according to one of paragraphs. 1-22, characterized in that the drive unit is a device driven by a pressure medium, for example, a hydraulic, hydropneumatic or pneumatic device.
 25. The device according to one of paragraphs. 1-24, characterized in that as a result of the movement of the spatial geometric circuit and the application of force to this circuit, the force action on the output element of the device is modulated as a function of the path to drive the output element.
 26. The device according to one of paragraphs. 1-25, characterized in that the power support occurs, at least on part of the path of actuating the output element.
 27. The device according to one of paragraphs. 1-26, characterized in that during the movement to activate the force support, if necessary, changes the sign of its direction.
 28. The device according to one of paragraphs. 1-27, characterized in that at least one energy accumulator exerts a force on the output element, and at least one energy accumulator is made in the form of a spring with a departure from the dead point.
 29. The device according to p. 28, characterized in that it is installed one opposite the other two energy storage, which act on the output element in the form of springs with departure from the dead point.
 30. The device according to p. 28, characterized in that at least one energy accumulator is made in the form of a spring with departure from the dead center, the first end section is pivotally connected to the output element, and the second end section, for example, is pivotally connected, for example, to the body.
 31. The device according to one of paragraphs. 1-30, characterized in that it is intended to control the driven element, for example, to switch, and (or) select the gear ratio of the gearbox, and (or) to actuate the torque transmission system in the drive circuit of the car, which includes a drive unit and, if necessary, a gearbox, as well as an output element operatively connected to them by means of a drive connection, for actuating with at least two energetically affecting output element batteries installed in a row one after another.
 32. The device according to one of paragraphs. 1-31, characterized in that at least one energy accumulator has a preliminary tension.
 33. The device according to one of paragraphs. 1-32, characterized in that at least one energy accumulator is a spring, for example a compression spring, leaf spring, loop spring or an elastic element made of metal, rubber material or plastic.
 34. The device according to one of paragraphs. 1-33, characterized in that the element with a spatial geometric contour is made of metal or plastic.
 35. The device according to one of paragraphs. 1-34, characterized in that the element with a spatial geometric contour is made in one piece with the detail of the gearbox.
 36. The device according to one of paragraphs. 1-34, characterized in that the element with a spatial geometric contour is made in one piece with the output element.
 37. The device according to one of paragraphs. 1-34, characterized in that the element with a spatial geometric contour is made in one piece with the element of the functional connection between the drive unit and the output element.
 38. The device according to one of paragraphs. 1-34, characterized in that the element with a spatial geometric contour is connected to the element in a functional connection between the drive unit and the output element.
RU97109351/28A 1996-06-05 1997-06-04 Change-over device RU2213017C2 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE19622643 1996-06-05
DE19622641.4 1996-06-05
DE19622643.0 1996-06-05
DE19622641 1996-06-05

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RU2213017C2 true RU2213017C2 (en) 2003-09-27

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JP (1) JPH1081158A (en)
BR (1) BR9703466A (en)
DE (2) DE19723393B4 (en)
FR (2) FR2749635B1 (en)
GB (1) GB2313886B (en)
IT (2) IT1292079B1 (en)
RU (1) RU2213017C2 (en)

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IT1292079B1 (en) 1999-01-25
GB2313886B (en) 2001-01-03
DE19723393A1 (en) 1997-12-11
ITMI971316A1 (en) 1998-12-04
FR2749635B1 (en) 2001-03-23
BR9703466A (en) 1998-11-10
GB2313886A (en) 1997-12-10
ITMI971317A1 (en) 1998-12-04
FR2796117B1 (en) 2002-03-01
ITMI971317D0 (en) 1997-06-04
JPH1081158A (en) 1998-03-31
FR2796117A1 (en) 2001-01-12
DE19723393B4 (en) 2016-02-18
GB9711401D0 (en) 1997-07-30
IT1292080B1 (en) 1999-01-25
DE19758518B4 (en) 2016-03-03
ITMI971316D0 (en) 1997-06-04
FR2749635A1 (en) 1997-12-12

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