WO2008071567A1 - Système de commande pour une boîte de vitesses - Google Patents

Système de commande pour une boîte de vitesses Download PDF

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Publication number
WO2008071567A1
WO2008071567A1 PCT/EP2007/063113 EP2007063113W WO2008071567A1 WO 2008071567 A1 WO2008071567 A1 WO 2008071567A1 EP 2007063113 W EP2007063113 W EP 2007063113W WO 2008071567 A1 WO2008071567 A1 WO 2008071567A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure medium
piston
control device
medium chamber
pressure
Prior art date
Application number
PCT/EP2007/063113
Other languages
German (de)
English (en)
Inventor
Ludger Ronge
Kai Heinrich
Markus Ulbricht
Henrik Schuh
Manfred Vetter
Klaus Wöhr
Gerhard Birkenmaier
Josef Bader
Andreas Graf
Karl-Fritz Heinzelmann
Hubert KÖNIG
Gerhard HÖRING
Kim Führer
Mario Steinborn
Bernhard Walter
Frank Gessler
Original Assignee
Zf Friedrichshafen Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2008071567A1 publication Critical patent/WO2008071567A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/006—Hydraulic "Wheatstone bridge" circuits, i.e. with four nodes, P-A-T-B, and on-off or proportional valves in each link
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F15B11/12—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action
    • F15B11/121—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action providing distinct intermediate positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1447—Pistons; Piston to piston rod assemblies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/2807—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted using electric control signals for shift actuators, e.g. electro-hydraulic control therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/30575—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve in a Wheatstone Bridge arrangement (also half bridges)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/68—Inputs being a function of gearing status
    • F16H2059/6807—Status of gear-change operation, e.g. clutch fully engaged
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/68—Inputs being a function of gearing status
    • F16H2059/683—Sensing pressure in control systems or in fluid controlled devices, e.g. by pressure sensors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H2061/283—Adjustment or calibration of actuator positions, e.g. neutral position

Definitions

  • the present invention relates to a control device for a transmission comprising a pressure medium source, to the pressure medium source connected first and second controllable valve devices, an adjusting device for adjusting the transmission and a control device for controlling the controllable valve devices.
  • the present invention further relates to a transmission with such a control device and a method for controlling a transmission.
  • DE 103 47 493 A1 discloses a vehicle transmission with a control device which has an adjusting device for adjusting the transmission.
  • the known adjusting device comprises an actuating cylinder, in which a piston is guided in the longitudinal direction, wherein a piston rod extends in the form of a switching rod from the actuating cylinder.
  • the actuating cylinder in this case comprises a first and a second cylinder part, wherein the first cylinder part is formed by a region of a connection plate which serves to connect a coupling device to the vehicle transmission.
  • the disclosed control device comprises a pressure medium source which is connected via a supply line to a pressure relief valve.
  • the pressure relief valve is followed by two parallel and controllable valve devices.
  • On the two valve devices in turn follows an adjusting device for adjusting the transmission.
  • the known adjusting device has in this case a first pressure medium chamber which can be supplied with pressure medium via the first valve device.
  • the adjusting device has a second pressure medium chamber, which in turn can be supplied with pressure medium via the second valve device.
  • the two pressure medium chambers are separated by a movable piston. separates, on which a piston rod is arranged, which serves as an actuator of the actuating device.
  • the document proposes to control the controllable valve devices as a function of the pressure determined within the pressure medium chambers.
  • the adjusting device can be moved by pressurizing the first pressure medium chamber and emptying the second pressure medium chamber from a first position to a second position.
  • the adjusting devices are constructed particularly expensive. For example, at a control device whose piston can be moved to a first position, an intermediate position and a second position, at least two drag pistons on the actual piston required to bring the piston in the intermediate position when the same pressure prevails in both pressure medium chambers. Only through the use of two drag pistons, it is possible to freely choose the piston diameter on the two sides of the piston, resulting in a greater freedom of design for the developer.
  • the present invention is therefore an object of the invention to provide a control device for a transmission, the adjusting device on the one hand can be particularly simple in construction and on the other hand allows greater latitude of development of the developer.
  • the present invention is also based on the object to provide a transmission with such an advantageous control device.
  • the invention has for its object to provide a method for controlling a transmission.
  • the present invention relates to a control device for a transmission.
  • the control device has a pressure medium source.
  • a pressure medium for example, air or oil in question, so it may be a pneumatic or hydraulic control device.
  • a first and second controllable valve device are connected.
  • the valve devices may be, for example, solenoid valves.
  • the control device further comprises an adjusting device for adjusting the transmission with a first pressure medium chamber, which is connected to the first controllable valve device, and a second pressure medium chamber, which is connected to the second controllable valve device.
  • the pressure medium chambers are separated by a movable piston, which can be moved from a first position via an intermediate position to a second position.
  • the movable piston or a piston rod attached thereto can thus act as an actuator for adjusting the transmission. Due to the three possible positions, a transmission can be switched thanks to the control device, for example in a first switching position, in a neutral position and a second switching position.
  • the adjusting device can serve, for example, the choice of the shift gate or the adjustment of the gears in the transmission.
  • the control device further comprises a control device for controlling the controllable valve devices, wherein the control device is preferably designed as an electrical control device.
  • the control device is in such a way with the controllable valve devices in the connection, that the respective pressures within the pressure medium chambers can be changed independently, so that the piston can be brought both into the intermediate position and held in the intermediate position. The latter can be achieved for example by appropriate modulation of the pressure within the pressure medium chambers, so that a balance of power is achieved.
  • the control device according to the invention has in contrast to the prior art has the advantage that the adjusting device no longer has to have two drag piston to bring the piston at different cylinder diameters on both sides in an intermediate position or center position.
  • the piston as well as the entire adjusting device on the side of the first pressure medium chamber be constructed differently than on the side of the second pressure medium chamber, wherein the intermediate position is achieved by the pressure in the first pressure medium chamber and the pressure in the second pressure medium chamber is changed or modulated accordingly ,
  • the developer of the actuator thus has a greater latitude in the design of the same.
  • the piston has an active surface facing the first pressure medium chamber and an active surface facing the second pressure medium chamber.
  • the effective surface are summarized those surfaces on the respective piston side to understand that would cause by their design displacement of the piston in the direction of movement, when a pressure acts on these surfaces.
  • the control device interacts with the controllable valve devices in such a way that the pressure in the first pressure medium chamber is matched to the active surface facing the first pressure medium chamber and the pressure in the second pressure medium chamber is matched to the effective surface facing the second pressure medium chamber Piston is held by an equilibrium of forces in the intermediate position.
  • the effective area facing the first pressure medium chamber could be larger than the effective area facing the second pressure medium chamber.
  • the pressure in the first pressure medium chamber would have to be selected to be correspondingly smaller than the pressure in the second pressure medium chamber in order to achieve an equilibrium of forces that keeps the piston in the intermediate position.
  • the two active surfaces of the piston are designed such that there is an imbalance of forces in pressure equality in the pressure medium chambers. This means that the piston can have completely differently shaped active surfaces on its two sides, so that the designer has greater freedom in designing the adjusting device for the control device.
  • the effective area of the piston facing the first pressure medium chamber is therefore greater or smaller than the effective area of the piston facing the second pressure medium chamber.
  • the first pressure medium chamber can be selectively connected to the pressure medium source or a pressure medium sink with the aid of the first controllable valve device.
  • the second pressure medium chamber can be selectively connected to the pressure medium source or the pressure medium sink by means of the second controllable valve device.
  • the first and / or second controllable valve device has a 3/2-way valve for the inlet and outlet of the pressure medium in the first and second pressure medium chamber.
  • the 3/2-way valves have proven themselves in practice and can be designed for example as a solenoid valve.
  • the first and / or second controllable valve device has an inlet valve for admitting and an outlet valve for discharging the pressure medium into or out of the respective pressure medium chamber.
  • an inlet valve for admitting and an outlet valve for discharging the pressure medium into or out of the respective pressure medium chamber.
  • this can also be achieved a valve position in which both the inlet valve and the exhaust valve is closed. As a result, a pressure generated in the respective pressure medium chamber can be securely held.
  • the inlet valve and / or outlet valve is a 2/2-way valve.
  • a pressure determining device for determining the pressure within the first and second pressure medium chamber.
  • the pressure determining device may for example have corresponding pressure sensors in the pressure medium chambers or in feeding lines.
  • the determined pressure can serve, for example, as a basis for the control by the control device.
  • a position determining device is furthermore provided for determining the position of the piston.
  • the determined position of the piston which can be determined for example via displacement or position sensors, serve as a basis for the control of the controllable valve devices.
  • controllable valve devices can be controlled in a particularly preferred embodiment of the control device according to the invention in dependence on the determined pressure within the pressure medium chambers and the determined position of the piston by the control device.
  • the control device on the piston further only a drag piston is provided, the effective surface of the first pressure fluid chamber is facing. Thanks to the control can therefore be dispensed with a second drag piston, while the intermediate position of the piston can be safely reached and maintained.
  • the design of such a control device is much shorter and the number of components is reduced.
  • the active surface of the drag piston and the first pressure medium chamber facing the effective surface of the piston together are greater than the second pressure medium chamber facing effective surface of the piston.
  • the effective area of the piston facing the first pressure medium chamber is smaller than the effective area of the piston facing the second pressure medium chamber.
  • the transmission according to the invention has a control device of the type described above.
  • the inventive method for controlling a transmission comprises the method steps: providing a control device for a transmission with an adjusting device for adjusting the transmission with a first pressure medium chamber and a second pressure medium chamber, wherein the pressure medium chambers are separated by a movable piston, which from a first Position can be moved via an intermediate position in a second position, and changing the pressures within the pressure medium chambers independently, so that the piston is brought into the intermediate position and held in the intermediate position.
  • the pressures within the pressure medium chambers are changed until the piston is held in the intermediate position by an equilibrium of forces. This means that the piston is acted upon by a force from the first pressure medium chamber, while a second force acts on the piston on the side of the second pressure medium chamber, these forces compensating each other.
  • the method steps furthermore include determining the pressure in the first and second pressure medium chambers, Determining the position of the piston and changing the pressures in the pressure medium chambers in dependence on the determined pressure in the first and second pressure medium chamber and the determined position of the piston performed.
  • FIG. 1 is a schematic representation of a first embodiment of the control device according to the invention for a transmission
  • Fig. 2 is a schematic representation of a second embodiment of the control device according to the invention for a transmission
  • Fig. 3 is a partial side view of a possible adjusting device for the control devices of Fig. 1 and 2 in a sectional view.
  • Fig. 1 shows a first embodiment of the control device 1 according to the invention for a transmission.
  • the control device 1 initially has a pressure medium source 2 which comprises both a pressure medium pump 3 and a pressure medium reservoir 4.
  • a pressure medium for example, air or oil come into question.
  • the pressure medium pump 3 is connected at its ansaug tenui- end with a pressure medium line 5, the end of which projects into a pressure medium sink 6.
  • a supply line 7, At the other end of the pressure medium pump 3 is followed by a supply line 7, to which also the pressure fluid reservoir 4 is provided.
  • the supply line 7 branches off at a branch point 8 in two supply sub-lines 9, 10.
  • a first controllable valve means 1 1 connected to the pressure medium source 2, while a second controllable valve means 12 is connected via the supply part line 10 to the pressure medium source 2.
  • the first and the second controllable valve device 1 1, 12 are each formed by a 3/2-way valve. Said valve devices 11, 12 can be adjusted via an electromagnet 13, 14, which is connected via a control line 15, 16 to an electrical control device 17.
  • Each of the two valve devices 1 1, 12 has a pressure medium input 18, 19, which is connected to the supply line part 9, 10.
  • each controllable valve device 1 1, 12 a pressure medium outlet 20, 21, which is connected via outlet lines 22, 23, 24 with the pressure medium sink 6.
  • the controllable valve devices 1 1, 12 further have a pressure medium output 25, 26, which leads via further supply line sections 27, 28 to an adjusting device 29 for adjusting the transmission.
  • the adjusting device 29 comprises a double-acting cylinder 30, in which a piston 32 which can be moved in the longitudinal direction 31 is arranged. On the movable piston 32, a piston rod 33 is arranged, which extends in the longitudinal direction of the cylinder 30 and protrudes from this. Thus, the piston rod 33 is suitable as an actuator for adjusting the transmission.
  • the piston 32 divides the interior of the cylinder 30 into a first pressure medium chamber 34 and a second pressure medium chamber 35.
  • the first pressure medium chamber 34 is connected via the supply branch line 27 to the pressure medium outlet 25 of the first controllable valve device 11, while the second pressure medium chamber 35 via the supply branch line 28 is connected to the pressure medium output 26 of the second controllable valve device 12.
  • the piston 32 can be displaced by appropriate pressurization of the pressure medium chambers 34 and 35 in the longitudinal direction 31 of the cylinder 30, the piston 32 from a first position in which the piston 32 is further displaced into the first pressure medium chamber 34, in an intermediate position, the is shown in Fig. 1, and moved to a second position, in which Piston 32 is moved further into the second pressure medium chamber 35.
  • a transmission not shown
  • the intermediate position which can also be referred to as a neutral position
  • the control device 1 also has a pressure determining device 36, by means of which the pressure within the first and second pressure medium chambers 34, 35 can be determined. The thus determined pressure can then be passed on to the electrical control device 17 via a corresponding signal line 37. Furthermore, a position-determining device 38 is provided which serves to determine the position of the piston 32. For this purpose, the position detection device 38 determines the position of the piston rod 33 fixedly or rigidly connected to the piston 32, in order subsequently to relay the determined position of the piston 32 via a further signal line 39 to the electrical control device 17.
  • the electrical control device 17 is designed such that it can control the valve devices 1 1, 12 in response to the determined pressure within the pressure medium chambers 34, 35 and the determined position of the piston 32.
  • control device 17 preferably emit a pulse width modulated control signal via the control lines 15, 16 to the controllable valve devices 1 1, 12.
  • the piston 32 has one of the first pressure medium chamber 34 facing active surface 40, which is annular in the present example, especially since this is interrupted by the piston rod 33.
  • the piston 32 also has a second pressure medium chamber 35 facing active surface 41, which is circular in the present example.
  • the annular pressure acting on the first pressure medium chamber 34 annular surface 40 of the piston 32 is smaller than the second pressure medium chamber 35 facing circular active surface 41 of the piston 32.
  • the control device 17 is now in operative connection with the controllable valve devices 1 1, 12 such that the respective pressures within the pressure medium chambers 34, 35 can be changed independently of each other.
  • the pressures within the pressure medium chambers 34, 35 can be changed such that the piston 32 can be brought to one in the intermediate position shown in FIG. 1 and on the other hand can be held in this intermediate position.
  • the control device 17 is designed such that the pressure in the pressure medium chambers 34, 35 is matched to the corresponding active surfaces 40, 41 in order to obtain an equilibrium of forces in the intermediate position.
  • controllable valve devices 1 1 and 12 are controlled via the control device 17, that in the first pressure medium chamber 34, a higher pressure than in the second pressure medium chamber 35 is generated because the first pressure medium chamber 34 facing active surface 40 smaller than that of the second pressure medium chamber 35 facing active surface 41 is.
  • the tuning by the control device 17 takes place in such a way that from the side of the first pressure medium chamber 34, the same force as on the side of the second pressure medium chamber 35 on the KoI- ben 32 is exercised to achieve the above-mentioned balance of power and to hold the piston in its intermediate position.
  • the control of the controllable valve devices 1 1, 12 can take place with the aid of a corresponding pulse-width-modulated control signal.
  • Fig. 2 shows a second embodiment of the control device 42 according to the invention, which substantially corresponds to the first embodiment of Fig. 1, so that below the same reference numerals for the same parts are used, the above description then applies accordingly. In the following, only the differences of the control device 42 with respect to the control device 1 will be discussed.
  • the first controllable valve device 43 and the second controllable valve device 44 are each formed by an inlet valve 45 and an outlet valve 46.
  • Inlet and exhaust valves are each formed by a 2/2-way valve, the lektromagneten via a 47 and corresponding control lines 48, which lead to the electrical control device 17, can be actuated.
  • an outlet line 49 leads to the outlet valve 46 of the first valve device 43 and from the second pressure medium chamber 35 an outlet line 50 leads to the outlet valve 46 of the second controllable valve device 44.
  • the controllable valve means 43, 44 can be brought into the closed position shown in FIG.
  • Fig. 3 shows a possible embodiment of the adjusting device 29 of FIGS. 1 and 2.
  • the drag piston 51 has a radially outwardly projecting stop 53, which can be brought into abutment with a radially inwardly projecting stop 54 of the cylinder 30.
  • the drag piston 51 is guided on the piston 32 in the longitudinal direction 31 of the cylinder 30, wherein the piston also has a stop 55 against which the drag piston 51 can strike.
  • the active surface 52 of the drag piston 51 which is annular in the present example, and the first pressure medium chamber 34 facing active surface 40 of the piston 32 are together greater than the second pressure medium chamber 35 facing active surface 41 of the piston 32.
  • This configuration would be at a pressure equality between cause the two pressure medium chambers 34, 35 first, that the drag piston 51 and the piston 32 are displaced from the first pressure medium chamber 34 in the direction of the second pressure medium chamber 35 until the drag piston 51 abuts with its stop 53 against the stop 54 of the cylinder 30. In this position, which is shown in Fig. 3, the pressure within the pressure medium chamber 34 can no longer lead to a displacement of the drag piston 51.
  • the pressure in the first pressure medium chamber 34 can no longer lead to a displacement of the piston 32 alone in the direction of the second pressure medium chamber 35, if still the same pressure in the two pressure medium chambers 34, 35 prevails. This is due to the fact that the effective area 40 facing the first pressure medium chamber 34 is smaller than the effective area 41 of the piston 32 facing the second pressure medium chamber 35. By this configuration, therefore, the intermediate position can be very easily achieved and maintained, even if pressure equality between the two pressure medium chambers 34, 35 exists.

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

Abstract

Système de commande pour une boîte de vitesses, qui comporte une source de fluide sous pression (2), des premier et second dispositifs soupapes (43, 44) pouvant être commandés et raccordés à la source de fluide sous pression (2), un dispositif d'ajustement (29) pour l'ajustement de la boîte de vitesses, pourvu d'une première chambre à fluide sous pression (34) raccordée au premier dispositif soupape (43) pouvant être commandé, et d'une seconde chambre à fluide sous pression (35) raccordée au second dispositif soupape (44) pouvant être commandé, les chambres à fluide sous pression (34, 35) étant séparées l'une de l'autre par un piston mobile (32) qui peut être déplacé d'une première position via une position intermédiaire dans une seconde position, et un dispositif de commande (17) destiné à la commande des dispositifs soupapes (43, 44) pouvant être commandés. Selon la présente invention, le dispositif de commande (17) se trouve en interaction avec les dispositifs soupapes (43, 44) pouvant être commandés de manière telle que les pressions respectives dans les chambres à fluide sous pression (34, 35) peuvent être modifiées indépendamment l'une de l'autre si bien que le piston (42) peut être amené dans la position intermédiaire et y être maintenu. La présente invention concerne en outre une boîte de vitesses pourvue d'un dispositif de commande (42) de ce type, ainsi qu'un procédé de commande de boîte de vitesses.
PCT/EP2007/063113 2006-12-13 2007-12-03 Système de commande pour une boîte de vitesses WO2008071567A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200610058913 DE102006058913A1 (de) 2006-12-13 2006-12-13 Steuerungsvorrichtung für ein Getriebe
DE102006058913.0 2006-12-13

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SE533131C2 (sv) * 2008-11-18 2010-07-06 Scania Cv Abp Pneumatiskt manöverdon, system och metod för reglering av detsamma
FR2975743B1 (fr) * 2011-05-25 2013-06-28 Peugeot Citroen Automobiles Sa Dispositif de commande hydraulique d'une boite de vitesses, procede et boite de vitesses associes
DE102011120767A1 (de) * 2011-12-10 2013-06-13 Robert Bosch Gmbh Elektrohydraulische Steuereinrichtung
DE102012001100A1 (de) 2012-01-23 2013-07-25 Wabco Gmbh Anordnung zur Ansteuerung eines doppelt wirkenden Schaltzylinders einer Schaltanord-nung eines automatisierten Getriebes eines Kraftfahrzeuges
DE102016206582A1 (de) 2016-04-19 2017-10-19 Zf Friedrichshafen Ag Pneumatische Steuerung
DE102016206822A1 (de) * 2016-04-21 2017-10-26 Festo Ag & Co. Kg Verfahren zur Druckluftversorgung eines Druckluftverbrauchers, Ventileinrichtung und Datenträger mit einem Computerprogramm
SE545154C2 (en) * 2021-02-11 2023-04-18 Staccato Technoligies Ab Pneumatic cylinder system

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US4416187A (en) * 1981-02-10 1983-11-22 Nystroem Per H G On-off valve fluid governed servosystem
FR2598526A1 (fr) * 1986-05-06 1987-11-13 Renault Vehicules Ind Dispositif de gestion electronique d'un actionneur de crabots de boite de vitesses.
EP0723097A2 (fr) * 1995-01-21 1996-07-24 New Holland U.K. Limited Système de commande hydraulique pour sychronisateur
WO1998013627A1 (fr) * 1996-09-27 1998-04-02 Kongsberg Automotive Asa Dispositif pour fluide sous pression
DE19725302A1 (de) * 1997-06-14 1998-12-17 Zahnradfabrik Friedrichshafen Stelleinrichtung mit einem Kolben und einem Zylinder
DE19931973A1 (de) * 1999-07-09 2001-01-11 Wabco Gmbh & Co Ohg Einrichtung zum Steuern einer Stelleinrichtung für ein Getriebe
EP1701067A1 (fr) * 2005-03-11 2006-09-13 Zf Friedrichshafen Ag Procédé de contrôle du déroulement des changements de rapports sur une transmission automatique à arbre de renvoi

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