EP1882859B1 - Improved hydraulic actuator for gearbox of an automobile - Google Patents

Improved hydraulic actuator for gearbox of an automobile Download PDF

Info

Publication number
EP1882859B1
EP1882859B1 EP07301179A EP07301179A EP1882859B1 EP 1882859 B1 EP1882859 B1 EP 1882859B1 EP 07301179 A EP07301179 A EP 07301179A EP 07301179 A EP07301179 A EP 07301179A EP 1882859 B1 EP1882859 B1 EP 1882859B1
Authority
EP
European Patent Office
Prior art keywords
valve
actuator
chamber
opening
piston
Prior art date
Legal status (The legal status 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 status listed.)
Not-in-force
Application number
EP07301179A
Other languages
German (de)
French (fr)
Other versions
EP1882859A1 (en
Inventor
Jean-Yves Gallier
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
PSA Automobiles SA
Original Assignee
Peugeot Citroen Automobiles SA
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 Peugeot Citroen Automobiles SA filed Critical Peugeot Citroen Automobiles SA
Publication of EP1882859A1 publication Critical patent/EP1882859A1/en
Application granted granted Critical
Publication of EP1882859B1 publication Critical patent/EP1882859B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
    • F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
    • F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
    • F15B9/09—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor with electrical control means
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B2211/3057—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 having two valves, one for each port of a double-acting output member
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/365—Directional control combined with flow control and pressure control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member

Definitions

  • the invention relates to a hydraulic actuator for a transmission mechanism of a vehicle, especially a motor vehicle, such as a semi-automatic or automatic gearbox.
  • a unit 5 controls the hydraulic actuator to ensure the passage from one speed to another, depending on the choice of driver when the gearbox is in semi-automatic mode, or in function of a speed management system when this gearbox operates in automatic mode.
  • the known actuator (for example, in the document WO 2004/085887 ), identified by 1 on the figure 1 , comprises a double-acting cylinder 2 defining two pressure chambers 3, 4 and a piston 6 displaceable in translation along a main direction A1, A'1 in two opposite directions.
  • This actuator 1 is further provided with two three-way valves 11, 12, each interposed between a chamber 3, 4 of the jack, a pressurized source 7 and a recovery container 8; the three channels 11a, 11b, 11c and 12a, 12b, 12c respectively leading to the valves 11 and 12 and respectively connecting these valves 11 and 12 to the source 7, the chamber 3, 4 and the container 8.
  • Each three-way valve 11, 12 can occupy an active state or an inactive state, in which the valve 11, 12 provides communication between two channels and isolates these channels from the third.
  • each valve 11, 12 in its active state, provides the connection between the chamber 3, 4 and the source 7 while isolating the chamber 3, 4 of the container 8, and in its inactive state, the valve 11, 12 connects the chamber 3, 4 to the container 8 and isolates this chamber 3, 4 from the source 7, the two valves 11, 12 occupying each instant different states so as to allow movement of the piston 6 in two opposite directions.
  • valves 11, 12 are further proportional type and each allow, in their active and inactive states, a modulation of the amounts of fluid flowing between the two channels in communication, so as to ensure a gradual displacement of the piston 7 in both opposite directions along the main axis A1, A'1.
  • the invention relates to a hydraulic actuator comprising a double-acting cylinder provided with two pressure chambers and a piston displaceable in translation in a main direction in two opposite directions, a hydraulic power unit for the cylinder, a non-pressurized recovery vessel, and two three-way valves each interposed between a chamber, the hydraulic unit and the vessel, and each capable of occupying an active state, wherein the valve provides communication between the two channels respectively connected to the chamber and the source and isolates this chamber from the container, and an inactive state, in which the valve provides communication between the two channels respectively connected to the chamber and the container and isolates this chamber from the source, the two valves occupying at each moment states different so as to allow a gradual movement of the actuator in two opposite directions.
  • one of the valves is proportional and defines in its two states, between the two channels in communication, a modulable amplitude opening, the other valve is binary and defines a fixed amplitude opening between the two. communication channels.
  • the proportional valve is of the pressure solenoid type, the amplitude of the opening being a function of the pressure of the fluid downstream of the valve.
  • the proportional valve is of solenoid type in flow, the amplitude of the opening being a function of the flow of fluid downstream of the valve.
  • the invention also relates to a gearbox of a motor vehicle comprising one of the actuators above and a control unit delivering a control current of the proportional valve of this actuator, the amplitude of the opening defined by the valve being proportional to the control current.
  • the hydraulic actuator 13 of the figure 2 is intended to equip an actuating mechanism for automated or semi-automated transmission, such as a gearbox of a motor vehicle (not shown).
  • the actuator When the actuator is used in an automatic transmission, its movement is controlled by a management system according to the current engine speed.
  • this actuator When this actuator is disposed within a semi-automatic gearbox, its movement is guided by a speed selection lever (not shown) manually operable by the driver of the vehicle.
  • a control unit 20 delivers a control current i depending on the desired direction of movement for the actuator 13 and the desired amplitude of this displacement.
  • This actuator 13 comprises a double-acting jack 14 provided with a piston 15 displaceable in a main horizontal direction A1, A'1 in two opposite directions marked respectively by F1 on the figure 2 and by F2 on the figure 3 , the body 16 of the piston 15 separating the jack 14 into two pressure chambers 17, 18.
  • Each of these chambers 17, 18 is selectively connected to a hydraulic unit such as a source of pressurized fluid 19 or to a fluid recovery vessel 21 located at a pressure lower than the pressure of the fluid within the source 19. the example of the figures, the container 21 is at ambient pressure.
  • a hydraulic unit such as a source of pressurized fluid 19 or to a fluid recovery vessel 21 located at a pressure lower than the pressure of the fluid within the source 19. the example of the figures, the container 21 is at ambient pressure.
  • the selective connection between the two chambers 17, 18 and the source 19 or between these chambers 17, 18 and the container 21 is provided by two three-way solenoid valves 22, 23. These solenoid valves 22, 23 are further controlled by the control unit. aforementioned control 20 so as to regulate the amount of fluid through which these valves 22, 23 are traversed as a function of the control current i delivered by this unit and thus the displacement of the piston 15 of the cylinder 14.
  • each valve 22, 23 is disposed at the intersection of three channels 22a, 22b, 22c, 23a, 23b, 23c which are a first channel 22a, 23a providing a connection between the valve 22, 23 and the source 19, a second channel 22b, 23b connecting the valve 22, 23 to the relevant chamber 17, 18 and a third channel 22c, 23c allowing communication between the valve 22, 23 and the recovery container 21.
  • the first channels 22a, 23a define a junction located downstream of the pressurized source 19.
  • Each valve 22, 23 can occupy an active state in which it puts in communication the channels 22a, 23a and 22b, 23b, and connects accordingly the concerned chamber 17, 18 with the source 19, as represented on the figure 2 for the valve 22, causing the pressurized fluid filling of this chamber 17, 18 and consequently preventing the flow of fluid from the chamber 17, 18 to the recovery container 21, the channel 22c connecting the valve 22 to the container 21 acting as a bypass for the fluid coming from the source 19 in the event of overflow of fluid in the chamber 17.
  • each valve 22, 23 can occupy an inactive state, as illustrated for the valve 23 of the figure 2 , in which it isolates the relevant chamber 17, 18 from the source 19 and establishes a communication between the channels 22b, 23b and 22c, 23c and thus a connection between the corresponding chamber 17, 18 and the container 21, so that the fluid pressurized from this chamber 17, 18 can flow to the unpressurized container 21.
  • the two valves 22, 23 occupy at each moment different states, to move the piston in the two opposite directions F1 and F2.
  • valve 23 occupies its inactive state and allows the fluid to flow from the second chamber 18 to the container 21.
  • the pressurized fluid from the source 19 exerts, on the side of the first chamber 17, a force on the body 16 of the piston 15 tending to move in the direction indicated by F1.
  • one of the valves 22 of the actuator 13 according to the invention is of the type proportional, the other valve 23 being of binary type.
  • the proportional valve 22 can define between the two channels in communication in its respective states, that is to say between the channels 22a and 22b in its active state and between the channels 22b and 22c in its inactive state, a partial opening of the passage of the fluid, the amplitude of which is regulated as a function of the control current i.
  • This valve 22 can therefore occupy a multitude of positions in each of its states (active / inactive), so as to modulate the amount of fluid passing through it.
  • the valve 22 is of the proportional pressure solenoid valve type, that is to say that the fluid pressure downstream of this valve 22 is proportional to the control current i, and c is the force exerted on the piston which is regulated.
  • the valve is of proportional flow type, in which case the flow rate of fluid downstream of the valve 22 is proportional to the control current i, so that it is the displacement of the piston 15 which is regulated.
  • the binary valve 23 does not define between the channels in communication in its respective states, namely between the channels 23a and 23b in its active state and between the channels 23b and 23c in its inactive state, that an amplitude opening fixed fluid passage and occupies a single position in each of its states, namely a full open position between the channels 23a and 23b and total closure of the channel 23c in its active state and a full open position between channels 23b and 23c and total closure of channel 23a in its inactive state.
  • the proportional valve 22 occupies an active state in which it defines a particular opening, directly dependent on the current delivered by the control unit, which is itself fixed by the aforementioned management system when the gearbox is in automatic mode , or by operating the shift lever exerted by the user when the gearbox is semi-automatic.
  • the binary valve is controlled to its inactive state, and occupies its unique inactive position, for which it isolates the second chamber 18 from the source 19 and connects it to the container 21, allowing the flow of surplus fluid due to to the displacement of piston 15 in the direction F1, from the second chamber 18 to the recovery container 21.
  • the binary valve 23 is controlled to its active state and occupies its unique position in which it connects the pressurized source 19 to the second chamber 18, so that the pressurized fluid exerts a force tending to move the piston 15 in the direction indicated by F2.
  • the proportional valve 22 is controlled to its inactive state and defines between the channels 22b and 22c a particular opening whose amplitude depends on the control current i, so as to regulate according to this current, the amount of excess fluid flowing between the first chamber 17 and the container 21 due to the displacement of the piston 15 in the direction F2.
  • the opening defined by the proportional valve 22 controls as a function of the control current i the amount of fluid that can flow from the first chamber 17 to the container and limits the displacement of the body 16 of the piston 15 to the first chamber 17 since the hydraulic fluid is incompressible. Consequently, this opening of the valve 22 controls the value of the force exerted on the piston on the side of the second chamber 18, again as a function of the control current i.
  • the piston 15 is moved in the direction indicated by F2 by the application of a force proportional to the control current, with as much precision as for a displacement in the direction of the arrow F1 or that for the actuator known from the figure 1 which has two solenoid valves proportional type.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gear-Shifting Mechanisms (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Transmission Device (AREA)
  • Magnetically Actuated Valves (AREA)
  • Motor Or Generator Frames (AREA)
  • Control Of Fluid Gearings (AREA)

Abstract

The actuator (13) has two pressure and flow rate solenoid valves (22, 23), where each valve is interposed between two pressure chambers (17, 18). The pressure solenoid valve is proportional and defines an flexible amplitude opening between two communication paths (22a, 22b, 22c, 23a, 23b, 23c), in two active and inactive states of the pressure solenoid valve. The flow rate solenoid valve is binary and defines an fixed amplitude opening between the two communication paths, in two active and inactive states of the flow rate solenoid valve.

Description

L'invention concerne un actionneur hydraulique pour un mécanisme de transmission d'un véhicule, notamment un véhicule automobile, tel qu'une boîte de vitesses semi-automatique ou automatique. Pour ce type de boîte de vitesses, une unité 5 commande l'actionneur hydraulique afin d'assurer le passage d'une vitesse à une autre, en fonction du choix du conducteur lorsque la boîte de vitesses est en mode semi-automatique, ou en fonction d'un système de gestion des vitesses lorsque cette boîte de vitesses fonctionne en mode automatique.The invention relates to a hydraulic actuator for a transmission mechanism of a vehicle, especially a motor vehicle, such as a semi-automatic or automatic gearbox. For this type of gearbox, a unit 5 controls the hydraulic actuator to ensure the passage from one speed to another, depending on the choice of driver when the gearbox is in semi-automatic mode, or in function of a speed management system when this gearbox operates in automatic mode.

Afin d'assurer la fonction de passage des vitesses, l'actionneur connu (par exemple, dans le document WO 2004/085887 ), repéré par 1 sur la figure 1, comprend un vérin à double effet 2 définissant deux chambres de pression 3, 4 et un piston 6 déplaçable en translation suivant une direction principale A1, A'1 selon deux sens opposés.In order to ensure the shifting function, the known actuator (for example, in the document WO 2004/085887 ), identified by 1 on the figure 1 , comprises a double-acting cylinder 2 defining two pressure chambers 3, 4 and a piston 6 displaceable in translation along a main direction A1, A'1 in two opposite directions.

Cet actionneur 1 est encore pourvu de deux vannes trois voies 11, 12, interposées chacune entre une chambre 3, 4 du vérin, une source pressurisée 7 et un récipient de récupération 8 ; les trois voies 11a, 11b, 11c et 12a, 12b, 12c aboutissant respectivement aux vannes 11 et 12 et reliant respectivement ces vannes 11 et 12 à la source 7, à la chambre 3, 4 et au récipient 8.This actuator 1 is further provided with two three-way valves 11, 12, each interposed between a chamber 3, 4 of the jack, a pressurized source 7 and a recovery container 8; the three channels 11a, 11b, 11c and 12a, 12b, 12c respectively leading to the valves 11 and 12 and respectively connecting these valves 11 and 12 to the source 7, the chamber 3, 4 and the container 8.

Chaque vanne trois voies 11, 12 peut occuper un état actif ou un état inactif, dans lesquels la vanne 11, 12 assure une communication entre deux voies et isole ces voies de la troisième.Each three-way valve 11, 12 can occupy an active state or an inactive state, in which the valve 11, 12 provides communication between two channels and isolates these channels from the third.

Plus précisément, dans son état actif, chaque vanne 11, 12 assure la liaison entre la chambre 3, 4 et la source 7 tout en isolant cette chambre 3, 4 du récipient 8, et dans son état inactif, la vanne 11, 12 relie la chambre 3, 4 au récipient 8 et isole cette chambre 3, 4 de la source 7, les deux vannes 11, 12 occupant à chaque instant des états différents de façon à permettre un déplacement du piston 6 selon les deux sens opposés.More specifically, in its active state, each valve 11, 12 provides the connection between the chamber 3, 4 and the source 7 while isolating the chamber 3, 4 of the container 8, and in its inactive state, the valve 11, 12 connects the chamber 3, 4 to the container 8 and isolates this chamber 3, 4 from the source 7, the two valves 11, 12 occupying each instant different states so as to allow movement of the piston 6 in two opposite directions.

Ces deux vannes 11, 12 sont en outre de type proportionnel et permettent chacune, dans leurs états actif et inactif, une modulation des quantités de fluide circulant entre les deux voies en communication, de façon à assurer un déplacement graduel du piston 7 dans les deux sens opposés selon l'axe principal A1, A'1.These two valves 11, 12 are further proportional type and each allow, in their active and inactive states, a modulation of the amounts of fluid flowing between the two channels in communication, so as to ensure a gradual displacement of the piston 7 in both opposite directions along the main axis A1, A'1.

Toutefois, les coûts de fabrication et d'entretien de cet actionneur sont importants et l'invention vise à palier cet inconvénient.However, the manufacturing and maintenance costs of this actuator are important and the invention aims to overcome this disadvantage.

A cet effet, l'invention concerne un actionneur hydraulique comprenant un vérin à double effet pourvu de deux chambres de pression et d'un piston déplaçable en translation suivant une direction principale selon deux sens opposés, un groupe hydraulique d'alimentation du vérin, un récipient de récupération non pressurisé, et deux vannes trois voies interposées chacune entre une chambre, le groupe hydraulique et le récipient, et pouvant occuper chacune un état actif, dans lequel la vanne assure une communication entre les deux voies reliées respectivement à la chambre et à la source et isole cette chambre du récipient, et un état inactif, dans lequel la vanne assure une communication entre les deux voies reliées respectivement à la chambre et au récipient et isole cette chambre de la source, les deux vannes occupant à chaque instant des états différents de façon à permettre un déplacement graduel de l'actionneur selon les deux sens opposés.For this purpose, the invention relates to a hydraulic actuator comprising a double-acting cylinder provided with two pressure chambers and a piston displaceable in translation in a main direction in two opposite directions, a hydraulic power unit for the cylinder, a non-pressurized recovery vessel, and two three-way valves each interposed between a chamber, the hydraulic unit and the vessel, and each capable of occupying an active state, wherein the valve provides communication between the two channels respectively connected to the chamber and the source and isolates this chamber from the container, and an inactive state, in which the valve provides communication between the two channels respectively connected to the chamber and the container and isolates this chamber from the source, the two valves occupying at each moment states different so as to allow a gradual movement of the actuator in two opposite directions.

Selon l'invention, l'une des vannes est proportionnelle et définit dans ses deux états, entre les deux voies en communication, une ouverture d'amplitude modulable, l'autre vanne est binaire et définit une ouverture d'amplitude fixe entre les deux voies en communication.According to the invention, one of the valves is proportional and defines in its two states, between the two channels in communication, a modulable amplitude opening, the other valve is binary and defines a fixed amplitude opening between the two. communication channels.

Selon une autre caractéristique, la vanne proportionnelle est de type électrovanne en pression, l'amplitude de l'ouverture étant fonction de la pression du fluide en aval de la vanne.According to another characteristic, the proportional valve is of the pressure solenoid type, the amplitude of the opening being a function of the pressure of the fluid downstream of the valve.

Selon encore une autre caractéristique, la vanne proportionnelle est de type électrovanne en débit, l'amplitude de l'ouverture étant fonction du débit de fluide en aval de la vanne.According to yet another characteristic, the proportional valve is of solenoid type in flow, the amplitude of the opening being a function of the flow of fluid downstream of the valve.

L'invention concerne également une boîte de vitesses d'un véhicule automobile comprenant l'un des actionneurs ci-dessus et une unité de commande délivrant un courant de commande de la vanne proportionnelle de cet actionneur, l'amplitude de l'ouverture définie par la vanne étant proportionnelle au courant de commande.The invention also relates to a gearbox of a motor vehicle comprising one of the actuators above and a control unit delivering a control current of the proportional valve of this actuator, the amplitude of the opening defined by the valve being proportional to the control current.

L'invention sera mieux comprise, et d'autres caractéristiques de celle-ci apparaîtront plus clairement dans la description suivante, faite en référence aux dessins annexés donnés uniquement à titre d'exemple parmi lesquels :

  • la figure 1 susmentionnée est un schéma de principe d'un actionneur hydraulique de type connu ;
  • la figure 2 est un schéma de principe d'un actionneur selon l'invention pour un sens de déplacement positif du piston de l'actionneur ;
  • la figure 3 est un schéma analogue à celui de la figure 2 pour un sens de déplacement négatif du piston de l'actionneur.
The invention will be better understood, and other features thereof will appear more clearly in the following description, made with reference to the accompanying drawings given solely by way of example, among which:
  • the figure 1 aforementioned is a block diagram of a hydraulic actuator of known type;
  • the figure 2 is a block diagram of an actuator according to the invention for a direction of positive displacement of the piston of the actuator;
  • the figure 3 is a diagram similar to that of the figure 2 for a direction of negative displacement of the piston of the actuator.

L'actionneur hydraulique 13 de la figure 2 est destiné à équiper un mécanisme d'actionnement pour transmission automatisée ou semi-automatisée, tel qu'une boîte de vitesses d'un véhicule automobile (non représentée).The hydraulic actuator 13 of the figure 2 is intended to equip an actuating mechanism for automated or semi-automated transmission, such as a gearbox of a motor vehicle (not shown).

Il permet d'actionner une fourchette de boîte de vitesses (non illustrée) du véhicule en vue du passage des rapports de vitesses dans ce véhicule.It allows to actuate a gearbox fork (not shown) of the vehicle for the passage of gears in this vehicle.

Lorsque l'actionneur est utilisé au sein d'une boîte de vitesses automatique, son déplacement est commandé par un système de gestion en fonction du régime courant du moteur.When the actuator is used in an automatic transmission, its movement is controlled by a management system according to the current engine speed.

Lorsque cet actionneur est disposé au sein d'une boîte de vitesse semi-automatique, son déplacement est guidé par un levier de sélection de vitesse (non représenté) actionnable manuellement par le conducteur du véhicule.When this actuator is disposed within a semi-automatic gearbox, its movement is guided by a speed selection lever (not shown) manually operable by the driver of the vehicle.

Dans les deux cas, une unité de commande 20 délivre un courant de commande i dépendant du sens du déplacement souhaité pour l'actionneur 13 et de l'amplitude désirée de ce déplacement.In both cases, a control unit 20 delivers a control current i depending on the desired direction of movement for the actuator 13 and the desired amplitude of this displacement.

Cet actionneur 13 comprend un vérin à double effet 14 pourvu d'un piston 15 déplaçable suivant une direction principale horizontale A1, A'1 selon deux sens opposés repérés respectivement par F1 sur la figure 2 et par F2 sur la figure 3, le corps 16 du piston 15 séparant le vérin 14 en deux chambres de pression 17, 18.This actuator 13 comprises a double-acting jack 14 provided with a piston 15 displaceable in a main horizontal direction A1, A'1 in two opposite directions marked respectively by F1 on the figure 2 and by F2 on the figure 3 , the body 16 of the piston 15 separating the jack 14 into two pressure chambers 17, 18.

Chacune de ces chambres 17, 18 est sélectivement reliée à un groupe hydraulique tel qu'une source de fluide pressurisée 19 ou à un récipient de récupération de fluide 21 situé à une pression inférieure à la pression du fluide au sein de la source 19. Dans l'exemple des figures, le récipient 21 est à pression ambiante.Each of these chambers 17, 18 is selectively connected to a hydraulic unit such as a source of pressurized fluid 19 or to a fluid recovery vessel 21 located at a pressure lower than the pressure of the fluid within the source 19. the example of the figures, the container 21 is at ambient pressure.

La liaison sélective entre les deux chambres 17, 18 et la source 19 ou entre ces chambres 17, 18 et le récipient 21 est assurée par deux électrovannes trois voies 22, 23. Ces électrovannes 22, 23 sont en outre commandées par l'unité de commande susmentionnée 20 de façon à réguler la quantité de fluide par laquelle ces vannes 22, 23 sont traversées en fonction du courant de commande i délivré par cette unité et ainsi le déplacement du piston 15 du vérin 14.The selective connection between the two chambers 17, 18 and the source 19 or between these chambers 17, 18 and the container 21 is provided by two three-way solenoid valves 22, 23. These solenoid valves 22, 23 are further controlled by the control unit. aforementioned control 20 so as to regulate the amount of fluid through which these valves 22, 23 are traversed as a function of the control current i delivered by this unit and thus the displacement of the piston 15 of the cylinder 14.

Plus précisément, chaque vanne 22, 23 est disposée à l'intersection de trois voies 22a, 22b, 22c, 23a, 23b, 23c qui sont une première voie 22a, 23a assurant une liaison entre la vanne 22, 23 et la source 19, une deuxième voie 22b, 23b reliant la vanne 22, 23 à la chambre concernée 17, 18 et une troisième voie 22c, 23c permettant une communication entre la vanne 22, 23 et le récipient de récupération 21. Il est à noter que les premières voies 22a, 23a définissent une jonction située en aval de la source pressurisée 19.More precisely, each valve 22, 23 is disposed at the intersection of three channels 22a, 22b, 22c, 23a, 23b, 23c which are a first channel 22a, 23a providing a connection between the valve 22, 23 and the source 19, a second channel 22b, 23b connecting the valve 22, 23 to the relevant chamber 17, 18 and a third channel 22c, 23c allowing communication between the valve 22, 23 and the recovery container 21. It should be noted that the first channels 22a, 23a define a junction located downstream of the pressurized source 19.

Chaque vanne 22, 23 peut occuper un état actif dans lequel elle met en communication les voies 22a, 23a et 22b, 23b, et relie en conséquence la chambre concernée 17, 18 avec la source 19, tel que représenté sur la figure 2 pour la vanne 22, provoquant le remplissage en fluide pressurisé de cette chambre 17, 18 et interdisant en conséquence l'écoulement du fluide depuis la chambre 17, 18 jusqu'au récipient de récupération 21, la voie 22c reliant la vanne 22 au récipient 21 servant de dérivation au fluide issu de la source 19 en cas de trop plein de fluide dans la chambre 17.Each valve 22, 23 can occupy an active state in which it puts in communication the channels 22a, 23a and 22b, 23b, and connects accordingly the concerned chamber 17, 18 with the source 19, as represented on the figure 2 for the valve 22, causing the pressurized fluid filling of this chamber 17, 18 and consequently preventing the flow of fluid from the chamber 17, 18 to the recovery container 21, the channel 22c connecting the valve 22 to the container 21 acting as a bypass for the fluid coming from the source 19 in the event of overflow of fluid in the chamber 17.

Au contraire, chaque vanne 22, 23 peut occuper un état inactif, comme illustré pour la vanne 23 de la figure 2, dans lequel elle isole la chambre concernée 17, 18 de la source 19 et établit une communication entre les voies 22b, 23b et 22c, 23c et donc une liaison entre la chambre correspondante 17, 18 et le récipient 21, de sorte que le fluide pressurisé issu de cette chambre 17, 18 puisse s'écouler vers le récipient non pressurisé 21.On the contrary, each valve 22, 23 can occupy an inactive state, as illustrated for the valve 23 of the figure 2 , in which it isolates the relevant chamber 17, 18 from the source 19 and establishes a communication between the channels 22b, 23b and 22c, 23c and thus a connection between the corresponding chamber 17, 18 and the container 21, so that the fluid pressurized from this chamber 17, 18 can flow to the unpressurized container 21.

Les deux vannes 22, 23 occupent à chaque instant des états différents, permettant de déplacer le piston selon les deux sens opposés F1 et F2.The two valves 22, 23 occupy at each moment different states, to move the piston in the two opposite directions F1 and F2.

Plus précisément, tel qu'illustré sur la figure 2, lorsque la première vanne 22 occupe son état actif, permettant l'alimentation en fluide de la première chambre 17, la vanne 23 occupe son état inactif et autorise l'écoulement du fluide depuis la deuxième chambre 18 jusqu'au récipient 21.More specifically, as illustrated on the figure 2 when the first valve 22 is in its active state, allowing the fluid supply of the first In chamber 17, the valve 23 occupies its inactive state and allows the fluid to flow from the second chamber 18 to the container 21.

Ainsi, le fluide pressurisé issu de la source 19 exerce, du côté de la première chambre 17, un effort sur le corps 16 du piston 15 tendant à le déplacer selon le sens repéré par F1.Thus, the pressurized fluid from the source 19 exerts, on the side of the first chamber 17, a force on the body 16 of the piston 15 tending to move in the direction indicated by F1.

De façon similaire et tel qu'illustré sur la figure 3, lorsque la première vanne 22 occupe son état inactif et que la deuxième vanne 23 occupe son état actif, le corps 16 du piston 15 est déplacé selon le sens repéré par F2.Similarly and as illustrated on the figure 3 when the first valve 22 is in its inactive state and the second valve 23 is in its active state, the body 16 of the piston 15 is moved in the direction indicated by F2.

Afin d'assurer un déplacement graduel du piston 15 suivant la direction A1, A'1, tout en présentant un coût de fabrication et d'entretien faibles, l'une des vannes 22 de l'actionneur 13 selon l'invention est de type proportionnel, l'autre vanne 23 étant de type binaire.In order to ensure a gradual displacement of the piston 15 in the direction A1, A'1, while having a low manufacturing and maintenance cost, one of the valves 22 of the actuator 13 according to the invention is of the type proportional, the other valve 23 being of binary type.

Plus précisément, la vanne proportionnelle 22 peut définir entre les deux voies en communication dans ses états respectifs, c'est-à-dire entre les voies 22a et 22b dans son état actif et entre les voies 22b et 22c dans son état inactif, une ouverture partielle de passage du fluide dont l'amplitude est réglée en fonction du courant de commande i. Cette vanne 22 peut donc occuper une multitude de positions dans chacun de ses états (actif/inactif), de façon à moduler la quantité de fluide la traversant.More precisely, the proportional valve 22 can define between the two channels in communication in its respective states, that is to say between the channels 22a and 22b in its active state and between the channels 22b and 22c in its inactive state, a partial opening of the passage of the fluid, the amplitude of which is regulated as a function of the control current i. This valve 22 can therefore occupy a multitude of positions in each of its states (active / inactive), so as to modulate the amount of fluid passing through it.

Selon un mode de réalisation possible de l'invention, la vanne 22 est de type électrovanne proportionnelle en pression, c'est-à-dire que la pression de fluide en aval de cette vanne 22 est proportionnelle au courant de commande i, et c'est l'effort exercé sur le piston qui est régulé.According to a possible embodiment of the invention, the valve 22 is of the proportional pressure solenoid valve type, that is to say that the fluid pressure downstream of this valve 22 is proportional to the control current i, and c is the force exerted on the piston which is regulated.

Selon un autre mode de réalisation, la vanne est de type proportionnel en débit, auquel cas le débit de fluide en aval de la vanne 22 est proportionnel au courant de commande i, si bien que c'est le déplacement du piston 15 qui est régulé.According to another embodiment, the valve is of proportional flow type, in which case the flow rate of fluid downstream of the valve 22 is proportional to the control current i, so that it is the displacement of the piston 15 which is regulated.

Au contraire, la vanne binaire 23 ne définit entre les voies en communication dans ses états respectifs, à savoir entre les voies 23a et 23b dans son état actif et entre les voies 23b et 23c dans son état inactif, qu'une ouverture d'amplitude fixe de passage du fluide et occupe une unique position dans chacun de ses états, à savoir une position d'ouverture complète entre les voies 23a et 23b et d'obturation totale de la voie 23c dans son état actif et une position d'ouverture complète entre les voies 23b et 23c et d'obturation totale de la voie 23a dans son état inactif.On the contrary, the binary valve 23 does not define between the channels in communication in its respective states, namely between the channels 23a and 23b in its active state and between the channels 23b and 23c in its inactive state, that an amplitude opening fixed fluid passage and occupies a single position in each of its states, namely a full open position between the channels 23a and 23b and total closure of the channel 23c in its active state and a full open position between channels 23b and 23c and total closure of channel 23a in its inactive state.

On détaille dans ce qui suit le fonctionnement de l'actionneur selon l'invention en référence aux figures 2 et 3 :In the following, the operation of the actuator according to the invention is described in detail with reference to figures 2 and 3 :

Sur la figure 2, la vanne proportionnelle 22 occupe un état actif dans lequel elle définit une ouverture particulière, dépendant directement du courant délivré par l'unité de commande, qui est lui-même fixé par le système de gestion précité lorsque la boîte de vitesses est en mode automatique, ou par l'actionnement du levier de vitesse exercé par l'utilisateur lorsque la boîte de vitesses est semi-automatique.On the figure 2 , the proportional valve 22 occupies an active state in which it defines a particular opening, directly dependent on the current delivered by the control unit, which is itself fixed by the aforementioned management system when the gearbox is in automatic mode , or by operating the shift lever exerted by the user when the gearbox is semi-automatic.

En conséquence, le fluide pressurisé issu de la source 19 exerce sur le piston 15 un effort proportionnel au courant de commande i, si bien que le piston 15 est déplacé selon le sens repéré par F1.As a result, the pressurized fluid from the source 19 exerts on the piston 15 a force proportional to the control current i, so that the piston 15 is moved in the direction indicated by F1.

Dans le même temps, la vanne binaire est commandée à son état inactif, et occupe son unique position inactive, pour laquelle elle isole la deuxième chambre 18 de la source 19 et la relie au récipient 21, permettant l'écoulement du surplus de fluide dû au déplacement du piston 15 selon le sens F1, depuis la deuxième chambre 18 jusqu'au récipient de récupération 21.At the same time, the binary valve is controlled to its inactive state, and occupies its unique inactive position, for which it isolates the second chamber 18 from the source 19 and connects it to the container 21, allowing the flow of surplus fluid due to to the displacement of piston 15 in the direction F1, from the second chamber 18 to the recovery container 21.

Sur la figure 3, la vanne binaire 23 est commandée à son état actif et occupe son unique position dans laquelle elle relie la source pressurisée 19 à la deuxième chambre 18, de sorte que le fluide pressurisé exerce un effort tendant à déplacer le piston 15 selon le sens repéré par F2.On the figure 3 , the binary valve 23 is controlled to its active state and occupies its unique position in which it connects the pressurized source 19 to the second chamber 18, so that the pressurized fluid exerts a force tending to move the piston 15 in the direction indicated by F2.

Dans le même temps, la vanne proportionnelle 22 est commandée à son état inactif et définit entre les voies 22b et 22c une ouverture particulière dont l'amplitude dépend du courant de commande i, de façon à réguler en fonction de ce courant, la quantité de surplus de fluide s'écoulant entre la première chambre 17 et le récipient 21 du fait du déplacement du piston 15 selon le sens F2.At the same time, the proportional valve 22 is controlled to its inactive state and defines between the channels 22b and 22c a particular opening whose amplitude depends on the control current i, so as to regulate according to this current, the amount of excess fluid flowing between the first chamber 17 and the container 21 due to the displacement of the piston 15 in the direction F2.

Or, l'ouverture définie par la vanne proportionnelle 22 contrôle en fonction du courant de commande i la quantité de fluide pouvant s'écouler depuis la première chambre 17 jusqu'au récipient et limite le déplacement du corps 16 du piston 15 vers la première chambre 17 puisque le fluide hydraulique est incompressible. En conséquence, cette ouverture de la vanne 22 contrôle la valeur de l'effort exercé sur le piston du côté de la deuxième chambre 18, toujours en fonction du courant de commande i.However, the opening defined by the proportional valve 22 controls as a function of the control current i the amount of fluid that can flow from the first chamber 17 to the container and limits the displacement of the body 16 of the piston 15 to the first chamber 17 since the hydraulic fluid is incompressible. Consequently, this opening of the valve 22 controls the value of the force exerted on the piston on the side of the second chamber 18, again as a function of the control current i.

Ainsi, le piston 15 est déplacé selon le sens repéré par F2 par l'application d'un effort proportionnel au courant de commande, avec autant de précision que pour un déplacement dans le sens de la flèche F1 ou que pour l'actionneur connu de la figure 1 qui comporte deux électrovannes de type proportionnel.Thus, the piston 15 is moved in the direction indicated by F2 by the application of a force proportional to the control current, with as much precision as for a displacement in the direction of the arrow F1 or that for the actuator known from the figure 1 which has two solenoid valves proportional type.

Claims (4)

  1. Hydraulic actuator comprising a double-acting cylinder actuator (13) provided with two pressure chambers (17, 18) and with a piston (15) that can be moved translationally in a main direction (A1, A'1) in two opposite senses, a hydraulic supply unit (19) that supplies the cylinder actuator (13), a non-pressurized collecting vessel (21), and two three-way valves (22, 23) each interposed between a chamber (17, 18), the hydraulic unit (19) and the vessel (21) and able each to occupy an active state in which the valve provides communication between two ports (22A, 22B, 23A, 23B) respectively connected to the chamber (17, 18) and to the hydraulic unit (19) and isolates a port (22C, 23C) connected to the vessel (21), and an inactive state in which the valve (22, 23) provides communication between the two ports (22B, 23B, 22C, 23C) respectively connected to the chamber (17, 18) and to the vessel (21) and isolates the port (22A, 23A) connected to the hydraulic unit (19), the two valves (22, 23) at each moment occupying different states so as to allow the piston (15) of the actuator (13) to move gradually in the two opposite senses, characterized in that one of the valves (22, 23) is a proportional valve and in its two states defines an opening of variable bore between the two communicating ports (22A, 22B, 22C, 23A, 23B, 23C), the other valve (23, 22) being binary and in its two states defining an opening of fixed bore between the two communicating ports.
  2. Actuator according to Claim 1, in which the proportional valve (22, 23) is of the pressure-controlled electrically operated valve type, the bore size of the opening being dependent on the pressure of the fluid downstream of the valve (22, 23).
  3. Actuator according to Claim 1, in which the proportional valve (22, 23) is of the flow-controlled electrically-operated valve type, the bore size of the opening being dependent on the flow rate of fluid downstream of the valve (22, 23).
  4. Motor vehicle gearbox characterized in that it comprises a hydraulic actuator (13) according to one of the preceding claims and a control unit (20) delivering a control current (i) to control the proportional valve (22, 23) of the actuator (13), the bore size of the opening defined by the valve (22, 23) being proportionate to the control current.
EP07301179A 2006-07-04 2007-06-29 Improved hydraulic actuator for gearbox of an automobile Not-in-force EP1882859B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0652797A FR2903460B1 (en) 2006-07-04 2006-07-04 IMPROVED HYDRAULIC ACTUATOR FOR A GEARBOX OF A MOTOR VEHICLE

Publications (2)

Publication Number Publication Date
EP1882859A1 EP1882859A1 (en) 2008-01-30
EP1882859B1 true EP1882859B1 (en) 2009-03-11

Family

ID=37813588

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07301179A Not-in-force EP1882859B1 (en) 2006-07-04 2007-06-29 Improved hydraulic actuator for gearbox of an automobile

Country Status (5)

Country Link
EP (1) EP1882859B1 (en)
AT (1) ATE425369T1 (en)
DE (1) DE602007000673D1 (en)
ES (1) ES2322780T3 (en)
FR (1) FR2903460B1 (en)

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4450753A (en) * 1980-05-12 1984-05-29 Ford Motor Company Electro-hydraulic proportional actuator
GB9512838D0 (en) * 1995-06-23 1995-08-23 Massey Ferguson Sa Synchromesh control apparatus and method
GB0307118D0 (en) * 2003-03-27 2003-04-30 Ricardo Uk Linmited Method for controlling a transmission of a vehicle

Also Published As

Publication number Publication date
FR2903460A1 (en) 2008-01-11
EP1882859A1 (en) 2008-01-30
FR2903460B1 (en) 2008-10-10
ATE425369T1 (en) 2009-03-15
ES2322780T3 (en) 2009-06-26
DE602007000673D1 (en) 2009-04-23

Similar Documents

Publication Publication Date Title
FR2703007A1 (en) Hydraulic control assembly, especially for a friction clutch of a motor vehicle
DE602005003151T2 (en) Hydraulic control device for hydraulic excavators
EP0179683B1 (en) Control device for an automatic transmission with four ratios
FR2671585A1 (en) HYDRAULIC DRIVE SYSTEM, IN PARTICULAR FOR AN EXCAVATOR.
GB2339249A (en) Hydraulic system with a single pressure transducer monitoring recharging and operating pressure
FR2516194A1 (en) HYDRAULICALLY CONTROLLED TRANSMISSION FOR MOTOR VEHICLE
FR2586780A1 (en) HYDRAULIC CIRCUIT ELEMENT FOR CONTROLLING A HYDRAULIC CLUTCH MOUNTED IN A VEHICLE TRANSMISSION HOUSING
FR2548291A1 (en) HYDRAULIC INSTALLATION COMPRISING TWO EQUIPMENT USING HYDRAULIC ENERGY
WO2012093240A1 (en) Pressure regulating device with detection of the neutral position
FR2507144A1 (en) POWER ASSISTED STEERING, IN PARTICULAR FOR UTILITY VEHICLES
FR2697872A1 (en) Hydraulic positioning servo drive, in particular for a motor vehicle friction clutch.
FR2578590A1 (en) Multiple hydraulic circuit for mobile equipment
EP1643139B1 (en) Exchange valve device
EP1882859B1 (en) Improved hydraulic actuator for gearbox of an automobile
EP0500419A1 (en) Proportional valve and control system with a plurality of actuators having each such a valve
FR2586775A1 (en) HYDRAULIC CIRCUIT ELEMENT FOR VEHICLE TRANSMISSION
FR2672090A1 (en) HYDRAULIC DRIVE SYSTEM, IN PARTICULAR FOR AN EXCAVATOR.
FR2621354A1 (en) LOAD INDEPENDENT CONTROL DEVICE FOR HYDRAULIC USER DEVICES
FR2652790A1 (en) ANTI-LOCK BRAKING HYDRAULIC SYSTEM FOR A MOTOR VEHICLE.
FR2656910A1 (en) HYDRAULICALLY CONTROLLED TRANSMISSION USED FOR PROPULSION OF A VEHICLE, ESPECIALLY FOR AN AGRICULTURAL TRACTOR.
JP4044283B2 (en) Swivel gear control device provided with braking valve and control valve
FR2778212A1 (en) HYDRAULIC OPERATION DEVICE
FR2732438A1 (en) TWO-WAY VALVE OF THE DOUBLE-WAY PRESSURE DETECTION TYPE
EP0289396B1 (en) Control valve, in particular for the hydraulic brakes of a vehicle
EP0809048A1 (en) Gear shift device for automotive vehicles with shifting assistance to certain ratios

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

17P Request for examination filed

Effective date: 20080625

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: FRENCH

REF Corresponds to:

Ref document number: 602007000673

Country of ref document: DE

Date of ref document: 20090423

Kind code of ref document: P

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2322780

Country of ref document: ES

Kind code of ref document: T3

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090611

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090824

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

REG Reference to a national code

Ref country code: GB

Ref legal event code: 746

Effective date: 20091012

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090711

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

BERE Be: lapsed

Owner name: PEUGEOT CITROEN AUTOMOBILES SA

Effective date: 20090630

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090630

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090611

26N No opposition filed

Effective date: 20091214

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090612

REG Reference to a national code

Ref country code: ES

Ref legal event code: GC2A

Effective date: 20110316

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100629

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090629

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090912

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090311

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110630

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110630

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20160524

Year of fee payment: 10

Ref country code: DE

Payment date: 20160524

Year of fee payment: 10

Ref country code: GB

Payment date: 20160527

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20160525

Year of fee payment: 10

Ref country code: FR

Payment date: 20160526

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602007000673

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20170629

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20180228

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180103

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170629

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170630

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170629

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20181113

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170630