Classifications

• • 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
  • F16H48/00—Differential gearings
  • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
  • F16H48/24—Arrangements for suppressing or influencing the differential action, e.g. locking devices using positive clutches or brakes
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H48/00—Differential gearings
  • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
  • F16H48/22—Arrangements for suppressing or influencing the differential action, e.g. locking devices using friction clutches or brakes
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H48/00—Differential gearings
  • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
  • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
• • 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
  • F16H48/00—Differential gearings
  • F16H48/38—Constructional details
• • 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
  • F16H48/00—Differential gearings
  • F16H48/38—Constructional details
  • F16H48/40—Constructional details characterised by features of the rotating cases
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
  • B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
  • B60K23/04—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for differential gearing
  • B60K2023/046—Axle differential locking means
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
  • B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
  • B60K23/08—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles
• • 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
  • F16H48/00—Differential gearings
  • F16H48/06—Differential gearings with gears having orbital motion
  • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
  • F16H2048/082—Differential gearings with gears having orbital motion comprising bevel gears characterised by the arrangement of output shafts
• • 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
  • F16H48/00—Differential gearings
  • F16H48/06—Differential gearings with gears having orbital motion
  • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
  • F16H2048/087—Differential gearings with gears having orbital motion comprising bevel gears characterised by the pinion gears, e.g. their type or arrangement
• • 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
  • F16H48/00—Differential gearings
  • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
  • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
  • F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
  • F16H2048/346—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators using a linear motor
• • 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
  • F16H48/00—Differential gearings
  • F16H48/06—Differential gearings with gears having orbital motion
  • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears

Definitions

• the invention relates to the field of transmission chains for motor vehicles.
• the differential drive device comprises a first element intended to be driven by a motor and a second element intended to drive one and/or the other of the two wheel shafts of the axle of the vehicle as well as a device for coupling capable of selectively coupling the first element to the second element.
• Patent application US2006/0270510 describes a differential assembly which includes a differential housing and a pinion housing.
• the gear housing includes a first gear and a second gear.
• a first side gear and a second side gear are operably coupled to the first gear and the second gear.
• a sliding band selectively engages at least one of the pinion housing and the first and second side gears.
• the sliding collar thus offers three engagement modes which are a disconnected mode, an open mode and a locked mode.
• the differential assembly includes a spring assembly that is disposed between the housing and the sliding collar to push the sliding collar in the opposite direction to that provided by the actuator.
• the invention aims to improve this type of device.
• the subject of the invention is therefore a differential drive device for a transmission system for a motor vehicle, having an axis of rotation and comprising:
• connection slider movable axially and provided with interconnection teeth, in particular axial, the connection slider and the locking slider being mobile to occupy three axial positions: o a disconnected position in which the interconnection teeth of the connection slider are disconnected from the interconnection teeth of the planet carrier, and the interconnection teeth of the locking slider are disconnected from the interconnection teeth of the output sun gear, o a position connected in which the interconnection teeth of the connection slider are connected to the interconnection teeth of the satellite carrier, and the interconnection teeth of the locking slider are disconnected from the interconnection teeth of the output sun gear, o a blocked position in which the interconnection teeth of the connection slider are connected to the interconnection teeth of the planet carrier, and the interconnection teeth of the locking slider are connected to the interconnection teeth of the output sun gear,
• a spring arranged to exert a force on the connection player towards the satellite carrier so as to, when moving from the disconnected position to the connected position, promote the engagement of the interconnection teeth of the connection player in the clutch teeth of the satellite carrier.
• An axial interconnection tooth comprises teeth which project axially, in the direction of the axis of rotation.
• a radial clutch tooth comprises teeth which project radially, and therefore perpendicular to the axis of rotation.
• the spring which is compressed, can act on the connection slider as soon as the relative rotation of the teeth places these teeth in a position of mutual commitment.
• the spring thus helps to accelerate the mutual engagement of the mated teeth, which improves the dynamics of the differential drive device. In fact, the spring can move the connection slider more quickly than an actuator alone would do because the inertia of the spring is lower.
• the torque transmission between the motor and the wheels is disconnected.
• the connected position it is possible to transmit torque between the motor and the wheel shafts by performing the differential function allowing different rotation speeds for the two wheel shafts.
• the spring is an axial spring.
• the spring is a preloaded spring.
• the spring stores elastic energy permanently, regardless of its position.
• the locking slider is fixed in rotation relative to the satellite carrier in the connected position.
• connection player is movable axially and fixed in rotation relative to the satellite carrier in the connected position.
• connection player and the blocking player are arranged so as to be moved by the same actuator.
• the spring is arranged between an actuator and the connection slider.
• the blocking slider and the connection slider are rigidly linked in translation along the axis of rotation, being for example made on the same part.
• the blocking slider and the connection slider are movable axially relative to each other, and the spring is interposed between the blocking slider and the connection slider so that the connection slider can be moved axially by the locking slider via the spring.
• the spring is notably arranged between the connection and blocking sliders.
• the stiffness of the spring is in particular such that the blocking slider and the connection slider are integral axially when no obstacle opposes the axial movement of the connection slider and/or the blocking slider.
• connection slider is arranged movable axially relative to the blocking slider, between a stop position on a stop of the locking slider and an axial recoil position, back from this stop , in which the spring is compressed.
• the spring is preloaded when the connection slider is in the abutment position against the stop of the locking slider.
• the pre-loaded spring tends to push the connection slider against this stop.
• the stop on the locking slider is formed by a circlip secured to this locking slider.
• connection player comes up against this circlip when you are in the disconnected position.
• the interconnection teeth of the connection slider and the interconnection teeth of the planet carrier do not overlap, and the interconnection teeth of the locking slider and the interconnection teeth of the output sun gear do not overlap either more.
• the spring can then be in a state of less stress, particularly in its initial preload state.
• connection slider In the connected position, the interconnection teeth of the connection slider and the interconnection teeth of the satellite carrier are in axial overlap, and the spring can still be in a state of less stress, in particular in its initial preloaded state.
• the interconnection teeth of the connection player and the interconnection teeth of the satellite carrier extend axially.
• the spring not only serves to facilitate the engagement of the connection slider by storing energy in the event of interference, but it also favors the implementation of axial rather than radial teeth.
• the use of axial teeth is advantageous because it allows in particular to have a tooth profile with anti-dropping. Without a spring, with such axial teeth, the connected/unblocked position would involve the use of long axial teeth with partial axial overlap of the teeth of these teeth, to allow additional axial movement to reach the other connected/blocked position, which is not optimal for the torque transmission. It is in fact preferable that the axial teeth engage all the way to the bottom of the teeth to transmit a torque. Thanks to the spring, it is possible to use teeth which completely engage with each other in the connected/unlocked position.
• the device comprises a friction device arranged to create a torque difference between two wheels linked to the differential drive device, in particular in the connected mode.
• a perfect differential that is to say without internal friction, would distribute the input torque perfectly symmetrically between the two wheels linked to this differential, in a ratio of 50/50.
• the torque on the other wheel is also canceled and the vehicle loses traction.
• the friction device which generates a constant and/or proportional friction between moving parts of the differential, it is possible to create a torque gap between the two wheels, constant or proportional to the input torque, and improve the crossing capacity. of the vehicle.
• the torque difference between the two wheels is in particular of the order of 3 to 5%.
• an additional friction device passive or active, deviations of around 30% can be achieved.
• the friction device comprises a stack of friction disks.
• the device further comprises an output sun gear opposite the aforementioned output sun gear and the friction device is placed between this opposite output sun gear and the planet carrier.
• a first set of fiction discs are secured in rotation to the opposite output planetary gear, in particular via teeth and splines.
• a second set of fiction disks are rotationally secured to the satellite carrier, in particular via teeth and grooves. The disks of the first set and the second set are arranged alternately so as to obtain a multitude of friction surfaces.
• the conical teeth of the opposite output sun gear allow, when the latter rotates, to press the friction discs against each other to generate a friction torque.
• the first set of friction discs may be driven by the differential housing.
• the manufacture of the satellite carrier is simplified.
• the axial teeth of the connection slider and the satellite carrier are in particular in axial overlap
• the connection slider is in axial abutment on the differential housing or the satellite carrier
• the spring is compressed
• the teeth of the connection Radial interconnection of the locking slider and the output sun gear are in radial overlap.
• the connection slider is in an axial recoil position, back from the stop of the locking slider.
• the teeth of the satellite carrier and the teeth of the output sun gear are arranged inside the differential housing.
• the device comprises a differential housing and the satellite carrier can rotate freely in the differential housing when the connection player is in a disconnected position.
• the device comprises a differential housing and the locking switch is in prismatic connection with the differential housing.
• this prismatic connection is produced by respective axial splines of the locking slider and of the differential housing, splines which are meshed to allow relative translation while blocking relative rotation.
• the locking slider is provided with radial clutch teeth.
• the interconnection teeth of the connection player and the interconnection teeth of the satellite carrier have axial interconnection teeth, in particular of the anti-dropping type.
• the anti-release type clutch teeth have undercuts and undercuts with angles chosen to ensure that the teeth cannot spontaneously disengage while they are transmitting a torque. , making it possible to avoid accidental disconnection.
• the combined tooth pairs can be axial or radial, with or without anti-release angle.
• the invention also relates to a transmission system comprising the aforementioned differential drive device and an actuator, this actuator being arranged to move the blocking slider and the connection slider in the three disconnected, connected and blocked positions, and in a reverse sequence.
• the actuator is arranged to return the players to the disconnected position.
• the locking switch transmits the force from the actuator to the connection switch, via the spring.
• the blocking slider comprises a groove arranged to cooperate with the actuator.
• Figure 1 is a sectional view of a transmission system comprising a differential drive device according to an example of implementation of the invention.
• Figure 2 is a view, in perspective and in section, of the differential drive device of Figure 1, in the disconnected position.
• Figure 3 is a view, in perspective and in section, of the differential drive device of Figure 1, in the connected position.
• Figure 4 is a view, in perspective and in section, of the differential drive device of Figure 1, in the blocked position.
• Figure 5 is a view, in perspective and in section, of the locking slider of the differential drive device of Figure 1.
• Figure 6 is a detailed perspective view of the differential housing and the sliders of Figure 1.
• Figure 7 is a schematic view of a second embodiment.
• the axis X of rotation of the differential housing defines the “axial” orientation.
• the “radial” orientation is directed orthogonal to the X axis.
• FIG. 1 illustrates a transmission system 1 according to one embodiment.
• the transmission system 1 comprises a differential drive device 2.
• the differential drive device 2 is intended to rotate two shafts of wheels 3, 4 of an axle of a vehicle and is configured to distribute a torque coming from a motor, not illustrated, towards the two wheel shafts 3, 4, allowing them to rotate at different speeds.
• Such a transmission system 1 is for example intended for a hybrid vehicle.
• the transmission system 1 is, for example, capable of transmitting a torque from an electric motor to a rear or front axle of the vehicle while another transmission system coupled to another motor, such as a heat engine , makes it possible to generate a torque and transmit it between this other motor and the two wheel shafts of the other axle of the vehicle.
• the vehicle can also be fully electric.
• the differential drive device 2 comprises a first assembly 5, movable in rotation around the axis X, which is intended to be kinematically coupled to a motor via a reduction device, not shown.
• the differential drive device 2 also includes a second assembly 6, also movable in rotation around the axis X and intended to drive the wheel shafts 3, 4.
• the first assembly 5 of the differential drive device 2 comprises a differential housing 8.
• the differential housing 8 comprises two parts 10, 11 which are fixed to each other.
• the second assembly 6 of the differential drive device 2 comprises a satellite carrier 12 of annular shape, which is guided in rotation, around the axis X, inside the differential housing 8.
• the second assembly 6 comprises, in addition, satellites 14 with gears, as well as two sun gears 15, 16 with gears.
• the satellites 14 are mounted in rotation on the satellite carrier 12 around an axis Y, perpendicular to the axis sun gears 15, 16.
• the two sun gears 15, 16 are mobile in rotation around the axis X and are each integral in rotation with one of the two wheel shafts 3, 4 respectively.
• the planet carrier 12, the satellites 14 and the sun gears 15, 16 thus form a differential allowing the two wheel shafts 3, 4 to rotate, if necessary, at different speeds.
• the differential drive device 2 includes:
• connection slider 27 and the locking slider 24 are mobile to occupy three axial positions:
• the device 2 further comprises a pre-stressed axial spring 30 arranged to exert a force on the connection slider 27 towards the satellite carrier 12 so as to, when moving from the disconnected position to the connected position, promote the engagement of the interconnection teeth 28 of the connection player 27 in the interconnection teeth 20 of the satellite carrier 12.
• This spring 30 is, in the example described, coiled.
• the axial clutch teeth 20 and 28 comprise teeth which project axially, in the direction of the axis of rotation.
• the radial clutch teeth 21 and 25 comprise teeth which project radially, and therefore perpendicular to the axis of rotation.
• the locking slider 24 is fixed in rotation relative to the differential housing 8.
• the locking slider 24 is fixed in rotation relative to the satellite carrier 12 in the connected position.
• connection slider 27 is fixed in rotation relative to the differential housing 8.
• the connection slider 27 is movable axially and fixed in rotation relative to the satellite carrier 12 in the connected position.
• connection slider 27 and the locking slider 24 are arranged so as to be moved by the same actuator 32.
• the blocking slider 24 and the connection slider 27 are movable axially relative to each other, and the spring 30 is interposed between the blocking slider 24 and the connection slider 27 so as to that the connection slider 27 can be moved axially by the locking slider 24 via the spring 30.
• the spring 30 is arranged between the connection 27 and blocking 24 sliders.
• the stiffness of the spring 30 is chosen such that the blocking slider 24 and the connection slider 27 are integral axially when no obstacle opposes the axial movement of the connection slider 27 and/or the blocking slider 24.
• connection slider 27 is arranged movable axially relative to the locking slider 24, between a stop position on a stop 33 of the locking slider 24 and an axial recoil position, back from this stop 33, in which the spring 30 is compressed.
• the spring 30 is preloaded when the connection slider 27 is in the abutment position against the stop 33 of the locking slider 24.
• connection slider 27 tends to push the connection slider 27 against this stop 33 formed by a circlip secured to this locking slider 24.
• the connection slider 27 abuts against this circlip 33 when it is in the disconnected position.
• the spring 30 rests, at its end opposite the connection slider 27, on a stop formed by a circlip 34.
• the interconnection teeth 28 of the connection slider 27 and the interconnection teeth 20 of the planet carrier 12 do not overlap, and the interconnection teeth 25 of the locking slider 24 and the interconnection teeth 21 of the planetary output 16 do not overlap either.
• the interconnection teeth 28 of the connection slider 27 and the interconnection teeth 20 of the planet carrier 12 are in axial overlap, and the spring 30 is in a state of less stress, in its initial preloaded state.
• connection slider 27 The interconnection teeth 28 of the connection slider 27 and the interconnection teeth 20 of the satellite carrier 12 extend axially.
• the device 2 comprises a friction device 40 arranged to create a torque difference between the shafts 3, 4 of the two wheels linked to the differential drive device 2, in the connected mode.
• the friction device 40 which generates a constant and/or proportional friction between moving parts of the differential, it is possible to create a torque gap between the two wheels, constant or proportional to the input torque, and improve the capacity of crossing of the vehicle. Without additional device, the torque difference between the two wheels is in particular of the order of 3 to 5%. With an additional friction device, passive or active, deviations of around 30% can be achieved.
• the friction device 40 comprises a stack of friction disks 41.
• the friction device 40 is placed between the opposite output sun gear 15 and the planet carrier 12.
• a first set 60 of fiction discs are secured in rotation to the opposite output sun gear 15, in particular via teeth and splines.
• a second set 61 of fiction disks are secured in rotation to the satellite carrier 12, in particular via teeth and splines.
• the disks of the first set 60 and the second set 61 are arranged alternately so as to obtain a multitude of friction surfaces.
• the conical teeth of the opposite output sun gear 15 make it possible, during the rotation of the latter, to press the friction discs 41 against each other to generate a friction torque.
• connection slider 27 In the blocked position illustrated in Figure 3, the axial teeth of the connection slider 27 and the satellite carrier 12 are in axial overlap, the connection slider 27 is in axial abutment on the planet carrier 12, the spring 30 is compressed , and the radial clutch teeth of the locking slider 24 and the output sun gear 16 overlap radially.
• the teeth 20 of the satellite carrier 12 and the teeth 21 of the output sun gear 16 are arranged inside the differential housing 8 and inside a gearbox housing.
• the mobile connection players 27 and locking devices 24 benefit from the lubrication of the gearbox.
• the satellite carrier 2 can rotate freely in the differential housing 8 when the connection player 27 is in a disconnected position (figure 1).
• the locking switch 24 is in prismatic connection with the differential box 8.
• This prismatic connection is produced by respective axial splines 47 and 48 of the locking slider 24 and the differential housing 8, splines which are meshed to allow relative translation while blocking relative rotation.
• the grooves 48 are made on a sleeve 49 of the differential housing 8.
• This sleeve 49 carries a circlip 50 forming a stop for the locking slider 24.
• the interlocking teeth 28 of the connection slider 27 and the interlocking teeth 20 of the planet carrier 12 have axial interlocking teeth of the anti-dropping type.
• the anti-release type clutch teeth have undercuts and undercuts with angles chosen to ensure that the teeth cannot spontaneously disengage while they are transmitting a torque. , making it possible to avoid accidental disconnection.
• the actuator 32 is arranged to move the blocking slider 24 and the connection slider 27 successively in the three positions disconnected (figures 1 and 2), connected (figure 3) and blocked (figure 4), and in an inverse sequence.
• the blocking slider 24 transmits the force of the actuator 32 to the connection slider, via the spring.
• the blocking slider 24 has a groove 55 arranged to cooperate with the actuator 32 which has a fork shape at this location.
• the actuator 32 here is an electro-magnetic type actuator.
• Figure 6 illustrates certain details of the locking sliders 24 and connection 27.
• complementary axial grooves 35, 36 provided respectively on the locking slider 24 and the connection slider 27 make it possible to block the relative rotation between these two sliders 24 and 27.
• the connection slider 27 is secured in rotation to the differential housing 8 via, on the one hand, the complementary grooves 35, 36 which secure it in rotation with the locking slider 24, and on the other hand share the axial grooves 47 and 48 of the locking slider 24 and the differential housing 8.
• the locking slider 24 and the connection slider 27 are secured in rotation with the differential housing 8 thanks to a correspondence in shape between the connection sliders 27 and the locking slider 24 and windows 51 of the differential housing 8.
• connection slider 27 and the locking slider 24 are axially integral.
• they can be manufactured in the same room. They jointly form a double player 65.
• the spring 30 is arranged kinematically between the actuator 32 and the double slider 65.
• the same spring makes it possible to manage both the interconnection interference of the connection slider 27 and the interconnection interference of the blocking slider 24.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Retarders (AREA)

Applications Claiming Priority (2)

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• 2022
  • 2022-04-14 FR FR2203460A patent/FR3134608B1/fr active Active
• 2023
  • 2023-04-13 CN CN202380039199.6A patent/CN119234100A/zh active Pending
  • 2023-04-13 WO PCT/EP2023/059610 patent/WO2023198803A1/fr not_active Ceased
  • 2023-04-13 EP EP23723823.3A patent/EP4508345A1/de active Pending
  • 2023-04-13 US US18/855,535 patent/US12607254B2/en active Active

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