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
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
  • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
  • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
  • F16F15/1336—Leaf springs, e.g. radially extending
• • 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
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
  • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
  • F16F15/123—Wound springs
  • F16F15/1238—Wound springs with pre-damper, i.e. additional set of springs between flange of main damper and hub
  • F16F15/12393—Wound springs with pre-damper, i.e. additional set of springs between flange of main damper and hub pre-damper springs are of non-wound type, e.g. leaf springs
• • 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
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
  • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
  • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
  • F16F15/1333—Spiral springs, e.g. lying in one plane, around axis of rotation
• • 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
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F2226/00—Manufacturing; Treatments
  • F16F2226/04—Assembly or fixing methods; methods to form or fashion parts
• • 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
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F2230/00—Purpose; Design features
  • F16F2230/0052—Physically guiding or influencing
  • F16F2230/0064—Physically guiding or influencing using a cam

Definitions

• the invention relates to a shock absorber, in particular a torsion damper, in particular for a clutch of a motor vehicle.
• FR 2 894 006, FR 2 913 256 and FR 2 922 620 illustrate torsion dampers equipping respectively a double damping flywheel, a clutch friction and a lock-up clutch.
• the elastic damping means fitted to these torsion dampers are helical springs with a circumferential effect whose ends come, on the one hand, in abutment with stops integral with the input elements and, on the other hand, in support against stops integral with the output elements.
• any rotation of one of said elements relative to the other causes a compression of the springs of the damper in one direction or the other and said compression exerts a restoring force able to return said elements to a relative angular position. rest.
• the coil springs can be straight or bent.
• Document FR 2 938 030 is also known which describes a torsion damper provided with elastic blades.
• the invention aims to improve the torsion dampers above.
• the invention thus relates to a shock absorber, in particular a torsion damper, in particular for an automobile clutch, comprising:
• damping means for transmitting torque and damping rotation acyclisms between the input and output elements; said damper being characterized in that the damping means comprise an elastic blade and this elastic blade is formed by a stack of lamellae, the thickness of each lamella being less than 15 mm, preferably less than 10 mm.
• the invention it is possible to produce blades of relatively large total thickness by assembling several lamella of relatively small thickness. This is advantageous because the manufacture of lamella of relatively low thickness is simpler and of better quality than the manufacture of thicker lamellae.
• the slats are stacked along the axis of rotation.
• the elastic blade is arranged to deform, during operation, in a plane perpendicular to the axis of rotation.
• the thickness of each lamella is less than 7 mm, being for example between 1 mm and 6 mm.
• the manufacture of lamellae is all the more simple as these lamellae are thin.
• the lamellae of the stack all have the same thickness. This simplifies the manufacture because there is only one type of coverslip.
• one of the slats may have a thickness different from that of the other slats.
• the elastic blade is composed of 2 to 20 lamellae, in particular 2 to 15 lamellae, for example 2, 3, 4, 6, 7, 8, 9, 10, 11, or 12 lamellae.
• the blade has a total thickness greater than 3 mm, especially greater than 5 or 10 mm, being for example about 12 mm or 16 mm.
• the lamellae of the blade are stacked so that the edge of the blade is a cylindrical surface, the lamellae being stacked exactly. In other words, when the blade is viewed from the side, the edge of the blade is not staged.
• the contour of the blade when the blade is observed along the axis of rotation, is curved.
• This contour is for example formed by a succession of circular arcs, or arcs of ellipse.
• arcs of circle or ellipse may, if desired, be tangents two by two.
• the blade comprises at least one connecting element for assembling the lamellae.
• the assembly element is a rivet.
• the slats can also be assembled by deformation of the slats, in particular by clinching.
• the slats are welded or brazed together.
• the lamellae are assembled by two different assembly methods, in particular using rivets and clinching.
• the slats are assembled together via assembly areas spaced apart from each other.
• the assembly zones are arranged along a portion of the blade, in particular substantially along the neutral axis of the blade.
• the invention is particularly advantageous in that each lamella is formed from a sheet, in particular cut. The cut can be made in a simple and very reliable manner because the slat has a small thickness.
• At least one of the slats is made of steel.
• all the lamellae are made of the same material.
• At least one of the lamellae is made of a material different from the other lamellae.
• one of the input and output elements is provided with a cam surface arranged to cooperate with said elastic blade.
• the elastic blade is provided with a cam surface and one of the input and output elements is provided with a cam follower, for example a roller rotatably mounted, arranged to cooperate with said cam follower.
• a cam follower for example a roller rotatably mounted, arranged to cooperate with said cam follower.
• cam surface for example, the blade has a curved, circumferentially extending portion at the free end of which the cam surface is formed.
• the elastic blade produces a reaction force able to recall said input and output elements to said angular position of rest.
• said cam surface is arranged such that, for angular displacement between the input member and the output member with respect to an angular rest position, the cam follower exerts a bending force on the elastic blade producing a reaction force adapted to return said input and output elements to said angular position of rest.
• the elastic blade has a fixing portion to one of the input and output elements.
• the cam follower is disposed radially outside the elastic blade.
• the damper has a second resilient blade provided with a cam surface and a second cam follower arranged to cooperate with the cam surface of said second resilient blade.
• the first and second resilient blades are carried by an annular body and are symmetrical with respect to the axis of rotation X.
• the input element comprises two flanges, integral in rotation, arranged on either side of the damping means and thus defining a housing cassette of said damping means .
• the resilient blade is rotationally integral with the output member and the cam follower is carried by a fastener for fixing the flanges to one another.
• the cam follower is a roller rotatably mounted on the fastener.
• the roller is rotatably mounted on the fastening element by means of a rolling bearing.
• the output element comprises a hub having internal splines for cooperating with splines of a gearbox input shaft and the elastic blade is carried by an annular body having a toothing cooperating with a toothing. complementary formed on the hub.
• the elastic blade is held axially on the hub.
• the toothing of the hub cooperating with the toothing of the annular body is bordered on the one hand by an abutment surface and on the other hand by a crimping formed on the hub so as to allow axial retention of the annular body on the hub.
• the invention also relates to a clutch friction disk comprising a damper according to the invention as described above.
• one of the two flanges of the input element of said torsion damper is advantageously constituted by an output web of a second damper.
• the invention also relates to a double damping flywheel, in particular for an automobile clutch, comprising a torsion damper, comprising:
• damping means for transmitting torque and damping rotation acyclisms between the input and output elements
• damping means comprise an elastic blade and this elastic blade is formed by a stack of lamellae.
• the thickness of each lamella is less than 15 mm, preferably less than 10 mm.
• the invention also relates to a clutch comprising a damper as described above.
• the invention also relates to a method of manufacturing a damper as described above, characterized in that the slats are stacked to be assembled, in particular by riveting and / or clinching and / or welding and / or brazing, and / or collage.
• Figure 1 is a front view of a clutch friction disc.
• FIG. 2 is an exploded view of the friction disk of FIG.
• Figure 3 is a sectional view of the friction disc of Figure 1 in the plane III-III.
• Figure 4 is a sectional view of the friction disk of Figure 1 in the plane IV-IV.
• FIG. 5 is a partially exploded view of the pre-damper.
• FIG. 6 is a perspective view of a subassembly of the pre-damper of FIG. 5.
• Figure 7 is a perspective view of the resilient blade damping means and the hub of the friction disk.
• Figure 8 is a perspective view of the resilient blade damping means.
• Figure 9 illustrates the deflection of a torsion damper blade during angular deflection between the input and output members of the damper in a forward direction.
• Figure 10 illustrates the deflection of the blade during an angular deflection in a retro direction.
• FIG. 11 is an example of characteristic curves of a pre-damper, representing the torque transmitted as a function of the angular deflection.
• Figure 12 is a perspective view of the resilient blade damping means and the hub of the friction disc according to an alternative embodiment.
• FIG. 13 is a sectional view of the resilient blade damping means and the hub of FIG. 12.
• Figure 14 is a detailed view of the assembly between the resilient blade and the hub of Figures 12 and 13.
• Figure 15 is an exploded view of an elastic blade composed of four lamellae.
• Figure 16 is a perspective view of an elastic blade composed of lamellae assembled with rivets.
• FIG. 17 is an exploded view of the resilient blade of Figure 16 before its assembly with rivets.
• Figure 18 is a front view of the resilient blade of Figure 16 with its neutral axis.
• Figure 19 is a view of the elastic blade according to a variant of the invention.
• Figure 20 is a perspective view of the elastic blade in a double damping flywheel.
• the clutch friction disk 1 shown in Figures 1 to 4, is intended to be mounted integral in rotation with a driven shaft and to be disposed between a pressure plate of a clutch and a reaction plate, integral in rotation of a driving shaft. During a clutch operation, the pressure plate clamps the friction disk 1 against the reaction plate and the torque of the driving shaft is then transmitted to the driven shaft.
• the friction disc 1 comprises a support disc 2, illustrated in Figures 3 and 4, bearing on each of its faces, friction linings 3, 4 to be clamped between the pressure plates and reaction.
• the support disk 2 is fixed on two guide washers 5, 6, forming the input element of the main damper, arranged on either side of a web 7, forming the output element of said damper main.
• the guide washers 5, 6 are fixed to one another by riveting, for example.
• the damping means of the main damper are circumferentially acting elastic members, such as helical springs 8.
• the coil springs 8 are mounted in housing windows 9, 10 formed, facing each other, in the guide washers 5, 6 and in the web 7.
• the coil springs 8 are for example mounted in pairs of concentric springs.
• the helical springs 8 are held axially in their respective housings by the outer edges 11 of the windows 9 of the guide washers 5, 6.
• the ends of the coil springs 8 bear against the radial edges of the housing windows 9, 10 in such a way that that said helical springs 8 are able to transmit a torque between the guide washers 5, 6 and the web 7.
• the coil springs 8 have a stiffness sufficient to allow the transmission of the maximum engine torque.
• the main damper is also equipped with axial-action friction means, represented in FIGS. 3 and 4, intended to dissipate the energy accumulated in the coil springs 8.
• the axial-action friction means comprise a friction washer 14 and an elastic washer 15, also called “Belleville” washer.
• the friction washer 14 is secured in rotation to the guide washer 6 by axial fingers, shown in FIG. 3, nested in orifices formed in said guide washer 6.
• the elastic washer 15 is interposed under stress between the washer guide 6 and the friction washer 15 so as to press said friction washer 15 against the web 7.
• the friction disk 1 is also equipped with a pre-damper which is shown in detail in FIG. 5.
• a pre-damper essentially has the function of filtering noises such as box noises or noise from dead point in the engine idle speed range while the main damper is intended to filter vibrations in the vehicle running speed.
• the pre-damper is here implanted radially below the helical springs 8 of the main damper and axially between the two guide rings 5, 6 of the main damper.
• the input element of the pre-damper comprises two flanges 12, 13, integral in rotation, arranged axially on either side of the damping means of the pre-damper.
• the flanges 12, 13 thus form a housing cassette damping means of the pre-damper.
• one of the flanges 13 is constituted by the veil 7 output of the main damper.
• the flange 12 is fixed in rotation on the web 7 by a plurality of fastening tabs 16 received in orifices 17 of complementary shape, formed in the web 7.
• the two flanges 13, 14 are separate from the output sail 7 of the main damper. They are in this case, fixed in rotation to said web 7 in order to couple in series the main damper and the pre-damper.
• the output element of the pre-damper is a hub 18 intended to be coupled in rotation to a driven shaft, such as an input shaft of a gearbox.
• the hub 18 has internal longitudinal grooves 19 intended to cooperate with complementary splines formed on the driven shaft.
• the hub 18 comprises on its outer periphery a toothing 20 intended to mesh, with a circumferential clearance determined, with a corresponding toothing 21 formed on an inner periphery of the web 7.
• the teeth 20, 21 form angular stops to limit the relative deflection between the input element and the output element of the pre-damper when the torque to be transmitted is greater than a threshold.
• the web 7 and the hub 18 cooperate with each other by stop. In this case, the pre-damper no longer intervenes in the transmission of the torque that is directly transmitted from the sail 7 to the hub 18.
• the damping means comprise at least one resilient blade 22 mounted to rotate with the hub 18.
• the elastic blade 22 is carried by an annular body 25 having an internal toothing 26, shown in FIG. 8, cooperating with a external toothing, of complementary shape, formed on the hub 18.
• the annular body 25 carrying the elastic blades 22 is held axially on the hub 22.
• the external toothing formed on the hub 18 and cooperating with the internal toothing 26 of the annular body 25 is bordered, on the one hand, by an abutment surface 29 and, on the other hand, by a crimp 30 formed on the body of the hub 18.
• the damping means comprise two resilient blades 22 carried by the annular body 25.
• the two resilient blades 22 are symmetrical with respect to the axis of rotation X of the disk. clutch.
• the resilient blades 22 have, at one free end, a cam surface 23 which is arranged to cooperate with a cam follower: the rollers 24.
• the resilient blades 22 comprise a curved portion 27 extending substantially circumferentially.
• the radius of curvature of the curved portion 27 as well as the length of this curved portion 27 are determined according to the desired stiffness of the elastic blade 22.
• the elastic blade 22 may optionally be made in one piece or, in accordance with the invention, be composed of a plurality of lamellae 28a, 28b, 28c, 28d arranged axially against each other, as illustrated in FIG. Figure 15.
• the resilient blades 22 and the annular body 25 are constituted by a plurality of lamellae 28a, 28b, 28c, 28d extending axially against each other.
• the slats can be glued to each other.
• the plurality of lamellae 28a, 28b, 28c, 28d is mounted on a hub 18 as shown in FIGS. 12 to 14. In this case, the assembly between the lamellae 28a, 28b, 28c, 28d is performed during the crimping of the hub 18.
• the rollers 24 are here borne by fastening lugs 16 for securing the flange 12 to the web 7.
• the rollers 24 are advantageously rotatably mounted on said fastening lugs 16 about an axis of rotation parallel to the axis of rotation. rotation X.
• the rollers 24 are held in abutment against their respective cam surface 23 and are arranged to roll against said cam surface 23 during relative movement between the input and output elements of the pre-damper.
• the rollers 24 are radially outwardly from their respective cam surfaces 23 so as to radially maintain the resilient blades 22 when subjected to centrifugal force.
• the rollers 24 can be mounted in rotation on the fastening lugs 16 by means of a rolling bearing.
• the rolling bearing may be a ball bearing or roller.
• the rollers 24 have an anti-friction coating.
• the cam surface 23 is arranged such that, for angular displacement between the input member and the output member, relative to a relative angular position of rest, the roller 24 moves on the cam surface 23 and, in doing so, exerts a bending force on the elastic blade 22.
• the elastic blade 22 exerts on the roller 24 a restoring force which tends to bring the input 1 and output 2 elements back to their position relative angular rest.
• the resilient blades 22 are capable of transmitting a driving torque from the input element to the output element (forward direction) and a resisting torque of the output element towards the input element (retro direction ).
• the torque to be transmitted causes a travel relative between the input member and the output member in a first direction (see Figure 9).
• the roller 24 is then moved by an angle ⁇ relative to the elastic blade 22.
• the displacement of the roller 24 on the cam surface 23 causes a flexion of the elastic blade 22 along an arrow ⁇ .
• the blade 22 is shown in solid lines in its angular position of rest and in dotted lines during an angular movement.
• the bending force P depends in particular on the geometry of the elastic blade 22 and its material, in particular its transverse modulus of elasticity.
• the bending force P is decomposed into a radial component Pr and a tangential component Pt.
• the tangential component Pt allows the transmission of the engine torque.
• the elastic blade 22 exerts on the roller 24 a reaction force whose tangential component constitutes a restoring force which tends to bring the input and output elements of the pre-damper to their relative angular position of rest.
• a resistive torque is transmitted from the output element to the input element (retro direction)
• the torque to be transmitted causes a relative deflection between the input element and the output element in a second direction opposite (see Figure 10).
• the roller 24 is then displaced by an angle ⁇ with respect to the elastic blade 22.
• the tangential component Pt of the bending force has a direction opposite to the tangential component of the bending force illustrated in FIG. Figure 9.
• the resilient blade 22 exerts a reaction force of direction opposite to that shown in Figure 9, so as to bring the input and output elements to their relative angular position of rest.
• FIG. 11 illustrates a characteristic curve of torsion dampers made in accordance with the teachings of the invention.
• This characteristic curve represents the transmitted torque, expressed in Nm, as a function of the angular deflection, expressed in degrees.
• the relative movement between the input and output elements, in the forward direction, is shown in dashed lines while the movement in the retro direction is shown in solid lines.
• a torsion damper according to the invention allows in particular to obtain damping characteristic curves whose slope varies gradually without discontinuity.
• the cam surface 23 and the elastic blade 22 are arranged in such a way that the characteristic function of the torque transmitted as a function of the angular displacement is a monotonic function.
• the cam surface 23 and the elastic blade 22 may be arranged in such a way that the characteristics of the torque transmitted as a function of the angular displacement, in the retro direction and in the forward direction, are symmetrical with respect to the angular position of rest.
• FIGS. 16 and 17 Another embodiment of the invention will now be described with reference to FIGS. 16 and 17.
• FIG. 15 show two elastic blades 122 substantially identical to the blades 22 described with reference to FIG. 15, with the exception in particular of the mode of assembly of the slats and the number of slats.
• Each elastic blade 122 is formed by a stack of lamellae 123, the thickness of each lamella 123 being less than 15 mm, preferably less than 10 mm.
• each lamella 123 is 2 mm.
• the lamellae 123 are stacked along the axis of rotation X.
• the elastic blade 122 is arranged to deform, during operation, in a plane P perpendicular to the axis of rotation X.
• the lamellae 123 of the stack all have the same thickness.
• the elastic blade 122 is composed of eight lamellae 123.
• the elastic blade 122 has a total thickness of about 16 mm.
• the lamellae 123 of the blade 122 are stacked so that the edge 124 of the blade is a cylindrical surface, the lamellae 123 being stacked exactly.
• the blade 122 has assembly elements 125 for assembling the lamellae 123.
• These connecting elements 125 are rivets.
• the lamellae 123 comprise openings 126 for receiving the rivets
• the lamellae 123 are assembled by clinching.
• the lamellae 123 comprise embossings 127 able to cooperate with an embossing 127 of the adjacent lamella 123.
• the slats are assembled together via assembly zones 130 spaced apart from each other. Each zone 130 is formed by a rivet 125 and the corresponding opening 126. These assembly zones 130 are arranged along a curved portion 131 of the blade, substantially along the neutral axis 132 of the blade.
• all the lamellae 123 are each formed from a cut sheet steel.
• elastic blades 122 in a double damping flywheel 201.
• the primary flywheel 202 comprises a radially inner hub 205, supporting a centering bearing 204 of the secondary flywheel 203, which is provided with orifices 227 for the passage of screws, for fixing the double damping flywheel 201 to the nose of the crankshaft.
• the damping means comprise two resilient blades 122 which are here rotatably mounted to the secondary flywheel 203 and which carry cam surfaces 220, arranged to cooperate with cam followers carried by the primary flywheel 202.
• the elastic blades 122 are carried by an annular body 218. Said annular body 218 is fixed on the primary flywheel 202 by means of a plurality of rivets 228 cooperating with orifices formed in the annular body 218 and in the primary flywheel 202.
• the blades 122 comprise a plurality of lamellae 123.
• the cam followers here are rollers 221, rotatably mounted, on the primary flywheel 202, about an axis parallel to the axis of rotation X.
• the rollers 221 are mounted on cylindrical rods 222, fixed on the steering wheel. primary 202, by rolling bearings.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Acoustics & Sound (AREA)
• Aviation & Aerospace Engineering (AREA)
• Mechanical Engineering (AREA)
• Mechanical Operated Clutches (AREA)

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• 2014
  • 2014-08-08 FR FR1457723A patent/FR3024758B1/fr not_active Expired - Fee Related
• 2015
  • 2015-06-23 WO PCT/FR2015/051678 patent/WO2016020584A1/fr active Application Filing
  • 2015-06-23 EP EP15748272.0A patent/EP3177851A1/de not_active Withdrawn

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