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    • 专利摘要:
    The present invention relates to a pneumatic type device, intended to equip a vehicle, with an improved flattening of its tread with respect to a conventional tire. The pneumatic-type device (1) comprises a radially outer revolution structure (2), intended to come into contact with a ground, a radially inner revolution structure (3), coaxial with the radially outer revolution structure and intended to ensure the connection with a mounting means (4), an inner annular space (5) radially delimited by the two structures of revolution, and a carrier structure (6) connecting at least partly the two structures of revolution, constituted by a plurality of bearing elements (7), two to two independent, subjected to compression buckling in the contact area (A) with the ground. According to the invention, the smallest characteristic dimension E of the section S of any carrier element (7) is at most equal to 0.02 times the average radial height H of the inner annular space (5), the surface density D of the elements carriers (7) per unit area of radially outer rotational structure, expressed in 1 / m2, is at least Z / (A * ΣFr / n), where Z is the nominal radial load, expressed in N, A is the ground contact area, expressed in m2, and ΣFr / n the average tensile breaking force of the n compression-stressed load bearing elements, expressed in N, and the pneumatic type device comprises two flanks (8), connected to the supporting structure (6) and closing the inner annular space (5), constituting a closed cavity that can be pressurized.
    公开号:FR3031932A1
    申请号:FR1550493
    申请日:2015-01-22
    公开日:2016-07-29
    发明作者:Florian Vilcot
    申请人:Michelin Recherche et Technique SA Switzerland ；Compagnie Generale des Etablissements Michelin SCA；Michelin Recherche et Technique SA France；
    IPC主号:
    专利说明:

    [0001] The present invention relates to a device of the pneumatic type, intended to equip a vehicle.  This pneumatic device can be used on all types of vehicles such as two-wheeled vehicles, passenger vehicles, trucks, agricultural vehicles, civil engineering or aircraft or, more generally, on any rolling device.  A conventional tire is a toric structure, intended to be mounted on a rim, pressurized by an inflation gas and crushed on a ground under the action of a load.  The tire has at all points of its rolling surface, intended to come into contact with a ground, a double curvature: a circumferential curvature and a meridian curvature.  By circumferential curvature is meant a curvature in a circumferential plane, defined by a circumferential direction, tangent to the running surface of the tire according to the rolling direction of the tire, and a radial direction, perpendicular to the axis of rotation of the tire.  By meridian curvature is meant a curvature in a meridian or radial plane, defined by an axial direction parallel to the axis of rotation of the tire, and a radial direction perpendicular to the axis of rotation of the tire.  In what follows, the expression "radially inner, respectively radially outer" means "closer to, respectively farther from the axis of rotation of the tire".  The expression "axially inner, respectively axially outer" means "closer or farther away from the equatorial plane of the tire", the equatorial plane of the tire being the plane passing through the middle of the running surface of the tire and perpendicular to the tire. rotation axis of the tire.  It is known that the flattening of the tire on a horizontal ground, in a circumferential plane and in a meridian plane, is conditioned by the values of the radii of curvature respectively circumferential and meridian, at the points of the surface of bearing positioned at the limits of the contact area of the tire with the ground.  This flattening is all the more facilitated as these radii of curvature are large, that is to say that the curvatures are small, the curvature at a point, in the mathematical sense, being the inverse of the radius of curvature.  It is also known that the flattening of the tire impacts the performance of the tire, in particular rolling resistance, adhesion, wear and noise.  Therefore, a person skilled in the art, a tire specialist, seeking to obtain the right compromise between the expected performances of the tire, such as, in a non-exhaustive manner, the wear, the adhesion, the endurance, rolling resistance and noise, has developed alternative solutions to the conventional tire to optimize its flattening.  [0006] A conventional tire of the state of the art generally has a large meridian curvature, i.e. a small radius of meridian curvature, at the axial ends of the tread, called shoulders, when the tire, mounted on its mounting rim and inflated to its recommended operating pressure, is subject to its service load.  The mounting rim, operating pressure and service load are defined by standards, such as, for example, the standards of the European Tire and Rim Technical Organization (ETRTO).  A conventional tire carries the load applied, essentially by the axial ends of the tread, or shoulders, and by the flanks connecting the tread to beads ensuring the mechanical connection of the tire with its mounting rim.  It is known that a meridian flattening of a conventional tire, with a small meridian curve at the shoulders, is generally difficult to obtain.  US Pat. No. 4,235,270 describes a tire having an annular body made of elastomeric material, comprising a radially external cylindrical part, at the periphery of the tire, which may comprise a tread, and a radially inner cylindrical part, intended to be mounted on a rim.  A plurality of circumferentially spaced walls extend from the radially inner cylindrical portion to the radially outer cylindrical portion and provide load bearing.  In addition, flanks may connect the two cylindrical portions respectively radially inner and radially outer, to form, in association with the tread and the sidewalls, a closed cavity and thus allow the pressurization of the tire.  Such a tire, however, has a high mass, compared to a conventional tire, and, because of its massive nature, is likely to dissipate a high energy, which can limit its endurance, and therefore its lifetime.  WO 2009087291 discloses a pneumatic structure comprising two annular rings respectively internal, or radially inner, and outer or radially outer, connected by two sidewalls and a carrier structure.  According to this invention, the carrier structure is pressurized and shares the annular volume of the tire in a plurality of compartments or cells, and the flanks are bonded or integrated with the carrier structure.  In this case, the load applied is carried by both the carrier structure and the sidewalls.  The pressure distribution in the contact area is not homogeneous in the axial width of the contact area, with overpressures at the shoulders due to the difficulty of lying flat meridian due to the connection between the flanks and the supporting structure.  These overpressures at the shoulders are likely to generate significant wear of the shoulders of the tread.  [0009] WO 2005007422 discloses an adaptive wheel comprising an adaptive band and a plurality of radii extending radially inwardly from the adaptive band to a hub.  The adaptive strip is intended to adapt to the surface of contact with a soil and to cover the obstacles.  The spokes transmit the load carried between the adaptive strip and the hub, thanks to the tensioning of the spokes which are not in contact with the ground.  Such an adaptive wheel requires an optimization of the distribution of the spokes to ensure a substantially cylindrical periphery.  In addition, an adaptive wheel has a relatively high mass compared to a conventional tire.  The present invention aims to provide a pneumatic type device with an improved flattening of its tread, when subjected to a load.  This object has been achieved according to the invention by a device of the pneumatic type, intended to equip a vehicle, comprising: a radially external structure of revolution whose axis of revolution is the axis of rotation of the device; pneumatic type and intended to come into contact with a ground through a tread comprising at least one elastomeric material, the radially outer revolution structure having two axial ends and comprising a reinforcing circumferential reinforcement, a structure radially inner revolution, coaxial with the radially outer revolution structure and intended to ensure the connection of the pneumatic type device with a mounting means on the vehicle, the radially inner revolution structure having two axial ends and comprising at least one polymeric material , an inner annular space of average radial height H, radially delimited by the respectively radially outer and radially inner revolution structures, a carrier structure consisting of a plurality of carrier elements, extending continuously from the radially outer revolution structure to the structure of radially inner revolution, two to two independent in the inner annular space, such that, when the pneumatic-type device is subjected to a radial nominal load Z and is in contact with a plane ground by a contact surface A, the n carrying elements, connected to the radially outer revolution structure portion in contact with the ground, are subjected to compression buckling and at least a portion of the carrier elements, connected to the portion of the radially outward revolution structure, in contact with the ground, are in tension, 10-each carrier element having a breaking force in tractio n Fr, and an average section S having a shape ratio K equal to L / E, where L and E are respectively the largest and the smallest dimension characteristic of the mean section S, the smallest characteristic dimension E of the S average section of any carrier element being at most equal to 0. Twice the average radial height H of the inner annular space, the surface density D of the carrier elements per unit area of radially outer revolution structure, expressed as 11 m 2, being at least equal to Z / (A * EFr / n), where Z is the nominal radial load, expressed in N, A is the ground contact area, expressed in m2, and EFrin is the average tensile breaking force of the n load bearing elements subjected to compression buckling, expressed in N And the pneumatic-type device comprising two flanks, connecting the axial ends of the respectively radially outer and radially inner revolution structures and axially delimiting the inner annular space, so that the inner annular space constitutes a closed cavity which can be pressurized by an inflation gas.  [0012] The principle of a pneumatic type device according to the invention is to have a carrier structure, consisting of independent two-to-two bearing elements in the inner annular space, and capable of carrying the load applied to the device pneumatic by the tensioning of a portion of the carrier elements positioned outside the contact area, the n carrier elements positioned in the contact area being subjected to buckling in compression and thus not participating in the carrying of the load applied.  Each carrier member extends continuously from the radially outer revolution structure to the radially inner revolution structure, i.e. in a trajectory comprising a first interface end. with the radially outer revolution structure and a second end interfacing with the radially inner revolution structure.  The carrier elements are two to two independent in the inner annular space, that is to say not mechanically linked to each other in the inner annular space, so that they have independent mechanical behaviors.  For example, they are not linked together to form a network or trellis.  They function as independent stays.  Each carrier element has a tensile force Fr and an average section S, these two characteristics are not necessarily identical for all the carrier elements.  The average section S is the average of the sections obtained by cutting the carrier element by all the cylindrical surfaces, coaxial with the two radially outer and radially outer surfaces of revolution, and radially between said two surfaces of revolution.  In the most frequent case of a constant section, the average section S is the constant section of the carrier element.  The middle section S comprises a larger characteristic dimension L and a smaller characteristic dimension E, whose ratio K = L / E is called the aspect ratio.  By way of example, a carrier element having a circular average section S, having a diameter equal to d, has a shape ratio K = 1, a carrier element having a rectangular average section S, having a length L and a width 1, has a form ratio K = L / 1, and a carrier element having an elliptical mean section S, having a major axis A and a minor axis a, has a form ratio K = A / a.  According to a first essential characteristic, the smallest characteristic dimension E of the average section S of any carrier element is at most equal to 0. 02 times the radial height 25 average H of the inner annular space.  This characteristic excludes any massive carrier element, having a large volume.  In other words, each carrier element has a high slenderness, in the radial direction, allowing it to flare at the passage in the contact area.  Outside the contact area, each carrier element returns to its original geometry, because its buckling is reversible.  Such a carrier element has a good resistance to fatigue.  According to a second essential characteristic, the surface density D of the carrier elements per unit area of radially external structure of revolution, expressed as 3031932 - 6 - 11m2, is at least equal to Z / (A * EFr / n) , where Z is the nominal radial load, expressed in N, A is the ground contact area, expressed in m2, and EFrin is the average tensile strength of the n load bearing elements subjected to compression buckling, expressed in N.  EFrin is the average tensile strength of the n compression-buckling load-bearing members, each having a tensile breaking force Fr which is not necessarily constant over all the load-bearing members.  Essentially, the distribution of the load-bearing elements is optimized and the surface density of the load-bearing elements is sufficiently high to guarantee a flattening of the tread, to the passage in the contact area, both in a circumferential plane and in a meridian plane, improved over conventional tires and other pneumatic devices known from the state of the art.  The distribution of the load-bearing members is more uniformly distributed and denser than in the pneumatic type devices of the state of the art, both circumferentially and axially, which contributes to conferring on the tread a quasi-cylindrical geometry, with a so-called "daisy effect" effect decreased.  According to a third essential characteristic, the pneumatic device of the invention comprises two flanks, connecting the axial ends of the respectively radially external and radially inner revolution structures and axially delimiting the inner annular space, so that the inner annular space constitutes a closed cavity which can be pressurized by an inflation gas.  Flanks, depending on their design and, in particular, their structural rigidity, may participate more or less in the carrying of the applied load.  The flanks generally comprise at least one elastomeric material and may optionally comprise a reinforcing reinforcement.  The flanks may or may not be directly related to the supporting structure.  In the case where they are not directly related to the supporting structure, the flanks have an independent mechanical behavior, without affecting the proper mechanical operation of the supporting structure.  In addition, in combination with the two respectively radially outer and radially inner revolution structures, they close the inner annular space which then constitutes a closed cavity that can be pressurized or not by an inflation gas.  In the case of effective pressurization by an inflation gas, the pneumatic type device then has a pneumatic rigidity, due to pressure, which will also contribute to the carrying of the applied load.  The higher the pressure, the higher the contribution of the pneumatic rigidity to the load carrying capacity applied, and, correlatively, the greater the contribution of the structural stiffness of the load-bearing structure and / or flanks and / or respectively radially outer and radially inner revolution structures at the port of the applied load is low.  In the absence of pressurization and in the case of a low structural stiffness of the flanks, the bearing structure and the respectively radially outer and radially inner revolution structures ensure the entire load port, the flanks playing only one side. role of protection vis-à-vis the possible attacks by elements external to the device of the pneumatic type.  The combination of these essential characteristics allows an improved flattening of the tread, particularly in a meridian plane, by increasing meridian radii of curvature at the axial ends of the tread.  This results, in particular, in homogenizing the pressures in the ground contact area, which contributes to an improvement in the wear life and the adhesion of the pneumatic type device.  The combination of these essential characteristics also makes it possible to increase the natural vibration frequencies of the pneumatic type device, which contributes to improving the vibratory and acoustic comfort of the pneumatic type device.  Finally, the rolling resistance of such a pneumatic type device is substantially reduced, which is favorable to a decrease in fuel consumption of the vehicle.  [0023] The surface density of the carrier elements per unit area of radially outer revolution structure, expressed in 1 / m 2, is advantageously at least equal to 3 * Z / (A * EFr / n).  A higher surface density of support elements improves the homogenization of pressures in the ground contact area and guarantees a higher safety factor with respect to the applied load and with respect to endurance. .  [0024] The surface density of the carrier elements per radially outer surface structure unit unit, expressed in 1 / m 2, is still advantageously at least equal to 6 * Z / (A * EFr / n).  An even higher surface density of carrier elements further improves the homogenization of the pressures in the ground contact area and further increases the safety factor with respect to the applied load and with respect to endurance.  Advantageously, all the carrier elements have an identical tensile strength Fr.  In other words, the load-bearing elements have the same tensile breaking strength, without necessarily having the same geometric characteristics and / or the same constituent materials.  This implies that the average tensile breaking force of the n EFrin compression buckling bearing members is equal to the tensile breaking force Fr of any bearing member.  Under these conditions, the surface density D of the carrier elements per unit area of radially external structure of revolution, expressed in 1 / m2, is at least equal to Z / (A * Fr), where Z is the nominal radial load, expressed in N, A is the ground contact area, expressed in m 2, and Fr is the tensile strength of any carrier element, expressed in N.  The probability of failure by tensile rupture of the carrier elements is thus the same at every point of the carrier structure.  According to a preferred embodiment, the carrier elements are identical, that is to say that their geometric characteristics and constituent materials are identical.  In particular, their tensile fracture forces Fr being identical, the surface density D of the carrier elements per unit area of radially outer revolution structure, expressed in 1 / m 2, is at least equal to Z / (A * Fr) , where Z is the nominal radial load, expressed in N, A is the ground contact area, expressed in m2, and Fr the tensile strength of any load bearing element, expressed in N.  A bearing structure with identical bearing elements advantageously has a homogeneous mechanical behavior and has the advantage of greater ease of manufacture.  According to a first variant of the preferred embodiment, any carrier element is unidimensional with a shape ratio K at most equal to 3.  In other words, a carrier element is considered unidimensional, when the largest characteristic dimension L of its mean section S is at most equal to 3 times the smallest characteristic dimension E 25 of its mean section S.  A one-dimensional carrier element has a wire-like mechanical behavior, i.e. it can only be subjected to extension or compression forces along its mean line.  Of the components commonly used in the tire field, textile reinforcements, consisting of an assembly of textile yarns, or metal cords, constituted by an assembly of metal threads, can be considered as one-dimensional load-bearing elements, since their average section S being substantially circular, the form ratio K is equal to 1, therefore less than 3.  When an unidimensional carrier element in extension has a rectilinear mean line, its mean line is not necessarily radial, that is to say perpendicular to the axis of rotation of the tire.  Such a carrier element is not comparable to a radius.  This non-radial direction of the mean line makes it possible, in particular, to adjust the stiffnesses of the pneumatic device in the respectively axial and circumferential directions.  In the case of the first variant of the preferred embodiment, the surface density D of the identical unidimensional carrier elements per unit area of radially external structure of revolution, expressed in 11 m 2, is advantageously at least equal to 10000.  According to a second variant of the preferred embodiment, any carrier element is two-dimensional with a shape ratio K of at least 3.  In other words, a carrier element is considered two-dimensional, when the greatest characteristic dimension L of its mean section S is at least equal to 3 times the smallest characteristic dimension E of its mean section S.  A two-dimensional carrier element has a membrane-like mechanical behavior, i.e. it can only be subjected to extension or compression forces in its thickness defined by the smallest characteristic dimension E of its middle section S.  According to a first alternative of the second variant of the preferred embodiment, any carrier element is two-dimensional of the strap type with a shape ratio K of at least 20 equal to 3 and at most equal to 50.  In the case of the first alternative of the second variant of the preferred embodiment, the surface density D of the identical two-dimensional carrier elements of the strap type per unit area of radially outer revolution structure, expressed in 1 / m2, is advantageously at least equal to 600 and at most equal to 15,000.  [0033] According to a second alternative of the second variant of the preferred embodiment, any carrier element is two-dimensional film type with a form ratio K at least equal to 50.  In the case of the second alternative of the second variant of the preferred embodiment, the surface density D of the identical two-dimensional carrier elements of the film type 3031932 - 10 - per unit area of radially external structure of revolution, expressed in 11 m 2 , is advantageously at least equal to 100 and at most equal to 1000.  Advantageously, the largest characteristic dimension L of the average section S of a two-dimensional film-type carrier element is at most equal to 0. 9 times the smallest of the 5 axial widths of the respective radially outer and radially inner revolution structures, the respective axial widths of the respectively radially outer and radially inner revolution structures being not necessarily equal.  Beyond this value, the carrier element is then a so-called through film then circumferentially separating the inner cavity of the tire into cells or cells.  When a two-dimensional carrier element is plane, its mean plane is not necessarily radial, that is to say perpendicular to the axis of rotation of the tire.  Such a carrier element is not comparable to a radius.  This non-radial direction of the average plane makes it possible, in particular, to adjust the rigidities of the pneumatic device in the directions respectively axial and circumferential.  As regards the nature of the material, any carrier element advantageously comprises a material of polymer or metal or glass or carbon type.  Polymers, in particular elastomers, and metal, such as steel, are commonly used in the tire field.  Glass and carbon are alternative materials conceivable for use in pneumatics.  In a first variant of material, any carrier element advantageously comprises polyethylene terephthalate (PET).  PET is commonly used in the tire field because of a good compromise between its mechanical properties, such as tensile strength and cost.  In a second variant of material, any carrier element also advantageously comprises an aliphatic polyamide, such as nylon.  Nylon is also commonly used in the tire field for the same reasons as PET.  According to a first structural variant, any carrier element has a homogeneous structure, comprising a single component.  It is the simplest structure envisaged, such as, for example, a wire or a membrane.  According to a second structural variant, any carrier element has a composite structure, comprising at least two constituents.  It is a structure constituted by an assembly of at least two elements, such as, for example, a cable constituted by a set of elementary wires.  In a first variant of composition, any carrier element comprises a single material: for example, a wire or a cable of textile material.  In a second variant of composition, any carrier element comprises at least two materials.  In this case, there is a composite structure from the point of view of the materials: for example, a hybrid cable comprising yarns having different materials, such as aramid and nylon, or a fabric comprising textile reinforcements embedded in a material. elastomeric material and arranged parallel to each other or in the form of weft.  As regards the sidewalls, advantageously the sidewalls are not directly related to the carrier structure.  They may or may not participate in carrying the load, according to their own structural rigidity.  In the case where they participate in carrying the load, they have an independent mechanical behavior and do not interfere in the mechanical behavior of the carrier structure.  However, in the case of a carrier structure comprising one-dimensional and / or two-dimensional load-bearing members of the strap type, the load-bearing elements positioned at the axial ends of the support structure may be connected to or integrated with the sidewalls.  Each flank having a curvilinear length LF, the curvilinear length LF of each flank is preferably at least 1. 05 times, preferably, 1. 15 times the average radial height H of the inner annular space.  Even more advantageously, the curvilinear length LF of each flank is at least equal to 1. 3 times and at most equal to 1. 6 times the average radial height H of the inner annulus.  This flank length feature ensures that sidewall deformation will not disturb the meridian flattening of the pneumatic type device with a small curvature.  The circumferential reinforcing reinforcement of the radially outer revolution structure advantageously comprises at least one reinforcing layer comprising textile or metal reinforcing elements.  To ensure transverse or axial rigidity of the pneumatic device, the radially outer revolution structure comprises a reinforcing reinforcement comprising at least one reinforcing layer consisting of reinforcing wire elements, most often metallic or textiles, coated in an elastomeric material.  This reinforcing reinforcement is most often radially interior to a tread.  The assembly constituted by the reinforcement and the tread constitutes the radially outer shell of revolution.  The radially inner revolution structure also advantageously comprises on a radially inner face a connecting layer intended to be fixed on the mounting means on the vehicle.  The tie layer generally comprises at least one elastomeric material, but not necessarily reinforcing reinforcement.  Attachment to the mounting means may be effected by the pressure forces resulting from inflating the pneumatic device.  According to an alternative embodiment, the radially inner revolution structure comprises on a radially inner face a connecting layer intended to be fixed on the mounting means on the vehicle, by gluing.  In particular, a glued connection makes it possible to avoid any rotation of the pneumatic type device with respect to the mounting means on the vehicle.  The invention also relates to a mounted assembly comprising a pneumatic device according to one of the embodiments described above, mounted on a mounting means on the vehicle.  The pneumatic device of the invention may be manufactured, for example, according to the method described hereinafter.  The supporting structure is manufactured separately in the form of a composite structure of sandwich type, consisting of a first elastomeric layer, intended to be secured to the radially inner revolution structure, a second elastomeric layer, intended to be secured to the structure of the structure. radially outer revolution and by carrying elements extending from the first elastomeric layer to the second elastomeric layer.  Any known method of manufacturing composite sandwich structure can be used.  Once the carrier structure has been made, the pneumatic type device can be manufactured according to the following process steps: winding of the radially inner revolution structure on a cylinder whose diameter is equal to that of the mounting means, on which is for mounting the pneumatic-type device, winding of the carrier structure on the radially inner revolution structure; placing flanks at the axial ends of the bearing structure so as to constitute a closed cavity, pressurizing said closed cavity, to deploy the carrier structure, winding the radially outer revolution structure on the supporting structure, depressurizing the closed cavity up to ambient atmospheric pressure, heating the device.  The assembly mounted according to the invention can be achieved by fixing the pneumatic type device on a mounting means, such as a rim.  This attachment can be achieved, for example, by bonding the radially inner face of the radially inner revolution structure to the radially outer face of the mounting means.  The present invention will be better understood with reference to FIGS. 1 to 7 presented below: FIG. 1 is a perspective view in partial section of a pneumatic type device according to the invention FIG. 2 view of a circumferential cut of a pneumatic type device according to the invention, in the crushed state -Figure 3A: view of a meridian section of a pneumatic type device according to the invention, in the case of A carrier structure with unidimensional carrying elements 20 -Figure 3B: perspective view of a one-dimensional bearing element -Figure 4A: view of a meridian section of a pneumatic type device according to the invention, in the case of a structure carrier with two-dimensional carrier elements of the strap type -Figure 4B: perspective view of a two-dimensional carrier element of the strap type -Figure 5A: view of a meridian section of a pneumatic-type device according to the invention, 25 in the case a supporting structure Two-dimensional film-type carrier elements -Figure 5B: Perspective view of a two-dimensional film-type carrying element -Figure 6: Comparative standard curves of the evolution of the load applied as a function of the arrow for a pneumatic-type device according to FIG. the invention (wired carrier elements) and a reference tire of the state of the art.  FIG. 7: Comparative standard curves of the evolution of drift rigidity as a function of the load applied for a pneumatic type device according to the invention (wired load-bearing elements) and a reference tire of the invention. state of the art.  FIG. 1 shows a perspective view in partial section of a pneumatic type device 1 according to the invention, mounted on a mounting means 4 or rim, and comprising a radially outer revolution structure 2, a radially inner revolution structure 3, an inner annular space 5, a carrier structure 6 and two sidewalls 8.  The radially outer revolution structure 2 has an axis of revolution which is the axis of rotation YY 'of the pneumatic device and is intended to contact a ground via a tread 21 comprising less an elastomeric material.  In addition, the radially outer revolution structure 2 comprises a reinforcing circumferential reinforcement 22 constituted, in the present case, by a single reinforcing layer.  The radially inner revolution structure 3, coaxial with the radially outer revolution structure 2, is intended to ensure the connection of the pneumatic device 1 with the mounting means 4.  The radially inner revolution structure 3 comprises at least one polymeric material, most often an elastomeric mixture.  The inner annular space 5 is radially delimited by the respectively radially outer and radially inner revolution structures 3.  The carrier structure 6, according to the invention, is constituted by a plurality of carrier elements 7, extending continuously from the radially outer revolution structure 2 to the radially inner revolution structure 3, two by two. independent in the inner annular space 5.  Finally, the pneumatic type device 1 comprises two flanks 8, connecting the axial ends of the respectively radially outer and radially inner revolution structures 3 and axially delimiting the inner annular space 5, so that the inner annular space 5 is a closed cavity that can be pressurized by an inflation gas.  FIG. 2 shows a circumferential section of a pneumatic type device 1 according to the invention, mounted on an assembly means 4, in its crushed state, that is to say subjected to a nominal radial load Z .  The carrier structure 6 is constituted by a plurality of carrier members 7, extending continuously from the radially outer revolution structure 2 to the radially inner revolution structure 3, two to two independent in each other. the inner annular space 5.  The pneumatic type device 1, subjected to a nominal radial load Z, is in contact with a plane ground by a contact surface A, having a circumferential length XA.  The carrier elements 71, connected to the radially outer rotational structure portion 2 in contact with the ground, are subjected to compression buckling, while at least a portion of the supporting elements 72, connected to the portion of the structure of radially outer revolution 2 not in contact with the ground, are in tension.  FIG. 2 represents a particular embodiment of the invention with identical and radially oriented bearing elements 7.  According to the invention, the surface density D of the carrier elements 7 per unit area of radially outer revolution structure 2, expressed in 1 / m 2, is at least equal to Z / (A * Fr), where Z is the nominal radial load, expressed in N, A is the ground contact area, expressed in m2, and Fr the tensile strength of any load bearing element, expressed in N.  FIG. 3A shows a meridian section of a pneumatic type device 1 according to the invention, mounted on an assembly means 4, in the case of a carrier structure 6 to 15 unidimensional carrying elements 7.  As described for FIG. 1, the pneumatic type device 1 comprises a radially outer revolution structure 2, a radially inner revolution structure 3, an inner annular space 5, a carrier structure 6 and two sidewalls 8.  The pneumatic type device 1, subjected to a nominal radial load Z, is in contact with a plane ground by a contact surface A, having an axial width YA.  In the case presented, all the carrier elements 7 are identical and are oriented radially, therefore have a length equal to the average radial height H of the inner annular space 5.  As seen above, the carrier elements 7, positioned opposite the contact area are in tension, while the carrier elements 7, connected to the radially outer revolution structure portion 2 in contact with the ground, are subject to buckling in compression.  FIG. 3B shows a one-dimensional carrier element 7 having a circular average section S, defined by a smaller characteristic dimension E and a larger characteristic dimension L both equal to the diameter of the circle, and characterized by its shape ratio. K equal to L / E.  The smallest characteristic dimension E of the average section S of the carrier element 7, i.e., in this case, its diameter, is at most equal to 0. 02 times the average radial height H of the inner annulus 5.  Moreover, in this particular case of circular section, the K-form ratio is equal to 1.  The carrier element 7 being oriented radially, its length 1 is equal to the average height H of the inner annular space 5.  Figure 4A shows a meridian section of a pneumatic type device 1 according to the invention, mounted on a mounting means 4, in the case of a carrier structure 6 to 5 two-dimensional carrier elements 7 of the strap type.  As described for FIG. 1, the pneumatic type device 1 comprises a radially outer revolution structure 2, a radially inner revolution structure 3, an inner annular space 5, a carrier structure 6 and two sidewalls 8.  The pneumatic type device 1, subjected to a nominal radial load Z, is in contact with a plane ground by a contact surface A, having an axial width YA.  In the case presented, all the carrier elements 7 are identical and are oriented radially, therefore have a length equal to the average radial height H of the inner annular space 5.  As seen above, the carrier elements 7, positioned opposite the contact area are in tension, while the carrier elements 7, connected to the radially outer revolution structure portion 2 in contact with the ground, are subject to 15 with buckling in compression.  FIG. 4B shows a two-dimensional stripe type carrier element 7 having a rectangular mean section S, defined by its smallest characteristic dimension E, or thickness, and its largest characteristic dimension L, or width, and characterized by its ratio. of form K equal to L / E.  The smallest characteristic dimension E of the average section S of the carrier element 7, that is to say, in this case, its thickness, is at most equal to 0. 02 times the average radial height H of the inner annulus 5.  In the case of a two-dimensional carrier element 7 type strap, the form ratio K at least equal to 3 and at most equal to 50.  The carrier element 7 being oriented radially, its length 1 is equal to the average height H of the inner annular space 5.  FIG. 5A shows a meridian section of a pneumatic type device 1 according to the invention, mounted on a mounting means 4, in the case of a carrier structure 6 with two-dimensional carrier elements 7 of the film type.  As described for FIG. 1, the pneumatic type device 1 comprises a radially outer revolution structure 2, a radially inner revolution structure 3, an inner annular space 5, a carrier structure 6 and two sidewalls 8.  The pneumatic type device 1, subjected to a nominal radial load Z, is in contact with a plane ground by a contact surface A, having an axial width YA.  In the case presented, all the carrier elements 7 are identical and are oriented radially, therefore have a length equal to the average radial height H of the inner annular space 5.  As previously seen, the carrier elements 7, positioned opposite the contact area are in tension, while the carrier elements 7, connected to the radially outer revolution structure portion 2 in contact with the ground, are subjected to buckling in compression.  FIG. 5B shows a two-dimensional film-type carrier member 7 having a rectangular mean section S, defined by its smallest characteristic dimension E, or thickness, and its largest characteristic dimension L, or width, and characterized by its form ratio K equal to L / E.  The smallest characteristic dimension E of the average section S of the carrier element 7, that is to say, in this case, its thickness, is at most equal to 0. 02 times the average radial height H of the inner annulus 5.  In the case of a two-dimensional film-type carrier element 7, the shape ratio K is at least equal to 50.  Since the carrier element 7 is oriented radially, its length 1 is equal to the average height 15 H of the inner annular space 5.  FIG. 6 shows two comparative standard curves of the evolution of the applied load Z, expressed in daN, as a function of the arrow F, expressed in mm, for a pneumatic type device according to the invention I, in the case of a carrier structure with identical one-dimensional carrying elements, and a reference tire R of the state of the art.  This figure shows that, for a given radial load Z, the arrow F of a pneumatic type device according to the invention I is smaller than that of the reference tire R.  Otherwise, the radial rigidity of the pneumatic device I is greater than the radial rigidity of the reference tire R.  FIG. 7 shows two compared standard curves of the evolution of the drift rigidity, expressed in N / °, as a function of the applied load, expressed in N, for a pneumatic type device according to the invention. , in the case of a carrier structure with identical one-dimensional bearing elements, and a reference tire of the state of the art.  This figure shows that, for a given radial load Z, the drift rigidity Z of a pneumatic type device according to the invention I is greater than that of the reference tire R.  The invention has been more particularly studied as an alternative solution to a conventional tire for a passenger vehicle.  The pneumatic type device studied, whose stiffness characteristics are presented in FIGS. 6 and 7 previously described, comprises two radially outer and radially inner revolution structures having respective average radii equal to 333 mm and 289 mm, and axial widths both equal to 250 mm.  The inner annular space 5, radially delimited by the respectively radially outer and radially inner revolution structures, has an average radial height H equal to 35 mm.  The supporting structure consists of one-dimensional son-type carrying elements.  Each carrier element, polyethylene terephthalate (PET), has a mean section S equal to 7 * 10-6 m2 and a breaking stress equal to 470 MPa.  The surface density D of the carrier elements per unit area of radially outer revolution structure is equal to 85000 threads / m2.  The pneumatic type structure, inflated has a pressure p between 1. 5 bar and 2. 5 bar, is subjected to a radial load Z equal to 1000 daN.  Although the carrier structure according to the invention preferably consists of identical bearing elements, both in shape K, in structure and in material, it can be constituted by any combination of carrier elements, such as that, for example and non-exhaustively: - one-dimensional carrier elements having K-form ratios and / or structures and / or different materials, - two-dimensional carrier elements having K-shape ratios and / or structures and / or different materials, unidimensional carrier elements and two-dimensional carrier elements.
    权利要求:
    Claims (16)
    [0001]
    REVENDICATIONS1. Pneumatic device (1), intended to equip a vehicle, comprising: a radially outer revolution structure (2) whose axis of revolution is the axis of rotation (YY ') of the pneumatic type device and intended for contacting a ground via a tread (21) comprising at least one elastomeric material, the radially outer revolution structure having two axial ends and comprising a circumferential reinforcing reinforcement (22), a structure of radially inner revolution (3), coaxial with the radially outer revolution structure (2) and intended to ensure the connection of the pneumatic type device with a mounting means (4) on the vehicle, the radially inner revolution structure (3). ) having two axial ends and comprising at least one polymeric material, -an inner annular space (5) of average radial height H, radially delimited by r respectively the radially outer (2) and radially inner (3) revolution structures, -a carrier structure (6) constituted by a plurality of carrier elements (7), extending continuously from the radially outer revolution structure (2) up to the radially inner revolution structure (3), two by two independent in the inner annular space (5), so that when the pneumatic type device is subjected to a nominal radial load Z and in contact with a planar ground by a contact surface A, the n carrying elements (71), connected to the radially outer rotational structure portion (2) in contact with the ground, are subjected to compression buckling and to at least a portion of the carrier elements (72), connected to the non-contacting portion of the radially outer revolution structure (2), are under tension, -each carrier member (7) having a breaking force e in traction Fr, and an average section S having a shape ratio K equal to L / E, where L and E are respectively the largest and the smallest dimension characteristic of the average section S, characterized in that the smallest characteristic dimension E of the average section S of any carrier element (7) is at most equal to 0.02 times the average radial height H of the inner annular space (5), in that the surface density D of the carrier elements (7) per unit area of radially outer revolution structure (2), expressed in 1 / m2, is at least equal to Z / (A * EFr / n), where Z is the nominal radial load, expressed in N, A is the ground contact area, expressed in m 2, and EFr the mean tensile breaking force of the n compressible buckling members, expressed in N, and that the pneumatic device (1) comprises two flanks (8), connecting the axial ends of the structures of revolution respectively radially outer (2) and radially inner (3) and axially delimiting the inner annular space (5), so that the inner annular space (5) 5 constitutes a closed cavity that can be pressurized by an inflation gas .
    [0002]
    2. Pneumatic device (1) according to claim 1, wherein the surface density D of the carrier elements (7) per unit area of radially outer revolution structure (2), expressed in 11m2, is at least 3. * Z / (A * EFr / n).
    [0003]
    3. Pneumatic device (1) according to one of claims 1 or 2, wherein the surface density D of the carrier elements (7) per unit area of radially outer revolution structure (2), expressed in 11m2, is at least 6 * Z / (A * EFr / n).
    [0004]
    4. Pneumatic device (1) according to any one of claims 1 to 3, wherein all the carrier elements (7) have a tensile strength Fr identical.
    [0005]
    Pneumatic device (1) according to any one of claims 1 to 3, wherein all the carrier elements (7) are identical.
    [0006]
    6. Pneumatic device (1) according to any one of claims 1 to 5, wherein any carrier element (7) is unidimensional with a form ratio K at most equal to 3.
    [0007]
    Pneumatic device (1) according to any one of claims 1 to 5, wherein any carrier element (7) is two-dimensional with a shape ratio K of at least 3.
    [0008]
    8. Pneumatic device (1) according to claim 7, wherein any carrier element (7) is two-dimensional strap type with a form ratio K at least equal to 3 and at most equal to 50. 25
    [0009]
    9. Pneumatic device (1) according to claim 7, wherein any carrier element (7) is two-dimensional film type with a form ratio K at least equal to 50.
    [0010]
    10. Pneumatic device (1) according to any one of claims 1 to 9, wherein any carrier element (7) comprises a polymer type material or metal or glass or carbon. 3031932 -21-
    [0011]
    Pneumatic device (1) according to any one of claims 1 to 10, wherein any carrier element (7) comprises polyethylene terephthalate (PET).
    [0012]
    Pneumatic device (1) according to any one of claims 1 to 11, wherein any carrier element (7) comprises an aliphatic polyamide, such as nylon. 5
    [0013]
    13. Pneumatic device (1) according to any one of claims 1 to 12, wherein the sidewalls (8) are not directly connected to the carrier structure (6).
    [0014]
    14. Pneumatic device (1) according to any one of claims 1 to 13, wherein the circumferential reinforcing armature (22) of the radially outer revolution structure (2) comprises at least one reinforcing layer comprising 10 textile or metal reinforcing elements.
    [0015]
    15. Pneumatic device (1) according to any one of claims 1 to 14, wherein the radially inner revolution structure (3) comprises on a radially inner face a bonding layer to be fixed on the mounting means. (4) on the vehicle. 15
    [0016]
    16. Mounted assembly (1, 4) comprising a pneumatic type device (1) according to any one of claims 1 to 15 mounted on a mounting means (4) on the vehicle.
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    同族专利:
    公开号 | 公开日
    FR3031932B1|2017-02-03|
    CN107223089A|2017-09-29|
    EP3247574B1|2018-12-05|
    WO2016116490A1|2016-07-28|
    JP2018504311A|2018-02-15|
    US10259264B2|2019-04-16|
    CN107223089B|2019-07-12|
    US20180009263A1|2018-01-11|
    EP3247574A1|2017-11-29|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US519976A|1894-05-15|Bicycle-tire |
    US4235270A|1978-06-30|1980-11-25|The Goodyear Tire & Rubber Company|Tire with supporting and cushioning walls|
    US20130048174A1|2011-08-30|2013-02-28|Societe De Technologie Michelin|Molded article and venting assembly for a rotating mold|
    US4285270A|1979-10-29|1981-08-25|Schweitzer Industrial Corporation|Paint spray booth with flooded floor|
    US7650919B2|1999-12-10|2010-01-26|Michelin Recherche of Technique S.A.|Non-pneumatic tire having web spokes|
    US7013939B2|2001-08-24|2006-03-21|Michelin Recherche Et Technique S.A.|Compliant wheel|
    FR2895936B1|2006-01-12|2010-06-04|Michelin Soc Tech|CARRIER STRUCTURE FOR SUPPORT SUPPORT AND OPTIMIZED SUPPORT SUPPORT|
    FR2922159B1|2007-10-15|2011-04-29|Michelin Soc Tech|PNEUMATIC ROLLER WITH CARRIER STRUCTURE|
    US9662939B2|2009-07-28|2017-05-30|Bridgestone Americas Tire Operations, Llc|Tension-based non-pneumatic tire|
    WO2012091754A1|2010-12-29|2012-07-05|Michelin Recherche Et Technique, S.A.|Structurally supported non-pneumatic wheel with reinforcements and method of manufacture|
    JP6043582B2|2012-10-22|2016-12-14|株式会社ブリヂストン|Non pneumatic tire|
    CN107107663A|2015-01-15|2017-08-29|株式会社普利司通|Non-inflatable tyre|FR3054485A1|2016-07-29|2018-02-02|Compagnie Generale Des Etablissements Michelin|PNEUMATIC TYPE DEVICE FOR VEHICLE|
    FR3054484A1|2016-07-29|2018-02-02|Compagnie Generale Des Etablissements Michelin|PNEUMATIC TYPE DEVICE FOR VEHICLE|
    FR3067981A1|2017-06-23|2018-12-28|Compagnie Generale Des Etablissements Michelin|PNEUMATIC TYPE DEVICE FOR VEHICLE|
    FR3069484A1|2017-07-27|2019-02-01|Compagnie Generale Des Etablissements Michelin|WHEEL FOR MOUNTING PNEUMATIC TYPE DEVICE FOR VEHICLE|
    WO2019077280A1|2017-10-18|2019-04-25|Compagnie Generale Des Etablissements Michelin|Assembly|
    FR3075100A1|2017-12-15|2019-06-21|Compagnie Generale Des Etablissements Michelin|MOUNTED ASSEMBLY FOR VEHICLE WITH CHARACTERISTIC MONITORING SYSTEM OF CLOSED PNEUMATIC BANDAGE|
    US20200376890A1|2017-12-21|2020-12-03|Steven M. Cron|Reinforced annular support for a tire|
    US20220010102A1|2018-11-22|2022-01-13|Bridgestone Corporation|Tire|
    WO2021094033A1|2019-11-15|2021-05-20|Compagnie Generale Des Etablissements Michelin|Turnup of rubber products without beadwires|
    法律状态:
    2016-01-21| PLFP| Fee payment|Year of fee payment: 2 |
    2016-07-29| PLSC| Search report ready|Effective date: 20160729 |
    2017-01-20| PLFP| Fee payment|Year of fee payment: 3 |
    2018-01-19| PLFP| Fee payment|Year of fee payment: 4 |
    2019-09-27| ST| Notification of lapse|Effective date: 20190906 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1550493A|FR3031932B1|2015-01-22|2015-01-22|PNEUMATIC TYPE DEVICE FOR VEHICLE|FR1550493A| FR3031932B1|2015-01-22|2015-01-22|PNEUMATIC TYPE DEVICE FOR VEHICLE|
    EP16701040.4A| EP3247574B1|2015-01-22|2016-01-20|Tyre-type device for a vehicle|
    CN201680006682.4A| CN107223089B|2015-01-22|2016-01-20|Tyre type equipment for vehicle|
    US15/545,404| US10259264B2|2015-01-22|2016-01-20|Tire-type device for a vehicle|
    PCT/EP2016/051099| WO2016116490A1|2015-01-22|2016-01-20|Tyre-type device for a vehicle|
    JP2017538434A| JP2018504311A|2015-01-22|2016-01-20|Tire type equipment for vehicles|
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