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
  • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
  • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
  • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
  • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
  • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
  • F16F13/1409—Units of the bushing type, i.e. loaded predominantly radially characterised by buffering features or stoppers
• • 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
  • F16F1/00—Springs
  • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
  • F16F1/38—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type
  • F16F1/3807—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type characterised by adaptations for particular modes of stressing
  • F16F1/3821—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type characterised by adaptations for particular modes of stressing characterised by adaptations to counter torsional forces
• • 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
  • F16F1/00—Springs
  • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
  • F16F1/38—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type
  • F16F1/3863—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type characterised by the rigid sleeves or pin, e.g. of non-circular cross-section
• • 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
  • F16F1/00—Springs
  • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
  • F16F1/38—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type
  • F16F1/387—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type comprising means for modifying the rigidity in particular directions

Definitions

• the invention relates, in general, to vibration control techniques, and in particular to an elastic articulation designed to assemble two parts of a force transmission structure, in particular of a motor vehicle, and to dampen the vibrations. transmitted from one of these rooms to another.
• the invention relates to an elastic hinge having first and second axial ends spaced apart from one another along a longitudinal axis, and comprising at least, at increasing radial distance from this axis, an internal reinforcement, an intermediate reinforcement and an outer sleeve, this articulation further comprising elastic and / or hydro-elastic damping means interposed on the one hand between the internal reinforcement and the intermediate reinforcement, and on the other hand between this intermediate reinforcement and the outer sleeve, these damping means being designed to oppose a static and / or dynamic resistance force to any relative displacement, perpendicular to the longitudinal axis, of the inner armature relative to the outer sleeve.
• the damping means consist exclusively of a lining of elastomeric material, the deformations of which generate a force of elastic resistance to radial relative displacement of the inner armature relative to the outer sleeve.
• the damping means comprise, in addition to an elastomeric lining, chambers filled with a liquid, the circulation of which inside the hinge opposes a force of dynamic resistance to the radial relative displacement of the inner armature relative to the outer sleeve.
• the invention which is indifferently applicable to one and the other of these two types of joints, is intended to provide a hinge usable under extreme conditions with minimal risk of damage and irreversible damage.
• the articulation of the invention is essentially characterized in that the intermediate reinforcement has a generally cylindrical shape supplemented by a plurality of reliefs rigid shaped and arranged to transmit a bearing force of the inner armature on the outer sleeve in case of relative radial displacement, greater than a functional limit, of the inner armature and the outer sleeve.
• the rigid reliefs of the intermediate reinforcement comprise substantially radial internal reliefs, pointing towards the internal reinforcement.
• the rigid reliefs of the intermediate reinforcement also comprise substantially radial external projections, pointing towards the outer sleeve.
• Each of the rigid reliefs of the intermediate frame is for example disposed substantially symmetrically on either side of a transverse median plane, located midway between the first and second axial ends of the joint.
• the rigid reliefs of the intermediate frame are preferably regularly arranged around the longitudinal axis of the joint.
• the rigid reliefs of the intermediate frame may for example be divided into two groups whose respective reliefs are diametrically opposed to one another with respect to the longitudinal axis of the joint.
• the rigid inner and outer reliefs of the intermediate frame form pairs of radial reliefs occupying the same angular position about the longitudinal axis of the joint.
• the rigid reliefs of the intermediate armature may advantageously extend, along the longitudinal axis, over a length of less than half the distance between the first and second axial ends of
• FIG. 1 is an axial sectional view of a hinge according to a first possible embodiment of the invention
• FIG. 2 is a cross-sectional view of the articulation illustrated in FIG. 1, this section being taken along the plane indicated by the arrows II-II of FIG. 1
• FIG. 3 is a view in axial section of the articulation illustrated in FIG. 1, this section being carried out according to the plane indicated by the arrows III-III of FIG. 2;
• FIG. 4 is an axial sectional view of a hinge according to a second possible embodiment of the invention.
• FIG. 5 is a cross-sectional view of the articulation illustrated in FIG. 4, this section being taken along the plane indicated by the arrows VV of FIG. 4.
• the invention relates to an elastic articulation having axial ends B and H spaced apart from each other along a longitudinal axis Y and by convention respectively designated as lower and upper.
• this articulation comprises at least, at increasing radial distance from this axis Y, an internal reinforcement 1, an intermediate reinforcement 2, and an outer sleeve 4.
• joint concerned may include one or more other parts radially more internal than the inner armature, or radially more external than the outer sleeve.
• This articulation also comprises damping means at least formed of an elastomer lining, a part 5A of which is interposed between the inner frame 1 and the intermediate frame 2, and of which another part 5B is interposed between this intermediate reinforcement 2 and the outer sleeve 4.
• damping means may be of a nature not only elastic, but hydro-elastic, and comprise at least two chambers of hydraulic fluid communicating with each other by the intermediate of one or more channels.
• damping means are designed to oppose a static and / or dynamic resistant force to any relative displacement, perpendicular to the longitudinal axis Y, of the inner armature 1 with respect to the outer sleeve 4.
• the intermediate frame 2 has a generally cylindrical shape, supplemented by a plurality of rigid reliefs such as 3A and 3B.
• the rigid reliefs of the intermediate reinforcement 2 which are shaped and arranged to fulfill this function, comprise for example (FIGS. 2 and 5) internal reliefs 3A, which are substantially radial and which point towards the internal reinforcement 1, and external reliefs 3B, which are themselves substantially radial but which point towards the outer sleeve 4.
• each of the rigid reliefs 3A and 3B is disposed substantially symmetrically on either side of the median transverse plane P of the joint, that is to say the plane which crosses transversely the longitudinal axis Y to mid-distance between the axial ends B and H of this joint.
• the internal reliefs 3A form a first group of reliefs regularly arranged around the longitudinal axis Y of the articulation, this group comprising for example two reliefs diametrically opposite one another with respect to this axis Y.
• the external reliefs 3B form a second group of reliefs regularly arranged around the longitudinal axis Y of the joint, this group comprising for example two reliefs diametrically opposite one another with respect to this axis Y.
• each internal relief 3A advantageously forms, with a corresponding external relief 3B, a pair of radial reliefs occupying the same angular position around the longitudinal axis Y of
• the relative movements of the inner armature 1 and the outer sleeve 4 may include a relative pivot about the X axis of FIG. 2, this axis being perpendicular to the longitudinal axis Y and belonging to the median plane P of the articulation. .
• the rigid reliefs 3A and 3B extend, along the longitudinal axis Y, on a length equal to or greater than half the distance between the axial ends B and H of the joint ( Figure 1), this distance being taken on the shortest of the elements that constitute the inner armature 1 and the outer sleeve 4.
• the rigid reliefs 3A and 3B extend along the longitudinal axis. Y, over a length equal to or less than half the distance between the axial ends B and H of the hinge (not shown).
• the reliefs 3A and 3B may be formed in one piece with the intermediate reinforcement 2, for example by molding a polymer material, an alloy, or a metal such as aluminum. This single piece can then be introduced as an insert into a mold inside which the elastomer packing 5A, 5B is then overmolded.
• Figures 4 and 5 illustrate a possible embodiment of a hydro-elastic joint of the type known from the international patent application WO 2207/118994, but also according to the invention.
• the hydro-elastic joint illustrated in Figures 4 and 5 also comprises a cage 6, for example formed integrally with the outer sleeve 4, and a distributor 7 threaded into a supply of axial molding of the elastomeric seal which constitutes the means of 5A and 5B damping.
• the internal face of the distributor 7 is locally spaced from the reliefs 3B and the lining 5B so as to define hydraulic chambers, such as 9A and 9B, which communicate with each other through the channels 8A and
• the dispenser 7 is for example made of rigid plastic, so as to retransmitting the outer sleeve 4 any bearing force that it is likely to receive the inner armature 1 through the rigid reliefs 3A and 3B.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Health & Medical Sciences (AREA)
• Child & Adolescent Psychology (AREA)
• Pivots And Pivotal Connections (AREA)
• Combined Devices Of Dampers And Springs (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=38137415

Family Applications (1)

Country Status (3)

Families Citing this family (3)

Citations (4)

Family Cites Families (7)

• 2006
  • 2006-12-01 FR FR0610542A patent/FR2909428A1/fr active Pending
• 2007
  • 2007-11-29 EP EP07870361A patent/EP2097656A2/de not_active Withdrawn
  • 2007-11-29 WO PCT/FR2007/001966 patent/WO2008071885A2/fr active Application Filing

Patent Citations (4)

Non-Patent Citations (1)

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