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
  • 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
  • F16F1/393—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 with spherical or conical sleeves
• • 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

Definitions

• Frequency decoupling device and hydroelastic articulation comprising a thin liquid chamber
• the invention relates to a device for frequency decoupling of a first piece with respect to a second piece, and a hydro-elastic joint comprising such a frequency decoupling device.
• the invention is more particularly applicable in the field of motor vehicles, particularly in connection with the ground connection of such a vehicle.
• the hydro-elastic joint can form a triangle ball of a front train of a motor vehicle whose main function is the maintenance of the wheel plane.
• the ground connection must be carried out by means of frequency decoupling devices which are arranged to filter the rolling noise on the ground, said devices being interposed between the suspension of the vehicle and its chassis.
• the aim of the invention is to solve the problems of the prior art by proposing a frequency decoupling device in particular in a frequency range between 180 Hz and 800 Hz, as well as a hydro-elastic articulation which makes it possible to provide guidance, deflection and filtering in such a frequency range.
• the invention proposes a device for frequency decoupling of a first part with respect to a second part, said device comprising a rigid outer reinforcement which is intended to be secured to the first part and, disposed inside said outer frame, a rigid inner frame which is intended to be secured to the second piece, an elastically deformable element being interposed between said frames so as to form between said frames at least one annular chamber containing a liquid, said characterized in that, the chamber being of small thickness, the elastically deformable element comprises an upper ring and a lower ring which axially delimit the chamber, respectively forming a seal for said chamber.
• said chamber has an inner perimeter "Pint", an average height "H” on said perimeter and an average thickness "E" on said perimeter, the average thickness E fulfills the following condition:
• the annular chamber has a form of revolution or a cylindrical shape or a cylindrical form of revolution.
• the average thickness E of the chamber is less than 4 mm, in particular between 0.5 mm and 2 mm.
• the thickness of the elastically deformable element is equal to the thickness E of the chamber.
• the chamber is provided radially facing respectively an axial wall of each of the reinforcements.
• the elastically deformable element further comprises an intermediate ring which, with respectively the upper and lower rings, delimits two spaces in the liquid chamber, said intermediate ring being discontinuous so as to form liquid passages between the two spaces.
• the upper crown and / or the lower crown has at least one wave which extends inside the chamber.
• the upper ring comprises two waves which are symmetrical with respect to a longitudinal plane of the chamber, two waves being provided on the lower ring being respectively disposed opposite a wave of the upper ring.
• the chamber has a conical geometry of revolution.
• the elastically deformable element is overmolded on the inner frame.
• the upper and / or lower crowns are attached to the inner frame.
• the volume of the chamber is at least partially formed by a deformation of the outer armature.
• the invention proposes a hydroelastic joint comprising such a frequency decoupling device said hinge comprising a rigid member which is disposed inside the inner frame, said member being associated with said frame via an elastically deformable body.
• FIG. 1 is a longitudinal sectional view of a frequency decoupling device according to one embodiment of the invention
• FIG. 2 is a view in longitudinal section of a hydro-elastic articulation according to a first embodiment of the invention
• FIGS. 4 are views of a hydro-elastic hinge according to a first variant of the embodiment of FIG. 3, respectively in longitudinal section (FIG. 4a) and in perspective without the external reinforcement (FIG. 4b).
• FIG. 5 is a perspective view of a hydro-elastic articulation according to a second variant of the embodiment of FIGS. 3, on which the outer armature is not shown;
• FIG. 6 is a longitudinal sectional view of a hydro-elastic joint according to a third embodiment of the invention, respectively before the elastically deformable element (FIG. 6a) is disposed, after the elastically deformable element has been disposed ( figure
• FIG. 7 is a view in longitudinal section of a hydro-elastic articulation according to a fourth embodiment of the invention
• FIGS. 8 and 9 are views in longitudinal section of a hydro-elastic joint incorporating a radial abutment according to a fifth and a sixth embodiment of the invention, respectively;
• FIG. 10 is a longitudinal sectional view of a hydroelastic joint according to a seventh embodiment of the invention.
• FIG. 11 is a view in longitudinal section of a hydro-elastic articulation according to an eighth embodiment of the invention.
• FIG. 12 is a view in longitudinal section of a hydro-elastic articulation according to a ninth embodiment of the invention
• FIG. 13 is a view in longitudinal section of a hydro-elastic articulation according to a tenth embodiment of the invention
• FIG. 14 is an axial sectional view of a frequency decoupling device according to an alternative embodiment of the invention.
• FIG. 15 is a longitudinal sectional view of a hydro-elastic joint according to an eleventh embodiment of the invention whose outer armature is not yet assembled;
• Figure 16 is a longitudinal sectional view of the fully assembled joint of Figure 15;
• FIG. 17 is a view in longitudinal section of a hydro-elastic articulation according to a twelfth embodiment of the invention.
• FIG. 18 is a longitudinal sectional view of a variant of the joint of Figure 17;
• FIG. 19 is a half-schematic longitudinal section of a hydro-elastic articulation according to a thirteenth embodiment of the invention.
• FIG. 20 is a longitudinal sectional view and in perspective of a hydroelastic joint according to a fourteenth embodiment of the invention.
• FIG. 21 is a longitudinal sectional view of a hydroelastic joint according to a fifteenth embodiment of the invention.
• a frequency decoupling device of a first part with respect to a second part is described below.
• the first part is a member of the suspension of a motor vehicle and the second part is an organ of the suspended chassis of said vehicle.
• the frequency decoupling device can filter the rolling noise of the vehicle on the ground so as to isolate the passenger compartment of said vehicle by limiting the transmission of said noise.
• the decoupling device comprises a rigid outer armature 1 which is intended to be secured to the first part and disposed inside said outer armature, a rigid inner frame 2 which is intended to be secured to the second piece.
• the armatures 1, 2 are parts, in particular made of metallic material or possibly reinforced plastic, which here have a cylindrical geometry of revolution, said armatures being arranged coaxially around one another with a game "E" between the two.
• the frequency decoupling device further comprises an elastically deformable element which is interposed between the armatures 1, 2, said element being made of an elastic material selected according to the intended application, and may be formed in particular of an elastomeric material.
• the elastically deformable element comprises an upper ring 3 and a lower ring 4 which are axially spaced so as to define a cylindrical chamber 5 of revolution between the frames 1, 2.
• the crowns 3, 4 form seal.
• the proposed arrangement allows the provision of a liquid incompressible tightly in said chamber.
• the rings 3, 4 are arranged, in particular by overmolding on the inner frame 2, respectively in the vicinity of an edge of the frames 1, 2.
• the crowns are overmoulded (also called “adhered") on the inner frame 2 they are tight on the outer frame.
• the chamber 5 is formed with respect to substantially the entire periphery of the inner armature 2.
• the liquid chamber 5 is provided radially facing respectively the axial wall of each of the armatures 1, 2.
• the frequency decoupling device is preferably arranged to allow noise filtering in a frequency range between 180 Hz and 800 Hz while ensuring sufficient guidance between the parts.
• the thickness E of the chamber 5 is defined according to the following geometrical condition:
• the thickness of the chamber 5 is sufficiently low to obtain a dynamic setting between 180 Hz and 800 Hz, in particular around 200 Hz, while benefiting from a very important static stiffness for guiding.
• the thickness E of the chamber 5 of liquid may be less than 4 mm, in particular between 0.5 mm and 2 mm and more precisely of the order of 1 millimeter for an average automotive application targeting a very high level of comfort.
• the thickness of the elastically deformable element, namely that of the crowns 3, 4 is also small, in particular equal to the thickness e p of the liquid chamber 5.
• the elastically deformable element is devoid of a holding cage such as that inserted in the deformable part of a conventional hydro-elastic articulation.
• the small relative thickness of the elastically deformable element induces a limitation of its deformation and thus a proper maintenance of it which is sufficient.
• the geometric data are:
• Dynamic stiffness 22 KN / mm which confers a very high swelling stiffness
• the dynamic stiffness is positive and less than 0.7 times the static stiffness and, between 330 Hz and more than 800 Hz, the real part of the stiffness is negative.
• such a device with another piece to allow the realization of a hydro-elastic joint of large amplitude.
• a joint can form a triangle ball of a front train of a motor vehicle.
• FIG. 2 shows a first embodiment of a hydroelastic articulation comprising a frequency decoupling device, said device being of similar design to that described with reference to FIG. 1.
• the height of the crowns 3 4 is larger and the height of the liquid chamber 5 is correspondingly reduced.
• the inner armature 2 has an extra thickness facing the chamber 5, so that the thickness of said chamber is reduced accordingly.
• the joint comprises a rigid member 7 which is disposed inside the inner armature 2, said member being associated with said armature by means of an elastically deformable body 6.
• the frequency decoupling device can be used with a rigid member such as an outer ring of a bearing, which is then associated with the inner armature 2 without the interposition of an elastically deformable body.
• the rigid member is formed of a ball 7 axis identical to that of the armatures 1, 2, said ball comprising a bore 8 allowing its association with the chassis of the motor vehicle.
• the elastically deformable body 6 is disposed at least around the spherical portion of the ball 7, in particular by overmoulding on said portion.
• a rigid fitting structure of the elastically deformable body 6 in the inner armature 2 is provided at the interface between said armature and said body. More specifically, the structure comprises a tubular sleeve 9 whose edges are curved radially inward to axially grip the elastically deformable body 6.
• FIGS. 3 a second embodiment of a hydro-elastic articulation according to the invention in which the rigid member 7 is similar to that of FIG. 2 is described.
• the elastically deformable body 6 is directly associated with the inner frame 2, in particular by overmolding.
• the inner armature 2 is constituted by the sleeve 9 according to Figure 2, on the outer surface of which the two deformable rings 3, 4 are disposed. More precisely, each ring 3, 4 is disposed respectively at the level of the radial fold so as to form the chamber 5 over substantially the entire height of the axial wall of the sleeve 9.
• the outer frame 1 can be fitted on the inner frame 2 by immersing the joint in a liquid bath to fill the chamber 5.
• this fitting is made possible even without the provision of a holding cage in the crowns 3, 4.
• the edges of the outer armature 1 are folded over the crowns 3, 4 so as to improve the sealing of the chamber 5 and the cohesion of the frames 1, 2 between them.
• FIG. 4 represents a first variant of the embodiment of FIG. 3 in which the elastically deformable element furthermore comprises an intermediate ring 10 which, with respectively the upper 3 and lower 4 crowns, defines two spaces in the chamber 5 of liquid, respectively upper and lower.
• FIG. 5 represents a second variant of the embodiment of FIG. 3 in which the upper ring 3 and the lower ring 4 have waves 11 which extend inside the chamber 5 of liquid. According to another embodiment, it could be provided that only one of the rings 3, 4 has at least one wave 11.
• the articulation according to FIG. 5 makes it possible to create two frequency wedges respectively along the X and Y axes.
• the upper crown 3 comprises two waves 11 which are here symmetrical with respect to a longitudinal plane of the chamber 5, two waves 11 being provided on the lower ring 4 being respectively disposed opposite a wave 11 of the upper ring 3.
• the waves 11 shown are of the same geometry, it is conceivable to modify this geometry and the respective arrangement of waves 11 according to the constraints of the intended application.
• the two frequency wedges respectively along the X and Y axes can be obtained with a liquid chamber 5 having an oval section.
• FIGS. 6 show the assembly of a hydro-elastic articulation according to a third embodiment of the invention in which the upper and lower crowns 3 are attached to the inner frame 2.
• the rigid member is formed of a tube 12 around which the elastically deformable body 6 is molded with the inner armature 2, said armature comprising outer peripheral grooves 13 for respectively receiving a crown 3, 4.
• the outer frame 1 is fitted on the inner frame 2 by immersing the joint in a liquid bath to fill the chamber 5. Finally, the edges of the outer frame 1 are folded over the crowns 3, 4.
• the crowns of the embodiment of FIGS. 6a to 6c are overmolded on neither of the two frames, they actually work exactly like independent joints. We see also that the crowns have in this example the form of O-rings.
• FIG. 7 shows another embodiment in which the rings are made in two distinct parts, a horizontal part 31 (respectively 41) and a vertical part 32 (respectively 42). It is understood that the axial stiffness of the decoupling device is then determined predominantly by the characteristics of the horizontal portions and that the radial stiffness of the decoupling device is then determined predominantly by the characteristics of the vertical portions.
• the elastomeric materials of both parts may further be the same or different.
• FIG. 8 there is shown a variant of the articulation of FIG. 3b in which a radial annular abutment 14 limits the relative displacements of the reinforcements 1 and 2 (and therefore the stresses) experienced by the deformable element.
• the abutment 14 can be a simple ring of relatively rigid plastic material such as polyamide.
• FIG. 9 there is shown the principle of a radial abutment 15 obtained by a circumferential fold of the internal armature 2.
• FIG. 10 shows another embodiment of the joint in which the inner armature is formed by the combination of two half-armatures 21 and 22, for example of relatively rigid plastics material such as polyamide, welded , glued or clipped (the outer armature 1 is not shown here).
• FIG 11 there is shown an embodiment in which the liquid chamber 5 is formed in an annular deformation 16 of the outer frame 1.
• the overmolding of the deformable element 3 can be simplified.
• Figure 12 there is shown an outer frame formed of two parts 17 and 18 partially fitted one into the other. This can make it possible to simplify the assembly of the joint and to obtain a peripheral collar 19.
• FIG. 13 shows a joint in which the relative displacements of the reinforcements 1 and 2 are authorized by an elastic deformation of flexible zones 101 and 102 of the outer reinforcement 1.
• the rings 33 and 43 retain their sealing function of the liquid chamber but are not necessarily predominant for the elastic characteristics of the decoupling device.
• the chamber 5 (preferably cylindrical) has a non-circular section.
• Figures 15 and 16 there is shown a joint in which the inner armature 2 is shaped so that the rings 3 and 4 have a thickness greater than the thickness E of the chamber 5 over a significant part of their height. In this way, the tightness of the thin chamber is further favored by the creation of a seal of greater thickness.
• Figure 16 shows the fully assembled hinge after the immersion fit and the conformation of the edges of the outer frame 1.
• FIG. 17 there is shown a joint in which the inner frame 2 is made of rigid plastic material. This allows in particular to give it a relatively precise shape as here a spherical inner shape which is concentric with the spherical shape of the central portion of the rigid member 7 and an outer shape similar to the inner frame of the embodiment of FIGS. and 16.
• the elastically deformable body 6 is molded (and thus adhered) between the rigid member and the inner frame.
• the crowns 3, 4 and the outer armature 1 are in this example identical to those of FIG.
• the inner armature 2 can be molded in one piece but it can preferably be obtained by molding two half-armatures which are then welded for example by ultrasound or as shown in FIG. 18 which is assembled by clipping before the molding of the elastically deformable body 6.
• FIG. 19 shows the schematic half section of a joint in which the outer armature 1 consists of two parts 101 and 102 made integral by an outer ring 103.
• the rings 31, 32, 41, 42 have here the form described above with reference to Figure 7. It is understood that the crowns are preferably overmoulded (and therefore adhered) on the parts 101 and 102 corresponding rather than the inner frame 2.
• the parts 101 and 102 are then assembled axially and thus come to tighten the crowns around the inner frame 2.
• the ferrule 103 is then immersed in order to close the chamber 5 filled with liquid.
• a first embodiment of the necessary seal between the two parts 101 and 102 obtained through a peripheral seal 104 from the same overmoulding operation as the rings 31 and 32.
• FIG. 20 represents a hinge according to an embodiment similar to the embodiment of FIG. 19. This embodiment differs however in that the peripheral seal 104 integral with the upper part 101 cooperates with a peripheral seal 104 '. secured to the lower part 102.
• the parts 101 and 102 are here perfectly identical. This further reduces the manufacturing cost of such a joint.
• FIG. 21 there is shown a joint in which the rigid member 71 is a ball slidably mounted in the inner frame 2 for example made of rigid plastic such as polyamide or metal.
• the crowns 3 and 4 are overmoulded on the inner frame which is shaped so that the crowns are thicker than the chamber 5 according to a principle described above with reference to FIGS. 2 and 15.
• the inner armature 2 may comprise a channel 51 for filling the fluid chamber 5 after the fitting of the outer armature 1.
• the fitting can naturally be carried out immersed in a bath of liquid.
• the outer armature 1 is here configured to receive a bellows protection of the ball and be secured by screwing on a vehicle part as a hub-holder while the tail of the ball can be attached to another part of the vehicle as a triangle or a suspension arm.
• a horizontal ring 41 provides the desired axial stiffness.
• the invention has been described in the case of joints intended to be mounted within a suspension system, for example at the end of an arm or a suspension triangle.
• the joint can also be formed directly in such an arm or triangle, which can then replace the outer armature.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Combined Devices Of Dampers And Springs (AREA)
• Vehicle Body Suspensions (AREA)
• Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
• Vibration Prevention Devices (AREA)
• Pivots And Pivotal Connections (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=38278698

Family Applications (1)

Country Status (5)

Cited By (1)

Families Citing this family (7)

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• 2006
  • 2006-12-20 FR FR0611230A patent/FR2910577A1/fr active Pending
• 2007
  • 2007-12-20 WO PCT/EP2007/011268 patent/WO2008074507A1/fr not_active Ceased
  • 2007-12-20 JP JP2009541890A patent/JP2010513810A/ja active Pending
  • 2007-12-20 EP EP07856991A patent/EP2102020A1/de not_active Withdrawn
  • 2007-12-20 US US12/520,847 patent/US20100127441A1/en not_active Abandoned

Non-Patent Citations (1)

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