WO2012028177A1 - Palier de butée de suspension doté d'un élément filtrant - Google Patents

Palier de butée de suspension doté d'un élément filtrant Download PDF

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Publication number
WO2012028177A1
WO2012028177A1 PCT/EP2010/062747 EP2010062747W WO2012028177A1 WO 2012028177 A1 WO2012028177 A1 WO 2012028177A1 EP 2010062747 W EP2010062747 W EP 2010062747W WO 2012028177 A1 WO2012028177 A1 WO 2012028177A1
Authority
WO
WIPO (PCT)
Prior art keywords
suspension
thrust device
lower cover
axial
bearing seat
Prior art date
Application number
PCT/EP2010/062747
Other languages
English (en)
Inventor
Samuel Viault
Richard Corbett
Désiré Vidot
Christophe Houdayer
Jérôme DUBUS
Original Assignee
Aktiebolaget Skf
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Aktiebolaget Skf filed Critical Aktiebolaget Skf
Priority to PCT/EP2010/062747 priority Critical patent/WO2012028177A1/fr
Publication of WO2012028177A1 publication Critical patent/WO2012028177A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G15/00—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type
    • B60G15/02—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring
    • B60G15/06—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper
    • B60G15/067—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper characterised by the mounting on the vehicle body or chassis of the spring and damper unit
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/02—Sliding-contact bearings
    • F16C23/04—Sliding-contact bearings self-adjusting
    • F16C23/043—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings
    • F16C23/048—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings for axial load mainly
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/22—Sliding surface consisting mainly of rubber or synthetic rubber
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/418—Bearings, e.g. ball or roller bearings
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
    • F16C2208/20—Thermoplastic resins
    • F16C2208/30—Fluoropolymers
    • F16C2208/32—Polytetrafluorethylene [PTFE]
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/60—Thickness, e.g. thickness of coatings
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/05—Vehicle suspensions, e.g. bearings, pivots or connecting rods used therein
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/16—Sliding surface consisting mainly of graphite
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/20—Sliding surface consisting mainly of plastics

Definitions

  • the present invention relates to the field of suspension bump thrust devices used, in particular, on motor vehicles in the suspension struts of steered wheels .
  • a suspension thrust bearing device is provided with a rolling bearing comprising an upper ring and a lower ring between which are positioned a row of rolling elements, for examp le balls or rollers .
  • the upper and lower rings are usually mounted in contact with upper and lower covers supporting or bearing parts, such as cups or covers.
  • the upper and lower covers form a housing for the rings o f the ro lling bearing and provide an interface between said rings and the neighboring elements.
  • Such a suspension bump thrust device is mounted in the upper portion o f a suspension strut, between the chassis o f the vehicle and a suspension spring.
  • the suspension spring is fitted around a damping piston rod, the end of which is linked to the chassis o f the vehicle through an elastic block filtering the vibrations.
  • the suspension spring axially bears, directly or indirectly, on the lower cover.
  • the upper cover is fixed relative to the chassis of the vehicle.
  • Such a suspension bump thrust device makes it possible to transmit axial forces between the suspension spring and the chassis o f the vehicle while allowing a relative angular movement between the lower cover, that may rotate, and the upper cover.
  • This relative angular movement can be the result o f a steer angle o f the steered wheels of the vehicle and/or of the compression o f the suspension spring.
  • the suspension bump thrust device needs a lubricant kept inside the rolling bearing. Moreover, solid and liquid pollutants must be prevented from entering the rolling bearing. Seals may thus be placed at the junction between the two races of the rolling bearing. Furthermore, fatigue failure may occur in the balls due to very small vibrations, making it difficult to maintain smooth steering operation over extended periods o f time.
  • European patent application EP0656483 which aims at so lving these problems, disclo ses a suspension bump thrust device comprising flat intermediate synthetic rings adapted to support axial or radial forces exerted by the suspension spring.
  • One aim of the present invention is therefore to overcome the aforementioned drawbacks .
  • the invention provides a suspension bump thrust device for a motor vehicle comprising an upper elastic bearing seat designed to be attached to the chassis of the motor vehicle and a lower supporting cover having a bearing surface adapted to come in contact with a suspension spring designed to exert axial and radial forces to the suspension device.
  • the lower supporting cover comprises an upper surface, opposite to the bearing surface and forming a sliding race adapted to cooperate with a complementary sliding race of the upper bearing seat, said sliding races mating and being slidable one with respect to the other, and able to take up axial and radial forces exerted by the suspension spring.
  • the upper seat and the lower cover are thus directly in contact with each other without any intermediate separate element, therefore reducing the number of elements forming the suspension thrust device.
  • At least one sliding race comprises a self- lubricating liner, in order to reduce the friction coefficient and the wear between the upper and the lower cover.
  • the sliding race o f the lower supporting cover is o f generally toroidal shape having an axis substantially coaxial to the vertical axis o f the suspension device.
  • the sliding races are o f generally frustoconical shape.
  • the perpendicular axis to the bearing surface o f the lower cover, adapted to come in contact with the suspension spring, and the axis o f the upper bearing seat are tilted compared to the vertical axis of the suspension device.
  • the lower cover having a sliding race of generally frustoconical shape, the axis of this sliding race being positively o ffset compared to the axis o f the suspension thrust device, which aims at reducing radial loads exerted by the suspension spring.
  • the sliding race o f the lower supporting cover is o f generally spherical shape, said lower supporting cover forming a knuckle which axis is angularly moveable compared to the vertical axis of the upper bearing seat.
  • the lower cover is angularly moveable compared to the upper seat in order to compensate the angular misalignment between the vertical axis of the upper seat and the axis of the suspension spring.
  • the lower cover is less radially stressed by the suspension spring.
  • the upper bearing seat comprises annular inner and outer skirts surrounding the lower cover and defining with the lower cover, a narrow passage forming a labyrinth seal.
  • At least one annular skirt of the upper bearing seat comprises a hook extending towards the lower cover, said hook being adapted to cooperate with a corresponding hook of the lower cover.
  • the lower cover may comprise at least one sealing means having a sealing lip in friction contact with the upper bearing seat.
  • the lower cover comprises at least two sealing means; said sealing means being overmoulded or glued or force-fitted onto the lower cover.
  • a layer of lubricant material is formed between the sliding races .
  • a suspension strut comprising a suspension bump thrust device according to any one o f the preceding claims .
  • Figure 1 is a view in axial section of a suspension bump thrust device according to a first embodiment of the invention ;
  • Figure 2 is an axial section, along line II - II of Figure 1 ;
  • Figure 3 is a view in axial section of a suspension bump thrust device according to a second embodiment of the invention ;
  • Figure 4 is a view in axial section of a suspension bump thrust device according to a third embo diment of the invention ;
  • Figure 5 a is a view in axial section o f a suspension bump thrust device according to a fourth embodiment of the invention ;
  • Figure 5b is a view according to the suspension device o f Figure 5 a showing the lower cover angularly moved compared to the upper cover ;
  • Figure 6 is a view in axial section according to a fifth embodiment of the invention.
  • a suspension bump thrust device designed by general reference number 10, is designed to be installed between a top retainer seat (not shown) suitable for resting, directly or indirectly, in an element o f a chassis of a motor vehicle (not illustrated), and a suspension helical spring 1 1 , of which only the end winding is illustrated.
  • the suspension thrust device 10 is disposed around a damper rod (not shown) extending along a substantially vertical axis Y, the suspension spring 1 1 being mounted around said damping rod.
  • the suspension thrust device 10 mainly comprises an upper elastic bearing seat 12 and a lower supporting cover 1 3 having beads 13 a with substantially rectangular cross section near its bore 13b.
  • the upper bearing seat 12 and the lower supporting cover 1 3 are designed to come in direct contact with each other and are conformed to transmit axial and radial forces exerted by the suspension spring 1 1 .
  • the upper bearing seat 12, of axis Y has the general shape o f an annular flange. As illustrated in Figures 1 and 2, the upper bearing seat 12 comprises an annular so lid portion 14 designed to be in contact with the top retainer seat (not shown) through an upper surface 14a.
  • the upper bearing seat 12 further comprises an annular inner axial skirt 15 less thick than the annular portion 14, and an annular outer axial skirt 16 also less thick than the annular portion 14, said outer axial skirt 16 radially surrounding the inner skirt 15.
  • the skirts 1 5 , 16 extend axially downwards from the annular so lid portion 14.
  • the outer axial skirt 16 has an annular flange 16a extending radially outwards and axially downwards and defining, with an annular flange 17a o f the lower cover 13 , a narrow passage 1 8 , so as to form a labyrinth seal.
  • the annular so lid portion 14 comprises a lower surface 14b having a sliding toroidal concave race 1 9 in direct contact with the lower supporting cover 13.
  • the bottom end of the inner axial skirt 15 is provided with several hooks 1 5 a, which may be continuous or discontinuous in the circumferential direction. Said hooks 15 a extend radially towards the lower cover 13 , so as to cooperate with corresponding hooks 20a extending radially inwards and being part of the lower cover 13.
  • the hooks 15 a o f the upper seat 12 have a radial top surface able to interfere with the hooks 20a of the lower cover 13 in order to prevent a separation o f the upper seat 12 from said lower cover 13 before the suspension device 10 is installed in the top part of the suspension strut.
  • the external diameter of the hooks 15 a of the upper seat 12 is greater than the internal diameter of the hooks 20a o f the lower cover 13 so that a diametral interference can exist between the upper seat 12 and the lower cover 13 in order to prevent an axial displacement o f said lower cover 13 downwards.
  • the hooks 15 a o f the upper seat 12 are positioned axially below the hooks 20a o f the lower cover 1 3.
  • An annular radial gap 20b exists between the hooks 15 a o f the upper seat 12 and an inner axial surface 20 o f the lower cover 13.
  • a hook 15 a continuous in the circumferential direction may be provided on the annular inner skirt 15 of the upper seat 12.
  • an axial gap 20c exists axially between the hooks 15 a, 20a so as to form a sealing means such as a labyrinth seal, in order to prevent the intrusion of foreign matter radially between the inner skirt 15 of the upper seat 12 and the bore 13b o f the lower cover 13.
  • the lower supporting cover 13 provides, at its bottom end, an annular axial portion 21 extending axially downwards .
  • the bottom end of said annular axial portion 21 is pro longed towards the inside and downwards through a rounded surface 2 1 a by an axial skirt 22 having radial inner ribs 22a extending inwards for retaining the damper, and radial outer ribs 22b extending outwards and defining a groove 22c for retaining, for example, a boot kit (not shown) for the damping rod.
  • Said inner and outer ribs 22a, 22b may be continuous or discontinuous in the circumferential direction.
  • the bottom end o f the annular axial portion 21 extends radially inwards with a radial portion 23 , slightly tilted downwards and having a bore 13b for the passage of the damping rod.
  • the upper end of the annular axial portion 2 1 extends radially outwards with a radial part 24 having a bearing surface 24a for the suspension spring 1 1 .
  • Said bearing surface 24a being substantially tilted compared to the perpendicular axis to Y and linked to an outer cylindrical surface 21 b o f the annular axial portion 21 via a rounded surface 21 c.
  • the outer cylindrical surface 21 b makes it possible to centre the suspension spring 1 1 .
  • the radial part 24 has an axial dimension varying according to the circumference of the lower cover 13.
  • the radial part 24 comprises a cylindrical axial external surface 24b, the upper end of which is prolonged towards the inside and upwards by a rounded surface 24c extending inwards to an annular radial surface 24d.
  • the annular radial surface 24d is then prolonged by a sliding race 25 having a substantially toroidal convex shape matching with the complementary toroidal concave race 19 o f the upper bearing seat 12.
  • the sliding race 25 extends inwards by a radial portion 20d providing the hooks 20a directed radially towards the inside and spaced apart from the hooks 15 a o f the upper seat 12, which may be continuous or discontinuous in the circumferential direction.
  • the sliding race 25 o f the lower cover 13 defining a toroidal convex shape, has an axis Yi substantially identical to the vertical axis Y o f the suspension thrust device 10.
  • the hooks 20a are prolonged by the inner axial surface 20 and a frustoconical portion 20e linking the radial part 24 to the annular axial portion 21 .
  • the radial part 24 has an axial dimension varying according to the circumference of the lower cover, and the bearing surface 24a as illustrated on Figure 2, is substantially tilted according to the circumference of the lower cover, so as to bear the suspension helical spring 1 1 .
  • Such a tilted bearing surface 24a allows a reduction o f radial lo ads exerted by the suspension spring 1 1 .
  • the cylindrical axial external surface 24b comprises a radial rib 24e extending radially outwards and having an external diameter greater than the external diameter of the annular outer skirt 16 of the upper seat 12.
  • the sliding races 19, 25 may comprise a self-lubricating liner, for example overmoulded on one of the sliding races 19, 25 , so as to reduce the friction coefficient between the upper seat 12 and the lower cover 13.
  • the self-lubricated liner may consist of a thin sheet of fabrics impregnated with oil, with a thickness greater than 0.05 mm but smaller than 1 mm, preferably around 0.2 mm.
  • the liner may also comprise a material reducing the friction coefficient, such as, for example, polytetrafluoroethylene.
  • a layer o f lubricant material such as grease may be formed between the sliding races 19, 25.
  • a sealing means 26 is provided on the lower supporting cover 13 , in order to limit the ingress of foreign matter towards the sliding races 19, 25.
  • the sealing means 26 has an annular shape and is resting axially on a lower radial surface 27 o f the lower cover 13 delimited between the annular radial surface 24d and the cylindrical axial external surface 24b.
  • the sealing means 26 comprises an annular axial portion 26a and a sealing lip 26b extending from said axial portion 26a towards the annular flange 16a of the upper seat 12. The axial contact between said annular flange 16a and the sealing lip 26b prevents the foreign particles from intruding towards the sliding races 19, 25.
  • the suspension thrust device 10 comprises a second sealing means 28 having an annular shape and resting axially on the radial inner surface 20d o f the lower cover 13 and radially against the sliding race 25 of the lower cover 13.
  • the second sealing means 28 comprises a radial portion 28a and a sealing lip 28b extending from the radial portion 28 a towards the lower surface 14b o f the upper seat 12.
  • Such sealing means 26, 28 can be overmoulded or glued or force-fitted onto the lower supporting cover 13.
  • the suspension bump thrust device 30 differs from the suspension thrust device 1 0 described according to Figures 1 and 2, by the shape o f the lower cover, the upper bearing seat and the sliding races.
  • the suspension bump thrust device 30 mainly comprises an upper elastic bearing seat 3 1 and a lower supporting cover 32 having beads 32a with substantially rectangular cross section near its bore 32b.
  • the suspension thrust device 1 0 illustrated on figures 1 and 2 the suspension thrust device 30 is designed to be installed between a top retainer seat (not shown) suitable for resting, directly or indirectly, in an element of a chassis o f the motor vehicle (not illustrated), and a suspension helical spring 33 .
  • the suspension thrust device 30 is disposed around a damper rod (not shown) extending along a substantially vertical axis Y, the suspension spring 33 being mounted around said damping rod.
  • the upper bearing seat 3 1 and the lower supporting cover 32 are designed to come in direct contact with each other and are conformed to transmit axial and radial forces exerted by the suspension spring 33.
  • the upper bearing seat 3 1 has the general shape of a truncated cone having a bore 3 1 a with an axis Yi slightly tilted compared to the axis Y of the suspension thrust device 30.
  • the upper seat 3 1 comprises an annular so lid portion 34 having an upper surface 34a designed to be in contact with the top retainer seat (not shown).
  • the annular solid portion 34 o f the upper bearing seat 3 1 provides an external section o f generally frustoconical shape varying according to the circumference of the upper bearing seat 3 1 .
  • the upper seat 3 1 further comprises an annular outer axial skirt 35 less thick than the annular solid portion 34, radially linked to the upper surface 34a by a rounded portion 34b and extending axially downwards and radially outwards by an annular flange 35 a defining, with an annular flange 36a o f the lower cover 32 , a narrow passage 37a, so as to form a labyrinth seal.
  • a hook 35b extending inwards and which may be continuous or discontinuous in the circumferential direction may be provided on the inner bore of the outer axial skirt 35. Said hook 35b extends radially towards the lower cover 32 so as to cooperate with corresponding hooks 38a o f the lower cover 32 extending radially outwards, in order to form a sealing means such as a labyrinth seal.
  • the annular so lid portion 34 comprises a lower surface 34 c having a sliding race o f generally frustoconical shape in direct contact with a corresponding sliding race 38b o f the lower supporting cover 32.
  • the lower supporting cover 32 comprises a radial part 37 and an annular axial skirt 39 extending axially downwards at the end opposite to the upper seat 3 1 .
  • the annular axial skirt 39 provides at its bottom end, a frustoconical portion 39a extending outwards by radial outer ribs 39b defining a groove 39c for retaining, for example, a boot kit (not shown) for the damping rod.
  • S aid outer ribs 39b may be continuous or discontinuous in the circumferential direction.
  • the bottom end o f the annular axial skirt 39 extends radially inwards with a radial portion 32c, slightly tilted downwards and having a bore 32b for the passage o f the damping rod.
  • the radial part 37 comprises a cylindrical axial surface 37b o f small axial dimension linked radially to a bearing surface 37c for the suspension spring 33.
  • Said bearing surface 37c being substantially tilted compared to the axis Y and linked to an outer cylindrical surface 39d of the axial skirt via a rounded surface 39e.
  • the axis Y 2 perpendicular to the bearing surface 37c of the lower cover 32 is slightly tilted compared to the vertical axis Y of the suspension thrust device 30, so as to reduce radial lo ads exerted by the suspension spring 33.
  • the outer cylindrical surface 39d makes it possible to centre the suspension spring 33.
  • the radial part 37 has an axial dimension varying according to the circumference of the lower cover 32 and may be provided, as illustrated on the figure, by a radial tongue 37d extending outwards so as to surround the outer axial skirt 35 o f the upper seat 3 1 .
  • the radial part 37 provides an axial rib 38 extending towards the upper seat 31.
  • the axial rib 38 comprises a hook 38a extending radially outwards towards the annular flange 35a of the upper seat 31, and has a radial top surface able to interfere with the hooks 35b of the upper seat 31 in order to prevent a separation of the upper seat 31 from said lower cover 32 before the suspension device 30 is installed in the top part of the suspension strut.
  • the external diameter of the hook 38a of the lower cover 32 is greater than the internal diameter of the hook 35b of the upper seat 31 so that a diametral interference can exist between the upper seat 31 and the lower cover 32 to prevent an axial displacement of said lower cover 32 downwards.
  • the hook 35b of the upper seat 31 is positioned axially below the hook 38a of the lower cover 32.
  • An annular radial gap 37e exists between the hooks 35b of the upper seat 31 and an inner axial surface 38c of the lower cover 32.
  • the axial rib 38 of the radial part 37 is prolonged inwards by a sliding race 38b having a substantially frustoconical shape matching with the complementary frustoconical race 34c of the upper bearing seat 31.
  • the upper seat 31 and the lower cover 32 are in direct contact with each other through the frustoconical sliding races 34c, 38b.
  • the sliding races 34c, 38b being of generally frustoconical shape, the suspension thrust device 30 may support axial and radial loads exerted by the suspension spring 33.
  • the axis Y 2 perpendicular to the bearing surface 37c and the axis Yi of the upper bearing seat 31 are positively offset compared to the axis Y of the suspension thrust device 30, which aims at reducing radial forces exerted by the suspension spring 33.
  • the axis Y, Yl, Y 2 can also be substantially parallel to each other.
  • Such a suspension thrust device 30 may comprise sealing means (not shown) as described in relation with figure 3.
  • the sliding races 34c, 38b as illustrated may comprise a self-lubricating liner or a layer of grease may be provided between the sliding races 19, 25, so as to reduce the friction coefficient between the upper seat 3 1 and the lower cover 32.
  • the suspension bump thrust device mainly comprises an upper elastic bearing seat 41 and a lower supporting cover 42 having a bore 42a.
  • the suspension thrust device 40 is designed to be installed between a top retainer seat (not shown) suitable for resting, directly or indirectly, in an element of a chassis o f the motor vehicle, and a suspension spring 43.
  • the suspension thrust device 40 is disposed around a damper rod (not shown) extending along a substantially vertical axis Y, the suspension spring 43 being mounted around said damping rod.
  • the upper bearing seat 41 and the lower supporting cover 42 are designed to come in direct contact with each other and are conformed to transmit axial and radial forces exerted by the suspension spring 43.
  • the upper bearing seat 41 has the general shape of an annular flange, with an axis Y, and comprises an annular so lid portion 44 having an upper surface 44a designed to be in direct contact with the top retainer seat (not shown) and a lower surface 44b having a sliding race 45 o f generally spherical shape in contact with a corresponding sliding race 46 of the lower supporting cover 42.
  • the lower supporting cover 42 comprises a radial part 47 and an annular axial skirt 48 extending axially downwards at the end opposite to the upper seat 41 .
  • the radial part 47 comprises a first cylindrical axial surface 47a extending upwards by a second cylindrical axial surface 47b, o f smaller axial dimension than the axial dimension o f the first cylindrical axial surface 47a, linked radially to a bearing surface 47c for the suspension spring 43 and to the sliding race 46 of generally spherical shape.
  • Said bearing surface 47c being substantially tilted compared to the sliding race 46 and linked to an outer cylindrical surface 48 a o f the axial skirt 48.
  • the outer cylindrical surface 48 a makes it possible to centre the suspension spring 43.
  • the annular axial skirt 48 provides at its bottom end, a frustoconical portion 48b extending inwards .
  • the annular axial skirt 48 may be provided with a radial portion (not shown) extending radially inwards for axially retaining the damping rod.
  • the upper seat 41 and the lower cover 42 are in direct contact with each other through the sliding races 45 , 46, o f generally spherical shape.
  • the lower cover 42 forming a knuckle having an axis Yi , is thus angularly moveable compared to the upper seat 41 in order to compensate for a possible angular misalignment between the vertical axis Y o f the upper seat and the axis Y 2 of the suspension spring 43 , perpendicular to the bearing surface 47c.
  • the lower cover 42 is less radially stressed by the suspension spring 43.
  • the lower cover 42 can move angularly in order to align itself with the axis Y 2 of the suspension spring 43 and thus to reduce radial load, as illustrated on Figure 5b.
  • the device illustrated on Figure 6 is substantially identical to the device illustrated on Figures 5 a and 5b with the fo llowing differences :
  • the suspension thrust device 40 o f Figure 6 is provided with means 49 in order to prevent a separation o f the upper seat 4 1 from said lower cover 42 before the suspension device 40 is installed in the top part of the suspension strut.
  • the upper cover 41 comprises an annular outer skirt 44c o f small thickness and of large diameter radially linked to the upper surface 44a by a rounded portion 44d and extending radially inwards by a hook 49, which may be continuous or discontinuous in the circumferential direction.
  • Said hook 49 extends radially towards the first axial surface 47a of the lower cover 42 and is lo cated axially below the second axial surface 47b, so as to form a labyrinth seal.
  • the axial outer skirt 44c is linked to the sliding race 45 by an annular extrusion 45 a adapted to cooperate with a sealing means 50 having a sealing lip in friction contact with the sliding race 46 o f the lower cover 42.
  • the invention is not limited to the embo diments described and may be the subj ect of many variants . Sealing lips may be mounted on all embodiments described above.
  • the upper seat and the lower cover are directly in contact with each other without any supplemental separate element, therefore reducing the number of elements forming the suspension thrust device.
  • the suspension bump thrust according to the invention makes it possible to reduce production costs by limiting the number of parts to be assembled.
  • the conformation o f the sliding races makes it possible to support axial and radial loads exerted by the suspension spring and to obtain a suspension device with good tolerance to relative misalignment of the lower cover and the upper seat.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)

Abstract

L'invention concerne un dispositif de butée de suspension (10) destiné à un véhicule à moteur comprenant un siège de palier élastique supérieur (12) conçu pour être fixé au châssis du véhicule à moteur et un couvercle de soutien inférieur (13) ayant une surface d'appui (24c) adaptée pour entrer en contact avec un ressort de suspension (11) conçu pour exercer une poussée axiale et radiale sur le dispositif de suspension (10). Le couvercle de soutien inférieur (13) comprend une surface supérieure (25) opposée à la surface d'appui (24c) et formant une cage de glissement adaptée pour coopérer avec une cage de glissement complémentaire (19) du siège de palier supérieur (12), lesdites cages de glissement (19, 25) s'assemblant et pouvant coulisser l'une par rapport à l'autre, et pouvant absorber les forces axiales et radiales exercées par le ressort de suspension (11).
PCT/EP2010/062747 2010-08-31 2010-08-31 Palier de butée de suspension doté d'un élément filtrant WO2012028177A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/EP2010/062747 WO2012028177A1 (fr) 2010-08-31 2010-08-31 Palier de butée de suspension doté d'un élément filtrant

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2010/062747 WO2012028177A1 (fr) 2010-08-31 2010-08-31 Palier de butée de suspension doté d'un élément filtrant

Publications (1)

Publication Number Publication Date
WO2012028177A1 true WO2012028177A1 (fr) 2012-03-08

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3002138A1 (fr) * 2014-10-02 2016-04-06 NTN-SNR Roulements Butée de suspension à coupelle monobloc multifonction
WO2019026655A1 (fr) * 2017-07-31 2019-02-07 オイレス工業株式会社 Cellule de charge et palier
US20190242430A1 (en) * 2016-05-16 2019-08-08 Roller Bearing Company Of America, Inc. Bearing system with self-lubrication features, seals, grooves and slots for maintenance-free operation
US20220024273A1 (en) * 2020-07-21 2022-01-27 Aktiebolaget Skf Suspension thrust bearing device with dust boot retainer
US20230025440A1 (en) * 2021-07-23 2023-01-26 Aktiebolaget Skf Suspension abutment device with seal
DE102022108422B3 (de) 2022-04-07 2023-08-03 Schaeffler Technologies AG & Co. KG Lager

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0656483A1 (fr) 1993-11-30 1995-06-07 Oiles Corporation Palier en résine synthétique avec un élément de palier axial sous forme d'un disque fendu, et d'un élément de palier radial sous forme d'un manchon fendu
JP2001099218A (ja) * 1999-09-30 2001-04-10 Bridgestone Corp ストラットマウント
FR2810586A1 (fr) * 2000-06-27 2001-12-28 Renault Sport Jambe de force a un seul palier de guidage pour une suspension du type macpherson
US20090315292A1 (en) * 2008-06-23 2009-12-24 Gm Global Technology Operations, Inc. Lightweight, polymeric automotive strut suspension upper mounting

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0656483A1 (fr) 1993-11-30 1995-06-07 Oiles Corporation Palier en résine synthétique avec un élément de palier axial sous forme d'un disque fendu, et d'un élément de palier radial sous forme d'un manchon fendu
JP2001099218A (ja) * 1999-09-30 2001-04-10 Bridgestone Corp ストラットマウント
FR2810586A1 (fr) * 2000-06-27 2001-12-28 Renault Sport Jambe de force a un seul palier de guidage pour une suspension du type macpherson
US20090315292A1 (en) * 2008-06-23 2009-12-24 Gm Global Technology Operations, Inc. Lightweight, polymeric automotive strut suspension upper mounting

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3002138A1 (fr) * 2014-10-02 2016-04-06 NTN-SNR Roulements Butée de suspension à coupelle monobloc multifonction
FR3026678A1 (fr) * 2014-10-02 2016-04-08 Ntn-Snr Roulements Butee de suspension a coupelle monobloc multifonction
US20190242430A1 (en) * 2016-05-16 2019-08-08 Roller Bearing Company Of America, Inc. Bearing system with self-lubrication features, seals, grooves and slots for maintenance-free operation
WO2019026655A1 (fr) * 2017-07-31 2019-02-07 オイレス工業株式会社 Cellule de charge et palier
US20220024273A1 (en) * 2020-07-21 2022-01-27 Aktiebolaget Skf Suspension thrust bearing device with dust boot retainer
US11833872B2 (en) * 2020-07-21 2023-12-05 Aktiebolaget Skf Suspension thrust bearing device with dust boot retainer
US20230025440A1 (en) * 2021-07-23 2023-01-26 Aktiebolaget Skf Suspension abutment device with seal
US11958325B2 (en) * 2021-07-23 2024-04-16 Aktiebolaget Skf Suspension abutment device with seal
DE102022108422B3 (de) 2022-04-07 2023-08-03 Schaeffler Technologies AG & Co. KG Lager

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