WO2006072693A1 - Device for mechanical coupling between two elements - Google Patents

Device for mechanical coupling between two elements Download PDF

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Publication number
WO2006072693A1
WO2006072693A1 PCT/FR2005/003236 FR2005003236W WO2006072693A1 WO 2006072693 A1 WO2006072693 A1 WO 2006072693A1 FR 2005003236 W FR2005003236 W FR 2005003236W WO 2006072693 A1 WO2006072693 A1 WO 2006072693A1
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WO
WIPO (PCT)
Prior art keywords
bearing
ring
driving element
friction
driven
Prior art date
Application number
PCT/FR2005/003236
Other languages
French (fr)
Inventor
Michel Descombes
Armel Louis Doyer
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
Publication of WO2006072693A1 publication Critical patent/WO2006072693A1/en

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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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/56—Systems consisting of a plurality of bearings with rolling friction in which the rolling bodies of one bearing differ in diameter from those of another
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
    • F16D7/021—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with radially applied torque-limiting friction surfaces
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/46—Fans, e.g. ventilators

Definitions

  • the present invention relates to the field of mechanical couplings used to transmit a torque between a driving element and a driven element.
  • This type of device is used for example in the case of cooling fans of motor vehicle alternators.
  • a cooling fan of the engine alternator is generally rotated by the alternator shaft, itself driven by a pulley cooperating with a drive belt.
  • the rotational speed of the alternator shaft is directly proportional to the rotational speed of the motor.
  • the airflow of the high speed fan is often too high compared to the flow required to ensure efficient cooling. This results in a significant waste of energy.
  • Some mechanical coupling devices between the fan and the fan drive member allow, beyond a certain speed of rotation of the driving part connected to the motor, to partially decouple the fan, so that the speed of rotation of the fan fan is limited, while the rotation speed of the driving part continues to grow.
  • Such partial fan decoupling occurs when the aerodynamic drag torque of the fan becomes greater than the mechanical drive torque between the drive member and the fan.
  • There is then a relative rotation between the fan and the alternator shaft which allows the engine to run at high speed without the fan running too fast and producing too much aerodynamic noise.
  • Such devices are known in particular from documents US 4,437,846 and DE 28 22 638.
  • the main disadvantage of these devices is their size and the large number of elements to be assembled by the generator manufacturer on the rotor and the fan, which is detrimental in terms of cost and duration. of production.
  • the invention proposes to remedy these drawbacks.
  • the invention provides a compact mechanical coupling device, simple structure, whose production can be easily automated and reasonable cost.
  • the coupling device between a driving element and a driven element is intended to rotate the driven element, mounted on the driving element by means of a bearing.
  • the bearing comprises two concentric rings between which is disposed at least one row of rolling elements in contact with the raceways formed on said rings.
  • the passage of the torque between the driving element and the driven element is effected by mechanical coupling.
  • the bearing comprises an annular friction element ensuring the passage of a calibrated torque limited to a predefined value between the driving element and the driven element, said friction element cooperating with an annular bearing surface of the driving element and having a diameter less than or equal to the outside diameter of said bearing.
  • the annular friction element is thus very compact.
  • the friction element is in the form of a seal.
  • the same element thus provides the friction function and the sealing function.
  • the friction element is supported by one of the bearing races and is in frictional contact with the other race of the bearing.
  • the device comprises two friction elements disposed inside the bearing.
  • the friction element is integral with the driven element and comes into frictional contact with an annular bearing surface of the driving element.
  • the friction element may be integral with the inner ring of the bearing.
  • the friction element may be in frictional contact with a bearing of the rotating race of another bearing.
  • one of the rings of the bearing is mounted on a non-rotating support.
  • Said non-rotating support may comprise the non-rotating ring of another bearing.
  • the coupling member is supported by the driven member and is in frictional contact with a ring belonging to the driving member.
  • a fan may comprise a hub provided with blades and a coupling device as described above fixed on said means.
  • the outer ring of the bearing can be fitted into a bore of the wheel provided with blades.
  • An alternator or an electric motor may comprise a rotating part, a non-rotating part and a fan mounted via said coupling device on said rotating part.
  • the coupling device may be disposed in or on a bearing supporting the fan.
  • Such a rolling bearing can be applied to any type of mechanical member, in which it is desired to transmit a torque and a rotational movement between a driving element and a driven element, with a possible speed differential between the two elements and a possible speed limitation of the driven element. This is ensured simply and particularly compactly with said rolling bearing, for example in an electric machine.
  • the present invention will be better understood on reading the detailed description of some embodiments taken as non-limiting examples and illustrated by the appended drawings, in which:
  • FIG 1 is an axial sectional view of a portion of an alternator
  • FIG. 2 is a detail view of FIG. 1;
  • FIGS. 3 to 6 are views in axial section of different embodiments of the rolling bearing; and FIG. 7 is a curve of the fan speed as a function of the speed of the alternator.
  • the electric machine 1 for example an alternator, of which only an end portion is shown, comprises a rotating part 2 and a non-rotating part 3.
  • the rotating part 2 comprises a shaft 4 , a rotor not visible in the drawing and a grooved pulley 6 in which passes a driving belt 7 designed to be driven by a drive pulley secured to the crankshaft with thermal engine not shown.
  • a spacer 5 mounted on the shaft 4 ensures the precise axial positioning of the rotor relative to the bearings that support it.
  • the non-rotating part 3 comprises a casing 8, for example made of light alloy.
  • the bore is fitted with clamping on the shaft 4, a non-rotating outer ring January 1 whose cylindrical outer surface is fitted in a cylindrical bore of the housing 8, a row of rolling elements 12, here balls, arranged between the races of the inner rings 10 and outer 1 1, a cage 13 for maintaining the circumferential spacing of the rolling elements 12, here realized sheet metal, and two seals 14 and 15 mounted in annular grooves of the outer ring January 1 and rubbing by flexible lips on an outer cylindrical surface of the inner ring 10.
  • the seals 14 and 15 are symmetrical with respect to a radial plane passing through the center of the rolling elements 12 and are provided with a frame covered with a flexible material, for example an elastomer.
  • the races of the inner and outer rings 11 1 are formed by machining with chip removal to give them the desired depth.
  • the outer ring 1 1 is held axially relative to the casing 8, in one direction by a radially inwardly projecting bead 16 forming part of the casing 8, and in the other direction by a flange 17 fixed to the casing 8 by suitable means such as screws (not shown).
  • the rotating part 2 further comprises a fan 18 in the form of a ring of blades 19 extending outwards and inclined substantially in a helix, and a ring hub
  • the hub 20 comprises an annular axial portion of small diameter 21 provided with a bore.
  • a coupling device 22 is arranged radially between the shaft 4 and the axial portion
  • the coupling device 22 is in the form of a rolling bearing provided with an inner ring 24, an outer ring 25, a row of rolling elements 26 , here balls, a cage 27 for maintaining the circumferential spacing of the rolling elements 26 and coupling seals 28 and 29.
  • the inner and outer rings 24 24 have raceways in the form of a deep groove for the rolling elements 26 and are provided with radial front surfaces.
  • the bore of the inner ring 24 is fitted on the shaft 4 and in contact on one side with the spacer 5 and on the opposite side with the spacer washer 23.
  • the inner ring 24 has an outer surface in the form of a cylindrical bearing, on one side and the other of the raceway.
  • the outer ring 25 has an axial outer surface fitted into the axial portion 21 of the central portion 20 of the fan 18.
  • the radial front surfaces of the outer ring 25 are aligned on the radial end surfaces of the inner ring 24.
  • the outer ring 25 has a cylindrical bore, on both sides of the raceway.
  • the cage 27 comprises a bead disposed on one side of the rolling elements, while the coupling seals 28 and 29 are arranged on the opposite side.
  • the coupling joints 28 and 29 are identical, each comprising an armature 30 and a flexible portion 31.
  • the armature 30 comprises an axial portion fitted into the bore of the outer ring 25 and a portion directed inwards from the edge the adjacent axial portion of the front surfaces of the inner ring 24 and outer 25 and slightly approximating the rolling elements 26 towards its free end.
  • the reinforcements 30 and the flexible portions 31 are annular and completely arranged in the radial space defined between the inner and outer rings 24 and in the axial space defined between the cage 27 and the plane of the radial front surface of the rings 24 and 24. 25.
  • the coupling joints 28 and 29 therefore have no significant influence on the bulk of the coupling device 22.
  • the flexible portion 31 can be made by overmolding a synthetic material, for example elastomer, on the metal frame 30.
  • the flexible portion 31 partially overlaps the inward facing portion of the frame 30 and extends inwardly to engage an axial bearing surface of the inner ring 24.
  • the flexible part 31 comprises two contact lips 32 and 33 spaced axially and in contact with the same scope of the inner ring 24 on which they rub, thus providing torque transmission economically.
  • the coupling device has the same bulk as a bearing of equal mechanical characteristics, thanks to the insertion of the coupling joints 28 and 29 between the rings 24 and 25.
  • the flange 17 comprises two parts 34 and 35 welded to each other, the outer portion 34 being screwed to the casing 8 and provided with a radial portion in contact with said casing. 8 and an axial portion directed away from the bead 16.
  • the inner portion 35 comprises an axial portion of large diameter welded to the axial portion of the outer portion 34, a radial portion directed inwardly to the opposite of the free ends welded together axial portions of the parts 34 and 35 and an axial flange directed towards the rolling elements 12 of the rolling bearing 9 and fitted on an axial bearing surface 36 of the outer ring 11 of the rolling bearing 9.
  • the coupling device 22 comprises a rolling bearing 37, similar in type to the rolling bearing 9, but having a much smaller diameter of rolling elements with a ring 38 outside fit into the bore of the large diameter portion of the inner portion 35 of the flange 17.
  • the coupling device 22 also comprises a coupling joint 40, seen in more detail in FIG. 4, fitted into the bore of the inner ring 39 of the bearing 37 and provided with a lip 44 which rubs against an outer cylindrical bearing surface of the inner ring 10 of the rolling bearing 9.
  • the axial portion 21 of the hub 20 is fitted into the bore of the coupling ring 40 to the right of the rolling bearing 37.
  • the spacer 5 is in direct contact with the inner ring 10 of the rolling bearing 9, the seal 40 having a diameter greater than that of said spacer 5.
  • the ring-shaped seal 40 comprises an armature 41 in the form of an L-shaped cup having an axial portion and an inwardly extending radial portion, and an flexible part 42 covering largely the armature 41, in particular on the two outer and inner faces of the axial portion of the armature 41 to ensure excellent rotational solidarity of the seal 40 with the inner ring 39, on the one hand, and with the hub 20, on the other hand.
  • the flexible portion 42 also extends inwards and towards the rolling elements 12 of the rolling bearing 9 and is provided with a lip in frictional contact with the inner ring 10.
  • the coupling joint 40 is completed by a 43 annular spring, ensuring the radial clamping of the lip 44 of the flexible portion 42 on the inner ring 10 of the rolling bearing 9 and therefore the transmission of a friction torque between said inner ring 10 and the hub 20.
  • the presence a spring 43 is particularly well suited for the transmission of calibrated friction torque, the spring maintaining a constant radial force of clamping the lip 44 on the inner ring 10, regardless of the wear of the lip 44.
  • the inner part 35 of the flange 17, on the one hand, ensures in cooperation with the outer part 34, the axial retention of the outer ring 11 of the rolling bearing 9 and, on the other hand, supports the outer ring 38 of the rolling bearing 37 ensuring its axial and radial retention relative to the outer ring 1 1 of the rolling bearing 9, thus avoiding that the flexible portion 42 of the coupling seal 40 is excessively close to the cage 13 of the rolling bearing 9, or that the friction torque does not vary due to possible eccentricity of the coupling ring 40 relative to the inner ring 10.
  • the coupling seal 40 has an outer diameter substantially equal to the bore of the inner ring 39 and is therefore not bulky radially.
  • the flange 17 has a radial portion of large diameter screwed to the housing 8, an axial portion in the bore of which is disposed the outer ring 38 of the rolling bearing 37 and a radial flange directed towards the inside from the end of the axial portion opposite to the radial portion and which maintains the axial position of the outer rings 1 1 and 38 of the rolling bearings 9 and 37.
  • a portion of the rolling bearing 37 and of the axial portion of the flange 17 are projecting into an annular recess formed by the hub 20, which ensures an excellent use of the available axial space.
  • the rolling bearing 37 is provided on the side of the hub 20 with a seal 45. As illustrated in the figures, the rolling bearing 37 may be without a seal on the opposite side. because of the seal offered by the coupling joint 40 and by the seal 14 of the rolling bearing 9. In the embodiment illustrated in FIG. 6, the flange
  • the axial portion 21 of the hub 20 is directly fitted into the bore of the inner ring 39 of the rolling bearing 37, while the coupling 40 is fitted into the bore of the axial portion 21 of said hub 20.
  • the coupling joint 40 has a shape slightly different from that illustrated in FIGS. 4 and 5, with a flexible portion 42 having a generally U-shaped shape of which an axial branch is fitted into the hub 20 and the end of a substantially axial leg is equipped with the spring 43 and rubs on a ring 46 of thin section and rectangular section fitted on part of its axial length on an outer axial surface of the inner ring 10 of the rolling bearing 9 and axially surrounding a portion of the spacer 5, thus providing an external friction surface to the coupling joint 40.
  • the coupling joint 40 is particularly compact radially and axially by occupying an axial space less than or equal to the axial length of the ring 39 while having an outer diameter less than the bore of the inner ring 39.
  • the ring 46 may consist of a portio n of thin tube of suitable length, for example less than the length of the inner ring 10.
  • the speed of rotation of the fan increases less rapidly than that of the electric machine from a certain speed, for example 4000 rpm, has a monotonous shape of decreasing slope in a range intermediate speeds, for example between 4000 and 14000 t / minute, then has a relatively constant low slope beyond.
  • the maximum torque transmissible by the coupling device depends on the material chosen to produce the flexible part of the prestressing exerted and the area of the facing surfaces. It is thus possible to calibrate, by construction or adjustment, the maximum torque that can be transmitted between the driving element and the driven element.
  • the maximum torque can be predefined, so that at a given rotational speed of the fan, the aerodynamic drag torque of the fan will exceed the maximum transmittable torque. There will then be a relative rotation between the fan rotor and the drive shaft.
  • the speed of the fan may grow slowly depending on the torque-speed curve of a fan which is monotonous increasing.
  • the coupling device is compact and can be easily disposed inside an electric machine. It provides both a reduction of fan noise and a reduction in power consumption by limiting the torque transmitted to the fan.
  • the coupling device is in the form of a simple bearing with deep groove rings or with sheet metal rings equipped with coupling seals.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

The invention concerns a coupling device (22) between a driving element designed to drive in rotation a driven element, the driven element being mounted on the driving element by means of a rolling bearing comprising two concentric rings (24, 25) between which is arranged at least one row of rolling elements (26) in contact with raceways provided on said rings, the passage of the torque between the driving element and the driven element being carried out by a mechanical coupling with an annular friction element allowing through a calibrated torque limited to a predefined value between the driving element and the driven element, said friction element co-operating with an annular seating of the driving element and having a diameter not greater than the outer diameter of said rolling bearing.

Description

Dispositif de couplage mécanique entre deux éléments. Mechanical coupling device between two elements.
La présente invention concerne le domaine des couplages mécaniques utilisés pour transmettre un couple entre un élément menant et un élément mené. Ce genre de dispositif est utilisé par exemple dans le cas des ventilateurs de refroidissement des alternateurs de véhicules automobiles. Or, on cherche de plus en plus, pour des raisons de confort, à réduire les bruits de toutes origines dans les moteurs thermiques et leurs accessoires. Un ventilateur de refroidissement d'alternateur de moteur thermique est en général entraîné en rotation par l'arbre de l'alternateur, lui-même entraîné par une poulie coopérant avec une courroie d'entraînement. La vitesse de rotation de l'arbre de l'alternateur est directement proportionnelle à la vitesse de rotation du moteur. Il en résulte que si le rotor de ventilateur est couplé rigidement à l'arbre d'alternateur, le bruit aérodynamique généré par le ventilateur devient extrêmement important à haute vitesse de rotation. D'autre part, le débit d' air du ventilateur à haute vitesse est souvent trop élevé par rapport au débit nécessaire pour assurer un refroidissement efficace. Il en résulte un gaspillage d'énergie non négligeable.The present invention relates to the field of mechanical couplings used to transmit a torque between a driving element and a driven element. This type of device is used for example in the case of cooling fans of motor vehicle alternators. However, we seek more and more, for reasons of comfort, to reduce the noise of all origins in engines and their accessories. A cooling fan of the engine alternator is generally rotated by the alternator shaft, itself driven by a pulley cooperating with a drive belt. The rotational speed of the alternator shaft is directly proportional to the rotational speed of the motor. As a result, if the fan rotor is rigidly coupled to the alternator shaft, the aerodynamic noise generated by the fan becomes extremely important at high rotational speeds. On the other hand, the airflow of the high speed fan is often too high compared to the flow required to ensure efficient cooling. This results in a significant waste of energy.
Certains dispositifs de couplage mécanique entre le ventilateur et l'organe menant du ventilateur permettent, au-delà d'une certaine vitesse de rotation de la partie menante liée au moteur, de découpler partiellement le ventilateur, de telle sorte que la vitesse de rotation du ventilateur est limitée, tandis que la vitesse de rotation de la partie menante continue à croître. Un tel découplage partiel du ventilateur se produit lorsque le couple de traînée aérodynamique du ventilateur devient supérieur au couple mécanique d'entraînement entre l'élément menant et le ventilateur. Il se produit alors une rotation relative entre le ventilateur et l'arbre d' alternateur, ce qui permet au moteur de tourner à haut régime sans que le ventilateur ne tourne trop vite et ne produise un bruit aérodynamique trop important. De tels dispositifs sont connus notamment par les documents US 4 437 846 et DE 28 22 638. Le principal inconvénient de ces dispositifs réside dans leur encombrement et dans le nombre important d'éléments à assembler par le fabriquant de l' alternateur sur le rotor et sur le ventilateur, ce qui s'avère néfaste en termes de coût et de durée de production. L'invention se propose de remédier à ces inconvénients.Some mechanical coupling devices between the fan and the fan drive member allow, beyond a certain speed of rotation of the driving part connected to the motor, to partially decouple the fan, so that the speed of rotation of the fan fan is limited, while the rotation speed of the driving part continues to grow. Such partial fan decoupling occurs when the aerodynamic drag torque of the fan becomes greater than the mechanical drive torque between the drive member and the fan. There is then a relative rotation between the fan and the alternator shaft, which allows the engine to run at high speed without the fan running too fast and producing too much aerodynamic noise. Such devices are known in particular from documents US 4,437,846 and DE 28 22 638. The main disadvantage of these devices is their size and the large number of elements to be assembled by the generator manufacturer on the rotor and the fan, which is detrimental in terms of cost and duration. of production. The invention proposes to remedy these drawbacks.
L'invention propose un dispositif de couplage mécanique compact, de structure simple, dont la production peut être aisément automatisée et de prix de revient raisonnable.The invention provides a compact mechanical coupling device, simple structure, whose production can be easily automated and reasonable cost.
Le dispositif de couplage entre un élément menant et un élément mené est destiné à entraîner en rotation l'élément mené, monté sur l'élément menant au moyen d'un roulement. Le roulement comprend deux bagues concentriques entre lesquelles est disposée au moins une rangée d'éléments roulants en contact avec des chemins de roulement ménagés sur lesdites bagues. Le passage du couple entre l'élément menant et l'élément mené s' effectue par un couplage mécanique. Le roulement comprend un élément annulaire de friction assurant le passage d'un couple calibré limité à une valeur prédéfinie entre l'élément menant et l'élément mené, ledit élément de friction coopérant avec une portée annulaire de l'élément menant et présentant un diamètre inférieur ou égal au diamètre extérieur dudit roulement.The coupling device between a driving element and a driven element is intended to rotate the driven element, mounted on the driving element by means of a bearing. The bearing comprises two concentric rings between which is disposed at least one row of rolling elements in contact with the raceways formed on said rings. The passage of the torque between the driving element and the driven element is effected by mechanical coupling. The bearing comprises an annular friction element ensuring the passage of a calibrated torque limited to a predefined value between the driving element and the driven element, said friction element cooperating with an annular bearing surface of the driving element and having a diameter less than or equal to the outside diameter of said bearing.
L'élément annulaire de friction est ainsi très compact.The annular friction element is thus very compact.
Avantageusement, l'élément de friction se présente sous la forme d'un joint d'étanchéité. Un même élément assure ainsi la fonction de friction et la fonction d'étanchéité. Dans un mode de réalisation, l'élément de friction est supporté par l'une des bagues du roulement et est en contact de frottement avec l'autre bague du roulement.Advantageously, the friction element is in the form of a seal. The same element thus provides the friction function and the sealing function. In one embodiment, the friction element is supported by one of the bearing races and is in frictional contact with the other race of the bearing.
Dans un mode de réalisation, le dispositif comprend deux éléments de friction disposés à l'intérieur du roulement. Alternativement, l'élément de friction est solidaire de l'élément mené et vient en contact de frottement avec une portée annulaire de l'élément menant. L'élément de friction peut être solidaire de la bague intérieure du roulement. L'élément de friction peut être en contact de frottement avec une portée de la bague tournante d'un autre roulement.In one embodiment, the device comprises two friction elements disposed inside the bearing. Alternatively, the friction element is integral with the driven element and comes into frictional contact with an annular bearing surface of the driving element. The friction element may be integral with the inner ring of the bearing. The friction element may be in frictional contact with a bearing of the rotating race of another bearing.
Dans un mode de réalisation, l'une des bagues du roulement est montée sur un support non tournant. Ledit support non tournant peut comprendre la bague non tournante d'un autre roulement.In one embodiment, one of the rings of the bearing is mounted on a non-rotating support. Said non-rotating support may comprise the non-rotating ring of another bearing.
Dans un mode de réalisation, l'élément de couplage est supporté par l'élément mené et est en contact de frottement avec un anneau appartenant à l'élément menant.In one embodiment, the coupling member is supported by the driven member and is in frictional contact with a ring belonging to the driving member.
Un ventilateur peut comprendre un moyeu pourvu de pales et un dispositif de couplage tel que décrit ci-dessus fixé sur ledit moyen.A fan may comprise a hub provided with blades and a coupling device as described above fixed on said means.
La bague extérieure du roulement peut être emmanchée dans un alésage de la roue pourvue de pales.The outer ring of the bearing can be fitted into a bore of the wheel provided with blades.
Un alternateur ou un moteur électrique peut comprendre une partie tournante, une partie non tournante et un ventilateur monté par l'intermédiaire dudit dispositif de couplage sur ladite partie tournante.An alternator or an electric motor may comprise a rotating part, a non-rotating part and a fan mounted via said coupling device on said rotating part.
Le dispositif de couplage peut être disposé dans ou sur un roulement supportant le ventilateur.The coupling device may be disposed in or on a bearing supporting the fan.
Un tel palier à roulement peut s'appliquer à tout type d' organe mécanique, dans lequel on souhaite transmettre un couple et un mouvement de rotation entre un élément menant et un élément mené, avec un différentiel de vitesse possible entre les deux éléments et une limitation de vitesse possible de l'élément mené. Ceci est assuré de façon simple et particulièrement compacte avec ledit palier à roulement, par exemple dans une machine électrique. La présente invention sera mieux comprise à la lecture de la description détaillée de quelques modes de réalisation pris à titre d' exemples nullement limitatifs et illustrés par les dessins annexés, sur lesquels:Such a rolling bearing can be applied to any type of mechanical member, in which it is desired to transmit a torque and a rotational movement between a driving element and a driven element, with a possible speed differential between the two elements and a possible speed limitation of the driven element. This is ensured simply and particularly compactly with said rolling bearing, for example in an electric machine. The present invention will be better understood on reading the detailed description of some embodiments taken as non-limiting examples and illustrated by the appended drawings, in which:
-la figure 1 est une vue en coupe axiale d'une partie d'un alternateur;FIG 1 is an axial sectional view of a portion of an alternator;
-la figure 2 est une vue de détail de la figure 1 ;FIG. 2 is a detail view of FIG. 1;
-les figures 3 à 6 sont des vues en coupe axiale de différents modes de réalisation du palier à roulement; et -la figure 7 est une courbe de la vitesse du ventilateur en fonction de la vitesse de l'alternateur.FIGS. 3 to 6 are views in axial section of different embodiments of the rolling bearing; and FIG. 7 is a curve of the fan speed as a function of the speed of the alternator.
Comme on peut le voir sur la figure 1 , la machine électrique 1 , par exemple un alternateur, dont seule une partie d'extrémité est représentée, comprend une partie tournante 2 et une partie non tournante 3. La partie tournante 2 comprend un arbre 4, un rotor non visible sur le dessin et une poulie 6 à gorge dans laquelle passe une courroie 7 d' entraînement prévue pour être entraînée par une poulie menante solidaire du vilebrequin à moteur thermique non représenté. Une entretoise 5 montée sur l'arbre 4 assure le positionnement axial précis du rotor par rapport aux paliers qui le supportent. La partie non tournante 3 comprend un carter 8, par exemple réalisé en alliage léger.As can be seen in FIG. 1, the electric machine 1, for example an alternator, of which only an end portion is shown, comprises a rotating part 2 and a non-rotating part 3. The rotating part 2 comprises a shaft 4 , a rotor not visible in the drawing and a grooved pulley 6 in which passes a driving belt 7 designed to be driven by a drive pulley secured to the crankshaft with thermal engine not shown. A spacer 5 mounted on the shaft 4 ensures the precise axial positioning of the rotor relative to the bearings that support it. The non-rotating part 3 comprises a casing 8, for example made of light alloy.
Entre l'arbre 4 et le carter 8, est disposé un palier à roulementBetween the shaft 4 and the casing 8 is disposed a rolling bearing
9, de type conventionnel, pourvu d'une bague intérieure tournante 10 dont l'alésage est emmanché avec serrage sur l'arbre 4, d'une bague extérieure non tournante 1 1 dont la surface extérieure cylindrique est emmanchée dans un alésage cylindrique du carter 8, d'une rangée d' éléments roulants 12, ici des billes, disposés entre des chemins de roulement des bagues intérieure 10 et extérieure 1 1 , d'une cage 13 de maintien de l'espacement circonférentiel des éléments roulants 12, ici réalisée en tôle, et de deux joints d' étanchéité 14 et 15 montés dans des rainures annulaires de la bague extérieure 1 1 et venant frotter par des lèvres souples sur une portée cylindrique extérieure de la bague intérieure 10. Les joints d' étanchéité 14 et 15 sont symétriques par rapport à un plan radial passant par le centre des éléments roulants 12 et sont pourvus d'une armature recouverte d'un matériau souple, par exemple un élastomère. Les chemins de roulement des bagues intérieure 10 et extérieure 1 1 sont formés par usinage avec enlèvement de copeaux pour leur conférer la profondeur souhaitée. La bague extérieure 1 1 est maintenue axialement par rapport au carter 8, dans un sens par un bourrelet radial 16 en saillie vers l'intérieur faisant partie du carter 8, et dans l'autre sens par un flasque 17 fixé au carter 8 par des moyens appropriés tels que des vis (non représentés). La partie tournante 2 comprend en outre un ventilateur 18 se présentant sous la forme d'une couronne de pales 19 s' étendant vers l'extérieur et inclinées sensiblement en hélice, et un moyeu annulaire9, of conventional type, provided with a rotating inner ring 10, the bore is fitted with clamping on the shaft 4, a non-rotating outer ring January 1 whose cylindrical outer surface is fitted in a cylindrical bore of the housing 8, a row of rolling elements 12, here balls, arranged between the races of the inner rings 10 and outer 1 1, a cage 13 for maintaining the circumferential spacing of the rolling elements 12, here realized sheet metal, and two seals 14 and 15 mounted in annular grooves of the outer ring January 1 and rubbing by flexible lips on an outer cylindrical surface of the inner ring 10. The seals 14 and 15 are symmetrical with respect to a radial plane passing through the center of the rolling elements 12 and are provided with a frame covered with a flexible material, for example an elastomer. The races of the inner and outer rings 11 1 are formed by machining with chip removal to give them the desired depth. The outer ring 1 1 is held axially relative to the casing 8, in one direction by a radially inwardly projecting bead 16 forming part of the casing 8, and in the other direction by a flange 17 fixed to the casing 8 by suitable means such as screws (not shown). The rotating part 2 further comprises a fan 18 in the form of a ring of blades 19 extending outwards and inclined substantially in a helix, and a ring hub
20 supportant les pales 19. Le moyeu 20 comprend une portion axiale annulaire de petit diamètre 21 pourvue d'un alésage. Un dispositif de couplage 22 est disposé radialement entre l'arbre 4 et la portion axialeThe hub 20 comprises an annular axial portion of small diameter 21 provided with a bore. A coupling device 22 is arranged radially between the shaft 4 and the axial portion
21 de la partie centrale 20 du ventilateur 18 et axialement entre l'entretoise 5 et une rondelle entretoise annulaire 23 en contact avec une surface radiale frontale de la bague intérieure 10 du roulement 9. Un serrage axial peut être assuré.21 of the central portion 20 of the fan 18 and axially between the spacer 5 and an annular spacer washer 23 in contact with a radial front surface of the inner ring 10 of the bearing 9. An axial clamping can be ensured.
Comme on le voit mieux sur la figure 2, le dispositif de couplage 22 se présente sous la forme d'un palier à roulement pourvu d'une bague intérieure 24, d'une bague extérieure 25, d'une rangée d' éléments roulants 26, ici des billes, d'une cage 27 de maintien de l'espacement circonférentiel des éléments roulants 26 et de joints de couplage 28 et 29. Les bagues intérieure 24 et extérieure 25 présentent des chemins de roulement sous la forme de gorge profonde pour les éléments roulants 26 et sont pourvues de surfaces frontales radiales. L'alésage de la bague intérieure 24 est emmanché sur l'arbre 4 et en contact d'un côté avec l' entretoise 5 et du côté opposé avec la rondelle entretoise 23. La bague intérieure 24 présente une surface extérieure sous la forme d'une portée cylindrique, d'un côté et de l'autre du chemin de roulement. La bague extérieure 25 présente une surface extérieure axiale emmanchée dans la portion axiale 21 de la partie centrale 20 du ventilateur 18. Les surfaces radiales frontales de la bague extérieure 25 sont alignées sur les surfaces frontales radiales de la bague intérieure 24. La bague extérieure 25 présente un alésage cylindrique, de part et d'autre du chemin de roulement. La cage 27 comprend un talon disposé d'un côté des éléments roulants, tandis que les joints de couplage 28 et 29 sont disposés du côté opposé.As best seen in Figure 2, the coupling device 22 is in the form of a rolling bearing provided with an inner ring 24, an outer ring 25, a row of rolling elements 26 , here balls, a cage 27 for maintaining the circumferential spacing of the rolling elements 26 and coupling seals 28 and 29. The inner and outer rings 24 24 have raceways in the form of a deep groove for the rolling elements 26 and are provided with radial front surfaces. The bore of the inner ring 24 is fitted on the shaft 4 and in contact on one side with the spacer 5 and on the opposite side with the spacer washer 23. The inner ring 24 has an outer surface in the form of a cylindrical bearing, on one side and the other of the raceway. The outer ring 25 has an axial outer surface fitted into the axial portion 21 of the central portion 20 of the fan 18. The radial front surfaces of the outer ring 25 are aligned on the radial end surfaces of the inner ring 24. The outer ring 25 has a cylindrical bore, on both sides of the raceway. The cage 27 comprises a bead disposed on one side of the rolling elements, while the coupling seals 28 and 29 are arranged on the opposite side.
Les joints de couplage 28 et 29 sont identiques, chacun comprenant une armature 30 et une partie souple 31. L'armature 30 comprend une partie axiale emmanchée dans l'alésage de la bague extérieure 25 et une partie dirigée vers l'intérieur à partir du bord de la partie axiale voisin des surfaces frontales des bagues intérieure 24 et extérieure 25 et se rapprochant légèrement des éléments roulants 26 vers son extrémité libre. Les armatures 30 et les parties souples 31 sont annulaires et entièrement disposées dans l'espace radial défini entre les bagues intérieure 24 et extérieure 25 et dans l'espace axial défini entre la cage 27 et le plan de la surface frontale radiale des bagues 24 et 25. Les joints de couplage 28 et 29 n'ont donc pas d'influence significative sur l'encombrement du dispositif de couplage 22. La partie souple 31 peut être réalisée par surmoulage d'un matériau synthétique, par exemple de l'élastomère, sur l'armature métallique 30. La partie souple 31 recouvre partiellement la partie dirigée vers l'intérieur de l'armature 30 et s'étend vers l'intérieur jusqu' à venir en contact avec une portée axiale de la bague intérieure 24. La partie souple 31 comprend deux lèvres de contact 32 et 33 espacées axialement et en contact avec la même portée de la bague intérieure 24 sur laquelle elles frottent, assurant ainsi une transmission de couple de façon économique. Le dispositif de couplage présente le même encombrement qu'un roulement de caractéristiques mécaniques égales, grâce à l'insertion des joints de couplage 28 et 29 entre les bagues 24 et 25.The coupling joints 28 and 29 are identical, each comprising an armature 30 and a flexible portion 31. The armature 30 comprises an axial portion fitted into the bore of the outer ring 25 and a portion directed inwards from the edge the adjacent axial portion of the front surfaces of the inner ring 24 and outer 25 and slightly approximating the rolling elements 26 towards its free end. The reinforcements 30 and the flexible portions 31 are annular and completely arranged in the radial space defined between the inner and outer rings 24 and in the axial space defined between the cage 27 and the plane of the radial front surface of the rings 24 and 24. 25. The coupling joints 28 and 29 therefore have no significant influence on the bulk of the coupling device 22. The flexible portion 31 can be made by overmolding a synthetic material, for example elastomer, on the metal frame 30. The flexible portion 31 partially overlaps the inward facing portion of the frame 30 and extends inwardly to engage an axial bearing surface of the inner ring 24. The flexible part 31 comprises two contact lips 32 and 33 spaced axially and in contact with the same scope of the inner ring 24 on which they rub, thus providing torque transmission economically. The coupling device has the same bulk as a bearing of equal mechanical characteristics, thanks to the insertion of the coupling joints 28 and 29 between the rings 24 and 25.
Dans le mode de réalisation illustré sur la figure 3, le flasque 17 comprend deux parties 34 et 35 soudées l'une à l'autre, la partie extérieure 34 étant vissée au carter 8 et pourvue d'une portion radiale en contact avec ledit carter 8 et d'une portion axiale dirigée à l'opposé du bourrelet 16. La. partie intérieure 35 comprend une portion axiale de grand diamètre soudée à la portion axiale de la partie extérieure 34, une portion radiale dirigée vers l'intérieur à l'opposé des extrémité libres soudées entre elles des portions axiales des parties 34 et 35 et un rebord axial dirigé en direction des éléments roulants 12 du palier à roulement 9 et emmanché sur une portée axiale 36 de la bague extérieure 11 du palier à roulement 9.In the embodiment illustrated in FIG. 3, the flange 17 comprises two parts 34 and 35 welded to each other, the outer portion 34 being screwed to the casing 8 and provided with a radial portion in contact with said casing. 8 and an axial portion directed away from the bead 16. The inner portion 35 comprises an axial portion of large diameter welded to the axial portion of the outer portion 34, a radial portion directed inwardly to the opposite of the free ends welded together axial portions of the parts 34 and 35 and an axial flange directed towards the rolling elements 12 of the rolling bearing 9 and fitted on an axial bearing surface 36 of the outer ring 11 of the rolling bearing 9.
Le dispositif de couplage 22 comprend un palier à roulement 37, de type semblable au palier à roulement 9, mais présentant un diamètre d' éléments roulants nettement plus faible avec une bague extérieure 38 emmanchée dans l'alésage de la portion de grand diamètre de la partie intérieure 35 du flasque 17.The coupling device 22 comprises a rolling bearing 37, similar in type to the rolling bearing 9, but having a much smaller diameter of rolling elements with a ring 38 outside fit into the bore of the large diameter portion of the inner portion 35 of the flange 17.
Le dispositif de couplage 22 comprend également un joint de couplage 40, visible plus en détail sur la figure 4, emmanché dans l'alésage de la bague intérieure 39 du roulement 37 et pourvu d'une lèvre 44 venant frotter sur une portée cylindrique extérieure de la bague intérieure 10 du palier à roulement 9. La portion axiale 21 du moyeu 20 est emmanchée dans l'alésage du joint de couplage 40 au droit du palier à roulement 37. L'entretoise 5 est en contact direct avec la bague intérieure 10 du palier à roulement 9, le joint 40 présentant un diamètre supérieur à celui de ladite entretoise 5.The coupling device 22 also comprises a coupling joint 40, seen in more detail in FIG. 4, fitted into the bore of the inner ring 39 of the bearing 37 and provided with a lip 44 which rubs against an outer cylindrical bearing surface of the inner ring 10 of the rolling bearing 9. The axial portion 21 of the hub 20 is fitted into the bore of the coupling ring 40 to the right of the rolling bearing 37. The spacer 5 is in direct contact with the inner ring 10 of the rolling bearing 9, the seal 40 having a diameter greater than that of said spacer 5.
Plus précisément, le joint 40, de forme annulaire, comprend une armature 41 sous la forme d'une coupelle en section en L pourvue d'une portion axiale et d'une portion radiale s' étendant vers l'intérieur, et d'une partie souple 42 recouvrant en grande partie l'armature 41 , notamment sur les deux faces extérieure et intérieure de la portion axiale de l'armature 41 pour assurer une excellente solidarisation en rotation du joint 40 avec la bague intérieure 39, d'une part, et avec le moyeu 20, d'autre part. La portion souple 42 s'étend également vers l'intérieur et en direction des éléments roulants 12 du palier à roulement 9 et est pourvue d'une lèvre en contact de frottement avec la bague intérieure 10. Le joint de couplage 40 se complète par un ressort 43 annulaire, assurant le serrage radial de la lèvre 44 de la partie souple 42 sur la bague intérieure 10 du palier à roulement 9 et par conséquent la transmission d'un couple de frottement entre ladite bague intérieure 10 et le moyeu 20. La présence d'un ressort 43 est particulièrement bien adaptée pour la transmission de couple de frottement calibré, le ressort maintenant un effort radial de serrage constant de la lèvre 44 sur la bague intérieure 10, quelle que soit l'usure de la lèvre 44.More specifically, the ring-shaped seal 40 comprises an armature 41 in the form of an L-shaped cup having an axial portion and an inwardly extending radial portion, and an flexible part 42 covering largely the armature 41, in particular on the two outer and inner faces of the axial portion of the armature 41 to ensure excellent rotational solidarity of the seal 40 with the inner ring 39, on the one hand, and with the hub 20, on the other hand. The flexible portion 42 also extends inwards and towards the rolling elements 12 of the rolling bearing 9 and is provided with a lip in frictional contact with the inner ring 10. The coupling joint 40 is completed by a 43 annular spring, ensuring the radial clamping of the lip 44 of the flexible portion 42 on the inner ring 10 of the rolling bearing 9 and therefore the transmission of a friction torque between said inner ring 10 and the hub 20. The presence a spring 43 is particularly well suited for the transmission of calibrated friction torque, the spring maintaining a constant radial force of clamping the lip 44 on the inner ring 10, regardless of the wear of the lip 44.
La partie intérieure 35 du flasque 17, d'une part, assure en coopération avec la partie extérieure 34, le maintien axial de la bague extérieure 11 du palier à roulement 9 et, d'autre part, supporte la bague extérieure 38 du palier à roulement 37 en assurant son maintien axial et radial par rapport à la bague extérieure 1 1 du palier à roulement 9, évitant ainsi que la partie souple 42 du joint de couplage 40 ne se rapproche excessivement de la cage 13 du palier à roulement 9, ou encore que le couple de frottement ne varie en raison d'une éventuelle excentration du joint de couplage 40 par rapport à la bague intérieure 10. Le joint de couplage 40 présente un diamètre extérieur sensiblement égal à l'alésage de la bague intérieure 39 et est donc peu encombrant radialement. Le mode de réalisation illustré sur la figure 5 se rapproche du précédent, à ceci près que la bague extérieure 38 du palier à roulement 37 est en contact direct avec la bague extérieure 1 1 du palier à roulement 9 par leurs surfaces frontales radiales respectives et y est fixée par un cordon de soudure 44. Le flasque 17 présente une portion radiale de grand diamètre vissée au carter 8, une portion axiale dans l'alésage de laquelle est disposée la bague extérieure 38 du palier à roulement 37 et un rebord radial dirigé vers l'intérieur à partir de l'extrémité de la portion axiale opposée à la portion radiale et qui assure le maintien en position axiale des bagues extérieures 1 1 et 38 des paliers à roulement 9 et 37. Une partie du palier à roulement 37 et de la portion axiale du flasque 17 sont en saillie dans un creux annulaire formé par le moyeu 20, ce qui garantit une excellente utilisation de l'espace axial disponible.The inner part 35 of the flange 17, on the one hand, ensures in cooperation with the outer part 34, the axial retention of the outer ring 11 of the rolling bearing 9 and, on the other hand, supports the outer ring 38 of the rolling bearing 37 ensuring its axial and radial retention relative to the outer ring 1 1 of the rolling bearing 9, thus avoiding that the flexible portion 42 of the coupling seal 40 is excessively close to the cage 13 of the rolling bearing 9, or that the friction torque does not vary due to possible eccentricity of the coupling ring 40 relative to the inner ring 10. The coupling seal 40 has an outer diameter substantially equal to the bore of the inner ring 39 and is therefore not bulky radially. The embodiment illustrated in FIG. 5 approaches the previous one, except that the outer ring 38 of the rolling bearing 37 is in direct contact with the outer ring 11 of the rolling bearing 9 by their respective radial front surfaces and is fixed by a weld bead 44. The flange 17 has a radial portion of large diameter screwed to the housing 8, an axial portion in the bore of which is disposed the outer ring 38 of the rolling bearing 37 and a radial flange directed towards the inside from the end of the axial portion opposite to the radial portion and which maintains the axial position of the outer rings 1 1 and 38 of the rolling bearings 9 and 37. A portion of the rolling bearing 37 and of the axial portion of the flange 17 are projecting into an annular recess formed by the hub 20, which ensures an excellent use of the available axial space.
L'on voit également que le palier à roulement 37 est pourvu du côté du moyeu 20 d'un joint d'étanchéité 45. Comme illustré sur les figures, le palier à roulement 37 peut être dépourvu de joint d'étanchéité du côté opposé en raison de l'étanchéité offerte par le joint de couplage 40 et par le joint d'étanchéité 14 du palier à roulement 9. Dans le mode de réalisation illustré sur la figure 6, le flasqueIt can also be seen that the rolling bearing 37 is provided on the side of the hub 20 with a seal 45. As illustrated in the figures, the rolling bearing 37 may be without a seal on the opposite side. because of the seal offered by the coupling joint 40 and by the seal 14 of the rolling bearing 9. In the embodiment illustrated in FIG. 6, the flange
17 et le palier à roulement 37 sont semblables à ceux illustrés sur la figure 5. La portion axiale 21 du moyeu 20 est directement emmanchée dans l' alésage de la bague intérieure 39 du palier à roulement 37, tandis que le joint de couplage 40 est emmanché dans l'alésage de la portion axiale 21 dudit moyeu 20. Le joint de couplage 40 présente une forme légèrement différente de celle illustrée sur les figures 4 et 5, avec une partie souple 42 présentant une forme générale d'U dont une branche axiale est emmanchée dans le moyeu 20 et l' extrémité d'une branche sensiblement axiale est équipée du ressort 43 et vient frotter sur un anneau 46 de section droite mince et rectangulaire emmanché sur une partie de sa longueur axiale sur une portée axiale extérieure de la bague intérieure 10 du palier à roulement 9 et entourant axialement une partie de l'entretoise 5, offrant ainsi une surface extérieure de frottement au joint de couplage 40. Le joint de couplage 40 est particulièrement compact radialement et axialement en occupant un espace axial inférieur ou égal à la longueur axiale de la bague intérieure 39 tout en présentant un diamètre extérieur inférieur à l'alésage de la bague intérieure 39. L'anneau 46 peut consister en une portion de tube de faible épaisseur et de longueur adaptée, par exemple inférieure à la longueur de la bague intérieure 10.17 and the rolling bearing 37 are similar to those shown in Figure 5. The axial portion 21 of the hub 20 is directly fitted into the bore of the inner ring 39 of the rolling bearing 37, while the coupling 40 is fitted into the bore of the axial portion 21 of said hub 20. The coupling joint 40 has a shape slightly different from that illustrated in FIGS. 4 and 5, with a flexible portion 42 having a generally U-shaped shape of which an axial branch is fitted into the hub 20 and the end of a substantially axial leg is equipped with the spring 43 and rubs on a ring 46 of thin section and rectangular section fitted on part of its axial length on an outer axial surface of the inner ring 10 of the rolling bearing 9 and axially surrounding a portion of the spacer 5, thus providing an external friction surface to the coupling joint 40. The coupling joint 40 is particularly compact radially and axially by occupying an axial space less than or equal to the axial length of the ring 39 while having an outer diameter less than the bore of the inner ring 39. The ring 46 may consist of a portio n of thin tube of suitable length, for example less than the length of the inner ring 10.
Comme on peut le voir sur la figure 7, la vitesse de rotation du ventilateur croît moins vite que celle de la machine électrique à partir d'une certaine vitesse, par exemple 4000 t/minute, présente une forme monotone de pente décroissante dans une plage de vitesses intermédiaire, par exemple entre 4000 et 14000 t/minute, puis présente une faible pente relativement constante au-delà.As can be seen in FIG. 7, the speed of rotation of the fan increases less rapidly than that of the electric machine from a certain speed, for example 4000 rpm, has a monotonous shape of decreasing slope in a range intermediate speeds, for example between 4000 and 14000 t / minute, then has a relatively constant low slope beyond.
Le couple maximum transmissible par le dispositif de couplage dépend du matériau choisi pour réaliser la partie souple de la précontrainte exercée et de l'aire des surfaces en regard. On peut ainsi calibrer, par construction ou par réglage, le couple maximum transmissible entre l'élément menant et l'élément mené. Le couple maximum peut être prédéfini, de telle sorte qu'à une vitesse de rotation donnée du ventilateur, le couple de traînée aérodynamique du ventilateur dépassera le couple maximum transmissible. Il se produira alors une rotation relative entre le rotor du ventilateur et l'arbre d' entraînement. La vitesse du ventilateur pourra croître lentement en fonction de la courbe couple-vitesse de rotation d'un ventilateur qui est monotone croissante. Le dispositif de couplage est compact et peut être disposé aisément à l'intérieur d'une machine électrique. Il assure à la fois une réduction du bruit du ventilateur et une réduction de la consommation d' énergie en limitant le couple transmis au ventilateur.The maximum torque transmissible by the coupling device depends on the material chosen to produce the flexible part of the prestressing exerted and the area of the facing surfaces. It is thus possible to calibrate, by construction or adjustment, the maximum torque that can be transmitted between the driving element and the driven element. The maximum torque can be predefined, so that at a given rotational speed of the fan, the aerodynamic drag torque of the fan will exceed the maximum transmittable torque. There will then be a relative rotation between the fan rotor and the drive shaft. The speed of the fan may grow slowly depending on the torque-speed curve of a fan which is monotonous increasing. The coupling device is compact and can be easily disposed inside an electric machine. It provides both a reduction of fan noise and a reduction in power consumption by limiting the torque transmitted to the fan.
Le dispositif de couplage se présente sous la forme d'un simple roulement à bagues à gorges profondes ou encore à bagues en tôle équipées de joints de couplage. The coupling device is in the form of a simple bearing with deep groove rings or with sheet metal rings equipped with coupling seals.

Claims

REVENDICATIONS
1 -Dispositif de couplage (22) entre un élément menant et un élément mené, destiné à entraîner en rotation l'élément mené, l'élément mené étant monté sur l'élément menant au moyen d'un roulement comportant deux bagues concentriques (24, 25) entre lesquelles est disposée au moins une rangée d' éléments roulants (26) en contact avec des chemins de roulement ménagés sur lesdites bagues, le passage du couple entre l' élément menant et l'élément mené s' effectuant par un couplage mécanique, caractérisé en ce qu'il comprend un élément annulaire de friction assurant le passage d'un couple calibré limité à une valeur prédéfinie entre l'élément menant et l'élément mené, ledit élément de friction coopérant avec une portée annulaire de l'élément menant et présentant un diamètre inférieur ou égal au diamètre extérieur dudit roulement. 2-Dispositif selon la revendication 1 , caractérisé par le fait que l'élément de friction se présente sous la forme d'un joint d'étanchéité.A coupling device (22) between a driving element and a driven element for rotating the driven element, the driven element being mounted on the driving element by means of a bearing comprising two concentric rings (24). , 25) between which is disposed at least one row of rolling elements (26) in contact with raceways provided on said bushings, the passage of torque between the driving element and the driven element being effected by a coupling mechanical, characterized in that it comprises an annular friction element ensuring the passage of a calibrated torque limited to a predefined value between the driving element and the driven element, said friction element cooperating with an annular bearing surface of the driving element and having a diameter less than or equal to the outer diameter of said bearing. 2-Device according to claim 1, characterized in that the friction element is in the form of a seal.
3-Dispositif selon la revendication 1 ou 2, caractérisé par le fait que l'élément de friction est supporté par l'une des bagues du roulement et est en contact de frottement avec l'autre bague dudit roulement.3-Device according to claim 1 or 2, characterized in that the friction element is supported by one of the bearing rings and is in frictional contact with the other ring of said bearing.
4-Dispositif selon l'une quelconque des revendications précédentes, caractérisé par le fait qu'il comprend deux éléments de friction disposés à l'intérieur dudit roulement.4-Device according to any one of the preceding claims, characterized in that it comprises two friction elements disposed within said bearing.
5-Dispositif selon l'une quelconque des revendications 1 à 3 , caractérisé par le fait que l'élément de friction est solidaire de l'élément mené et vient en contact de frottement avec une portée annulaire de l'élément menant.5-Device according to any one of claims 1 to 3, characterized in that the friction element is integral with the driven member and comes into frictional contact with an annular bearing surface of the driving element.
6-Dispositif selon la revendication 5, caractérisé par le fait que l'élément de friction est solidaire de la bague intérieure du roulement. 7-Dispositif selon la revendication 5 ou 6, caractérisé par le fait que l'élément de friction est en contact de frottement avec une portée de la bague tournante d'un autre roulement.6-Device according to claim 5, characterized in that the friction element is secured to the inner ring of the bearing. 7-Device according to claim 5 or 6, characterized in that the friction element is in frictional contact with a bearing of the rotating ring of another bearing.
8-Dispositif selon l'une quelconque des revendications précédentes, caractérisé par le fait que l'une des bagues dudit roulement est montée sur un support non tournant.8-Device according to any one of the preceding claims, characterized in that one of the rings of said bearing is mounted on a non-rotating support.
9-Dispositif selon la revendication 8, caractérisé par le fait que ledit support non tournant comprend la bague non tournante d'un autre roulement. 10-Dispositif selon l'une quelconque des revendications 1 à 4, caractérisé par le fait que l'élément de couplage est supporté par l'élément mené et est en contact de frottement avec un anneau appartenant à l'élément menant.9-Device according to claim 8, characterized in that said non-rotating support comprises the non-rotating ring of another bearing. 10-Device according to any one of claims 1 to 4, characterized in that the coupling element is supported by the driven element and is in frictional contact with a ring belonging to the driving element.
1 1 -Machine électrique comprenant un rotor, un stator et un dispositif selon l'une quelconque des revendications précédentes. 1 1 -Electric machine comprising a rotor, a stator and a device according to any one of the preceding claims.
PCT/FR2005/003236 2005-01-06 2005-12-21 Device for mechanical coupling between two elements WO2006072693A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0500116A FR2880395B1 (en) 2005-01-06 2005-01-06 DEVICE FOR MECHANICAL COUPLING BETWEEN TWO ELEMENTS
FR0500116 2005-01-06

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WO2006072693A1 true WO2006072693A1 (en) 2006-07-13

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PCT/FR2005/003236 WO2006072693A1 (en) 2005-01-06 2005-12-21 Device for mechanical coupling between two elements

Country Status (2)

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FR (1) FR2880395B1 (en)
WO (1) WO2006072693A1 (en)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2822638A1 (en) 1978-05-24 1979-11-29 Bosch Gmbh Robert Slipping clutch for generator drive - has spring member with friction linings preloaded against other half
US4437846A (en) 1979-10-23 1984-03-20 Robert Bosch Gmbh Speed limiting rotary coupling
DE29916854U1 (en) * 1999-09-06 2000-01-20 Liesegang Sabine roller bearing
EP1217258A2 (en) * 2000-12-21 2002-06-26 Ntn Corporation Pulley ball bearing and pulley
DE10151795A1 (en) * 2001-10-19 2003-04-30 Ina Schaeffler Kg pulley
US20040062461A1 (en) * 2002-09-30 2004-04-01 Johnson James P. Roller bearing having high performance bearing seal and cartridge

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2822638A1 (en) 1978-05-24 1979-11-29 Bosch Gmbh Robert Slipping clutch for generator drive - has spring member with friction linings preloaded against other half
US4437846A (en) 1979-10-23 1984-03-20 Robert Bosch Gmbh Speed limiting rotary coupling
DE29916854U1 (en) * 1999-09-06 2000-01-20 Liesegang Sabine roller bearing
EP1217258A2 (en) * 2000-12-21 2002-06-26 Ntn Corporation Pulley ball bearing and pulley
DE10151795A1 (en) * 2001-10-19 2003-04-30 Ina Schaeffler Kg pulley
US20040062461A1 (en) * 2002-09-30 2004-04-01 Johnson James P. Roller bearing having high performance bearing seal and cartridge

Also Published As

Publication number Publication date
FR2880395A1 (en) 2006-07-07
FR2880395B1 (en) 2008-12-05

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