FR2839396A1 - Electric motor with improved support for shaft, uses a packing ring made of an elastic material between bearing and bearing housing to avoid vibration and compensate misalignment - Google Patents
Electric motor with improved support for shaft, uses a packing ring made of an elastic material between bearing and bearing housing to avoid vibration and compensate misalignment Download PDFInfo
- Publication number
- FR2839396A1 FR2839396A1 FR0205646A FR0205646A FR2839396A1 FR 2839396 A1 FR2839396 A1 FR 2839396A1 FR 0205646 A FR0205646 A FR 0205646A FR 0205646 A FR0205646 A FR 0205646A FR 2839396 A1 FR2839396 A1 FR 2839396A1
- Authority
- FR
- France
- Prior art keywords
- bearing
- ring
- casing
- shaft
- motor according
- Prior art date
- Legal status (The legal status 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 status listed.)
- Withdrawn
Links
Classifications
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K5/00—Casings; Enclosures; Supports
- H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
- H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
- H02K5/173—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings
- H02K5/1732—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings radially supporting the rotary shaft at both ends of the rotor
-
- 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
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
- F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
-
- 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
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
- F16C27/066—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
- F16C2380/00—Electrical apparatus
- F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Power Engineering (AREA)
- Motor Or Generator Frames (AREA)
Abstract
Description
une enveloppe (101) selon l'une des revendications 1 a 21.an envelope (101) according to one of claims 1 to 21.
La presente invention concerne un moteur electrique, du type comportant un stator pourvu d'un carter moteur, un rotor pourvu d'un arbre rotatif par rapport au stator, ainsi qu'au moins un palier annulaire et une The present invention relates to an electric motor, of the type comprising a stator provided with a motor housing, a rotor provided with a rotary shaft relative to the stator, as well as at least one annular bearing and one
entretoise de calage disposes entre l'arbre et le carter. timing spacer arranged between the shaft and the housing.
Generalement, un arbre rotorique est pourvu de deux paliers, tels que des roulements a billes, disposes de part et d'autre du bobinage rotorique de fa,con a assurer le guidage radial et la tenue longitudinale de l'arbre par rapport au carter. La bague exterieure de chaque roulement est reliee au carter d u moteu r par l' i ntermed iaire d' u n insert metalliq ue forma nt entretoise, Generally, a rotor shaft is provided with two bearings, such as ball bearings, arranged on either side of the rotor winding so as to provide radial guidance and the longitudinal holding of the shaft relative to the casing. The outer ring of each bearing is connected to the motor housing by the intermediate of a metal insert form a spacer,
relic rigidement au carter et menageant un leger jeu axial avec le roulement. rigidly connected to the housing and providing a slight axial clearance with the bearing.
Lorsqu'un desalignement existe entre l'axe de l'arbre et les axes des alesages de reception des inserts menages dans le carter, ce type de moteur engendre des vibrations, voire des chocs dans les roulements, reduisant alors notablement leur duree de vie. Cette usure prematuree est d'autant plus marquee lorsque les vitesses de rotation de l'arbre vent elevees. De plus, les vibrations vent transmises jusqutau carter moteur, ce qui genere des When a misalignment exists between the axis of the shaft and the axes of the receiving bores of the housings inserts in the casing, this type of motor generates vibrations, or even shocks in the bearings, then considerably reducing their service life. This premature wear is all the more marked when the rotational speeds of the shaft are high. In addition, vibrations are transmitted to the crankcase, which generates
nuisances sonores.noise.
On a propose par le passe de former une entretoise en munissant ['insert metallique qui relic le roulement au carter d'un joint torique retenu dans une gorge menagee interieurement a ['insert. Ce joint permet a la fois d'amortir partiellement les vibrations entre le roulement et le carter, et de bloquer en rotation la bague exterieure du roulement par rapport a ['insert. Cependant, les capacites d'amortissement d'une telle entretoise restent d'une part incertaines en raison des dispersions d 'u sin age d es inserts metalli ques, et d 'autre part limitees. De plus, de part et d'autre du joint, un jeu radial subsiste entre ['insert et la bague exterieure du roulement, propice a transmettre des vibrations et a susciter des chocs entre ['insert et la bague exterieure du roulement, surtout It has been proposed in the past to form a spacer by providing the metal insert which connects the bearing to the housing with an O-ring retained in a groove formed internally with the insert. This seal makes it possible both to partially dampen the vibrations between the bearing and the casing, and to block the outer ring of the bearing in rotation relative to the insert. However, the damping capacities of such a spacer remain, on the one hand, uncertain due to dispersions of a metal inserts, and on the other hand limited. In addition, on either side of the seal, a radial clearance remains between the insert and the outer ring of the bearing, which is conducive to transmitting vibrations and causing shocks between the insert and the outer ring of the bearing, especially
lorsque les vitesses de rotation de l'arbre vent elevees. when the rotational speeds of the shaft are high.
Le but de la presente invention est de proposer un moteur electrique du type precise et dans lequel l'entretoise comporte une bague d'amortissement en un materiau elastique disposee au moins partiellement autour de la peripherie du palier, qui permette d'amortir considerablement les perturbations et les secousses transmises de l'arbre rotatif au carter moteur, et par la de diminuer l'usure du ou des paliers, et ce meme a des vitesses d'entranement The object of the present invention is to provide an electric motor of the precise type and in which the spacer comprises a damping ring made of an elastic material arranged at least partially around the periphery of the bearing, which makes it possible to considerably dampen disturbances and the shocks transmitted from the rotary shaft to the crankcase, and thereby reduce wear on the bearing (s), even at drive speeds
d'arbre elevees, par exemple superieures a 10 000 tours/mn. high trees, for example greater than 10,000 rpm.
A cet effet, I'invention a pour objet un moteur electrique du type defini ci-dessus, dans lequel la bague d'amortissement a une dimension axiale superieure a 0,5 fois celle du palier. Suivant d'autres caracteristiques de ce moteur, prises isolement ou selon toutes les combinaisons techniquement possibles: - I'entretoise comporte une bague interieure et une bague exterieure, qu i vent rig ides et coaxiales, et entre lesq u elles la bague d' amo rtissement est adherisee, la bague interieure etant reliee rigidement a la face exterieure du palier et la bague exterieure etant montee en contact glissant par rapport au carter; - I'epaisseur de chacune des bagues rigides est inferieure a l'epaisseur de la bague d'amortissement; - la bague interieure est emmanchee a force sur le palier; - la bague exterieure est re,cue dans un logement menage dans le carter et de dimension radiale legerement plus grande que celle de ladite bague exterieure; - la bague d'amortissement presente une jupe annulaire prolongee radialement par un talon d'appui pour l'extremite axiale du palier, la jupe etant disposee entre la peripherie du palier et le carter, et le talon etant dispose axialement entre le carter et une surface frontale d'extremite du palier; - le talon de la bague d'amortissement est venu de matiere avec la jupe de ladite bague d'amortissement; - le talon de la bague d'amortissement possede une epaisseur axiale differente de l'epaisseur radiale de la jupe; - le talon de la bague d'amortissement est monte comprime entre le carter et la surface frontale d'extremite du palier; et To this end, the invention relates to an electric motor of the type defined above, in which the damping ring has an axial dimension greater than 0.5 times that of the bearing. According to other characteristics of this engine, taken in isolation or in all technically possible combinations: - the spacer comprises an inner ring and an outer ring, which are rigid and coaxial, and between them the amo ring rtissement is adherisee, the inner ring being rigidly connected to the outer face of the bearing and the outer ring being mounted in sliding contact relative to the housing; The thickness of each of the rigid rings is less than the thickness of the damping ring; - the inner ring is force fitted onto the bearing; - The outer ring is received, received in a household in the housing and of slightly larger radial dimension than that of said outer ring; the damping ring has an annular skirt extended radially by a bearing heel for the axial end of the bearing, the skirt being disposed between the periphery of the bearing and the casing, and the heel being disposed axially between the casing and a front end surface of the bearing; - The heel of the damping ring has come into material with the skirt of said damping ring; - the heel of the damping ring has an axial thickness different from the radial thickness of the skirt; - the heel of the damping ring is mounted compressed between the casing and the front end surface of the bearing; and
- le palier est un roulement a billes. - the bearing is a ball bearing.
L'invention sera mieux comprise a la lecture de la description qui va The invention will be better understood on reading the description which will
suivre, donnee uniquement a titre d'exemple et faite en se referent aux dessins sur lesquels: - la figure 1 est une vue en coupe longitudinale d'un moteur electrique selon ['invention; follow, given only by way of example and made with reference to the drawings in which: - Figure 1 is a longitudinal sectional view of an electric motor according to the invention;
3 28393963 2839396
- la figure 2 est une vue a plus grande echelle d'un detail cercle 11 sur la figure 1; et - la figure 3 est une vue a plus grande echelle d'un detail cercle lil sur la - Figure 2 is a view on a larger scale of a circle detail 11 in Figure 1; and - Figure 3 is a view on a larger scale of a detail circle lil on the
figure 1.figure 1.
S Sur la figure 1 est represente un moteur electrique asynchrone 1, destine par exemple a entraner un ventilateur non represente. Ce moteur comprend un rotor 2 et un stator 6, le rotor etant destine a etre entrane en S In Figure 1 is shown an asynchronous electric motor 1, for example for driving a fan not shown. This motor comprises a rotor 2 and a stator 6, the rotor being intended to be driven in
rotation par rapport au stator.rotation relative to the stator.
Plus precisement, le stator 6 comporte un carter moteur 8 forme en partie d'une enveloppe exterieure 10 de forme sensiblement cylindrique, d'axe XX. L'enveloppe 10 est ouverte a l'une de ses extremites par un alesage 12 coaxial a l'axe X-X, se prolongeant par un rebord peripherique 14, radialement en saillie vers cet axe. Wile est fermee a l'autre extremite par un flasque 16, solidarise a l'enveloppe au moyen de vis 18. L'enveloppe et le flasque formant le carter 8 vent constitues d'un materiau rigide, par exemple d'aluminium ou More precisely, the stator 6 comprises a motor housing 8 partly forms an outer casing 10 of substantially cylindrical shape, of axis XX. The casing 10 is open at one of its ends by a bore 12 coaxial with the axis X-X, extending by a peripheral flange 14, radially projecting towards this axis. Wile is closed at the other end by a flange 16, secured to the casing by means of screws 18. The casing and the flange forming the casing 8 wind made of a rigid material, for example aluminum or
d'un alliage d'aluminium.of an aluminum alloy.
Le flasque 16 menage, du cote dirige vers l'interieur de l'enveloppe 10, une cuvette cylindrique 20 et d'axe X'-X', confondu avec l'axe X-X sur la figure 1. Le rotor 2 comporte un arbre rotatif 22, d'axe Y-Y confondu avec l'axe X-X sur la figure 1. L'arbre s'etend depuis la face du flasque 16 tournee vers l'interieur de l'enveloppe 10, a l'exterieur de l'enveloppe, en empruntant l'alesage 12. II est forme de piusieurs tron, cons successifs etages, references 22A a 22E, en s'eloignant du flasque 6. L'arbre 22 menage de la sorte un The flange 16 provides, on the side directed towards the interior of the casing 10, a cylindrical cup 20 and of axis X'-X ', merged with the axis XX in FIG. 1. The rotor 2 comprises a rotary shaft 22, of axis YY merged with axis XX in FIG. 1. The shaft extends from the face of the flange 16 turned towards the interior of the envelope 10, outside the envelope, in borrowing the bore 12. It is formed of several sections, successive stages cons, references 22A to 22E, moving away from the flange 6. The shaft 22 thus provides a
epaulement 24 cote flasque et un epaulement 25 cote alesage. shoulder 24 flange side and one shoulder 25 bore side.
Un ensemble de parties actives rotoriques 26 est flxe sur la partie courante de l'arbre 22, et un ensemble de bobinages statoriques 28 est flxe sur la face interieure de l'enveloppe 10. Ces elements rotoriques et statoriques vent alimentes electriquement de fa,con convenable pour engendrer un champ magnetique tournant destine a entraner le rotor, et done l'arbre 22 autour de l'axe Y-Y. Cet agencement asynchrone etant bien connu, il ne sera pas A set of active rotor parts 26 is affixed to the current part of the shaft 22, and a set of stator windings 28 is affixed to the inside face of the casing 10. These rotor and stator elements are electrically supplied in fa, con suitable for generating a rotating magnetic field intended to drive the rotor, and therefore the shaft 22 around the axis YY. As this asynchronous arrangement is well known, it will not be
detaille plus avant.in more detail.
Pour assurer le soutien axial et le guidage radial de l'arbre 22 par rapport au carter moteur 8, deux ensembles de support vent prevus dans le moteur 1, a savoir du cote flasque, un premier ensemble 30 monte sur la partie d'arbre 22A, et un second ensemble 31 du cote de l'alesage 12 monte To provide axial support and radial guidance of the shaft 22 relative to the motor housing 8, two wind support assemblies provided in the motor 1, namely on the flange side, a first assembly 30 mounts on the shaft part 22A , and a second assembly 31 on the side of the bore 12 goes up
sur la partie d'arbre 22D.on the shaft part 22D.
Comme represente plus en detail sur les figures 2 et 3, chaque ensemble 30, 31 comporte un roulement a billes 32, 33 dont une bague interieure 32A, 33A est en contact serre sur la partie d'arbre 22A, 22D et dont une bague exterieure 32B, 33B est reliee au carter du moteur 8 de fa,con amortie par une entretoise de calage 34, 35 detaillee ci-dessous et disposee, As shown in more detail in FIGS. 2 and 3, each assembly 30, 31 comprises a ball bearing 32, 33 of which an inner ring 32A, 33A is in tight contact on the shaft part 22A, 22D and of which an outer ring 32B, 33B is connected to the motor casing 8 in fa, con damped by a timing spacer 34, 35 detailed below and arranged,
au moins partiellement, entre le roulement 22, 23 et le carter moteur 8. at least partially, between the bearing 22, 23 and the crankcase 8.
Les entretoises 34, 35 vent formees, pour chaque ensemble 30, 31, d'une part d'une bague 36, 37 en elastomere, dont la longueur est au moins superieure a 0,5 fois, par exemple sensiblement egale a environ deux fois, celle de la bague exterieure 32B, 33B du roulement correspondent 32, 33, et, d'autre part, d'une padre de bagues metalliques 38A, 38B et 39A, 39B, entre lesquelles la bague correspondante 36, 37 est adherisee. Avantageusement, les bagues 36, 37 vent formees en un materiau alveolaire. De plus, chaque bague metallique possede une epaisseur nettement plus petite que celle de la bague en elastomere correspondante, et est par exemple realisee en acier inoxydable, choisi pour ses proprietes physicochimiques vis-a-vis des bagues The spacers 34, 35 are formed, for each set 30, 31, on the one hand of an elastomer ring 36, 37, the length of which is at least greater than 0.5 times, for example substantially equal to approximately twice. , that of the outer ring 32B, 33B of the bearing correspond 32, 33, and, on the other hand, a padre of metal rings 38A, 38B and 39A, 39B, between which the corresponding ring 36, 37 is adhered. Advantageously, the rings 36, 37 are formed from a cellular material. In addition, each metal ring has a thickness significantly smaller than that of the corresponding elastomer ring, and is for example made of stainless steel, chosen for its physicochemical properties vis-à-vis the rings
de roulement.of rolling.
La bague metallique interieure 38A est reliee rigidement a la bague exterieure 32B du roulement 32, une telle liaison etant obtenue notamment par emmanchement a force de l'entretoise 34 sur le roulement 32. De meme, la bague interieure 39A est reliee rigidement a la bague exterieure 33B du roulement 33, une telle liaison etant obtenue notamment par emmanchement a force de l'entretoise 35 sur le roulement 33. En variante, la liaison rigide des bagues interieures 38A et 39A avec les roulements 32 et 33 est obtenue par collage. La bague exterieure 38B est re,cue a l'interieur du cylindre forme par la cuvette 20 du flasque 16, en etant ecarte de la surface peripherique interieure de cette cuvette d'un leger jeu radial. De meme, la bague exterieure 39B est re,cue a l'interieur de l'alesage 12 menage a l'extremite de l'enveloppe 10, en The inner metal ring 38A is rigidly connected to the outer ring 32B of the bearing 32, such a connection being obtained in particular by press fit of the spacer 34 on the bearing 32. Similarly, the inner ring 39A is rigidly connected to the ring 33B exterior of the bearing 33, such a connection being obtained in particular by force fitting the spacer 35 on the bearing 33. Alternatively, the rigid connection of the inner rings 38A and 39A with the bearings 32 and 33 is obtained by bonding. The outer ring 38B is received inside the cylinder formed by the bowl 20 of the flange 16, being moved away from the inner peripheral surface of this bowl with a slight radial clearance. Likewise, the outer ring 39B is received, inside the bore 12 leading to the end of the casing 10, in
etant ecarte de la surface interieure de cet alesage d'un leger jeu radial. being moved away from the interior surface of this bore with a slight radial clearance.
28393962839396
Les entretoises 34 et 35 vent chacune formees d'une partie axiale formant jupe annulaire disposee radialement entre le roulement 32, 33 et le carter 8, et d'une partie radialement epaulee formant talon et destinee a assurer le blocage axial des bagues exterieures 32B, 33B des roulements 32 et 33. Plus precisement, la bague en elastomere 36 et les bagues metalliques 38A et 38B de l'entretoise 34 presentent chacune une section transversale en forme de L, dont des talons radialement saillants vers l'interieur (pointes par la reference generale 40) vent axialement disposes entre la bague exterieure 32B du roulement 32 et le flasque 16 (figure 2). De meme, la bague en elastomere 37 et les bagues metalliques 39A et 39B de l'entretoise 35 presentent une section transversale en forme de L, dont des talons radialement saillants vers l'interieur (pointes par la reference generale 41) vent axialement disposes entre la bague exterieure 33B du roulement 33 et le The spacers 34 and 35 are each formed by an axial part forming an annular skirt disposed radially between the bearing 32, 33 and the casing 8, and by a radially shoulder part forming a heel and intended to ensure the axial locking of the outer rings 32B, 33B of the bearings 32 and 33. More precisely, the elastomer ring 36 and the metal rings 38A and 38B of the spacer 34 each have an L-shaped cross section, with heels radially projecting inward (points through the general reference 40) wind axially disposed between the outer ring 32B of the bearing 32 and the flange 16 (Figure 2). Likewise, the elastomer ring 37 and the metal rings 39A and 39B of the spacer 35 have an L-shaped cross section, of which heels radially projecting inwards (points by the general reference 41) are axially disposed between the outer ring 33B of the bearing 33 and the
rebord peripherique 14 de l'enveloppe 10. peripheral rim 14 of the envelope 10.
Les epaisseurs des talons 40, 41 des entretoises 34, 35 vent superieures a celles des jupes annulaires de ces entretoises. De plus, ces talons 40, 41, notamment les talons de bague en elastomere, vent avantageusement montes comprimes dans ['ensemble de support 30, 31. Les epaisseurs de montage des talons 40 et 41, inferieures a leur epaisseur au repos avant montage, vent determinees de fapon a imposer un appui axial de poussee sur les bagues exterieures du roulement 32B et 33B, dtintensite The thicknesses of the heels 40, 41 of the spacers 34, 35 are greater than those of the annular skirts of these spacers. In addition, these heels 40, 41, in particular the elastomer ring heels, are advantageously mounted compressed in the support assembly 30, 31. The mounting thicknesses of the heels 40 and 41, less than their thickness at rest before assembly, determined wind of force to impose an axial thrust support on the outer rings of the bearing 32B and 33B, stress reduction
predeterminee, de fa,con a diminuer les jeux internee des roulements 32 et 33. predetermined, so as to reduce the internal clearance of bearings 32 and 33.
La reduction de ces jeux assure un guidage strict des billes de roulement a l'interieur de leurs bagues, diminuant ainsi leur usure a haute vitesse de sollicitation. A titre d'exemple, pour le moteur represente, pour un arbre entrane a plus de 10 000 tours/mn, une intensite de chargement axiale de The reduction in these clearances ensures strict guiding of the rolling balls inside their rings, thereby reducing their wear at high loading speed. For example, for the motor represented, for a shaft driven at more than 10,000 rpm, an axial loading intensity of
N est conseillee.N is recommended.
L' assembl age d u moteu r 1 est le su ivant. The assembly of motor 1 is the following.
On solidarise d'abord les parties actives rotoriques 26 a l'arbre 22, puis on met en place sur l'arbre 22 les roulements 32 et 33, en butee axiale contre The rotor active parts 26 are first secured to the shaft 22, then the bearings 32 and 33 are placed on the shaft 22, in axial abutment against
respectivement les epaulements 24 et 25. shoulders 24 and 25 respectively.
Puis, on emmanche a force l'entretoise 34 sur le roulement 32, jusqu'a ce que la partie epaulee de la bague metallique 38A soit en butee axiale contre le flanc de la bague exterieure 32B du roulement 32. De la meme Then, the spacer 34 is force-fitted onto the bearing 32, until the shoulder part of the metal ring 38A is in axial abutment against the side of the outer ring 32B of the bearing 32. Similarly
- 2839396- 2839396
fa,con, du cote oppose de l'arbre 22, on emmanche en force l'entretoise 35 sur le roulement 33, jusqu'a ce que la partie epaulee de la bague metallique interne 39A soit en butee axiale avec le flanc de la bague exterieure 33B du roulement. S L'arbre 22 est alors introduit a l'interieur de l'enveloppe 10 a l'interieur de laquelle vent fixes les bobinages statoriques 28, en passant par son cote destine a recevoir ulterieurement le flasque 16. L'entretoise 35 est de la sorte positionnee a l'interieur de l'alesage 12, en laissant entre eux un leger jeu radial assurant un contact glissant. La partie epaulee de la bague metallique exterieure 39B vient en blocage axial sur le rebord peripherique 14 de fa, con, on the opposite side of the shaft 22, the spacer 35 is force fitted onto the bearing 33, until the shoulder part of the internal metal ring 39A is in axial abutment with the flank of the ring 33B bearing exterior. S The shaft 22 is then introduced inside the casing 10 inside which the stator windings 28 are fixed, passing through its dimension intended to subsequently receive the flange 16. The spacer 35 is of the so positioned inside the bore 12, leaving a slight radial clearance between them ensuring sliding contact. The shoulder part of the outer metal ring 39B comes into axial locking on the peripheral flange 14 of
l'enveloppe 10.envelope 10.
On fixe ensuite au moyen des vis 18 le flasque 16 sur l'enveloppe 10, de fa,con a ce que l'entretoise 34 soit positionnee a l'interieur du cylindre delimite par la cuvette 20 du flasque 16, en laissant entre eux un leger jeu radial assurant un contact glissant. La partie epaulee de la bague metallique The flange 16 is then fixed by means of the screws 18 on the casing 10, so that the spacer 34 is positioned inside the cylinder delimited by the bowl 20 of the flange 16, leaving between them a slight radial clearance ensuring sliding contact. The shoulder part of the metal ring
exterieure 38B est alors en blocage axial contre le flasque 16. 38B is then axially locked against the flange 16.
Le serrage du flasque sur l'enveloppe 10 entrane la mise en charge axiale de la ligne d'arbre ainsi forme, essentiellement au niveau des The tightening of the flange on the casing 10 causes the axial loading of the shaft line thus formed, essentially at the level of the
entretoises 34 et 35 en appui axial contre le flasque 16 et le rebord 14. spacers 34 and 35 in axial abutment against the flange 16 and the flange 14.
Comme evoque plus haut, cette pre-charge permet de contraindre axialement les roulements 32 et 33, et ainsi de reduire leurs jeux internee en augmentant As mentioned above, this preload allows the bearings 32 and 33 to be axially constrained, and thus reducing their internal play by increasing
les surfaces de contact des billes avec les bagues interieures et exterieures. the contact surfaces of the balls with the inner and outer rings.
L'usure du roulement sollicite a haute vitesse s'en trouve alors reduite. The wear of the bearing requested at high speed is thereby reduced.
En fonctionnement, notamment a des vitesses superieures a 10 000 tours/mn, l'arbre rotorique 22 est entrane, tout en etant retenu axialement et In operation, in particular at speeds greater than 10,000 rpm, the rotor shaft 22 is driven, while being retained axially and
radialement par les ensembles 30 et 31. radially by the assemblies 30 and 31.
Le desalignement des axes X-X, X'-X' et Y-Y entrane des mouvements d'oscillation et/ou de balourd de l'arbre a l'interieur du carter moteur fixe 8 forme de l'enveloppe 10 et du flasque 16. Ces mouvements oscillants vent transmis de l'arbre aux roulements, puis vent amortis par les bagues en elastomere 36 et 37. Les vibrations et les chocs subis par les organes de roulement 32 et 33 restent ainsi d'intensite limitee, voire sensiblement nulle, la longueur axiale des bagues d'amortissement 36, 37, au moins egale a 0,5 fois The misalignment of the axes XX, X'-X 'and YY causes oscillation and / or unbalance movements of the shaft inside the fixed crankcase 8 forming the casing 10 and the flange 16. These movements oscillating wind transmitted from the shaft to the bearings, then wind damped by the elastomer rings 36 and 37. The vibrations and shocks undergone by the rolling members 32 and 33 thus remain of limited intensity, even substantially zero, the axial length damping rings 36, 37, at least equal to 0.5 times
celle des roulements 32,33, etant dimensionnees en consequence. that of bearings 32,33, being dimensioned accordingly.
De plus, il est possible de conna^tre a priori les capacites d'amortissement des ensembles 30 et 31, notamment en fonction de l'epaisseur des bagues d'amortissement, du materiau dont elles vent constituees et de leur structure alveolaire. Ainsi, pour un arbre rotatif destine a tourner a plus de 10 000 tours/mn, la frequence de resonance du moteur 1 se situe entre 20 et 140 Hz. En choisissant des bagues en elastomere 36 et 37 d'epaisseur appropriee, comprise entre par exemple 5 a 10 mm, eVou constituee d'un materiau alveolaire adequat, il est possible de dimensionner les ensembles 30 et 31 de maniere a supprimer sensiblement totalement In addition, it is possible to know a priori the damping capacities of the assemblies 30 and 31, in particular as a function of the thickness of the damping rings, of the material of which they are made and of their cellular structure. Thus, for a rotary shaft intended to rotate at more than 10,000 revolutions / min, the resonance frequency of the motor 1 is between 20 and 140 Hz. By choosing elastomer rings 36 and 37 of suitable thickness, between example 5 to 10 mm, eVou is made of an adequate cellular material, it is possible to size the assemblies 30 and 31 so as to remove substantially completely
I'intensite des oscillations generees entre l'arbre 22 et le carter 8. The intensity of the oscillations generated between the shaft 22 and the casing 8.
De la meme fac,on, les talons 40 et 41 des entretoises 34 et 35 vent dimensionnes pour assurer une intensite de precharge predeterminee, necessaire au calage axial de la ligne d'arbre formee. Cette structure a talon permet ainsi de se passer de systeme mecanique de precharge utilise jusqu'ici, tel que des ressorts ou des structures a lamelles elastiques. La fiabilite du moteur electrique selon ['invention est ainsi amelioree, notamment In the same way, we, the heels 40 and 41 of the spacers 34 and 35 are dimensioned to ensure a predetermined preload intensity, necessary for the axial setting of the formed shaft line. This heel structure thus makes it possible to dispense with the mechanical preload system used up to now, such as springs or structures with elastic lamellae. The reliability of the electric motor according to the invention is thus improved, in particular
par diminution du nombre d'elements le constituent. by reduction in the number of elements constitute it.
Bien que l'exemple decrit jusqu'ici concerne un moteur asynchrone, tous les types de moteur electrique a arbre rotorique et carter statorique vent envisageables pour recevoir au moins un ensemble d'amortissement tel que Although the example described so far concerns an asynchronous motor, all types of electric motor with rotor shaft and stator wind casing can be envisaged to receive at least one damping assembly such as
['ensemble 30 ou 31 detaille ci-dessus. ['set 30 or 31 detailed above.
Claims (10)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR0205646A FR2839396A1 (en) | 2002-05-06 | 2002-05-06 | Electric motor with improved support for shaft, uses a packing ring made of an elastic material between bearing and bearing housing to avoid vibration and compensate misalignment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR0205646A FR2839396A1 (en) | 2002-05-06 | 2002-05-06 | Electric motor with improved support for shaft, uses a packing ring made of an elastic material between bearing and bearing housing to avoid vibration and compensate misalignment |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| FR2839396A1 true FR2839396A1 (en) | 2003-11-07 |
Family
ID=29226218
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| FR0205646A Withdrawn FR2839396A1 (en) | 2002-05-06 | 2002-05-06 | Electric motor with improved support for shaft, uses a packing ring made of an elastic material between bearing and bearing housing to avoid vibration and compensate misalignment |
Country Status (1)
| Country | Link |
|---|---|
| FR (1) | FR2839396A1 (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007002903A1 (en) * | 2005-06-29 | 2007-01-04 | The Timken Company | Vibration damping device for bearings and method of dampening vibrations |
| WO2009144171A1 (en) * | 2008-05-30 | 2009-12-03 | Ln 2 S.R.L. A Socio Unico | Improved electric motor |
| CN102102722A (en) * | 2011-02-16 | 2011-06-22 | 东南大学 | Rub-impact damping protection device for high-speed rotating machinery |
| WO2012123710A1 (en) * | 2011-03-16 | 2012-09-20 | Flybrid Automotive Limited | High speed flywheel |
| WO2012155959A1 (en) * | 2011-05-16 | 2012-11-22 | Aktiebolaget Skf | Rolling bearing having insulating material. |
| EP1950433A3 (en) * | 2007-01-26 | 2013-05-01 | JTEKT Corporation | Rolling bearing device |
| WO2013086589A1 (en) * | 2011-12-13 | 2013-06-20 | Weg Equipamentos Elétricos S.A. - Motores | Segmented viscoelastic bushing for the bearings of rotary electric machines |
| US20210167660A1 (en) * | 2019-12-03 | 2021-06-03 | China Drive Motors (Shenzhen) Co., Ltd. | High-speed Fan Motor |
| CN112994331A (en) * | 2019-12-12 | 2021-06-18 | 法雷奥电机设备公司 | Rotating electrical machine comprising an elastic unit |
| WO2022069696A1 (en) * | 2020-10-01 | 2022-04-07 | Valeo Embrayages | Moving element damper |
| CN114704548A (en) * | 2022-04-07 | 2022-07-05 | 北京航空航天大学 | Elastic ring type damper with metal rubber layer |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB496282A (en) * | 1936-02-28 | 1938-11-28 | Roulements A Billes Miniatures | Improvements in shaft bearings |
| GB553760A (en) * | 1942-01-28 | 1943-06-03 | Wright Howard Clayton | Improvements in or relating to bearings |
| US2728593A (en) * | 1946-04-15 | 1955-12-27 | Silentbloc | Flanged resilient bearings |
| EP0423616A1 (en) * | 1989-10-16 | 1991-04-24 | ELCO S.p.A. | Electric motor of minimal axial dimensions, particularly for use with fans |
-
2002
- 2002-05-06 FR FR0205646A patent/FR2839396A1/en not_active Withdrawn
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB496282A (en) * | 1936-02-28 | 1938-11-28 | Roulements A Billes Miniatures | Improvements in shaft bearings |
| GB553760A (en) * | 1942-01-28 | 1943-06-03 | Wright Howard Clayton | Improvements in or relating to bearings |
| US2728593A (en) * | 1946-04-15 | 1955-12-27 | Silentbloc | Flanged resilient bearings |
| EP0423616A1 (en) * | 1989-10-16 | 1991-04-24 | ELCO S.p.A. | Electric motor of minimal axial dimensions, particularly for use with fans |
Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007002903A1 (en) * | 2005-06-29 | 2007-01-04 | The Timken Company | Vibration damping device for bearings and method of dampening vibrations |
| EP1950433A3 (en) * | 2007-01-26 | 2013-05-01 | JTEKT Corporation | Rolling bearing device |
| WO2009144171A1 (en) * | 2008-05-30 | 2009-12-03 | Ln 2 S.R.L. A Socio Unico | Improved electric motor |
| CN102102722A (en) * | 2011-02-16 | 2011-06-22 | 东南大学 | Rub-impact damping protection device for high-speed rotating machinery |
| CN103443503B (en) * | 2011-03-16 | 2016-03-02 | 飞轮汽车制造有限公司 | high speed flywheel |
| WO2012123710A1 (en) * | 2011-03-16 | 2012-09-20 | Flybrid Automotive Limited | High speed flywheel |
| US9360082B2 (en) | 2011-03-16 | 2016-06-07 | Flybird Automotive Limited | High speed flywheel |
| GB2489021B (en) * | 2011-03-16 | 2013-08-14 | Flybrid Automotive Ltd | High speed flywheel |
| CN103443503A (en) * | 2011-03-16 | 2013-12-11 | 飞轮汽车制造有限公司 | High speed flywheel |
| WO2012155959A1 (en) * | 2011-05-16 | 2012-11-22 | Aktiebolaget Skf | Rolling bearing having insulating material. |
| CN103534501A (en) * | 2011-05-16 | 2014-01-22 | Skf公司 | Rolling bearing having insulating material. |
| WO2013086589A1 (en) * | 2011-12-13 | 2013-06-20 | Weg Equipamentos Elétricos S.A. - Motores | Segmented viscoelastic bushing for the bearings of rotary electric machines |
| US20210167660A1 (en) * | 2019-12-03 | 2021-06-03 | China Drive Motors (Shenzhen) Co., Ltd. | High-speed Fan Motor |
| EP3832139A1 (en) * | 2019-12-03 | 2021-06-09 | China Drive Motors (Shenzhen) Co., Ltd. | High speed fan with bearing dampers |
| CN112994331A (en) * | 2019-12-12 | 2021-06-18 | 法雷奥电机设备公司 | Rotating electrical machine comprising an elastic unit |
| WO2022069696A1 (en) * | 2020-10-01 | 2022-04-07 | Valeo Embrayages | Moving element damper |
| FR3117180A1 (en) * | 2020-10-01 | 2022-06-10 | Valeo Embrayages | Damping of a moving element |
| CN114704548A (en) * | 2022-04-07 | 2022-07-05 | 北京航空航天大学 | Elastic ring type damper with metal rubber layer |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP1112884B1 (en) | Mounting device for an electrical equipment, such as a starter-generator, in a vehicle clutch housing | |
| FR2839396A1 (en) | Electric motor with improved support for shaft, uses a packing ring made of an elastic material between bearing and bearing housing to avoid vibration and compensate misalignment | |
| CN101262161B (en) | Brushless motor and manufacturing method thereof | |
| EP3048701B1 (en) | Cradle for electric machine and associated transmission system | |
| FR2560349A1 (en) | LUBRICANT DEFLECTOR FOR ELECTRIC MOTOR AND MOUNTING METHOD THEREOF | |
| FR2729440A1 (en) | ROLLING BEARING, IN PARTICULAR REAR BEARING OF A MOTOR VEHICLE ALTERNATOR | |
| WO2016177549A1 (en) | Electromechanical assembly comprising an electrical machine coupled to a reducer | |
| US6388351B1 (en) | Bearing load washer | |
| FR2729442A1 (en) | Bearing for rotating machine with roller between axle and support | |
| EP1167793A2 (en) | A rolling contact bearing for an electric motor | |
| FR2684729A1 (en) | Housing for radially fixing rolling-contact bearings | |
| FR3020425A1 (en) | TORQUE TRANSMISSION DEVICE FOR A MOTOR VEHICLE | |
| FR2907529A1 (en) | FILTER CRANKSHAFT PULLEY. | |
| FR2733810A1 (en) | TORSION SHOCK ABSORBER, PARTICULARLY FOR MOTOR VEHICLE | |
| JP4632792B2 (en) | Pulley with damper function | |
| US6867513B1 (en) | Electric motor | |
| JP5730185B2 (en) | Scroll compressor | |
| FR2698934A1 (en) | Torsional damper, especially for a motor vehicle. | |
| FR2833775A1 (en) | RING FOR MAINTAINING AND DECOUPLING THE ELECTRIC MOTOR IN ITS BRACKET AND ASSEMBLY PROCEDURE | |
| KR101969789B1 (en) | Electric turbocharger with oilless bearing | |
| FR2944654A1 (en) | Supporting frame for stator of rotating electric machine e.g. motor, has connection elements distributed around stator and extended parallel to machine axle, and plate connected to internal flanges by elements adjustable in length | |
| FR2648207A1 (en) | BELT PULLEY FOR DRIVING THE SHAFT OF A WATER PUMP AND PROCESS FOR MANUFACTURING THE SAID BELT PULLEY | |
| US9546657B2 (en) | Compressor having a lower frame and a method of manufacturing the same | |
| WO2006111657A1 (en) | Alternator comprising an antifriction bearing having a fastening collar | |
| JP2010106802A (en) | Vane rotary compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| ST | Notification of lapse |