FR2795147A1 - Disc brake of Zero Noise kind has brake caliper, clevis and two inverted small columns which can slide above the disk - Google Patents
Disc brake of Zero Noise kind has brake caliper, clevis and two inverted small columns which can slide above the disk Download PDFInfo
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- FR2795147A1 FR2795147A1 FR9907524A FR9907524A FR2795147A1 FR 2795147 A1 FR2795147 A1 FR 2795147A1 FR 9907524 A FR9907524 A FR 9907524A FR 9907524 A FR9907524 A FR 9907524A FR 2795147 A1 FR2795147 A1 FR 2795147A1
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- columns
- disk
- clevis
- caliper
- bore
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Classifications
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- 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
- F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
- F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
- F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
- F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
- F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
- F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
- F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
- F16D55/22655—Constructional details of guide pins
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- 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
- F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
- F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
- F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
- F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
- F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
- F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
- F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
- F16D55/227—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing by two or more pins
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- 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
- F16D65/00—Parts or details
- F16D65/0006—Noise or vibration control
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Abstract
Description
La présente invention concerne les freins<B>à</B> disque de type ZN (Zéro Noise) de deuxième génération<B>à</B> deux colonnettes, peu sensibles aux phénomènes NVH (Noise Vibrations and Harshness), plus précisément la présente invention concerne une architecture de frein<B>à</B> disque<B>à</B> deux colonnettes coulissantes placées au-dessus du disque, de type Zéro Offset (ou sans déport) et<B>à</B> faible couple résiduel. The present invention relates to the brakes <B> to </ B> disk type ZN (Zero Noise) second generation <B> to </ B> two columns, little sensitive to NVH phenomena (Noise Vibrations and Harshness), more precisely the present invention relates to a brake architecture <B> to </ B> disk <B> to </ B> two sliding columns placed above the disk, type Zero Offset (or without offset) and <B> to < / B> low residual torque.
On connaît<B>déjà</B> de nombreux dispositifs de coulissement au-dessus du disque, principalement<B>à</B> deux colonnettes, l'une de guidage, l'autre de verrouillage, fixées sur l'étrier et coulissant dans les alésages d'une chape ou dans le diamètre intérieur d'un manchon lui-même solidaire de la chape. Ces deux colonnettes montées symétriquement de part et d'autre de l'axe de poussée du piston ont l'inconvénient d'être sensibles aux vibrations par effet de battements angulaires ou de surtension en fréquence, principalement dans le cas d'usure maximale des patins, lors de la sortie extrême des colonnettes de leur alésage en raison de l'augmentation du jeu' angulaire relatif entre alésage et partie non dégagée de la colonnette. Many sliding devices are already known on top of the disk, mainly two columns, one of guide, the other of locking, fixed on the stirrup and sliding in the bores of a yoke or in the inner diameter of a sleeve itself secured to the yoke. These two columns symmetrically mounted on either side of the piston thrust axis have the disadvantage of being sensitive to vibrations by angular beats or frequency overvoltage, mainly in the case of maximum wear of the pads at the extreme exit of the columns of their bore due to the increase in clearance relative angular between bore and not cleared portion of the column.
Ces colonnettes étant fixées d'un même côté du disque dans l'étrier, il s'en suit que le côté de fixation nécessite une parfaite perpendicularité entre le plan d'accostage des colonnettes et l'axe de ces colonnettes, ainsi qu'un très bon parallélisme entre les colonnettes elles-mêmes, du fait des raideurs antagonistes d'ancrages situés d'un même côté, d'où des tolérances d'exécution serrées, le moindre écart de réalisation entre l'alésage de coulissement sur la chape et la position géométrique de montage de la colonnette induisant des contraintes préjudiciables de coulissement. Dans ce type de conception<B>-</B> cf. figure 4<B>-</B> le nez d'étrier (partie de l'étrier<B>(1)</B> située<B>à</B> l'opposé de l'entrée de l'alésage du piston), et le piston<B>(9),</B> se trouvent toujours aux fortes accélérations, selon les conceptions connues, en bascule autour de l'axe (c#a,) reliant les, deux points d'ancrage des colonnettes (2) et <B>(5)</B> du fait de la flexibilité de ces dernières. Au freinage, dans ce type de conception, les couples de rappel
et générés entre colonnettes (2)
et<B>(5)</B> et étrier<B>(1)</B> s'additionnent et forment un couple résultant Ce couple
participe<B>à</B> l'usure en biais<B>(6)</B> des patins<B>(8)</B> et<B>(F)</B> lors
des flexions successives des colonnettes, par pseudo-rotation de l'étrier<B>(1)</B> autour d'un axe perpendiculaire<B>à</B> sa voûte. Cette pseudo-rotation au freinage de l'étrier<B>(1)</B> sous l'effet du couple
peut provoquer en outre des arcs-boutements en bout des colonnettes (2) et<B>(5)</B> préjudiciables au coulissement et donc<B>à</B> la trainée. Enfin, toujours dans ce type de conception, la protection anti-corrosion des coulissements fait souvent appel selon le choix des constructeurs<B>à</B> des soufflets de protection des colonnettes augmentant le couple résiduel par suite des variations de température de l'air emprisonné. These columns being fixed on the same side of the disk in the caliper, it follows that the fixing side requires a perfect perpendicularity between the docking plane of the columns and the axis of these columns, and a very good parallelism between the columns themselves, because of antagonistic stiffness anchors located on the same side, resulting in tight execution tolerances, the slightest difference in embodiment between the sliding bore on the yoke and the geometric mounting position of the column inducing damaging sliding stresses. In this type of design <B> - </ B> cf. Figure 4 <B> - </ B> Stirrup nose (part of the caliper <B> (1) </ B> located <B> to </ B> the opposite of the entry of the piston bore), and the piston <B> (9), </ B> are always at high accelerations, according to the known designs, tilts around the axis (c # a,) connecting the two points of anchorage of the balusters (2) and <B> (5) </ B> due to the flexibility of the latter. When braking, in this type of design,
and generated between balusters (2)
and <B> (5) </ B> and caliper <B> (1) </ B> add up and form a resulting couple
participates <B> in <B> wear <B> (6) </ B> of the <B> (8) </ B> and <B> (F) </ B> pads when
successive bending of the columns, pseudo-rotation of the stirrup <B> (1) </ B> around a perpendicular axis <B> to </ B> its vault. This pseudo-rotation while braking the caliper <B> (1) </ B> under the effect of the torque
can also cause end-stops at the end of the columns (2) and <B> (5) </ B> detrimental to the sliding and therefore <B> to </ B> the drag. Finally, still in this type of design, the anti-corrosion protection of the sliding is often used according to the choice of the manufacturers <B> to </ B> of the bellows of protection of the columns increasing the residual torque due to the variations of temperature of the trapped air.
Selon figure<B>1,</B> le système, objet de l'invention, comporte deux colonnettes (2) et<B>(5),</B> coulissant au-dessus du disque<B>(7),</B> montées en opposition avec ancrage de part et d'autre du disque<B>(7),</B> l'une fixée sur l'étrier<B>(1)</B> et l'autre sur la chape<B>(10),</B> et permet d'éviter tous ces inconvénients. Par dissymétrie d'architecture, recourant au mode vibratoire antagoniste, il neutralise au freinage les bruits émis par l'une des colonnettes (2) ou<B>(5),</B> annulant dans un large spectre les phénomènes d'harmoniques ou de résonance par émission de contre-bruits de mêmes fréquences mais opposés en phase. According to figure <B> 1, </ B> the system, object of the invention, comprises two columns (2) and <B> (5), </ B> sliding above the disk <B> (7) , </ B> mounted in opposition with anchorage on both sides of the disk <B> (7), </ B> one fixed on the stirrup <B> (1) </ B> and the other on the coping <B> (10), </ B> and avoids all these disadvantages. By dissymmetry of architecture, resorting to the vibratory mode antagonist, it neutralizes under braking the noises emitted by one of the columns (2) or <B> (5), </ B> canceling in a broad spectrum the phenomena of harmonics or resonance by emission of counter-noise of the same frequencies but opposite in phase.
L'interposition de manchons caoutchouc<B>(3)</B> et<B>(6) -</B> cf. figure 2<B>-</B> amortissant les sollicitations en battement des colonnettes amplifie l'effet recherché par filtration des bruits entre chape et étrier. Les ancrages étant placés en diagonale au-dessus du disque, selon un axe (a2a.), avec évidement au centre<B>(A)</B> de la voûte de l'étrier<B>(1),</B> les phénomènes de mode propre seront par construction écartés. Les flexibilités inverses et conjuguées du montage en opposition des colonnettes (2) et<B>(5)</B> permettent d'avoir des déplacements parallèles de l'étrier<B>(1)</B> lors du freinage. Ainsi au freinage<B>-</B> selon figure<B>5 -</B> il est constaté que les couples
et
de rappel des colonnettes (2) et<B>(5)</B> s'opposent et s'annulent sensiblement au centre de la voûte de l'étrier<B>(1)</B> avec pour effet principal de ne point provoquer la moindre sollicitation en rotation de l'étrier<B>(1),</B> rotation participant<B>à</B> l'origine des biais sur les patins<B>(8)</B> et (8') comme dans le cas des freins traditionnels. Dans cette conception particulière les moments de flexion inverses
et se neutralisant mutuellement les
colonnettes ne travaillent plus qu'en cisaillement simple, sans arc-boutement puisque le déplacement de l'étrier est toujours parallèle<B>à</B> l'axe de poussée du piston<B>(9),</B> ce qui permet de réduire la longueur et le diamètre de ces colonnettes sans porter préjudice<B>à</B> la résistance et<B>à</B> la performance globales du frein. Cette conception permet enfin d'encaisser le couple de freinage
avec une répartition en équipression sur toute la longueur de la colonnette permettant d'utiliser valablement des manchons amortissant sans risque de dépasser les contraintes admissibles et de provoquer des phénomènes d'extrusion, et ceci bien que des coulissements métal sur métal avec capuchon de protection puissent être utilisés dans le cas des colonnettes inversées. The interposition of rubber sleeves <B> (3) </ B> and <B> (6) - </ B> cf. figure 2 <B> - </ B> damping the beating stresses of the balusters amplifies the desired effect by filtering the noise between the yoke and the stirrup. The anchors being placed diagonally above the disc, along an axis (a2a.), With recess in the center <B> (A) </ B> of the stirrup arch <B> (1), </ B> the phenomena of clean mode will be by construction excluded. The inverse and conjugate flexibilities of the assembly in opposition of the balusters (2) and <B> (5) </ B> make it possible to have parallel movements of the stirrup <B> (1) </ B> during braking. So under braking <B> - </ B> according to figure <B> 5 - </ B> it is found that couples
and
of the balusters (2) and <B> (5) </ B> oppose and cancel each other substantially in the center of the vault of the stirrup <B> (1) </ B> with the main effect of do not cause the slightest urging in rotation of the stirrup <B> (1), </ B> participating rotation <B> to </ B> the origin of the bias on the skids <B> (8) </ B > and (8 ') as in the case of traditional brakes. In this particular design the inverse bending moments
and mutually neutralizing each other
Columns work only in simple shear, without jamming since the displacement of the caliper is always parallel <B> to </ B> the axis of thrust of the piston <B> (9), </ B> which allows to reduce the length and diameter of these columns without damaging <B> to </ B> the resistance and <B> to </ B> the overall performance of the brake. This design finally makes it possible to cash in the braking torque
with an equipressure distribution over the entire length of the column allowing valid use damping sleeves without risk of exceeding the allowable stresses and causing extrusion phenomena, and this although metal-on-metal sliding with protective cap can be used in the case of inverted columns.
Comparé aux systèmes connus avec deux colonnettes fixées d'un même côté du disque et générant des biais en friction, le cas de deux colonnettes (2) et<B>(5)</B> antagonistes et de même flexibilité simultanée (isoflexibilité) conduit<B>à</B> considérer sous couple une déformation théorique en "S" fonction de la flexibilité réelle de celles-ci<B>-</B> cf. figure<B>1 -.</B> Cette déformation en "S" limite le coulissement des colonnettes (2) et<B>(5)</B> et donc les bruits, par autocentrage de l'étrier<B>(1)</B> sur le disque<B>(7)</B> et bandage des colonnettes dans leur alésage par les chasses (Pl <B>)</B> et (P2<B>)</B> avec pour avantage la stabilisation du frein au freinage. Au lâcher du freinage cette même déformation en "S" aide au recul des patins<B>(8)</B> et (8'). <B>Il</B> est possible avec une telle architecture d'avoir des colonnettes (2) et<B>(5)</B> de plus faible diamètre tout en ayant une bonne raideur et un bon coulissement en fin d'usure des patins grâce<B>à</B> la caractéristique d'isoflexibilité du système et<B>à</B> son peu de sensibilité en NVH, critère bruits et vibrations. Compared to known systems with two columns fixed on the same side of the disk and generating frictional biases, the case of two columns (2) and <B> (5) </ B> antagonists and of the same simultaneous flexibility (isoflexibility) leads <B> to </ B> consider under torque a theoretical deformation in "S" according to the real flexibility of these <B> - </ B> cf. figure <B> 1 -. </ B> This "S" deformation limits the sliding of the balusters (2) and <B> (5) </ B> and therefore the noises, by self-centering the caliper <B> (1) </ B> on the disk <B> (7) </ B> and bandage of the balusters in their bore by the hunts (Pl <B>) </ B> and (P2 <B>) </ B > with the advantage of stabilizing the braking brake. At the release of braking this same deformation in "S" helps the retreat of the pads <B> (8) </ B> and (8 '). <B> It </ B> is possible with such an architecture to have balusters (2) and <B> (5) </ B> of smaller diameter while having a good stiffness and a good sliding at the end of skid wear thanks to the system's isoflexibility characteristic and its low NVH sensitivity, noises and vibrations criterion.
Selon cette conception les colonnettes seront coulissantes au-dessus du disque, de préférence dans des manchons<B>(3)</B> et<B>(6)</B> amortissants graissés et/ou autolubrifiants, avec racleur antipoussière en extrémité<B>-</B> cf. figure 2<B>- .</B> Elles seront en acier inoxydable ou protégées contre la corrosion, avec empreinte de vissage/dévissage. L'ouverture de l'étrier<B>(1)</B> pour changement des patins<B>(8)</B> et<B>(W)</B> se fera par dépose de l'une des colonnettes, cette colonnette pouvant pour raison de sécurité après montage être verrouillée par une épingle (4) traversant de part en part l'extrémité de son filetage ou par tout autre moyen provoquant le même résultat tel un contre-écrou. La colonnette (2) fixée sur l'étrier<B>(1)</B> coulisse dans le manchon<B>(3),</B> autolubrifiant ou graissé, solidaire d'un alésage de la chape<B>(10);</B> l'autre colonnette<B>(5)</B> est fixée dans le bras de la chape<B>(10)</B> et coulisse dans le manchon<B>(6)</B> monté serré dans un alésage de l'étrier<B>(1)</B> et de même nature que le manchon<B>(3).</B> Selon une autre conception c'est la colonnette intérieure qui sera démontable pour le changement des patins<B>(8)</B> et<B>(8%</B> dans ce cas l'alésage de la chape contenant le manchon<B>(3)</B> et la colonnette (2) ne sera pas obligatoirement débouchant côté roue et il n'y aurait plus nécessité du contre-écrou ou de l'épingle (4). According to this design the balusters will slide over the disc, preferably in greased and / or self-lubricating <B> (3) </ B> and <B> (6) </ B> damping sleeves, with dust scraper in place. end <B> - </ B> cf. figure 2 <B> -. </ B> They will be stainless steel or protected against corrosion, with screwing / unscrewing impression. The opening of the caliper <B> (1) </ B> to change the pads <B> (8) </ B> and <B> (W) </ B> will be done by removing one Columns, this column may for safety reasons after mounting be locked by a pin (4) passing through the end of its thread or by any other means causing the same result as a lock nut. The column (2) fixed on the bracket <B> (1) </ B> slides in the sleeve <B> (3), </ B> self-lubricating or greased, secured to a bore of the yoke <B> (10) </ B> the other balancer <B> (5) </ B> is fixed in the arm of the clevis <B> (10) </ B> and slides in the sleeve <B> (6) ) </ B> mounted tightly in a bore of the caliper <B> (1) </ B> and of the same nature as the sleeve <B> (3). </ B> According to another design this is the internal column which will be removable for the change of the skates <B> (8) </ B> and <B> (8% </ B> in this case the bore of the yoke containing the sleeve <B> (3) < / B> and the column (2) will not necessarily open on the wheel side and there is no need for the locknut or the pin (4).
Lorsque le piston<B>(9)</B> plaque par effet de la pression hydraulique les patins<B>(8)</B> et (8') contre le disque<B>(7)</B> les mouvements des colonnettes (2) et<B>(5)</B> sont des mouvements de traction inverses, l'une (2) sortant du manchon<B>(3),</B> l'autre<B>(5)</B> sortant du manchon<B>(6).</B> Chaque freinage ayant tendance<B>à</B> générer un couple de pivotement de la roue, il serait avantageux de tenir compte de l'orientation (a2a3 <B>)</B> de l'axe reliant les deux points d'ancrage pour générer une contre-réaction sur la chape<B>(10)</B> du vecteur poussée des patins<B>(8)</B> et<B>(F)</B> vers le porte-fusée en opposition avec le couple de pivotement précité. When the piston <B> (9) </ B> plates by the effect of the hydraulic pressure the pads <B> (8) </ B> and (8 ') against the disk <B> (7) </ B> the movements of the balusters (2) and <B> (5) </ B> are reverse pulling movements, one (2) coming out of the sleeve <B> (3), </ B> the other <B > (5) </ B> coming out of the sleeve <B> (6). </ B> As each braking has a tendency <B> to </ B> to generate a pivoting torque of the wheel, it would be advantageous to take account of the orientation (a2a3 <B>) </ B> of the axis connecting the two anchor points to generate a feedback on the clevis <B> (10) </ B> of the thrust vector of the skates <B > (8) </ B> and <B> (F) </ B> to the stub axle in opposition to the aforementioned pivoting torque.
Selon une option particulière les colonnettes (2) et<B>(5)</B> pourraient être fixées respectivement sur l'étrier<B>(1)</B> et sur la chape<B>(10)</B> par une vis ou un écrou en bout de colonnette. De même que le coulissement pourrait être protégé par un manchon en élastomère, graissé ou autolubrifiant. According to a particular option the balusters (2) and <B> (5) </ B> could be fixed respectively on the bracket <B> (1) </ B> and on the clevis <B> (10) </ B> by a screw or a nut at the end of the column. Just as the sliding could be protected by an elastomer sleeve, greased or self-lubricating.
Selon une autre variante, les colonnettes (2) et<B>(5) -</B> cf. figure<B>3 -</B> comporteraient une tête avec empreinte de vissage/dévissage, type vis CHC par exemple; les deux manchons (3') et<B>(6)</B> étant montés serrés sur ces colonnettes, autolubrifiants ou graissés sur leur périphérie extérieure, ils coulisseraient par leur diamètre extérieur avec un jeu légèrement gras d'un côté dans un alésage de la chape, de l'autre côté dans un alésage de l'étrier, les alésages intérieurs des manchons restant évidemment fixes par rapport aux colonnettes afin d'éviter le retroussage du manchon lors du coulissement. Le manchon pourrait être surmoulé sur la colonnette et pourrait comporter sur sa surface extérieure des ondulations facilitant le glissement et le logement de la graisse tout en assurant une étanchéité renforcée<B>à</B> chaque sortie d'ondulation - cf. figure 3'- <B>.</B> According to another variant, the balusters (2) and <B> (5) - </ B> cf. figure <B> 3 - </ B> would have a head with screw-in / unscrewing screw, such as CHC screws; the two sleeves (3 ') and <B> (6) </ B> being mounted tight on these columns, self-lubricating or greased on their outer periphery, they would slide by their outer diameter with a lightly greasy game on one side in a boring of the yoke, on the other side in a bore of the yoke, the inner bores of the sleeves obviously remaining fixed relative to the columns in order to avoid rolling the sleeve during sliding. The sleeve could be overmoulded on the column and could have on its outer surface corrugations facilitating the sliding and housing of the grease while ensuring a reinforced seal <B> to </ B> each corrugation output - cf. figure 3'- <B>. </ B>
Bien évidemment les descriptions qui précèdent ne limitent pas les revendications du système<B>;</B> d'autres présentations pourraient être effectuées en fonction de l'évolution des technologies utilisées par l'homme de l'art tout en restant dans le cadre de l'invention (un frein<B>à</B> disque avec les deux colonnettes implantées en opposition, tête-bêche, donnant une isoflexibilité autocentrante - cf. figure<B>1 -</B> par les chasses (Pl <B>)</B> et (92<B>)</B> du système au freinage sous couple peu sensible aux vibrations et avec un couple résultant au centre de la voûte d( l'étrier pratiquement nul au freinage).Of course, the foregoing descriptions do not limit the claims of the system; other presentations could be made according to the evolution of the technologies used by those skilled in the art while remaining within the scope of the present invention. of the invention (a brake <B> to </ B> disk with the two columns implanted in opposition, head to tail, giving a self-centering isoflexibility - see figure <B> 1 - </ B> by hunts ( Pl <B>) </ B> and (92 <B>) </ B> of the braking system under low vibration torque and with a resulting torque in the center of the vault d (the caliper practically zero braking) .
Claims (1)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR9907524A FR2795147B1 (en) | 1999-06-15 | 1999-06-15 | DISC BRAKE WITH "ZERO NOISE SECOND GENERATION" REVERSE COLUMNS |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR9907524A FR2795147B1 (en) | 1999-06-15 | 1999-06-15 | DISC BRAKE WITH "ZERO NOISE SECOND GENERATION" REVERSE COLUMNS |
Publications (2)
Publication Number | Publication Date |
---|---|
FR2795147A1 true FR2795147A1 (en) | 2000-12-22 |
FR2795147B1 FR2795147B1 (en) | 2003-09-05 |
Family
ID=9546777
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
FR9907524A Expired - Fee Related FR2795147B1 (en) | 1999-06-15 | 1999-06-15 | DISC BRAKE WITH "ZERO NOISE SECOND GENERATION" REVERSE COLUMNS |
Country Status (1)
Country | Link |
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FR (1) | FR2795147B1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002099303A1 (en) * | 2001-05-31 | 2002-12-12 | Robert Bosch Corporation | Floating caliper brake guide pin arrangement |
DE102014019112A1 (en) * | 2014-12-19 | 2016-06-23 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Disc brake for a commercial vehicle |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1573305A (en) * | 1976-02-12 | 1980-08-20 | Girling Ltd | Vehicle brakes |
GB2041122A (en) * | 1979-01-18 | 1980-09-03 | Lucas Industries Ltd | Disc brakes |
US4347917A (en) * | 1976-12-07 | 1982-09-07 | Sumitomo Electric Industries, Ltd. | Floating type disc brake |
US5226510A (en) * | 1989-04-28 | 1993-07-13 | Bendix Europe Services Techniques | Disc brake with slidable caliper |
FR2747751A1 (en) * | 1996-04-22 | 1997-10-24 | Bosch Syst Freinage | Disc brake |
-
1999
- 1999-06-15 FR FR9907524A patent/FR2795147B1/en not_active Expired - Fee Related
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1573305A (en) * | 1976-02-12 | 1980-08-20 | Girling Ltd | Vehicle brakes |
US4347917A (en) * | 1976-12-07 | 1982-09-07 | Sumitomo Electric Industries, Ltd. | Floating type disc brake |
GB2041122A (en) * | 1979-01-18 | 1980-09-03 | Lucas Industries Ltd | Disc brakes |
US5226510A (en) * | 1989-04-28 | 1993-07-13 | Bendix Europe Services Techniques | Disc brake with slidable caliper |
FR2747751A1 (en) * | 1996-04-22 | 1997-10-24 | Bosch Syst Freinage | Disc brake |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002099303A1 (en) * | 2001-05-31 | 2002-12-12 | Robert Bosch Corporation | Floating caliper brake guide pin arrangement |
DE102014019112A1 (en) * | 2014-12-19 | 2016-06-23 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Disc brake for a commercial vehicle |
Also Published As
Publication number | Publication date |
---|---|
FR2795147B1 (en) | 2003-09-05 |
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