WO2005106282A1 - Hydraulic rebound stop for hydraulic shock absorbers - Google Patents

Hydraulic rebound stop for hydraulic shock absorbers Download PDF

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Publication number
WO2005106282A1
WO2005106282A1 PCT/ES2005/000147 ES2005000147W WO2005106282A1 WO 2005106282 A1 WO2005106282 A1 WO 2005106282A1 ES 2005000147 W ES2005000147 W ES 2005000147W WO 2005106282 A1 WO2005106282 A1 WO 2005106282A1
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WO
WIPO (PCT)
Prior art keywords
hydraulic
ring
chamber
shock absorbers
rod
Prior art date
Application number
PCT/ES2005/000147
Other languages
Spanish (es)
French (fr)
Inventor
Pedro ARMENDÁRIZ SÁNCHEZ
Mario Peru Beramendi
Original Assignee
Ap Amortiguadores, S.A.
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Filing date
Publication date
Application filed by Ap Amortiguadores, S.A. filed Critical Ap Amortiguadores, S.A.
Publication of WO2005106282A1 publication Critical patent/WO2005106282A1/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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/58—Stroke limiting stops, e.g. arranged on the piston rod outside the cylinder
    • F16F9/585—Stroke limiting stops, e.g. arranged on the piston rod outside the cylinder within the cylinder, in contact with working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
    • F16F9/49—Stops limiting fluid passage, e.g. hydraulic stops or elastomeric elements inside the cylinder which contribute to changes in fluid damping

Definitions

  • HYDRAULIC REBOUND BUMPER FOR HYDRAULIC SHOCK ABSORBERS OBJECT OF THE INVENTION refers to a hydraulic rebound stop for hydraulic shock absorbers, these importantly participating in the suspension of vehicles in a manner that this new stop softens its annual recovery of the shock absorber when there is a distance between the wheel and the chassis of the vehicle, either as a result of a depression or bump in the ground or simply during the recovery of the shock itself tending to place the shock absorber in an equilibrium position.
  • Shock absorbers that are preferably used in vehicles, regardless of the type, are part of the suspension system, together with the wheels and the crossbows or springs.
  • shock absorbers In the case of hydraulic shock absorbers, these are made up of a cylinder through which a piston connected to an actuating rod runs, the piston defining inside the cylinder two chambers, one compression and one traction, both flooded with fluid, Generally oil In the movements of the wheels with respect to the chassis, displacements of rise and fall of the same ones take place and the shock absorber works in this case, displacing the drive rod in the sense that the piston compresses the fluid contained inside the cylinder. When the shock absorber operates on traction, that is, when the wheel moves away from the chassis, it may occur that it encounters a depression, which can cause abrupt displacement and a blow that is transmitted to the end of the traction stroke. bodywork.
  • the hydraulic rebound stop corresponding to the invention patent No. 200000532, improves the stops described above and basically comprises in the traction chamber a head of coaxial closure to the rod that closes tightly against the walls of a tubular body, dividing this chamber into two subchambers, so that said closing head can be moved against a spring by the action of a closing washer that rests on a wall of a bushing integral with the actuating rod, defining between both subchambers several steps of strategically placed and finely calibrated fluid.
  • the hydraulic rebound stop of the invention is applicable to hydraulic shock absorbers for vehicles which in principle have a compression chamber and a traction chamber, which in turn is divided into two sub-chambers: one upper and one lower, separate both by a closing head. Starting from this premise, ' what is about is to soften and slow down the displacement of the rod-piston assembly essentially in the direction of traction, reaching a point in the race where the hydraulic stop system begins to operate.
  • the closing head that separates both subchambers comprises a rebound stop washer coupled around the piston rod and axially retained by a retaining element that is in correspondence with the lower subchamber. It is also characterized in that it comprises an annular rubber stop fitted around the piston rod, while it sits on the free base of the washer, such an annular rubber stop being in correspondence with the upper subchamber.
  • This rubber stop prevents metal-to-metal contact between parts when the shock absorber is in the position of maximum extension.
  • Another feature is the incorporation of a split ring located in an annular channel of the washer, at the same time that said ring is adjusted, in the final path of the shock absorber towards the extension position, against the inner surface of a socket embedded in the section end of the interior of the shock absorber in correspondence with the traction chamber, so that during the movement and movement of the shock absorber the ring is in contact against the inner surface of said bushing.
  • the bushing comprises an extreme conical portion in correspondence with the bottom edge.
  • This conical portion facilitates the guiding and initial engagement of the ring when it is inserted into the bushing, that is, when the ring during the final stroke of the head and rod-piston assembly is directed towards the extended position of the shock absorber.
  • a narrow permanent calibrated step Between the free ends of the split ring is a narrow permanent calibrated step.
  • the rebound stop washer In the event that the rebound stop washer reaches the end of the stroke, as mentioned above, extending to the maximum allowed for the shock absorber, it is the rubber rebound stop that is in charge of avoiding metal-to-metal contacts between parts.
  • the hydraulic load is also controlled by the different calibrated steps mentioned above. The first corresponding to the opening of the ring (same opening that causes tensile loads) and the second will be determined by at least one upper window of the ring. With these two steps the compression load can be regulated even by canceling it if necessary. Said windows are essentially determined by small recesses that affect at least one of the flat faces of said ring.
  • a part of a corresponding hydraulic damper 1 is shown with the traction chamber 2 separated from the compression chamber by a piston not shown in the figures, nor is the compression chamber, so that the end of such traction chamber 2 can be said to be sealed in a conventional manner .
  • the shock absorber 1 is of the type that includes two coaxial tubular bodies 3 and 4, where the piston evidently fits into the inner tubular body 3.
  • a head 5 is also included located in the traction chamber 2 which in turn separates a upper subchamber 6 corresponding to the end closure of that traction chamber 2 and a lower subchamber 7 that would be limited by the piston not shown in the figures.
  • the hydraulic stop consists of a precise regulation during the passage of fluid from the upper subchamber 6 to the lower subchamber 7 in the final section of the extension of the shock absorber 2 to brake and soften such extension.
  • the hydraulic rebound stop also offers other regulated loads at the start of the compression stroke.
  • the head 5 coupled to the rod 8 of the shock absorber 1 comprises an affected washer 9 of an annular channel 10 where a split ring 11 is housed between whose ends a narrow calibrated fluid passage space 12 is defined.
  • the annular channel 10 has a greater height than the ring 11, at the same time that it is adjusted by its outer side face against an inner surface of a bushing 13 embedded in an end section of the inner tubular body 3 that limits an extreme part of the traction chamber 2.
  • the head 5 complements with a rubber stop 14 fitted around the rod 8, while it sits on the upper base of the washer 9.
  • the lower base includes an annular recess adapted to an element of axial retention 15 integral with rod 8 and located in correspondence with the lower sub-chamber 7, the rubber stop 14 being located in correspondence with the upper sub-chamber 6.
  • This stop prevents metal parts from contacting each other in the most extended position of the shock absorber.
  • the bushing 13 includes a conical end portion 16 corresponding to the lower sub chamber 7, thus facilitating the entry of the split ring 11 into the bushing 13 in the final section of the extension of the shock absorber 1.
  • the ring 11 incorporates the recesses 17 as second passages of the fluid between the subchambers 6 and 7, the other step being the narrow calibrated space 12 limited by the ends of the split ring 11.

Abstract

The invention relates to shock absorbers comprising a compression chamber and a pull chamber (2) which are separated by a piston which is solidly connected to a rod (8) that is disposed inside a tubular body (3). According to the invention, the pull chamber comprises an upper sub-chamber (6) and a lower (7) sub-chamber which are separated by a head (5) which is connected to the rod (8). The invention is essentially characterised by the structure with which the head (5) is equipped in order to regulate the passage of fluid between the two sub-chambers and, above all, to slow down and smooth the final extension of the shock absorber (1) when the wheel is at the farthest position from the chassis of the vehicle. The aforementioned head essentially consists of a washer (9) comprising an annular channel for housing a ring (11) which is pressed against an end bushing (13) when the shock absorber is in the extreme extended position. Furthermore, the ends (12) of the ring (11) limit a first calibrated passage and comprise recesses (15) for a second fluid passage.

Description

TOPE DE REBOTE HIDRÁULICO PARA AMORTIGUADORES HIDRÁULICOS OBJETO DE LA INVENCIÓN La presente invención según se expresa en el enunciado de esta memoria descriptiva, se refiere a un tope de rebote hidráulico para amortiguadores hidráulicos, participando éstos de forma importante en la suspensión de los vehículos de manera que este nuevo tope suaviza sus ancialmente la recuperación del amortiguador cuando se produce un alejamiento entre la rueda y el chasis del vehículo, bien como consecuencia de una depresión o bache en el suelo o simplemente durante la recuperación del amortiguador propiamente dicha tendente a situar el amortiguador en una posición de equilibrio. ANTECEDENTE DE LA INVENCIÓN Los amortiguadores que se emplean preferentemente en vehículos, independientemente del tipo que sean, forman parte del sistema de suspensión, conjuntamente con las ruedas y las ballestas o muelles. En el caso de amortiguadores hidráulicos, éstos se conforman por un cilindro por cuyo interior discurre un pistón conectado a un vastago de accionamiento, definiendo el pistón en el interior del cilindro dos cámaras, una de compresión y otra de tracción, inundadas ambas de fluido, generalmente aceite. En los movimientos de las ruedas respecto al chasis, se producen desplazamientos de subida y bajada de las mismas y el amortiguador funciona en este caso, desplazando el vastago de accionamiento en el sentido de que el pistón comprime el fluido contenido en el interior del cilindro. Cuando el amortiguador funciona a tracción, es decir, cuando la rueda se aleja del chasis, puede ocurrir que ésta encuentre una depresión, lo que puede provocar al final del recorrido de la carrera de tracción un desplazamiento brusco y un golpe que se trasmite a la carrocería. Se han previsto medios de tope de rebote que amortiguan dicho golpe, generalmente determinados por piezas de plástico o incluso topes de rebote de tipo hidráulico que utilizan mecanismos simples, que añaden poco amortiguamiento o mucha dispersión funcional . Por otro lado, el tope de rebote hidráulico correspondiente a la patente de invención n° 200000532, mejora los topes descritos anteriormente y comprende básicamente en la cámara de tracción un cabezal de cierre coaxial al vastago que cierra estancamente contra las paredes de un cuerpo tubular, dividiendo esta cámara en dos subcámaras, de manera que dicho cabezal de cierre puede desplazarse en contra de un resorte por la acción de una arandela de cierre que apoya en una valona de un casquillo solidario del vastago de accionamiento, definiéndose entre ambas subcámaras varios pasos de fluido estratégicamente situados y finamente calibrados. DESCRIPCIÓN DE LA INVENCIÓN El tope de rebote hidráulico de la invención es aplicable a amortiguadores hidráulicos para vehículos que cuentan en principio con una cámara de compresión y una cámara de tracción, dividida ésta a su vez en dos subcámaras: una superior y otra inferior, separadas ambas mediante un cabezal de cierre. Partiendo de esta premisa,' de lo que se trata es de suavizar y frenar el desplazamiento del conjunto vastago- pistón esencialmente en el sentido de tracción, llegando un punto de la carrera donde el sistema de tope hidráulico comienza a actuar. Este momento en que comienza a actuar el tope hidráulico corresponderá con un tramo final de esa carrera en el sentido de tracción hacia la máxima dimensión del amortiguador, es decir, cuando el fluido está pasando de forma más controlada desde la cámara de tracción a la cámara de compresión y también cuando el fluido pasa desde la subcámara superior a la subcámara inferior. Se caracteriza porque el cabezal de cierre que separa ambas subcámaras, comprende una arandela tope rebote acoplada alrededor del vastago-pistón y retenida axialmente por un elemento de retención que se encuentra en correspondencia con la subcámara inferior. También se caracteriza porque comprende un tope anular de goma ajustado alrededor del vastago-pistón, a la vez que asienta sobre la base libre de la arandela, encontrándose tal tope anular de goma en correspondencia con la subcámara superior. Este tope de goma evita el contacto de metal contra metal entre piezas cuando el amortiguador está en la posición de máxima extensión. Otra característica es la incorporación de un anillo partido ubicado en un canal anular de la arandela, a la vez que tal anillo se ajusta, en el recorrido final del amortiguador hacia la posición de extensión, contra la superficie interior de un casquillo encastrado en el tramo final del interior del amortiguador en correspondencia con la cámara de tracción, de forma que durante el desplazamiento y movimiento del amortiguador el anillo está en contacto contra la superficie interna del citado casquillo. Otra característica es que el casquillo comprende una porción cónica extrema en correspondencia con el borde de abajo. Esta porción cónica facilita el guiado y encaje inicial del anillo cuando se introduce dentro del casquillo, o sea, cuando el anillo durante el recorrido final del cabezal y conjunto vastago-pistón se dirigen hacia la posición extendida del amortiguador. Entre los extremos libres del anillo partido resulta un estrecho paso calibrado permanente. Así pues, en el momento en que el anillo entra dentro del casquillo, el aceite que se encuentra en la subcámara superior se ve obligado a pasar a la subcámara inferior a través del paso permanente permitido por el citado anillo (el anillo no está cerrado 360°, o sea que tiene una pequeña abertura calibrada) , dando así una carga hidráulica extra. En caso de que la arandela tope rebote llegue al final de carrera, tal como se ha referido anteriormente, extendiéndose al máximo admitido para el amortiguador, es el tope rebote de goma el encargado de evitar contactos metal contra metal entre piezas. Durante la vuelta o carrera de compresión, la carga hidráulica también está controlada por los diferentes pasos calibrados citados anteriormente. El primero correspondiente con la abertura del anillo (misma abertura causante de las cargas a tracción) y el segundo estará determinado por al menos una ventana superior del anillo. Con estos dos pasos puede regularse la carga de compresión incluso anulándola si fuese necesario. Dichas ventanas están determinadas esencialmente por unas pequeños rebajes que afectan al menos a una de las caras planas de dicho anillo. A continuación, para facilitar una mejor comprensión de esta memoria descriptiva y formando parte integrante de la misma se acompañan unas figuras en las que con carácter ilustrativo y no limitativo se ha representado el objeto de la invención. BREVE DESCRIPCIÓN DE LOS DIBUJOS Figura 1.- Muestra una vista en sección de una parte de un amortiguador hidráulico correspondiente con la cámara de tracción, incluyendo dicha parte un tope de rebote hidráulico que es el objeto de la invención. Figura 2.- Muestra una vista de un anillo partido que forma parte del conjunto de la invención. DESCRIPCIÓN DE LA FORMA DE REALIZACIÓN PREFERIDA Considerando la numeración adoptada en las figuras y atendiendo especialmente a la figura 1, se muestra una parte de un amortiguador hidráulico 1 correspondiente con la cámara de tracción 2 separada de la cámara de compresión por un pistón no representado en las figuras, como tampoco lo está la cámara de compresión, de manera que el extremo de tal cámara de tracción 2 se puede decir que está cerrada herméticamente de forma convencional . El amortiguador 1 es del tipo de los que incluyen dos cuerpos tubulares coaxiales 3 y 4, donde el pistón se ajusta evidentemente en el cuerpo tubular interior 3. Se incluye también un cabezal 5 ubicado en la cámara de tracción 2 que separa a su vez una subcámara superior 6 correspondiente con el cierre extremo de esa cámara de tracción 2 y una subcámara inferior 7 que estaría limitada por el pistón no representado en las figuras. Partiendo de esta premisa, el tope hidráulico consiste en una regulación precisa durante el paso de fluido desde la subcámara superior 6 a la subcámara inferior 7 en el tramo final de la extensión del amortiguador 2 para frenar y suavizar tal extensión. El tope de rebote hidráulico también ofrece otras cargas reguladas en el inicio de la carrera de compresión. Para ello, el cabezal 5 acoplado al vastago 8 del amortiguador 1 comprende una arandela 9 afectada de un canal anular 10 donde se aloja un anillo partido 11 entre cuyos extremos se define un estrecho espacio calibrado 12 de paso de fluido. El canal anular 10 posee una mayor altura que el anillo 11, a la vez que éste se ajusta por su cara lateral exterior contra una superficie interna de un casquillo 13 encastrado en un tramo extremo del cuerpo tubular interior 3 que limita una parte extrema de la cámara de tracción 2. El cabezal 5 de complementa con un tope de goma 14 ajustado alrededor del vastago 8, a la vez que asienta sobre la base superior de la arandela 9. En cambio, la base inferior incluye un rebaje anular adaptado a un elemento de retención axial 15 solidario del vastago 8 y ubicado en correspondencia con la subcámara inferior 7 , ubicándose el tope de goma 14 en correspondencia con la subcámara superior 6. Este tope evita que en la posición más extendida del amortiguador contacten partes metálicas entre sí . El casquillo 13 incluye un porción extrema cónica 16 que se corresponde con la subcámara inferior 7, facilitándose así la entrada del anillo partido 11 dentro del casquillo 13 en el tramo final de la extensión del amortiguador 1. Por último, el anillo 11 incorpora los rebajes 17 como segundos pasos del fluido entre las subcámaras 6 y 7, siendo el otro paso el estrecho espacio calibrado 12 limitado por los extremos del anillo partido 11. HYDRAULIC REBOUND BUMPER FOR HYDRAULIC SHOCK ABSORBERS OBJECT OF THE INVENTION The present invention, as expressed in the statement of this specification, refers to a hydraulic rebound stop for hydraulic shock absorbers, these importantly participating in the suspension of vehicles in a manner that this new stop softens its annual recovery of the shock absorber when there is a distance between the wheel and the chassis of the vehicle, either as a result of a depression or bump in the ground or simply during the recovery of the shock itself tending to place the shock absorber in an equilibrium position. BACKGROUND OF THE INVENTION Shock absorbers that are preferably used in vehicles, regardless of the type, are part of the suspension system, together with the wheels and the crossbows or springs. In the case of hydraulic shock absorbers, these are made up of a cylinder through which a piston connected to an actuating rod runs, the piston defining inside the cylinder two chambers, one compression and one traction, both flooded with fluid, Generally oil In the movements of the wheels with respect to the chassis, displacements of rise and fall of the same ones take place and the shock absorber works in this case, displacing the drive rod in the sense that the piston compresses the fluid contained inside the cylinder. When the shock absorber operates on traction, that is, when the wheel moves away from the chassis, it may occur that it encounters a depression, which can cause abrupt displacement and a blow that is transmitted to the end of the traction stroke. bodywork. Bounce stop means are provided that cushion said blow, usually determined by plastic parts or even rebound stops of hydraulic type that use simple mechanisms, which add little damping or much functional dispersion. On the other hand, the hydraulic rebound stop corresponding to the invention patent No. 200000532, improves the stops described above and basically comprises in the traction chamber a head of coaxial closure to the rod that closes tightly against the walls of a tubular body, dividing this chamber into two subchambers, so that said closing head can be moved against a spring by the action of a closing washer that rests on a wall of a bushing integral with the actuating rod, defining between both subchambers several steps of strategically placed and finely calibrated fluid. DESCRIPTION OF THE INVENTION The hydraulic rebound stop of the invention is applicable to hydraulic shock absorbers for vehicles which in principle have a compression chamber and a traction chamber, which in turn is divided into two sub-chambers: one upper and one lower, separate both by a closing head. Starting from this premise, ' what is about is to soften and slow down the displacement of the rod-piston assembly essentially in the direction of traction, reaching a point in the race where the hydraulic stop system begins to operate. This moment when the hydraulic stop begins to act will correspond to a final section of that stroke in the direction of traction towards the maximum dimension of the shock absorber, that is, when the fluid is passing in a more controlled way from the traction chamber to the chamber compression and also when the fluid passes from the upper subchamber to the lower subchamber. It is characterized in that the closing head that separates both subchambers comprises a rebound stop washer coupled around the piston rod and axially retained by a retaining element that is in correspondence with the lower subchamber. It is also characterized in that it comprises an annular rubber stop fitted around the piston rod, while it sits on the free base of the washer, such an annular rubber stop being in correspondence with the upper subchamber. This rubber stop prevents metal-to-metal contact between parts when the shock absorber is in the position of maximum extension. Another feature is the incorporation of a split ring located in an annular channel of the washer, at the same time that said ring is adjusted, in the final path of the shock absorber towards the extension position, against the inner surface of a socket embedded in the section end of the interior of the shock absorber in correspondence with the traction chamber, so that during the movement and movement of the shock absorber the ring is in contact against the inner surface of said bushing. Another feature is that the bushing comprises an extreme conical portion in correspondence with the bottom edge. This conical portion facilitates the guiding and initial engagement of the ring when it is inserted into the bushing, that is, when the ring during the final stroke of the head and rod-piston assembly is directed towards the extended position of the shock absorber. Between the free ends of the split ring is a narrow permanent calibrated step. Thus, at the time the ring enters the bushing, the oil that is in the upper subchamber is forced to pass to the lower subchamber through the passage permanent allowed by the mentioned ring (the ring is not closed 360 °, that is to say it has a small calibrated opening), thus giving an extra hydraulic load. In the event that the rebound stop washer reaches the end of the stroke, as mentioned above, extending to the maximum allowed for the shock absorber, it is the rubber rebound stop that is in charge of avoiding metal-to-metal contacts between parts. During the lap or compression stroke, the hydraulic load is also controlled by the different calibrated steps mentioned above. The first corresponding to the opening of the ring (same opening that causes tensile loads) and the second will be determined by at least one upper window of the ring. With these two steps the compression load can be regulated even by canceling it if necessary. Said windows are essentially determined by small recesses that affect at least one of the flat faces of said ring. Next, in order to facilitate a better understanding of this descriptive report and forming an integral part thereof, some figures are attached in which the object of the invention has been shown as an illustrative and non-limiting nature. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1.- Shows a sectional view of a part of a corresponding hydraulic shock absorber with the traction chamber, said part including a hydraulic rebound stop which is the object of the invention. Figure 2.- Shows a view of a split ring that is part of the assembly of the invention. DESCRIPTION OF THE PREFERRED EMBODIMENT Considering the numbering adopted in the figures and paying particular attention to Figure 1, a part of a corresponding hydraulic damper 1 is shown with the traction chamber 2 separated from the compression chamber by a piston not shown in the figures, nor is the compression chamber, so that the end of such traction chamber 2 can be said to be sealed in a conventional manner . The shock absorber 1 is of the type that includes two coaxial tubular bodies 3 and 4, where the piston evidently fits into the inner tubular body 3. A head 5 is also included located in the traction chamber 2 which in turn separates a upper subchamber 6 corresponding to the end closure of that traction chamber 2 and a lower subchamber 7 that would be limited by the piston not shown in the figures. Starting from this premise, the hydraulic stop consists of a precise regulation during the passage of fluid from the upper subchamber 6 to the lower subchamber 7 in the final section of the extension of the shock absorber 2 to brake and soften such extension. The hydraulic rebound stop also offers other regulated loads at the start of the compression stroke. For this, the head 5 coupled to the rod 8 of the shock absorber 1 comprises an affected washer 9 of an annular channel 10 where a split ring 11 is housed between whose ends a narrow calibrated fluid passage space 12 is defined. The annular channel 10 has a greater height than the ring 11, at the same time that it is adjusted by its outer side face against an inner surface of a bushing 13 embedded in an end section of the inner tubular body 3 that limits an extreme part of the traction chamber 2. The head 5 complements with a rubber stop 14 fitted around the rod 8, while it sits on the upper base of the washer 9. Instead, the lower base includes an annular recess adapted to an element of axial retention 15 integral with rod 8 and located in correspondence with the lower sub-chamber 7, the rubber stop 14 being located in correspondence with the upper sub-chamber 6. This stop prevents metal parts from contacting each other in the most extended position of the shock absorber. The bushing 13 includes a conical end portion 16 corresponding to the lower sub chamber 7, thus facilitating the entry of the split ring 11 into the bushing 13 in the final section of the extension of the shock absorber 1. Finally, the ring 11 incorporates the recesses 17 as second passages of the fluid between the subchambers 6 and 7, the other step being the narrow calibrated space 12 limited by the ends of the split ring 11.

Claims

REIVINDICACIONES 1.- TOPE DE REBOTE HIDRÁULICO PARA AMORTIGUADORESCLAIMS 1.- HYDRAULIC REBOUND BUMPER FOR SHOCK ABSORBERS
HIDRÁULICOS, que siendo los amortiguadores de aquéllos que comprenden una cámara de compresión y una cámara de tracción (2) , separadas ambas por un pistón solidario de un vastago (8) que se encuentra dentro de un cuerpo tubular (3) y donde la cámara de tracción comprende a su vez dos subcámaras, superior (6) e inferior (7) , separadas por un cabezal (5) asociado al vastago (8) , se caracteriza porque el cabezal incluye una arandela (9) afectada de un canal anular (10) donde se acopla un anillo con al menos un estrecho paso que afecta al menos a la periferia de ese anillo, estando ajustado ese anillo contra la superficie interior de un casquillo (13) encastrado en el tramo extremo del cuerpo tubular (3) , incluyéndose además un tope de goma (14) ajustado alrededor del vastago (8) y asentado contra la base de la arandela (9) en correspondencia con la subcámara superior (6) , estando retenida la arandela (9) por su base pareja mediante un elemento de retención axial (15) solidario del vastago (8) . 2.- TOPE DE REBOTE HIDRÁULICO PARA AMORTIGUADORES HIDRÁULICOS, según la reivindicación 1, caracterizado porque el estrecho paso consiste en una ranura pasante calibrada (12) limitada entre los extremos del anillo partido (11) . 3 . - TOPE DE REBOTE HIDRÁULICO PARA AMORTIGUADORES HIDRÁULICOS , según una cualquiera de las reivindicaciones anteriores , caracterizado porque el anillo incluye al menos un segundo paso que consiste en un rebaj e ( 17 ) que afecta al menos a una de las caras o bases planas de ese anillo . 4 . - TOPE DE REBOTE HIDRÁULICO PARA AMORTIGUADORES HIDRÁULICOS , según una cualquiera de las reivindicaciones anteriores, caracterizado porque el casquillo (13) comprende una porción extrema cónica (16) que facilita la introducción del anillo cuando el amortiguador se extiende hacia su posición extendida. HYDRAULICS, which being the shock absorbers of those comprising a compression chamber and a traction chamber (2), both separated by a piston integral with a rod (8) that is inside a tubular body (3) and where the chamber In turn, it comprises two subchambers, upper (6) and lower (7), separated by a head (5) associated with the rod (8), characterized in that the head includes a washer (9) affected by an annular channel ( 10) where a ring is coupled with at least one narrow passage that affects at least the periphery of that ring, that ring being fitted against the inner surface of a bushing (13) embedded in the end section of the tubular body (3), also including a rubber stop (14) fitted around the rod (8) and seated against the base of the washer (9) in correspondence with the upper sub chamber (6), the washer (9) being retained by its even base by means of a axial retention element (15) so rod bearing (8). 2. HYDRAULIC REBOOT BUMPER FOR HYDRAULIC SHOCK ABSORBERS, according to claim 1, characterized in that the narrow passage consists of a calibrated through groove (12) limited between the ends of the split ring (11). 3 . - HYDRAULIC REBOOT BUMPER FOR HYDRAULIC SHOCK ABSORBERS, according to any one of the preceding claims, characterized in that the ring includes at least a second step consisting of a recess e (17) that affects at least one of the flat faces or bases of that ring Four . - HYDRAULIC REBOOT BUMPER FOR HYDRAULIC SHOCK ABSORBERS, according to any one of the preceding claims, characterized in that the bushing (13) comprises a conical end portion (16) that facilitates the introduction of the ring when the damper extends towards its extended position.
PCT/ES2005/000147 2004-04-28 2005-03-21 Hydraulic rebound stop for hydraulic shock absorbers WO2005106282A1 (en)

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ESP200401015 2004-04-28
ES200401015A ES2246138B1 (en) 2004-04-28 2004-04-28 HYDRAULIC REBOOT BUMPER FOR HYDRAULIC SHOCK ABSORBERS.

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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2302252A1 (en) 2009-09-18 2011-03-30 Delphi Technologies, Inc. Shock absorber with a hydraulic rebound stop
KR101166295B1 (en) 2004-11-25 2012-07-18 아딜 카니즈 A friction shock absorber
WO2013092084A1 (en) * 2011-12-20 2013-06-27 Zf Friedrichshafen Ag Vibration damper with a hydraulic end stop
WO2015011314A1 (en) * 2013-07-25 2015-01-29 Kyb Suspensions Europe, S.A. System for controlling variable load in a hydraulic device
DE102014203598A1 (en) * 2014-02-27 2015-08-27 Zf Friedrichshafen Ag Vibration damper with an end stop
JP2015197142A (en) * 2014-03-31 2015-11-09 日立オートモティブシステムズ株式会社 cylinder device
WO2016146660A1 (en) * 2015-03-16 2016-09-22 Sistemi Sospensioni S.P.A. Hydraulic compression stop member for a hydraulic shock-absorber for a vehicle suspension
EP3121479A1 (en) * 2015-07-06 2017-01-25 Bayerische Motoren Werke Aktiengesellschaft Telescopic vibration damper with hydraulic end stop
JP2017072246A (en) * 2015-10-05 2017-04-13 ベイジンウェスト・インダストリーズ・カンパニー・リミテッドＢｅｉｊｉｎｇｗｅｓｔ Ｉｎｄｕｓｔｒｉｅｓ Ｃｏ．， Ｌｔｄ． Buffer including hydraulic repulsion system
WO2017089425A1 (en) * 2015-11-27 2017-06-01 Volkswagen Aktiengesellschaft Vibration damper having a hydraulic traction stop
KR20180022708A (en) 2015-06-30 2018-03-06 히다치 오토모티브 시스템즈 가부시키가이샤 Cylinder device
US9909638B2 (en) 2015-12-02 2018-03-06 Beijingwest Industries Co., Ltd. Hydraulic suspension damper with hydro-mechanical stroke stop
DE102019212966A1 (en) * 2019-08-29 2021-03-04 Zf Friedrichshafen Ag Damping valve device with progressive damping force characteristic
DE102015203482B4 (en) 2014-02-28 2022-04-28 Hitachi Astemo, Ltd. cylinder device

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB763557A (en) * 1954-11-16 1956-12-12 Newtcn & Bennett Ltd Improvements in or relating to hydraulic shock absorbers
US3150747A (en) * 1961-06-30 1964-09-29 Ford Motor Co Hyraulic shock absorber having hydraulic stop means
US4852703A (en) * 1987-07-31 1989-08-01 Kayaba Kogyo K.K Shock absorber
FR2723624A1 (en) * 1994-08-10 1996-02-16 Soframca Pressurised hydraulic damper for vehicle suspensions
JPH11117983A (en) * 1997-09-22 1999-04-27 Kayaba Ind Co Ltd Front fork

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB763557A (en) * 1954-11-16 1956-12-12 Newtcn & Bennett Ltd Improvements in or relating to hydraulic shock absorbers
US3150747A (en) * 1961-06-30 1964-09-29 Ford Motor Co Hyraulic shock absorber having hydraulic stop means
US4852703A (en) * 1987-07-31 1989-08-01 Kayaba Kogyo K.K Shock absorber
FR2723624A1 (en) * 1994-08-10 1996-02-16 Soframca Pressurised hydraulic damper for vehicle suspensions
JPH11117983A (en) * 1997-09-22 1999-04-27 Kayaba Ind Co Ltd Front fork

Cited By (26)

* Cited by examiner, † Cited by third party
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KR101166295B1 (en) 2004-11-25 2012-07-18 아딜 카니즈 A friction shock absorber
EP2302252A1 (en) 2009-09-18 2011-03-30 Delphi Technologies, Inc. Shock absorber with a hydraulic rebound stop
WO2013092084A1 (en) * 2011-12-20 2013-06-27 Zf Friedrichshafen Ag Vibration damper with a hydraulic end stop
CN103890441B (en) * 2011-12-20 2015-09-30 Zf腓特烈斯哈芬股份公司 There is the vibration damper of hydraulic end blocked part
CN105637252B (en) * 2013-07-25 2017-07-04 凯迩必欧洲总部有限责任公司 System for controlling the variable load in hydraulic means
WO2015011314A1 (en) * 2013-07-25 2015-01-29 Kyb Suspensions Europe, S.A. System for controlling variable load in a hydraulic device
ES2540004A1 (en) * 2013-07-25 2015-07-07 Kyb Suspensions Europe, S.A. Variable load control system in a hydraulic device (Machine-translation by Google Translate, not legally binding)
CN105637252A (en) * 2013-07-25 2016-06-01 凯迩必欧洲总部有限责任公司 System for controlling variable load in a hydraulic device
US10323712B2 (en) 2013-07-25 2019-06-18 Kyb Europe Headquarters, Gmbh System for controlling variable load in a hydraulic device
DE102014203598A1 (en) * 2014-02-27 2015-08-27 Zf Friedrichshafen Ag Vibration damper with an end stop
DE102015203482B4 (en) 2014-02-28 2022-04-28 Hitachi Astemo, Ltd. cylinder device
JP2015197142A (en) * 2014-03-31 2015-11-09 日立オートモティブシステムズ株式会社 cylinder device
US10371226B2 (en) 2015-03-16 2019-08-06 Sistemi Sospensioni S.P.A. Hydraulic shock-absorber for a vehicle suspension
WO2016146660A1 (en) * 2015-03-16 2016-09-22 Sistemi Sospensioni S.P.A. Hydraulic compression stop member for a hydraulic shock-absorber for a vehicle suspension
KR20180022708A (en) 2015-06-30 2018-03-06 히다치 오토모티브 시스템즈 가부시키가이샤 Cylinder device
US10533624B2 (en) 2015-06-30 2020-01-14 Hitachi Automotive Systems, Ltd. Cylinder device
EP3121479A1 (en) * 2015-07-06 2017-01-25 Bayerische Motoren Werke Aktiengesellschaft Telescopic vibration damper with hydraulic end stop
JP2017072246A (en) * 2015-10-05 2017-04-13 ベイジンウェスト・インダストリーズ・カンパニー・リミテッドＢｅｉｊｉｎｇｗｅｓｔ Ｉｎｄｕｓｔｒｉｅｓ Ｃｏ．， Ｌｔｄ． Buffer including hydraulic repulsion system
CN108291602B (en) * 2015-11-27 2019-11-15 大众汽车有限公司 Vibration damper with hydraulic drawing backstop
WO2017089425A1 (en) * 2015-11-27 2017-06-01 Volkswagen Aktiengesellschaft Vibration damper having a hydraulic traction stop
CN108291602A (en) * 2015-11-27 2018-07-17 大众汽车有限公司 The vibration damper of backstop is pulled with hydraulic pressure
CN110886805A (en) * 2015-11-27 2020-03-17 大众汽车有限公司 Vibration damper with hydraulic traction stop
EP3734106A1 (en) * 2015-11-27 2020-11-04 Volkswagen Ag Vibration absorber with hydraulic cable stop
CN110886805B (en) * 2015-11-27 2023-10-13 大众汽车有限公司 Vibration damper with hydraulic traction stop
US9909638B2 (en) 2015-12-02 2018-03-06 Beijingwest Industries Co., Ltd. Hydraulic suspension damper with hydro-mechanical stroke stop
DE102019212966A1 (en) * 2019-08-29 2021-03-04 Zf Friedrichshafen Ag Damping valve device with progressive damping force characteristic

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