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WO2005108131A1 - Hydraulic damper comprising a hydraulic compression shut-off means - Google Patents

Hydraulic damper comprising a hydraulic compression shut-off means Download PDF

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Publication number
WO2005108131A1
WO2005108131A1 PCT/ES2005/000232 ES2005000232W WO2005108131A1 WO 2005108131 A1 WO2005108131 A1 WO 2005108131A1 ES 2005000232 W ES2005000232 W ES 2005000232W WO 2005108131 A1 WO2005108131 A1 WO 2005108131A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
hydraulic
shock absorber
coil
distributor
Prior art date
Application number
PCT/ES2005/000232
Other languages
Spanish (es)
French (fr)
Other versions
WO2005108131B1 (en
Inventor
José Àngel RECALDE ARTÀZCOZ
Original Assignee
Ap Amortiguadores, S.A.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ap Amortiguadores, S.A. filed Critical Ap Amortiguadores, S.A.
Publication of WO2005108131A1 publication Critical patent/WO2005108131A1/en
Publication of WO2005108131B1 publication Critical patent/WO2005108131B1/en

Links

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
    • F16F9/3207—Constructional features
    • F16F9/3235—Constructional features of cylinders
    • F16F9/3257—Constructional features of cylinders in twin-tube type devices
    • 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
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
    • 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
    • F16F9/56—Means for adjusting the length of, or for locking, the spring or damper, e.g. at the end of the stroke

Definitions

  • the present invention refers to a hydraulic shock absorber with hydraulic compression lock, which entails significant relevant characteristics in relation to conventional shock absorbers which They can be considered of this type.
  • the object of the invention is to achieve precise control of the fluid from the compression chamber to the auxiliary chamber and vice versa by means of an electric coil.
  • the shock absorbers that are preferably used in vehicles, regardless of the type, are part of the suspension system, together with the wheels and crossbows, torsion bars or springs and are the elements that collect the oscillations of the springs or crossbows, absorbing them and transforming them into heat.
  • Hydraulic shock absorbers are based on the resistance offered by all viscous fluid when passing through a calibrated hole. In the case of hydraulic shock absorbers, generally used in motor vehicles, these are made up of a cylinder whose interest runs a piston connected to a drive rod, the piston defining inside the cylinder two chambers, one compression and one traction , both flooded with fluid, usually oil.
  • the piston has a series of holes and valves that block the passage of the fluid to a greater or lesser extent, thus achieving a variable difficulty in the circulation of oil that passes from one chamber to another.
  • the shock absorber works in this case, displacing the drive rod in the sense that the piston compresses the fluid contained inside the cylinder. It is said that the shock absorber works under compression when the wheel axle travels towards the body or chassis, or by passing the wheel through an obstacle.
  • the shock absorber works by traction or expansion when the wheel returns to its previous position or goes through a depression or bump.
  • the behavior of a hydraulic shock absorber is determined by the forces obtained at given speeds of the drive rod.
  • the device that allows hydraulic compression locking is of the sliding type, in which the auxiliary chamber is divided into two subchambers through a valve that slides axially inside a distributor and is actuated by a coil electric This valve is constantly propelled towards the piston through a spring, a washer of copper or non-magnetic material being provided between the valve and said spring, so that there is no contact between the valve and the coil when the valve is attracted by the coil.
  • the non-magnetic material washer makes it possible to improve the passage time from the activated to deactivated state, avoiding the magnetization of the contact valve and allowing the spring to bring the valve to the deactivated position in the shortest possible time.
  • a pin is provided in the valve and a blind hole in the coil.
  • the valve has holes in its base to allow the fluid to pass from one side to the other, thus reducing the hydraulic resistance to sliding and balancing the pressures on both sides.
  • the valve has grooves on its cylindrical surface, which, when coinciding with other grooves of the distributor, allow the passage of the compression chamber fluid into the auxiliary chamber and vice versa.
  • This distributor has a cylindrical portion in its upper part that fits with the cylinder or inner tubular body of the shock absorber, either by means of an elastic seal, or by means of interference in the assembly of the two metal parts.
  • To position the distributor with respect to the coil it has the cylindrical lower part so that there is only one possible mounting position in the direction of the shaft, the angular position of one piece relative to the other not being important.
  • This cylinder admits the two possible constructions, interior or exterior, with respect to that of the coil.
  • a series of slots are provided in the intermediate zone of the distributor that can allow the passage of fluid from the compression chamber to the auxiliary chamber, depending on the position of the valve, said valve will prevent the passage of fluid between the chambers when the cylindrical part with grooves thereof is facing the cylindrical wall without grooves of the distributor.
  • the fluid flow due to the difference in diameters between the two pieces, necessary for assembly, is minimal and irrelevant against the passage of fluid in the radial direction when the grooves of the two pieces coincide.
  • the shock absorber also includes a concentric bushing to reduce undue radial movements when lateral forces are applied, including an intercalated joint between the distributor and the coil.
  • Figure 3. Shows a plan view of a valve that is part of the invention.
  • Figure 4. Shows a sectional view of the valve represented in the previous figure.
  • Figures 5 and 6. They show each section of a distributor that is also part of the whole of the invention.
  • Figure 7. It shows a sectional view where the housing of a spring or spring that is also part of the assembly of the invention is shown in detail.
  • Figure 8. Shows a detailed view of the fluid passages from the compression chamber to the auxiliary chamber of the shock absorber.
  • Figure 9. Shows a sectional view similar to that shown in figure 3 with some modifications.
  • a conventional shock absorber basically comprising an outer cylinder or tubular body 1, in which a tube or tubular body is housed inside internal coaxial 2 in which adjusts the piston 3 connected to the drive rod 4.
  • the piston 3 divides the internal compartment into two chambers: one of traction 5 and another of compression 6.
  • This piston also incorporates calibrated holes 7 and valves 8 that allow the passage of fluid from one chamber to another.
  • a bitube damper has been shown which includes the valves and intercom passages between the compression chamber 6 and an auxiliary chamber 9 limited between the two coaxial tubes 1 and 2.
  • a hydraulic blocking valve 10 is provided associated with an electric coil 13 and housed inside a tubular distributor 11 which in principle closes one end of the inner tube 2 corresponding to one end of the outer tube 1 closed by the electric coil 13, these two ends being arranged on the opposite side of the shock absorber from which the rod 4 appears.
  • This valve has a general configuration of a bowl. The bottom of this blocking valve 10 is facing in proximity to the coil 13 against the resistance of a spring 12 and with interposition of a flat washer 14 of non-magnetic material, specifically located between the spring 12 and the valve 10.
  • This washer 14 prevents contact between the surfaces of the valve 10 and the coil 13 when it is activated, which is when the passage of greater flow is essentially allowed of fluid from the compression chamber 6 to the auxiliary chamber 9 and vice versa through the valve 10 and the distributor 11.
  • the side wall of the valve 10 incorporates calibrated through grooves 19, which in the activated position of the coil 13 will be faced with other rear through slots 18 of the distributor 11.
  • valve slots 19 will face the distributor wall blocking the passage of the fluid through said slots 19 and 18 of the valve 10 and the distributor 11, respectively.
  • this case of blockage there is a small flow of fluid that will pass through small notches 20 arranged at the free edge of the valve 10, and through other anterior grooves 17 arranged in the distributor wall, being in this if that free edge is abutted against a stepped surface 16 of the distributor 11 by the action of the spring 12.
  • the fluid will also flow into the auxiliary chamber 9 through the anterior slots 17 of the distributor 11.
  • front holes 15 are provided in the bottom of this valve 10 that allow the passage of the retained fluid part between the base or bottom of the valve 10 and coil 13.
  • This coil 13 has a blind hole that helps guide the spring 12, into which a central pin of the valve 10 also enters when it is attracted by the coil 13.
  • a separation seal is provided. and sealing 23 disposed between the tubular distributor 11 and the coil 13, said seal 23 being located in correspondence with the corner perimeter contour of a recess of the coil 13, at the bottom of which is the blind hole for housing the spring.
  • This gasket has an inclined plane complemented by an inclined seat of the tubular distributor 11, the gasket will prevent oil leaks.
  • a bushing 24 concentrically arranged with respect to the outer and inner tubes 1 is also provided, while being located at the end of the inner tube 2, in correspondence with the distributor 11 and the coil 13.
  • This bushing 24 has axial passages 25 to allow the passage of fluid.
  • This bushing 24 serves to reduce the radial movements of the lower end of the inner tube 2 when lateral forces are applied to the shock absorber.
  • the bushing also has the utility of facilitating the guidance between the two tubes: inner and outer.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

The invention relates to a damper comprising a hydraulic shut-off valve (10) which is disposed inside a distributor (11) such that a coil (13) can be used to control and regulate the passage of fluid from the compression chamber to the auxiliary chamber (9) which is defined between two co-axial tubular bodies (1 and 2) that form part of the damper assembly. According to the invention, the activation of the coil (13) causes the axial movement of the valve (10) such that, in the activated position, the fluid passes from the compression chamber (6) to the auxiliary chamber (9) through opposing grooves in the valve and the distributor. Alternatively, when the coil is in the deactivated position, the flow of fluid is almost completely stopped.

Description

AMORTIGUADOR HIDRÁULICO CON BLOQUEO HIDRÁULICO EN COMPRESIÓN OBJETO DE LA INVENCIÓN La presente invención según se expresa en el enunciado de esta memoria descriptiva, se refiere a un amortiguador hidráulico con bloqueo hidráulico en compresión, el cual comporta notables características relevantes en relación con los amortiguadores convencionales que pueden considerarse de este mismo tipo. El objetivo de la invención es conseguir un control preciso del fluido desde la cámara de compresión a la cámara auxiliar y viceversa mediante una bobina eléctrica. ANTECEDENTES 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, barras de torsión o muelles y son los elementos que recogen las oscilaciones de los muelles o ballestas, absorbiéndolas y transformándolas en calor. Los amortiguadores hidráulicos están basados en la resistencia que ofrece todo fluido viscoso al paso por un orificio calibrado. En el caso de amortiguadores hidráulicos, generalmente utilizados en vehículos automóviles, éstos se conforman por un cilindro por cuyo interés 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. El pistón cuenta con una serie de orificios y válvulas que obturan en mayor o menor medida el paso del fluido, consiguiéndose así una dificultad variable a la circulación del aceite que pasa de una cámara a otra. 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. Se dice que el amortiguador funciona a compresión cuando el eje de la rueda se desplaza hacia la carrocería o chasis, o por el paso de la rueda por un obstáculo. El amortiguador trabaja a tracción o expansión cuando la rueda regresa a su posición anterior o bien pasa por una depresión o bache. El comportamiento de un amortiguador hidráulico queda determinado por los esfuerzos obtenidos a unas velocidades dadas del vastago de accionamiento. Este comportamiento es un compromiso entre confort y ¡seguridad. Constituye un objeto de la invención el que el bloqueo del movimiento de compresión aumenta de manera significativa el nivel de seguridad sin modificar el nivel de confort de un amortiguador convencional. DESCRIPCIÓN DE LA INVENCIÓN El dispositivo que permite el bloqueo hidráulico de la compresión es del tipo deslizante, en el que la cámara auxiliar queda dividida en dos subcámaras a través de un válvula que desliza axialmente en el interior de un distribuidor y está accionada por una bobina eléctrica. Esta válvula está constantemente impulsada hacia el pistón a través de un muelle, habiéndose previsto entre la válvula y dicho muelle una arandela de cobre o material no magnético, de manera que no haya contacto entre la válvula y la bobina cuando la válvula es atraída por la bobina. La arandela de material no magnético permite mejorar el tiempo de paso del estado activado a desactivado, evitando el magnetizado de la válvula por contacto y permitiendo que el muelle lleve a la válvula a la posición de desactivado en el menor tiempo posible. Para lograr un buen guiado del muelle, se ha previsto un tetón en la válvula y un orificio ciego en la bobina. La válvula presenta orificios en su base para permitir el paso del fluido de un lado al otro reduciendo de este modo la resistencia hidráulica al deslizamiento y equilibrando las presiones en ambas caras. Además, la válvula presenta en su superficie cilindrica ranuras, que al coincidir en posición con otras ranuras del distribuidor permiten el paso del fluido de la cámara de compresión hacia la cámara auxiliar y viceversa. Como pieza de unión entre la bobina, el cilindro interior y la válvula hay un distribuidor. Este distribuidor cuenta con una porción cilindrica en su parte superior que encaja con el cilindro o cuerpo tubular interior del amortiguador de forma estanca, bien por medio de una junta de estanqueidad elástica, bien por medio de interferencia en el montaje de las dos piezas metálicas . Para posicionar el distribuidor respecto a la bobina, éste tiene la parte inferior cilindrica de forma que solo haya una posible posición de montaje en la dirección del eje, no teniendo importancia la posición angular de una pieza respecto a la otra. Este cilindro admite las dos construcciones posibles, interior o exterior, respecto del de la bobina. De otro lado, y de acuerdo con la invención, en la zona intermedia del distribuidor se han previsto una serie de ranuras que pueden permitir el paso de fluido de la cámara de compresión a la cámara auxiliar, en función de la posición de la válvula, dicha válvula impedirá el paso de fluido entre las cámaras cuando la parte cilindrica con ranuras de ésta esté enfrentada con la pare cilindrica sin ranuras del distribuidor. El paso de fluido debido a la diferencia de diámetros entre las dos piezas, necesario para el montaje, es mínimo e irrelevante frente al paso de fluido en dirección radial cuando las ranuras de las dos piezas coinciden. El amortiguador incluye además un casquillo concéntrico para reducir movimientos radiales indebidos cuando se aplican esfuerzos laterales, incluyéndose además una junta intercalada entre el distribuidor y la bobina. Para suavizar la subida de presión en la cámara de compresión, y en consecuencia de los esfuerzos de compresión, existe la posibilidad de realizar ranuras que definan un paso permanente de fluido en la parte superior de la válvula. Para facilitar la comprensión de las características de la invención y formando parte integrante de la memoria descriptiva, se acompañan unas hojas de planos en cuyas figuras, con carácter ilustrativo y no limitativo se ha representado el objeto de la invención. BREVE DESCRIPCIÓN DE LOS DIBUJOS Figura 1.- Muestra una vista esquemática de un amortiguador hidráulico convencional bitubo, cuyo pistón le divide en dos cámaras ocupadas por un fluido. Figura 2.- Es una vista parcial de un amortiguador, bitubo, que incluye el dispositivo para el bloqueo de la compresión, acorde con la invención. Figura 3.- Muestra una vista en planta de una válvula que forma parte de la invención. Figura 4.- Muestra una vista en sección de la válvula representada en la figura anterior. Figuras 5 y 6. - Muestran sendas secciones de un distribuidor que forma parte también del conjunto de la invención. Figura 7. - Muestra una vista en sección donde se muestra con detalle el alojamiento de un resorte o muelle que forma parte también del conjunto de la invención. Figura 8.- Muestra una vista con detalle de los pasos de fluido desde la cámara de compresión a la cámara auxiliar del amortiguador. Figura 9.- Muestra una vista en sección similar a la representada en al figura 3 con algunas modificaciones. DESCRIPCIÓN DE LA FORMA DE REALIZACIÓN PREFERIDA Considerando la numeración adoptada en las figuras, y en principio atendiendo a la figura 1, podemos ver esquemáticamente un amortiguador convencional comprendiendo básicamente un cilindro o cuerpo tubular exterior 1, en cuyo interior queda alojado un tubo o cuerpo tubular coaxial interior 2 en el que ajusta el pistón 3 conectado al vastago de accionamiento 4. El pistón 3 divide el compartimento interno en dos cámaras: una de tracción 5 y otra de compresión 6. Este pistón incorpora asimismo unos orificios calibrados 7 y unas válvulas 8 que posibilitan el paso del fluido de una cámara a otra. Acorde con la invención y atendiendo ahora a la figura 2 y sucesivas, se ha mostrado un amortiguador bitubo donde se incluyen las válvulas y pasos de intercomunicación entre la cámara de compresión 6 y una cámara auxiliar 9 limitada entre los dos tubos coaxiales 1 y 2. También de acuerdo con la invención, se ha previsto una válvula de bloqueo hidráulico 10 asociada a una bobina eléctrica 13 y alojada dentro de un distribuidor tubular 11 que cierra en principio un extremo del tubo interior 2 que se corresponde con un extremo del tubo exterior 1 cerrado mediante la bobina eléctrica 13, estando dispuestos estos dos extremos en el lado opuesto del amortiguador por donde asoma el vastago 4. Esta válvula presenta una configuración en forma general de cazoleta. El fondo de esta válvula de bloqueo 10 está enfrentado en proximidad a la bobina 13 en contra de la resistencia de un resorte 12 y con interposición de una arandela plana 14 de material no magnético, situada concretamente entre el resorte 12 y la válvula 10. Esta arandela 14 evita el contacto entre las superficies de la válvula 10 y la bobina 13 cuando la misma está activada, que es cuando se permite esencialmente el paso de mayor caudal de fluido desde la cámara de compresión 6 a la cámara auxiliar 9 y viceversa a través de la válvula 10 y del distribuidor 11. Para ello, la pared lateral de la válvula 10 incorpora ranuras pasantes calibradas 19, que en la posición activada de la bobina 13 estarán enfrentadas con otras ranuras pasantes posteriores 18 del distribuidor 11. Así pues, cuando la bobina 13 se activa, la válvula 10 es atraída axialmente según el sentido indicado por la flecha 22 (figura 8), tomando contacto con la bobina 13, a través de la arandela 14, permitiéndose el paso de fluido a través de las ranuras 19 de la válvula 10 y ranuras posteriores 18 del distribuidor 11, tal como se ha referido anteriormente . En cambio, cuando la bobina 13 no está activada, las ranuras 19 de la válvula estarán enfrentadas con la pared del distribuidor bloqueando el paso del fluido a través de dichas ranuras 19 y 18 de la válvula 10 y del distribuidor 11, respectivamente. No obstante, en este caso de bloqueo existe un pequeño flujo de fluido que pasará a través de unas pequeñas muescas 20 dispuestas en el borde libre de la válvula 10, y a través de otras ranuras anteriores 17 dispuestas en la pared del distribuidor, estando en este caso ese borde libre haciendo tope contra una superficie escalonada 16 del distribuidor 11 por la acción del resorte 12. Por otro lado, cabe señalar que en la posición activada de la bobina 13, el fluido también discurrirá hacia la cámara auxiliar 9 a través de las ranuras anteriores 17 del distribuidor 11. Además y con objeto de facilitar el deslizamiento de la válvula 10 en el interior del distribuidor 11, se han previsto unos orificios frontales 15 en el fondo de esta válvula 10 que permiten el paso de la parte de fluido retenido entre la base o fondo de la válvula 10 y la bobina 13. Esta bobina 13 posee un orificio ciego que ayuda al guiado del resorte 12, en el cual entra también un tetón central de la válvula 10 cuando ésta es atraída por la bobina 13. Se ha previsto una junta de separación y estanqueidad 23 dispuesta entre el distribuidor tubular 11 y la bobina 13, estando ubicada dicha junta 23 en correspondencia con el contorno perimetral esquinado de un cajeado de la bobina 13, en cuyo fondo se encuentra el orificio ciego de alojamiento del resorte. Esta junta posee un plano inclinado complementado con un asiento inclinado del distribuidor tubular 11, la junta evitará fugas de aceite. También se ha previsto un casquillo 24 dispuesto concéntricamente con respecto a los tubos exterior 1 e interior 2, a la vez que se ubica al final del tubo interior 2, en correspondencia con el distribuidor 11 y la bobina 13. Este casquillo 24 posee pasos axiales 25 para permitir el paso de fluido. Este casquillo 24 sirve para poder reducir los movimientos radiales del extremo inferior del tubo interior 2 cuando se aplican esfuerzos laterales al amortiguador. El casquillo también tiene la utilidad de facilitar el guiado entre los dos tubos: interior y exterior. HYDRAULIC SHOCK ABSORBER WITH HYDRAULIC BLOCK IN COMPRESSION OBJECT OF THE INVENTION The present invention, as expressed in the statement of this specification, refers to a hydraulic shock absorber with hydraulic compression lock, which entails significant relevant characteristics in relation to conventional shock absorbers which They can be considered of this type. The object of the invention is to achieve precise control of the fluid from the compression chamber to the auxiliary chamber and vice versa by means of an electric coil. BACKGROUND OF THE INVENTION The shock absorbers that are preferably used in vehicles, regardless of the type, are part of the suspension system, together with the wheels and crossbows, torsion bars or springs and are the elements that collect the oscillations of the springs or crossbows, absorbing them and transforming them into heat. Hydraulic shock absorbers are based on the resistance offered by all viscous fluid when passing through a calibrated hole. In the case of hydraulic shock absorbers, generally used in motor vehicles, these are made up of a cylinder whose interest runs a piston connected to a drive rod, the piston defining inside the cylinder two chambers, one compression and one traction , both flooded with fluid, usually oil. The piston has a series of holes and valves that block the passage of the fluid to a greater or lesser extent, thus achieving a variable difficulty in the circulation of oil that passes from one chamber to another. In the movements of the wheels with respect to the chassis there are displacements of rise and fall of the same 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. It is said that the shock absorber works under compression when the wheel axle travels towards the body or chassis, or by passing the wheel through an obstacle. The shock absorber works by traction or expansion when the wheel returns to its previous position or goes through a depression or bump. The behavior of a hydraulic shock absorber is determined by the forces obtained at given speeds of the drive rod. This behavior is a compromise between comfort and safety. It is an object of the invention that blocking the compression movement significantly increases the level of safety without modifying the comfort level of a conventional shock absorber. DESCRIPTION OF THE INVENTION The device that allows hydraulic compression locking is of the sliding type, in which the auxiliary chamber is divided into two subchambers through a valve that slides axially inside a distributor and is actuated by a coil electric This valve is constantly propelled towards the piston through a spring, a washer of copper or non-magnetic material being provided between the valve and said spring, so that there is no contact between the valve and the coil when the valve is attracted by the coil. The non-magnetic material washer makes it possible to improve the passage time from the activated to deactivated state, avoiding the magnetization of the contact valve and allowing the spring to bring the valve to the deactivated position in the shortest possible time. To achieve a good guidance of the spring, a pin is provided in the valve and a blind hole in the coil. The valve has holes in its base to allow the fluid to pass from one side to the other, thus reducing the hydraulic resistance to sliding and balancing the pressures on both sides. In addition, the valve has grooves on its cylindrical surface, which, when coinciding with other grooves of the distributor, allow the passage of the compression chamber fluid into the auxiliary chamber and vice versa. As a connecting piece between the coil, the inner cylinder and the valve there is a distributor. This distributor has a cylindrical portion in its upper part that fits with the cylinder or inner tubular body of the shock absorber, either by means of an elastic seal, or by means of interference in the assembly of the two metal parts. To position the distributor with respect to the coil, it has the cylindrical lower part so that there is only one possible mounting position in the direction of the shaft, the angular position of one piece relative to the other not being important. This cylinder admits the two possible constructions, interior or exterior, with respect to that of the coil. On the other hand, and according to the invention, a series of slots are provided in the intermediate zone of the distributor that can allow the passage of fluid from the compression chamber to the auxiliary chamber, depending on the position of the valve, said valve will prevent the passage of fluid between the chambers when the cylindrical part with grooves thereof is facing the cylindrical wall without grooves of the distributor. The fluid flow due to the difference in diameters between the two pieces, necessary for assembly, is minimal and irrelevant against the passage of fluid in the radial direction when the grooves of the two pieces coincide. The shock absorber also includes a concentric bushing to reduce undue radial movements when lateral forces are applied, including an intercalated joint between the distributor and the coil. To soften the pressure rise in the compression chamber, and as a result of the compression efforts, there is the possibility of making grooves that define a permanent passage of fluid in the upper part of the valve. To facilitate the understanding of the features of the invention and forming an integral part of the specification, some sheets of drawings are attached in whose figures, for illustrative and non-limiting purposes, the object of the invention has been represented. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1.- Shows a schematic view of a conventional twin-tube hydraulic shock absorber, whose piston divides it into two chambers occupied by a fluid. Figure 2.- It is a partial view of a shock absorber, bitube, which includes the device for blocking compression, according to the invention. Figure 3.- Shows a plan view of a valve that is part of the invention. Figure 4.- Shows a sectional view of the valve represented in the previous figure. Figures 5 and 6. - They show each section of a distributor that is also part of the whole of the invention. Figure 7. - It shows a sectional view where the housing of a spring or spring that is also part of the assembly of the invention is shown in detail. Figure 8.- Shows a detailed view of the fluid passages from the compression chamber to the auxiliary chamber of the shock absorber. Figure 9.- Shows a sectional view similar to that shown in figure 3 with some modifications. DESCRIPTION OF THE PREFERRED EMBODIMENT Considering the numbering adopted in the figures, and in principle according to Figure 1, we can schematically see a conventional shock absorber basically comprising an outer cylinder or tubular body 1, in which a tube or tubular body is housed inside internal coaxial 2 in which adjusts the piston 3 connected to the drive rod 4. The piston 3 divides the internal compartment into two chambers: one of traction 5 and another of compression 6. This piston also incorporates calibrated holes 7 and valves 8 that allow the passage of fluid from one chamber to another. In accordance with the invention and in accordance with Figure 2 and following, a bitube damper has been shown which includes the valves and intercom passages between the compression chamber 6 and an auxiliary chamber 9 limited between the two coaxial tubes 1 and 2. Also according to the invention, a hydraulic blocking valve 10 is provided associated with an electric coil 13 and housed inside a tubular distributor 11 which in principle closes one end of the inner tube 2 corresponding to one end of the outer tube 1 closed by the electric coil 13, these two ends being arranged on the opposite side of the shock absorber from which the rod 4 appears. This valve has a general configuration of a bowl. The bottom of this blocking valve 10 is facing in proximity to the coil 13 against the resistance of a spring 12 and with interposition of a flat washer 14 of non-magnetic material, specifically located between the spring 12 and the valve 10. This washer 14 prevents contact between the surfaces of the valve 10 and the coil 13 when it is activated, which is when the passage of greater flow is essentially allowed of fluid from the compression chamber 6 to the auxiliary chamber 9 and vice versa through the valve 10 and the distributor 11. For this, the side wall of the valve 10 incorporates calibrated through grooves 19, which in the activated position of the coil 13 will be faced with other rear through slots 18 of the distributor 11. Thus, when the coil 13 is activated, the valve 10 is axially attracted according to the direction indicated by the arrow 22 (Figure 8), making contact with the coil 13, a through the washer 14, allowing the passage of fluid through the slots 19 of the valve 10 and rear slots 18 of the distributor 11, as referred to above. On the other hand, when the coil 13 is not activated, the valve slots 19 will face the distributor wall blocking the passage of the fluid through said slots 19 and 18 of the valve 10 and the distributor 11, respectively. However, in this case of blockage there is a small flow of fluid that will pass through small notches 20 arranged at the free edge of the valve 10, and through other anterior grooves 17 arranged in the distributor wall, being in this if that free edge is abutted against a stepped surface 16 of the distributor 11 by the action of the spring 12. On the other hand, it should be noted that in the activated position of the coil 13, the fluid will also flow into the auxiliary chamber 9 through the anterior slots 17 of the distributor 11. In addition and in order to facilitate the sliding of the valve 10 inside the distributor 11, front holes 15 are provided in the bottom of this valve 10 that allow the passage of the retained fluid part between the base or bottom of the valve 10 and coil 13. This coil 13 has a blind hole that helps guide the spring 12, into which a central pin of the valve 10 also enters when it is attracted by the coil 13. A separation seal is provided. and sealing 23 disposed between the tubular distributor 11 and the coil 13, said seal 23 being located in correspondence with the corner perimeter contour of a recess of the coil 13, at the bottom of which is the blind hole for housing the spring. This gasket has an inclined plane complemented by an inclined seat of the tubular distributor 11, the gasket will prevent oil leaks. A bushing 24 concentrically arranged with respect to the outer and inner tubes 1 is also provided, while being located at the end of the inner tube 2, in correspondence with the distributor 11 and the coil 13. This bushing 24 has axial passages 25 to allow the passage of fluid. This bushing 24 serves to reduce the radial movements of the lower end of the inner tube 2 when lateral forces are applied to the shock absorber. The bushing also has the utility of facilitating the guidance between the two tubes: inner and outer.

Claims

REIVINDICACIONES 1.- AMORTIGUADOR HIDRÁULICO CON BLOQUEO HIDRÁULICO EN COMPRESIÓN, siendo del tipo que comprende dos cuerpos tubulares coaxiales, exterior (1) e interior (2) , entre los que se forma una cámara auxiliar, conteniendo ésta y el tubo interior un fluido y un pistón (3) con su vastago de accionamiento (4), definiendo el pistón (3) dos cámaras: una de tracción (5) y ora de compresión (6) , realizándose el paso de fluido en los movimientos relativos entre la rueda y el chasis del vehículo donde el amortiguador está montado, de una a otra cámara, a través de orificios calibrados y válvulas previstas en el pistón (3) , existiendo una válvula que permite el bloqueo hidráulico del recorrido de la rueda cuando ésta se aproxima al chasis del vehículo, caracterizado porque la válvula de bloqueo hidráulico (10) está asociada a una bobina eléctrica (13) para controlar y limitar el paso del fluido desde la cámara de compresión (6) a la cámara auxiliar (9) ; todo ello en orden a que en la posición activada de la bobina se permite el paso de un caudal de fluido controlado hacia la cámara auxiliar (9) , mientras que en la posición de reposo ese caudal de fluido se ve minimizado, regulándose así la velocidad a la que el vastago de accionamiento (4) se introduce en el amortiguador. 2.- AMORTIGUADOR HIDRÁULICO CON BLOQUEO HIDRÁULICO EN COMPRESIÓN, según la reivindicación 1, caracterizado porque la válvula (10) presenta una estructura en forma de cazoleta y se encuentra ajustada dentro de un distribuidor fijo tubular (11) cerrando un extremo del cuerpo interior (2) del amortiguador, a la vez que la pared lateral de tal válvula (10) posee unas ranuras anteriores calibradas (17) y otras ranuras posteriores también calibradas (18) que en la posición activa de la bobina eléctrica (13) están enfrentadas con otras ranuras (19) de la válvula (10) para el paso de fluido a la cámara auxiliar (9) , que también discurre a través de las ranuras anteriores (17) , mientras que en la posición de reposo las ranuras (19) de la válvulaCLAIMS 1.- HYDRAULIC SHOCK ABSORBER WITH HYDRAULIC COMPRESSION LOCK, being of the type comprising two coaxial tubular bodies, exterior (1) and interior (2), between which an auxiliary chamber is formed, containing this and the inner tube a fluid and a piston (3) with its actuating rod (4), the piston (3) defining two chambers: one of traction (5) and one of compression (6), the fluid passing in the relative movements between the wheel and the chassis of the vehicle where the shock absorber is mounted, from one chamber to another, through calibrated holes and valves provided in the piston (3), there being a valve that allows the hydraulic blockage of the wheel travel when it approaches the chassis of the vehicle, characterized in that the hydraulic blocking valve (10) is associated with an electric coil (13) to control and limit the flow of fluid from the compression chamber (6) to the auxiliary chamber (9); all this in order that in the activated position of the coil the passage of a controlled fluid flow to the auxiliary chamber (9) is allowed, while in the rest position that fluid flow is minimized, thus regulating the speed to which the drive rod (4) is inserted into the shock absorber. 2. HYDRAULIC SHOCK ABSORBER WITH HYDRAULIC COMPRESSION LOCK, according to claim 1, characterized in that the valve (10) has a bowl-shaped structure and is fitted inside a fixed tubular distributor (11) closing one end of the inner body ( 2) of the shock absorber, while the side wall of such a valve (10) has calibrated anterior grooves (17) and other calibrated posterior grooves (18) that in the active position of the electric coil (13) are faced with other slots (19) of the valve (10) for the passage of fluid to the auxiliary chamber (9), which also runs through the previous grooves (17), while in the idle position the grooves (19) of the valve
(10) estarán enfrentadas con una superficie cerrada de la pared lateral del distribuidor (11) . 3.- AMORTIGUADOR HIDRÁULICO CON BLOQUEO HIDRÁULICO EN COMPRESIÓN, según la reivindicación 2, caracterizado porque la válvula (10) incluye unas muescas (20) en su borde libre que hace tope contra una superficie escalonada frontal (16) del distribuidor (11) en la posición de reposo de la bobina (13) , por la acción de un resorte (12) ubicado entre el fondo de la válvula (10) y la bobina (13) con interposición de una arandela no magnética (14) ; todo ello en orden a que en esta posición de reposo existe un pequeño flujo de fluido hacia la cámara auxiliar (9) que discurre por esas muescas (20) y ranuras anteriores (17) del distribuidor (11) • 4.- AMORTIGUADOR HIDRÁULICO CON BLOQUEO HIDRÁULICO EN COMPRESIÓN, según la reivindicación 3, caracterizado porque el fondo de la válvula (10) incluye al menos un pequeño orificio pasante (15) . 5.- AMORTIGUADOR HIDRÁULICO CON BLOQUEO HIDRÁULICO EN COMPRESIÓN, según la reivindicación 3, caracterizado porque una porción del resorte (12) se aloja dentro de un hueco central de la bobina (13) , mientras que otra porción extrema del resorte (12) se ajusta alrededor de un tetón central del fondo de la válvula (10) . 6.- AMORTIGUADOR HIDRÁULICO CON BLOQUEO HIDRÁULICO DE COMPRESIÓN, según la reivindicación 2, caracterizado porque la bobina (13) se encuentra encastrada dentro del cuerpo tubular exterior (1) cerrando un extremo del mismo en correspondencia con el distribuidor (11) que cierra otro extremo parejo del cuerpo tubular interior (2) del amortiguador . 7.- AMORTIGUADOR HIDRÁULICO CON BLOQUEO HIDRÁULICO DE COMPRESIÓN, según una cualquiera de las reivindicaciones anteriores, caracterizado porque incluye un casquillo (24) dispuesto concéntricamente con respecto a los tubos exterior (1) e interior (2) , a la vez que se ubica al final del tubo interior (2) en correspondencia con el distribuidor (11) , incluyendo el casquillo (24) pasos axiales (25) para permitir el paso de fluido. 8.- AMORTIGUADOR HIDRÁULICO CON BLOQUEO HIDRÁULICO DE COMPRESIÓN, según una cualquiera de las reivindicaciones anteriores, caracterizado porque incluye una junta (23) intercalada entre el distribuidor (11) y la bobina (13) . (10) will be faced with a closed surface of the side wall of the distributor (11). 3. HYDRAULIC SHOCK ABSORBER WITH HYDRAULIC COMPRESSION LOCK, according to claim 2, characterized in that the valve (10) includes notches (20) in its free edge that stops against a front stepped surface (16) of the distributor (11) in the resting position of the coil (13), by the action of a spring (12) located between the bottom of the valve (10) and the coil (13) with interposition of a non-magnetic washer (14); all this in order that in this resting position there is a small flow of fluid to the auxiliary chamber (9) that runs through those notches (20) and anterior grooves (17) of the distributor (11) • 4.- HYDRAULIC SHOCK ABSORBER WITH HYDRAULIC COMPRESSION LOCK, according to claim 3, characterized in that the bottom of the valve (10) includes at least a small through hole (15). 5. HYDRAULIC SHOCK ABSORBER WITH HYDRAULIC COMPRESSION LOCK, according to claim 3, characterized in that a portion of the spring (12) is housed within a central recess of the coil (13), while another end portion of the spring (12) is fit around a central pin on the bottom of the valve (10). 6. HYDRAULIC SHOCK ABSORBER WITH HYDRAULIC COMPRESSION LOCK, according to claim 2, characterized in that the coil (13) is embedded inside the outer tubular body (1) closing one end thereof in correspondence with the distributor (11) closing another even end of the inner tubular body (2) of the shock absorber. 7. HYDRAULIC SHOCK ABSORBER WITH HYDRAULIC COMPRESSION LOCK, according to any one of the claims above, characterized in that it includes a bushing (24) arranged concentrically with respect to the outer (1) and inner (2) tubes, while being located at the end of the inner tube (2) in correspondence with the distributor (11), including the bushing (24) axial passages (25) to allow the passage of fluid. 8. HYDRAULIC SHOCK ABSORBER WITH HYDRAULIC COMPRESSION LOCK, according to any one of the preceding claims, characterized in that it includes a gasket (23) inserted between the distributor (11) and the coil (13).
PCT/ES2005/000232 2004-05-04 2005-04-29 Hydraulic damper comprising a hydraulic compression shut-off means WO2005108131A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ES200401064A ES2251293B1 (en) 2004-05-04 2004-05-04 HYDRAULIC SHOCK ABSORBER WITH HYDRAULIC LOCK IN COMPRESSION.
ESP200401064 2004-05-04

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WO2005108131A1 true WO2005108131A1 (en) 2005-11-17
WO2005108131B1 WO2005108131B1 (en) 2006-01-05

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018108419A1 (en) * 2016-12-16 2018-06-21 Zf Friedrichshafen Ag Hydraulic twin-tube shock absorber

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GB1363303A (en) * 1971-07-16 1974-08-14 Blazquez A G Hydraulic shock absolbers
US4031989A (en) * 1975-02-22 1977-06-28 Antonio Giner Blazquez Double effect hydraulic shock absorber
JPS5920712A (en) * 1982-07-26 1984-02-02 Showa Mfg Co Ltd Hydraulic shock absorber
DE4404963A1 (en) * 1993-04-24 1994-10-27 Bilstein August Gmbh Co Kg Controllable vibration damper for motor vehicles
DE4342763A1 (en) * 1993-12-15 1995-06-22 Bilstein August Gmbh Co Kg Adjustable hydraulic suspension strut for vehicle
JP2001088529A (en) * 1999-09-20 2001-04-03 Kayaba Ind Co Ltd Anti-rolling type hydraulic shock absorber

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Publication number Priority date Publication date Assignee Title
GB1363303A (en) * 1971-07-16 1974-08-14 Blazquez A G Hydraulic shock absolbers
US4031989A (en) * 1975-02-22 1977-06-28 Antonio Giner Blazquez Double effect hydraulic shock absorber
JPS5920712A (en) * 1982-07-26 1984-02-02 Showa Mfg Co Ltd Hydraulic shock absorber
DE4404963A1 (en) * 1993-04-24 1994-10-27 Bilstein August Gmbh Co Kg Controllable vibration damper for motor vehicles
DE4342763A1 (en) * 1993-12-15 1995-06-22 Bilstein August Gmbh Co Kg Adjustable hydraulic suspension strut for vehicle
JP2001088529A (en) * 1999-09-20 2001-04-03 Kayaba Ind Co Ltd Anti-rolling type hydraulic shock absorber

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018108419A1 (en) * 2016-12-16 2018-06-21 Zf Friedrichshafen Ag Hydraulic twin-tube shock absorber

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ES2251293B1 (en) 2007-06-16
WO2005108131B1 (en) 2006-01-05

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