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    • 专利摘要:
    Shock absorber (1) with hydraulic load regulation as a function of frequency, comprising a cylinder (2) and a piston (3) immersed in a hydraulic fluid (5), where the shock absorber (1) comprises a charge regulator (4) which in turn comprises at least one sealed chamber (41, 41 ', 41 ") with a gas inside it, a housing (42, 42', 42"), and at least one displaceable wall (43, 43 ', 43' ', 46) in contact with the hydraulic fluid (5), where the damper (1) is configured so that when the pressure inside the inner chamber (21) of the cylinder (2) reaches a level By default, the hydraulic fluid (5) pushes the at least one displaceable wall (43, 43 ', 43 ", 46) of the at least one sealed chamber (41, 41', 41") of the charge regulator (4), thereby compressing the gas contained within the at least one sealed chamber (41, 41 ', 41 ").
    公开号:ES2655310A1
    申请号:ES201631105
    申请日:2016-08-18
    公开日:2018-02-19
    发明作者:Javier LIZARRAGA SENAR
    申请人:Kyb Europe Headquarters GmbH；
    IPC主号:
    专利说明:


    Shock absorber with hydraulic load regulation according to frequency

    DESCRIPTION
     5
    Object of the invention

    The present invention relates to a shock absorber capable of regulating the hydraulic load of the hydraulic fluid as a function of the frequency of the relative movement between the piston and the cylinder of the shock absorber. 10

    The shock absorber with hydraulic load regulation according to the frequency object of the present invention has application in the field of industry dedicated to the manufacture of mechanical and hydraulic components for machines and, more specifically, in the industry responsible for the manufacture of shock absorbers for 15 vehicles.

    Technical problem to be solved and Background of the invention

    A shock absorber is a device whose function is to mitigate the forces transmitted to the chassis of a vehicle generated during the movement of the vehicle, efforts that can be axial, radial, centrifugal. The purpose of the installation of the shock absorbers in the vehicles is to promote their stability by keeping them in balance in their movement. Another important purpose of the shock absorbers in the vehicles is to guarantee the comfort of the passengers, by absorbing a large part of the forces acting on the vehicle, thus causing the passengers not to perceive, or perceive in an attenuated manner said acting forces on the vehicle. vehicle.

    At present, a large part of the industrially used shock absorbers are basically composed of a cylinder and a piston, where the piston moves within a hydraulic fluid that occupies together with said piston the inner chamber of the cylinder.

    The piston divides the inner chamber of the cylinder into two sub-chambers.

    The piston is provided with conduits that allow the hydraulic fluid to flow from one sub-chamber to the other, as the piston travels longitudinally through the interior of the cylinder, due to the forces acting on the vehicle and which are transmitted 5 to the cylinder and piston.

    Normally, the piston is attached to the chassis of the vehicle while the cylinder is attached to the axle of the vehicle's wheels.
     10
    Due to the low compressibility of the liquids, when a shock absorber is subjected to an external force of great magnitude and of rapid variation in time (high frequency), the hydraulic fluid flows almost instantaneously from one sub-chamber to another of the cylinder , transmitting without external filtering the external forces to the chassis of the vehicle. Therefore, given high and high frequency external forces, the passengers 15 of the vehicle experience the external forces acting on the vehicle to a greater extent, which may lead to a situation of little comfort.

    In this sense, vehicle designers have been urged for years to develop more sophisticated shock absorber designs that somehow mitigate the effect described above.

    One of the dilemmas faced by shock absorber designers is the necessary compromise that must be reached between passenger comfort and vehicle stability. 25

    When the suspension moves in high frequency areas, passenger comfort means that low damping forces are required (soft suspension)

    However, the problem with a soft suspension is that adhesion and stability in the vehicle are lost.

    On the other hand, when the suspension moves in low frequency areas (for example, when reaction forces are generated on the vehicle derived from maneuvers such as cornering at high speed and / or with reduced radius),
    Vehicle stability means that high damping forces (hard suspension) are required.

    The problem with a hard suspension is that comfort is lost inside the vehicle when the firm is irregular or a pothole is traversed. 5

    One way to face the compromise between comfort and stability is to design dampers that, depending on the dynamic and ground conditions, allow the gauge of the ducts that allow the hydraulic fluid to flow from one sub-chamber to another of the cylinder. 10

    There are adjustable hardness dampers on the market that have a thread that makes it possible to dwarf or enlarge the diameter of the piston duct through which the hydraulic fluid (oil) flows, which allows the user to obtain a greater or lesser damping hardness, according to your needs. fifteen

    Another possibility is the use of rheological dampers, these dampers have particles in the fluid that allow altering the properties of said fluid by passing an electric current, hardening or softening the suspension. twenty

    The problem with these shock absorbers, especially the rheological one, is that they are expensive systems to produce and with a high price. Likewise, although said hardness control can be carried out automatically by means of the use of electronics that, by means of sensors and depending on the position of the vehicle chassis, act on the shock absorber (inconvenience: economic cost that this entails ), the usual thing is that it is carried out in a manual way at the user's discretion (inconvenient: it is the user who, under his criteria, establishes control).

    A solution to these problems is that described in document ES 2261747 T3, in which the shock absorber is able to adapt the level of damping force taking into account the frequency of its movement.

    The system described in ES 2261747 T3 allows, by controlling the flow of the hydraulic fluid using a valve system, to generate a greater or lesser resistance 35
    to the flow depending on the frequency of the relative movement between the piston and the cylinder, which results in hardening or softening of the shock absorber.

    However, the problem of this solution lies in the complexity of the valve system necessary for the regulation of the flow of the hydraulic fluid, the size it occupies within the cylinder and the production and economic costs thereof.

    Description of the invention

    In order to provide a solution to the aforementioned problems, the shock absorber with hydraulic load regulation according to the frequency object of the present invention is described below.

    The shock absorber with hydraulic load regulation as a function of the frequency object of the present invention comprises, in a conventional manner, a cylinder which in turn comprises an inner chamber.

    The shock absorber also comprises, in a conventional manner, a piston configured to move in a longitudinal direction of the cylinder along the inner chamber of the cylinder. twenty

    As with other conventional shock absorbers, the piston is immersed in a hydraulic fluid (typically an oil) that occupies the inner chamber of the cylinder.

    The piston divides the volume of the inner chamber of the cylinder into a compression chamber and a traction chamber.

    The piston comprises at least one conduit configured to allow bidirectional flow of hydraulic fluid between the traction chamber and the compression chamber of the cylinder. 30

    In a novel way, the shock absorber with hydraulic load regulation as a function of the frequency object of the present invention comprises a charge regulator located in the inner chamber of the cylinder.
     35
    The charge regulator comprises at least one load regulation chamber and load regulation means comprised within the load regulation chamber.

    The at least one load regulation chamber comprises a housing and at least 5 a movable wall that is in contact with the hydraulic fluid of the inner chamber of the cylinder.

    The displacement of the at least one movable wall allows to increase or decrease the volume of the at least one load regulation chamber. 10

    According to a possible embodiment, the load regulation means comprise at least one spring, with adjustable stiffness and preload.

    Preferably, the at least one charge regulating chamber of the charge regulator is a sealed chamber, and the charge regulating means comprise a gas inside the waterproof chamber.

    The increase or decrease in the volume of the at least one sealed chamber implies respectively an expansion or compression of the gas contained within the at least one sealed chamber.

    The damper is configured so that when the pressure inside the inner chamber of the cylinder reaches a predetermined level, the hydraulic fluid pushes the at least one movable wall of the at least one sealed chamber of the charge regulator 25, thereby compressing the gas contained inside the at least one waterproof chamber.

    In the manner described, it is allowed to relieve the internal pressure of the inner chamber of the cylinder in cases where said pressure reaches a predetermined level. This allows a greater percentage of the external forces acting on the vehicle and applied on the shock absorber to not finally reach the chassis of the vehicle, thus softening the suspension of the vehicle.

    According to a first embodiment, the shock absorber comprises a sealed chamber 35 coupled, by coupling means, to the piston.

    In this case, the sealed chamber is preferably coupled to a piston shaft.

    According to the first embodiment of the shock absorber, the sealed chamber of the charge regulator is coupled to the piston by the side of the compression chamber of the cylinder.

    According to a possible embodiment, the coupling means between the sealed chamber and the piston include a nut tightly connected by its perimeter to the housing of the sealed chamber, and threaded by its central hollow (also in a sealed manner) with the piston shaft

    According to this first embodiment of the shock absorber, a connecting channel travels inside the piston shaft.
     fifteen
    Said connection channel communicates the traction chamber of the cylinder with a space in contact with a first movable wall of the sealed chamber of the charge regulator. This allows the flow of the hydraulic fluid between the traction chamber of the cylinder and the first movable wall, thus enabling the transmission of the pressure of the hydraulic fluid to the gas contained inside the sealed chamber, through the first movable wall.

    According to the first embodiment of the shock absorber, there is a hole in the housing of the sealed chamber that communicates the compression chamber of the cylinder with a space in contact with a second movable wall of the sealed chamber. 25

    This allows the flow of the hydraulic fluid between the compression chamber of the cylinder and the second movable wall, thus enabling the transmission of the pressure of the hydraulic fluid to the gas contained inside the sealed chamber, through the second movable wall. 30

    According to a second embodiment of the shock absorber, the housing of the waterproof chamber has no hole, and the waterproof chamber has no second movable wall.

    In a third embodiment of the shock absorber, the housing of the waterproof chamber comprises a hole that communicates the compression chamber with a space in contact with a first movable wall of the waterproof chamber of the charge regulator.
     5
    In this third embodiment of the shock absorber, the piston shaft does not comprise a connection channel that communicates the traction chamber with a movable wall of the gas-tight chamber. In this third embodiment, the first movable wall of the waterproof chamber is analogous to the second movable wall in the first embodiment. 10

    According to a fourth embodiment of the shock absorber, the charge regulator comprises a first sealed chamber and a second sealed chamber.

    The first sealed chamber is coupled to the piston by the side of the traction chamber, by means of coupling means existing in the housing of the first sealed chamber.

    The second sealed chamber is coupled to one end of the inner chamber of the cylinder. The second sealed chamber is coupled to the bottom of the compression chamber opposite the piston, by means of coupling means existing in the housing of the second sealed chamber.

    According to this fourth embodiment of the shock absorber, there is a hole in the housing of the first sealed chamber that communicates the traction chamber with a space in contact with a movable wall of the first sealed chamber of the charge regulator.

    Also according to this fourth embodiment, there is a hole in the housing of the second sealed chamber that communicates the compression chamber with a space in contact with a movable wall of the second sealed chamber of the charge regulator.

    Preferably, in the contact area between the movable wall of the first sealed chamber and the piston shaft, there are sealing gaskets that 35
    ensure that the gas contained inside the first sealed chamber cannot leave the first sealed chamber, and that the hydraulic fluid cannot penetrate inside the first sealed chamber.

    Also, according to any of the embodiments of the shock absorber, in the contact zone 5 between the at least one movable wall and the housing, there are preferably sealing gaskets that guarantee that the gas contained inside the at least one chamber airtight can not leave the at least one waterproof chamber, and that the hydraulic fluid cannot penetrate inside the at least one waterproof chamber. 10

    The shock absorber object of the present invention comprises means for regulating the pressure of the gas contained within the at least one sealed chamber of the charge regulator, as well as means for controlling the volume of said at least one sealed chamber. fifteen

    By means of the various embodiments described herein, the shock absorber allows to regulate and attenuate the force of the suspension of a vehicle, either in the piston extension stroke, either in the piston compression stroke, or in both extension and compression strokes. of the piston. twenty

    By means of the configuration described in any of the proposed embodiments of the shock absorber, it is allowed that, in the case of relative high-frequency movements between piston and cylinder, the hydraulic fluid transmits a significant percentage of its internal pressure to the sealed chamber and, therefore, to the gas contained in its interior, thus partially discharging the hydraulic fluid, which will stop transmitting to the vehicle chassis the pressure discharged on the charge regulator, thereby softening the suspension of the vehicle.

    On the other hand, when the relative movement between piston and cylinder is not of high frequency, the hydraulic fluid will transmit in a smaller amount its pressure to the gas contained inside the at least one sealed chamber of the charge regulator, so The suspension will be somewhat harder, increasing in these cases the stability of the vehicle.
     35
    It is understood that, since the relative movement between piston and shock absorber is low frequency, the forces transmitted to the chassis of the vehicle, even being of greater magnitude, will not suppose an excessive decrease in the comfort of the passengers, since the passengers withstand better forces Large low frequency than large and repetitive forces. 5

    Through the described shock absorber, a regulation of the hydraulic force generated in the sense of reducing the response of the system (damping force) when working at high frequency is performed, by means of pressure control.
     10
    The principle of operation of the invention consists in increasing the compressibility inherent in all liquids with dissolved gas, in a controlled and regulable manner, in order to retard the generation of force of opposition to the relative movement in a hydraulic system.
     fifteen
    This delay means that when the relative movement generated by the hydraulic force varies at high frequencies, the response of the system (damping force) is less than that in which said movement takes place at a low frequency.

    The low frequency operation gives the shock absorber the necessary time for 20 to develop the level of force that would correspond to it in stationary conditions.

    On the contrary, the high frequencies only allow to reach a level of hydraulic force lower than the stationary one, transmitting as it has been said the rest of the efforts to the watertight chamber and, therefore, to the gas contained inside, which experiences compression .

    The type of behavior described in the previous paragraph, can be used in a shock absorber for car suspensions as follows.
     30
    The displacements of the suspension associated with the dynamic control of the vehicle (stability) take place at a low frequency, around the natural frequency chosen by the vehicle manufacturer.

    Under these conditions, the damper of the invention introduces a small modification in the response of the system, allowing to keep the vehicle dynamics practically unchanged.

    The oscillations introduced by the road and associated with comfort take place at 5 medium and high frequencies.

    The response of a conventional shock absorber associated with these operating conditions introduces force peaks in the passenger compartment and, therefore, acceleration peaks perceived by the user as uncomfortable. 10

    The limited time available for the system to develop its force of opposition to the movement causes, when the shock absorber object of the present invention is introduced, a notable reduction in the maximum force that it is capable of generating. Said decrease in the forces introduced by the invention provides a greater perception of comfort on the part of the passengers.

    Additionally, the progressivity that the present shock absorber with hydraulic load regulation as a function of the frequency contributes to the increase of the force generated by the response of the shock absorber, is positive in any operating regime. twenty

    The shock absorber object of the present invention adapts to high frequency phenomena without major difficulty.

    Likewise, the incorporation of a controlled and progressive delay greatly reduces noise and vibration in those systems or vehicles in which the present shock absorber is installed.

    The magnitude of the displacement of the at least one movable wall is fixed by the balance of pressures reached between the hydraulic fluid and the gas. 30

    It is by means of this displacement of the at least one movable wall that a delay in the increase of the pressure of the hydraulic fluid is induced, delaying in the same way the generation of damping force.
     35
    If this delay is of the order of magnitude of the duration of the displacement induced in the hydraulic system, the maximum force generated by the shock absorber will be less than what it would provide in a steady state. This behavior resembles that of a frequency filter that attenuates high frequencies.
     5
    A low frequency oscillation keeps the stresses on the shock absorber for longer, allowing the floating piston to reach its equilibrium position and generate the level of stationary effort.

    The effect of the damper of the invention is to provide greater progressivity to fluctuations in the force of opposition to the movement it generates.

    The adjustment of the invention is carried out by controlling the volume and pressure of the gas contained in the sealed chamber.
     fifteen
    Higher gas pressure leads to a buffer with a lower response delay, while a reduction in gas pressure has the opposite effect.

    The gas pressure increases more than proportionally depending on the stroke of the movable wall, allowing two work zones to be clearly differentiated. twenty

    The beginning of the displacement of the hydraulic fluid coincides with the beginning of the movement of the movable wall. In this initial phase, the increase in gas pressure associated with its compression is markedly lower than that recorded in the final zone of the displacement of the movable wall. 25

    Thus, it is possible to have an initial zone of movement where the transmission of force from the fluid to the gas is minimal but, if the action is maintained, the system will provide reaction force quickly until it reaches its maximum value.
     30
    On the other hand, the pneumatic base of the application causes the pressure of the gas retained inside the sealed chamber to increase with temperature increases and be reduced with decreases thereof.

    As explained above, an increase in gas pressure leads to a reduction in the filtering effect of hydraulic stress. Now this fact coincides with
    a reduction in the maximum hydraulic force performed by any damping system, based on hydraulic fluids such as oils, due to the reduction in the viscosity of the hydraulic fluid due to the increase in temperature.

    Consequently, the evolution of gas and hydraulic fluid are opposite and 5 tend to compensate, so that at a lower force of opposition to the movement, the system delay decreases.

    If the operating temperature drops, the effects are the opposite, increasing the maximum response force of the hydraulic fluid (due to the increase in the viscosity of the fluid) and also increasing the delay introduced by the charge regulator (due to the reduction of gas pressure).

    Brief description of the figures
     fifteen
    As part of the explanation of at least one preferred embodiment of the shock absorber with hydraulic load regulation as a function of frequency, the following figures have been included.

    Figure 1: Shows a sectional view of a first embodiment of the shock absorber with hydraulic load regulation as a function of frequency.

    Figure 2: Shows a schematic view of the forces acting on the hydraulic load regulator, during the extension stroke of the shock absorber piston, according to the first embodiment of the shock absorber with hydraulic load regulation depending on the frequency.

    Figure 3: Shows a schematic view of the forces acting on the hydraulic load regulator, during the compression stroke of the shock absorber piston, according to the first embodiment of the shock absorber with hydraulic load regulation 30 as a function of frequency.

    Figure 4: Shows a sectional view of a second embodiment of the shock absorber with hydraulic load regulation as a function of frequency, where
    the forces acting on the hydraulic load regulator are schematically observed during the extension stroke of the piston of the shock absorber.

    Figure 5: Shows a sectional view of a third embodiment of the shock absorber with hydraulic load regulation as a function of frequency, where 5 the forces acting on the hydraulic load regulator are observed schematically during the stroke of damper piston compression.

    Figure 6: Shows a sectional view of a fourth embodiment of the shock absorber with hydraulic load regulation as a function of frequency. 10

    Detailed description

    The present invention relates, as already mentioned above, to a shock absorber (1) with hydraulic load regulation as a function of frequency. fifteen

    The shock absorber (1) comprises a cylinder (2) and a piston (3). The cylinder (2) internally comprises an inner chamber (21) along which the piston (3) circulates in their respective extension and compression strokes.
     twenty
    The piston (3) divides the inner chamber (21) into two spaces corresponding respectively to a compression chamber (22) and a traction chamber (23).

    A hydraulic fluid (5) (typically oil) occupies the inner chamber (21) of the cylinder (2), filling all the space of the inner chamber (21) that is not occupied by the piston (3) itself.

    The piston (3) comprises an axle (31) and at least one conduit (32) configured to allow bidirectional flow of the hydraulic fluid (5) between the traction chamber (23) and the compression chamber (22). 30

    When the piston (3) makes its extension stroke, the hydraulic fluid (5) flows, through the conduit (32), from the traction chamber (23) to the compression chamber (22).
     35
    Similarly, when the piston (3) performs its compression stroke, the hydraulic fluid (5) flows, through the conduit (32), from the compression chamber (22) to the traction chamber (23).

    The shock absorber (1) comprises a charge regulator (4) located in the inner chamber 5 (21) of the cylinder (2).

    The charge regulator (4) comprises a sealed chamber (41) which in turn comprises a gas inside. The sealed chamber (41) comprises a rigid housing (42) and at least one first movable wall (43) in contact with the hydraulic fluid 10 (5) of the inner chamber (21) of the cylinder (2).

    The displacement of the first movable wall (43) allows to increase or decrease the volume of the waterproof chamber (41).
     fifteen
    The increase or decrease in the volume of the sealed chamber (41) implies respectively an expansion or compression of the gas contained inside the sealed chamber (41).

    The shock absorber (1) is configured so that when the pressure inside the inner chamber (21) of the cylinder (2) reaches a predetermined level, the hydraulic fluid (5) pushes the first movable wall (43) of the regulator of load (4), thus compressing the gas contained inside the sealed chamber (41).

    In the manner described in the previous paragraph, it is allowed to relieve the internal pressure of the inner chamber (21) of the cylinder (2) in cases where said pressure reaches a predetermined level. This allows that a greater percentage of the external forces acting on the vehicle (not shown) and applied on the shock absorber (1) do not finally reach the chassis of the vehicle, thus smoothing the vehicle suspension.
     30
    Figure 1 shows a schematic sectional view of a first embodiment of the shock absorber (1).

    According to the first embodiment of the shock absorber (1), the sealed chamber (41) of the charge regulator (4) is coupled to the piston (3), by the side of the compression chamber (22), by means of coupling means. The means of
    Coupling can consist, for example, of a nut (44), tightly connected by its perimeter to the housing (42) of the sealed chamber (41), and threaded by its central hollow with the shaft (31) of the piston ( 3).

    Also according to the first embodiment of the shock absorber (1), through a 5 connection channel (33) that runs inside the shaft (31) of the piston (3), the flow of the hydraulic fluid (5) between the traction chamber (23) of the cylinder (2) and a space in contact with the first movable wall (43).

    Also according to the first embodiment of the shock absorber (1), a hole (45) 10 existing in the housing (42) of the sealed chamber (41) allows the flow of hydraulic fluid (5) between the compression chamber (22) of the cylinder (2) and a space in contact with a second movable wall (46) of the sealed chamber (41).

    In the contact area between the first movable wall (43) and the housing (42), as well as in the contact area between the second movable wall (46) and the housing (42), there are sealing gaskets (47 ) that ensure that the gas contained inside the waterproof chamber (41) cannot leave the waterproof chamber (41) and that the hydraulic fluid (5) cannot penetrate inside the waterproof chamber (41).
     twenty
    When the piston (3) performs its extension stroke, as indicated by the arrow above the shaft (31) of the piston (3) in Figure 2, a part of the hydraulic fluid (5) flows from the traction chamber ( 23) towards the compression chamber (22) through the conduit (32), and another part of the hydraulic fluid (5) penetrates from the traction chamber (23), inside the connection channel (33) towards the first movable wall (43) 25 of the watertight chamber (41) of the charge controller (4).

    When, during the extension stroke of the piston (3), the pressure inside the traction chamber (23) reaches a predetermined value, the hydraulic fluid (5) penetrating the connection channel (33) exerts a force on the first movable wall 30 (43) (as shown by the force field on the first movable wall (43) in Figure 2) that overcomes the resistance to displacement of the first movable wall (43) and the resistance to Compression of the gas contained inside the waterproof chamber (41), displacing the first movable wall (43) and reducing the volume of the waterproof chamber (41). 35

    Similarly, when the piston (3) performs its compression stroke, as indicated by the arrow above the shaft (31) of the piston (3) in Figure 3, a part of the hydraulic fluid (5) flows from the chamber of compression (22) towards the traction chamber (23) through the conduit (32), and another part of the hydraulic fluid (5) penetrates from the compression chamber (22), inside the hole (45) towards the second movable wall 5 (46) of the watertight chamber (41) of the charge controller (4).

    When, during the compression stroke of the piston (3), the pressure inside the compression chamber (22) reaches a predetermined value, the hydraulic fluid (5) that penetrates through the hole (45) exerts a force on the second movable wall 10 (46) (as shown by the force field under the second movable wall (46) in Figure 3) that overcomes the resistance to displacement of the second movable wall (46) and the compressive strength of the gas contained inside the watertight chamber (41), displacing the second movable wall (46) and reducing the volume of the watertight chamber (41). fifteen

    Figure 4 shows a schematic sectional view of a second embodiment of the shock absorber (1).

    The second embodiment of the shock absorber (1) differs from the first embodiment of the shock absorber (1) in that, in the second embodiment, the housing (42) of the sealed chamber (41) of the charge regulator (4) has no hole (45) and in which the sealed chamber (41) also lacks the second movable wall (46).
     25
    As in the first embodiment of the shock absorber (1), in the second embodiment of the shock absorber (1), when the piston (3) performs its extension stroke, as indicated by the arrow above the shaft (31) of the piston (3) in Figure 4, a part of the hydraulic fluid (5) flows from the traction chamber (23) to the compression chamber (22) through the conduit (32), and another part of the 30 hydraulic fluid (5) penetrates from the traction chamber (23), inside the connection channel (33) to the first movable wall (43) of the sealed chamber (41) of the charge regulator (4).

    When, during the extension stroke of the piston (3), the pressure inside the traction chamber (23) reaches a predetermined value, the hydraulic fluid (5) that
    penetrates through the connection channel (33) exerts a force on the first movable wall (43) (as shown by the force field on the first movable wall (43) in Figure 4) that overcomes the resistance to displacement of the first movable wall (43) and the compressive strength of the gas contained inside the watertight chamber (41), displacing the first movable wall (43) 5 and reducing the volume of the watertight chamber (41).

    Figure 5 shows a schematic sectional view of a third embodiment of the shock absorber (1).
     10
    The third embodiment of the shock absorber (1) differs from the first embodiment of the shock absorber (1) in that, in the third embodiment, the shaft (31) of the piston (3) lacks a connecting channel ( 33) that runs inside the shaft (31).
     fifteen
    Therefore, only the hydraulic fluid (5) that occupies the compression chamber (22) can flow, through the hole (45) of the housing (42) to the first movable wall (43) of the waterproof chamber (41) .

    The wall of the sealed chamber (41) opposite the hole (45) of the housing (42) and 20 opposite the first movable wall (43) may or may not in turn be a movable wall. In Figure 5 it has been represented as if it were a movable wall, although it could be a non-movable wall.

    Similarly to the first embodiment of the shock absorber, 25 when the piston (3) carries out its compression stroke, as indicated by the arrow above the shaft (31) of the piston (3) in Figure 5, a part of the hydraulic fluid (5) flows from the compression chamber (22) to the traction chamber (23) through the conduit (32), and another part of the hydraulic fluid (5) penetrates from the compression chamber (22) , inside the hole (45) towards the first movable wall (43) 30 of the watertight chamber (41) of the charge regulator (4).

    When, during the compression stroke of the piston (3), the pressure inside the compression chamber (22) reaches a predetermined value, the hydraulic fluid (5) that penetrates through the hole (45) exerts a force on the first movable wall 35 (43) (as shown by the force field under the first movable wall (43)
    in Figure 5) overcoming the resistance to displacement of the first movable wall (43) and the compressive strength of the gas contained inside the watertight chamber (41), displacing the first movable wall (43) and reducing the volume of the waterproof chamber (41).
     5
    Figure 6 shows a schematic sectional view of a fourth embodiment of the shock absorber (1).

    According to the fourth embodiment of the shock absorber (1), the charge regulator (4) comprises a first waterproof chamber (41 ’) and a second waterproof chamber (41’). 10

    The first sealed chamber (41 ') of the charge regulator (4) is coupled to the piston (3), by the side of the traction chamber (23), by means of coupling means existing in the housing (42') of the first waterproof chamber (41 ').
     fifteen
    The second sealed chamber (41 '') of the charge regulator (4) is coupled to one end of the inner chamber (21) of the cylinder (2), at the bottom of the compression chamber (22) opposite the piston (3) ), by means of coupling means existing in the housing (42 '') of the second sealed chamber (41 '').
     twenty
    According to the fourth embodiment of the shock absorber (1), a hole (45 ') existing in the housing (42') of the first sealed chamber (41 ') allows the flow of hydraulic fluid (5) between the traction chamber ( 23) of the cylinder (2) and a space in contact with a first movable wall (43 ') of the first sealed chamber (41') of the charge regulator (4). 25

    In the contact area between the first movable wall (43 ') and the housing (42') of the first waterproof chamber (41 '), as well as in the contact area between the first movable wall (43') of the first sealed chamber (41 ') and shaft (31) of the piston (3), there is at least one seal (47) that guarantees that the gas contained in the interior of the first sealed chamber (41') cannot leave the first sealed chamber (41 ') and that the hydraulic fluid (5) cannot penetrate inside the first sealed chamber (41').

    Likewise, according to the fourth embodiment of the shock absorber (1), a hole (45 ’) existing in the housing (42’) of the second sealed chamber (41 ’) allows the flow of
    hydraulic fluid (5) between the compression chamber (22) of the cylinder (2) and a space in contact with a first movable wall (43 '') of the second sealed chamber (41 '') of the charge regulator (4) .

    In the contact area between the first movable wall (43 '') and the casing (42 '') of the second sealed chamber (41 ''), there are sealing gaskets (47) that guarantee that the gas contained in the inside of the second waterproof chamber (41 '') cannot leave the second waterproof chamber (41 '') and that the hydraulic fluid (5) cannot penetrate inside the second waterproof chamber (41 '').
     10
    According to the fourth embodiment of the shock absorber (1), when the piston (3) performs its compression stroke, a part of the hydraulic fluid (5) flows from the compression chamber (22) to the traction chamber (23) a through the conduit (32) existing in the piston (3), and another part of the hydraulic fluid (5) penetrates from the compression chamber (22), through the hole (45 '') of the second sealed chamber (41 '') 15 towards the first movable wall (43 '') of the second waterproof chamber (41 '') of the charge controller (4).

    When, during the compression stroke of the piston (3), the pressure inside the compression chamber (22) reaches a predetermined value, the hydraulic fluid (5) 20 that penetrates through the hole (45 '') exerts a force on the first movable wall (43 '') of the second watertight chamber (41 '') that overcomes the resistance to displacement of the first movable wall (43 '') and the compressive strength of the gas contained inside of the second waterproof chamber (41 ''), displacing the first movable wall (43 '') and reducing the volume of the second waterproof chamber (41 ''). 25

    Similarly, also according to the fourth embodiment of the shock absorber (1), when the piston (3) performs its extension stroke, a part of the hydraulic fluid (5) flows from the traction chamber (23) to the compression chamber ( 22) through the conduit (32), and another part of the hydraulic fluid (5) penetrates from the traction chamber (23), through the hole (45 ') of the first sealed chamber (41') towards the first movable wall (43 ') of the first waterproof chamber (41') of the charge controller (4).

    When, during the extension stroke of the piston (3), the pressure inside the traction chamber (23) reaches a predetermined value, the hydraulic fluid (5) that
    penetrates through the hole (45 '), exerts a force on the first movable wall (43') of the first waterproof chamber (41 ') that overcomes the resistance to displacement of the first movable wall (43') and the resistance to the Compression of the gas contained inside the first waterproof chamber (41 '), displacing the first movable wall (43') and reducing the volume of the first waterproof chamber (41 '). 5
    权利要求:
    Claims (16)
    [1]

    1. Shock absorber (1) with hydraulic load regulation as a function of frequency, where the shock absorber (1) comprises a cylinder (2) which in turn comprises an inner chamber (21), where the shock absorber comprises a 5 piston (3 ) configured to move in a longitudinal direction of the cylinder (2) along the inner chamber (21), where the piston is immersed in a hydraulic fluid (5) that occupies the inner chamber (21) of the cylinder (2), where the piston (3) divides the volume of the inner chamber (21) into a compression chamber (22) and into a traction chamber (23), where the piston (3) 10 comprises at least one conduit (32) configured to allow bidirectional flow of hydraulic fluid (5) between the traction chamber (23) and the compression chamber (22), characterized in that the shock absorber (1) comprises a charge regulator (4) located in the inner chamber ( 21) of the cylinder (2), where the charge regulator (4) comprises at least one c load regulating mara 15 which in turn comprises a means of load regulation inside, where the at least one load regulation chamber comprises a housing (42, 42 ', 42' ') and at least one movable wall (43, 43 ', 43' ', 46) in contact with the hydraulic fluid (5) of the inner chamber (21) of the cylinder (2), where the damper (1) is configured so that when the pressure in the inside the inner chamber (21) of the cylinder (2) reaches a predetermined level, the hydraulic fluid (5) pushes the at least one movable wall (43, 43 ', 43' ', 46) of the at least one chamber of load regulation of the load regulator (4), thereby compressing the load regulation means comprised within the at least one load regulation chamber 25.

    [2]
    2. Shock absorber (1) with hydraulic load regulation according to the frequency according to claim 1, characterized in that the load regulation chamber is a sealed chamber (41, 41 ', 41' '), and wherein the means of Load regulation 30 comprises a gas comprised inside the sealed chamber (41, 41 ', 41' ').

    [3]
    3. Shock absorber (1) with hydraulic load regulation according to the frequency according to claim 2, characterized in that the sealed chamber (41) of the
    Load regulator (4) is coupled, by coupling means, to the piston (3).

    [4]
    4. Shock absorber (1) with hydraulic load regulation as a function of claim 3, characterized in that the sealed chamber (41) of the load regulator (4) is coupled to an axis (31) of the piston (3) ).

    [5]
    5. Shock absorber (1) with hydraulic load regulation according to the frequency according to claim 4, characterized in that the sealed chamber (41) of the charge regulator (4) is coupled to the piston (3) by the side of the chamber 10 compression (22).

    [6]
    6. Shock absorber (1) with hydraulic load regulation according to the frequency according to claim 5, characterized in that the coupling means comprise a nut (44) tightly connected by its perimeter to the housing (42) of the sealed chamber (41) and threaded by its central hollow with the shaft (31) of the piston (3).

    [7]
    7. Shock absorber (1) with hydraulic load regulation according to the frequency according to claim 5, characterized in that a connecting channel (33) 20 travels inside the shaft (31) of the piston (3), wherein said connecting channel communicates the traction chamber (23) of the cylinder (2) with a space in contact with a first movable wall (43) of the sealed chamber (41) of the charge regulator (4).
     25
    [8]
    8. Shock absorber (1) with hydraulic load adjustment according to the frequency according to claim 7, characterized in that a hole (45) existing in the housing (42) of the waterproof chamber (41) communicates the compression chamber (22 ) with a space in contact with a second movable wall (46) of the sealed chamber (41) of the charge controller (4). 30

    [9]
    9. Shock absorber (1) with hydraulic load regulation according to the frequency according to claim 5, characterized in that a hole (45) existing in the housing (42) of the sealed chamber (41) communicates the compression chamber
    (22) with a space in contact with a first movable wall (43) of the watertight chamber (41) of the charge controller (4).

    [10]
    10. Shock absorber (1) with hydraulic load regulation according to the frequency according to claim 2, characterized in that the charge regulator (4) 5 comprises a first sealed chamber (41 ') and a second sealed chamber (41' ' ), where the first sealed chamber (41 ') is coupled to the piston (3) by the side of the traction chamber (23), by means of coupling means existing in the housing (42') of the first sealed chamber (41 '), and the second sealed chamber (41' ') is coupled to one end of the inner chamber (21) of the 10 cylinder, at the bottom of the compression chamber (22) opposite the piston (3), by means of coupling means existing in the housing (42 '') of the second sealed chamber (41 '').

    [11]
    11. Shock absorber (1) with hydraulic load regulation according to frequency 15 according to claim 10, characterized in that a hole (45 ') existing in the housing (42') of the first sealed chamber (41 ') communicates the traction chamber (23) with a space in contact with a movable wall (43 ') of the first watertight chamber (41') of the charge regulator (4), and a hole (45 '') existing in the housing (42 '') of the second sealed chamber (41 '') communicates the 20 compression chamber (22) with a space in contact with a movable wall (43 '') of the second sealed chamber (41 '') of the charge regulator (4).

    [12]
    12. Shock absorber (1) with hydraulic load regulation according to frequency 25 according to claim 11, characterized in that in the contact area between the movable wall (43 ') of the first waterproof chamber (41') and an axis (31) of the piston (3), there are sealing gaskets (47) that guarantee that the gas contained inside the first sealed chamber (41 ') cannot leave the first sealed chamber (41'), and that the hydraulic fluid (5) no 30 can penetrate inside the first waterproof chamber (41 ').

    [13]
    13. Shock absorber (1) with hydraulic load regulation according to the frequency according to any of claims 2 to 12, characterized in that in the contact area between the at least one movable wall (43, 43 ', 43' ', 46) and 35
    the housing (42, 42 ', 42' '), there are some gaskets (47) that guarantee that the gas contained inside the at least one sealed chamber (41, 41', 41 '') cannot leave the at least one sealed chamber (41, 41 ', 41' ') and that the hydraulic fluid (5) cannot penetrate inside the at least one sealed chamber (41, 41', 41 ''). 5

    [14]
    14. Shock absorber (1) with hydraulic load regulation according to the frequency according to any of claims 2 to 13, characterized in that it comprises means for regulating the pressure of the gas contained within the at least one sealed chamber (41, 41 ', 41' ') of the charge controller (4). 10

    [15]
    15. Shock absorber (1) with hydraulic load regulation according to the frequency according to any of claims 2 to 14, characterized in that it comprises means for regulating the volume of the at least one sealed chamber (41, 41 ', 41' ' ) of the charge controller (4). fifteen

    [16]
    16. Shock absorber (1) with hydraulic load regulation according to the frequency according to claim 1, characterized in that the load regulating means comprise a spring.
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    同族专利:
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE1678044U|1953-09-18|1954-06-16|Opel Adam Ag|LIQUID SHOCK ABSORBER.|
    US4614255A|1979-12-07|1986-09-30|Honda Giken Kogyo Kabushiki Kaisha|Hydraulic shock absorber for vehicles|
    DE3643056A1|1986-12-17|1988-06-30|Bayerische Motoren Werke Ag|Shock absorber|
    ES2035492T3|1988-10-04|1993-04-16|Audi Ag|HYDRAULIC TELESCOPIC SHOCK ABSORBER.|
    US20050230202A1|2004-04-20|2005-10-20|Andreas Nevoigt|Shock absorber with amplitude damping|
    WO2008037372A1|2006-09-26|2008-04-03|Zf Friedrichshafen Ag|Noise-optimized vibration damper|
    法律状态:
    2018-11-30| FG2A| Definitive protection|Ref document number: 2655310 Country of ref document: ES Kind code of ref document: B1 Effective date: 20181130 |
    2019-09-12| FA2A| Application withdrawn|Effective date: 20190906 |
    优先权:
    申请号 | 申请日 | 专利标题
    ES201631105A|ES2655310B1|2016-08-18|2016-08-18|Shock absorber with hydraulic load regulation according to frequency|ES201631105A| ES2655310B1|2016-08-18|2016-08-18|Shock absorber with hydraulic load regulation according to frequency|
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