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    • 专利摘要:
    Variable load control system in a hydraulic device. The hydraulic device comprises a tubular casing inside which is located a rod to which a piston that separates an upper space and a lower space filled with a hydraulic fluid, so that during the mobility of the plunger and rod, these two elements are fixed together. They move relative and axially together inside the tubular housing, passing the hydraulic fluid through the interior of the tubular housing, passing the hydraulic fluid from one space to the other varying its volumes. It also comprises a modular mechanism located inside the lower space, so that by means of this modular mechanism the damping is regulated at the end of the maximum compression of the hydraulic device and also in other relative positions. (Machine-translation by Google Translate, not legally binding)
    公开号:ES2561132A1
    申请号:ES201431107
    申请日:2014-07-23
    公开日:2016-02-24
    发明作者:Javier LIZARRAGA SENAR
    申请人:KYB Suspensions Europe SA；
    IPC主号:
    专利说明:

    VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE
    DESCRIPTION
    OBJECT OF THE INVENTION

    The present invention, as expressed in the statement of this specification 5, refers to a variable load control system in a hydraulic device that has the purpose of controlling the development of hydraulic load in at least some time of its operation.
    The system is applicable to hydraulic devices, such as shock absorbers, managing to reduce the problems of abruptness, during a first run that ends in a maximum compressed and also during a second run that ends in a maximum extended, so that the attenuation of roughness is controlled especially at the end of the first and second runs of the hydraulic device.
    Therefore, the system of the invention has the purpose of providing damping in the hydraulic device as a function of the length of the shock absorber at every 15 moments and also as a function of the linear speed of the shock absorber when it is active, both when it mobilizes towards its maximum extension and / or when it mobilizes in the opposite direction towards its maximum compression.
    It is further emphasized that the system of the invention allows a wide and varied range of geometries, arrangements and materials, ensuring its adaptability and configurability to the boundary conditions with dimensions in each application case.
    Therefore, in the invention, an operation of the hydraulic device has been chosen as a hydraulic understanding stop in a vehicle shock absorber.
    BACKGROUND OF THE INVENTION
    At present, some hydraulic devices, such as shock absorbers, comprise two parts assembled together.
    A first part comprising a piston rod assembly, and a second part comprising a housing that includes a tube with sufficient cylindricalness so that a piston rod or piston assembly can slide inside in the presence of a hydraulic fluid. 30
    This assembly allows to decouple the movement of the solidarity assembly to the tubular housing of the movement of the solidarity assembly to the piston rod assembly, so that the hydraulics filter, partially or totally, the frequencies that are not desired to be transmitted from one assembly to another.
    In response to the geometric impositions of the physical environment where the shock absorber 5 operates, the maximum stroke of the piston allowed inside the housing (stroke of the shock absorber), is limited. In certain devices these limitations are implemented through mechanical stops:
    - When the minimum length of the shock absorber is limited, these stops are known as compression stops, maximum compresses, etc. 10
    - When the maximum length of the shock absorber is limited, these stops are known as bounce stops, maximum extension, etc.
    In certain applications of the shock absorber, the relative abruptness of these mechanical stop mechanisms may be undesirable, due to a lack of comfort, excessive noise, deterioration due to repeated use, etc. fifteen
    DESCRIPTION OF THE INVENTION
    In order to achieve the objectives and avoid the inconveniences mentioned in the previous sections, the invention proposes a variable load control system in a hydraulic device, where the hydraulic device comprises a tubular housing inside which a rod is located to which jointly fixes a piston that separates an upper space and a lower space filled with a hydraulic fluid, so that during the mobility of the piston and rod, these two elements move together in both directions of an axial direction through the interior of the tubular housing, passing the hydraulic fluid from one space to another by varying its volumes; where the piston advances towards a maximum compression position of the hydraulic device in which the displacement of the piston towards the maximum compression position progressively reduces the volume of the lower space; the hydraulic device also adopting a resting position of maximum extension.
    It comprises a modular mechanism located inside the lower space of the tubular housing closed by its lower end by means of a cover. 30
    The upper space and the lower space communicate with each other through through perforations established in the plunger.
    The modular mechanism comprises an upper tubular head within which a lower tube is fitted and guided at the lower end of which an annular support is embedded, the upper tubular head having axial mobility when moving in a downward direction 5 towards the position of maximum compression of the hydraulic device, such as when moving in the opposite direction up to the position of maximum extension of the hydraulic device.
    The upper tubular head integrates through its wall through openings that communicate an internal chamber delimited by the inner faces of the lower tube and upper tubular head 10, with an annular outer chamber delimited by the inner face of the tubular housing and the outer faces of the head upper tubular and lower tube.
    The annular support has through holes that communicate with the outer annular chamber.
    In one embodiment, the through holes of the annular support are faced with a front disk fixed to the lid; where the combination of the through holes and the front disk constitute a valve device that regulates the passage of hydraulic fluid through those through holes when the annular support rests on its lower face against the front disk.
    In another alternative embodiment to that described in the previous paragraph, the front disk 20 is dispensed with, whereby the through holes of the annular support are now facing the cover; where the combination of the through holes and the cover constitute a valve device that regulates the passage of hydraulic fluid through those through holes when the annular support rests on its lower face against the front disk.
    The annular support fits against the inner face of the tubular housing. 25
    A lower face of the annular support comprises a lower recess where the through holes open while an upper face of the annular support comprises a recess
    upper where a lower end of the lower tube is embedded.
    The through openings of the upper tubular head comprise through slots that reach a lower edge of the upper tubular head.
    In one embodiment, the upper tubular head of the modular mechanism is attached to the plunger, while in another alternative embodiment, the upper tubular head of the modular mechanism and the plunger are two independent elements that are separated from each other.
    In one embodiment, the modular mechanism is complemented by a coaxial spring that works under compression and whose ends abut against the annular support and also against radial extensions of the upper tubular head, which fit against the inner face of the tubular housing, the upper tubular head having axial mobility both against the resistance of the coaxial spring when it travels in a downward direction against the resistance of the coaxial spring towards the maximum compression position of the hydraulic device, and when it travels in the opposite direction towards up towards the position of maximum extension of the hydraulic device in which the coaxial spring tends to move axially upward to the upper tubular head; the coaxial spring being located inside the annular outer chamber.
    The rod integrates a lower extension that extends below the plunger; where in some positions of the damping device, that lower extension fits snugly into the lower tube, that gap defining an annular passage of the hydraulic fluid.
    The upper tubular head integrates a trunk-conical upper mouth.
    In one embodiment, the upper head of the annular mechanism includes a region of lower surface hardness than the area of the piston with which it contacts; where the initial contact between a part of the piston and the upper tubular head when they approach between 25 yes is a damped contact that is carried out by that region of less hardness
    In line with what was said in the previous paragraph, the region of least surface hardness is determined by an annular body attached to an upper edge of the upper tubular head.
    Considering the embodiment in which the coaxial spring is not included, the lower tube assembly and annular support are joined by interference with the tubular housing, where the annular support is fixedly attached to the tubular housing, so that in this case The coaxial spring is not necessary to restore the original position of the system of the invention after a duty cycle. 5
    Thus, the variable load control system of the invention is relevant when mitigating problems arising from abrupt operation of the hydraulic device as specified below.
    The upper tubular head contacts the piston of the hydraulic device and marks the entry into operation of the system. 10
    The front disk, in combination with the through holes of the annular support, constitute a valve device for regulating the passage of fluid through such through holes, which flow into the coaxial outer chamber.
    The through grooves located in the wall of the upper tubular head control the passage section of the hydraulic fluid through them depending on the relative position 15 between the lower tube and the upper tubular head itself which is the element that travels with respect to the tube lower.
    The coaxial spring assembled by interference with the annular support and upper tubular head, has the mission of returning the system to its initial state after a work cycle.
    Thus, with the system of the invention it is possible to provide damping according to the length and speed of the hydraulic device. In addition, its design is such that it provides a function for a wide and varied range of geometries, arrangements and materials, ensuring its adaptability and configurability to the specific contour conditions in each application case.
    Next, in order to facilitate a better understanding of this descriptive report and forming an integral part thereof, some figures are attached in which the object of the invention has been shown as an illustrative and non-limiting nature.
    BRIEF DESCRIPTION OF THE DRAWINGS
    Figure 1.- Shows a sectioned elevation view of a hydraulic device incorporating the variable load control system, object of the invention. The hydraulic device 30 is a shock absorber that is in a position of maximum extension.
    Figure 2.- Shows a sectional elevation view of the hydraulic device similar to that shown in Figure 1, where the shock absorber is located in a position close to its maximum extent.
    Figure 3.- It shows a view similar to the previous ones where the shock absorber is in an intermediate position. 5
    Figure 4.- Shows a sectioned elevation view where the shock absorber is in a position close to its maximum compression.
    Figure 5.- Represents a sectional view of the shock absorber where a second embodiment is highlighted that has some differences with respect to the first embodiment shown in the previous figures. 10
    Figure 6.- Shows a sectional view of the shock absorber that presents a third embodiment of the invention that has differences with respect to that shown in the previous figures.
    Figure 7.- Shows a perspective view of a modular mechanism that is housed inside a tubular housing below a piston integral with a rod that moves axially in both directions through the interior of the tubular housing during the operation of the shock absorber. .
    Figure 8.- Represents a perspective view of the modular mechanism also shown in the previous figure.
    Figure 9.- Shows a sectional view of the shock absorber presenting a fourth embodiment of the invention that has a smaller number of geometric elements for its implementation.
    DESCRIPTION OF AN EXAMPLE OF EMBODIMENT OF THE INVENTION
    Considering the numbering adopted in the figures, the variable load control system in a hydraulic device contemplates the following nomenclature used in the description:
    1.- Tubular housing
    2.- Modular mechanism
    3.- Stem
    3rd.- Lower extension
    4.- Embolo
    4th.- Perimeter skirt
    5.- First upper space
    6.- Second lower space 5
    7.- Cover
    8.- Through perforations
    9.- Annular grooves
    10.- Upper tubular head
    10a.- Radial extensions 10
    11.- Bottom tube
    12.- Ring support
    12a.- Upper recess
    12b.- Lower recess
    13.- Coaxial spring 15
    14.- Front disk
    15.- Through holes
    16.- Annular outer chamber
    17.- Internal chamber
    18.- Trunk-conical upper mouth 20
    19.- Through slots
    20.- Highlight
    21.- Annular step
    22.- Central body
    23.- Upper level.
    24.- Annular body.
    The hydraulic device shown in the figures is a shock absorber arranged in a vertical direction comprising a tubular housing (1) within which the modular mechanism (2) is housed above which a rod (3) jointly and severally attached is located. 5 to a piston (4) that separates a first upper space (5) above the piston (4) and a second lower space (6) disposed below the piston (4), being basically located in this second lower space (6) the assembly of the modular mechanism (2).
    Below the modular mechanism (2) and closing the tubular housing (1) is a cover (7) fixed to the lower end of said tubular housing (1). 10
    The mentioned spaces, upper (5) and lower (6), communicate with each other by means of through holes (8) established in the piston (4) to allow the passage of a hydraulic fluid when the shock absorber is in motion.
    The piston (4) integrates a perimeter skirt (4a) whose outer face adjusts against the inner face of the tubular housing (1), at the same time as such outer face of the perimeter skirt (4a) 15 has a set of annular grooves ( 9).
    In one embodiment, the plunger (4) is separated from the modular mechanism (2) without being joined together, while in another embodiment, the plunger (4) is attached to the modular mechanism (2) through the perimeter skirt (4a) of said plunger (4).
    When the plunger (4) is separated from the modular mechanism (2) without being joined together, 20 in one embodiment of the invention, the upper tubular head (10) includes a region of less surface hardness than the hardness of the plunger material ( 4), so that when the piston (4) and modular mechanism (2) approach each other until they contact each other, this initial contact between the perimeter skirt (4a) and the upper tubular head (10) is a soft damped contact which results in a better operation of the hydraulic device 25.
    For this, the region of least hardness in an embodiment of the invention is determined by an annular body (24) attached to an upper edge of the upper tubular head (10).
    The modular mechanism (2), as shown more clearly in Figures 7 and 8, comprises an upper tubular head (10) into which a lower tube 30 (11) is fitted and guided at whose lower end a support is coupled cancel (12), completing the
    Modular mechanism (2) with a coaxial spring (13) that works under compression and whose ends stop against the annular support (12) and also against radial extensions (10a) of the upper tubular head (10), which fit against the internal face of the tubular housing (1) ensuring correct guidance of the upper tubular head during its axial mobility within the tubular housing (1), both against the resistance of the coaxial spring (13) when the upper tubular head ( 10) travels in a downward direction against the resistance of the coaxial spring (13) towards the maximum compression position of the shock absorber, such as when it moves in the opposite direction towards the maximum extension position of the shock absorber in which the coaxial spring (13) tends to axially move the upper tubular head (10) upwards. 10
    The annular support (12) has a first upper recess (12a) where the lower end of the lower tube (11) is embedded, with a second lower recess (12b) facing a front disc (14) fixed to the cover (7) ) that closes the lower end of the tubular housing (1).
    The annular support (12) also incorporates through holes (15) that connect the lower recess (12b) of said annular support (12) with an annular outer chamber (16) outside the lower tube (11), so that such outer annular chamber (16) is basically delimited between the inner face of the tubular housing (1) and the outer faces of the lower tube (11) and upper tubular head (10). It should be noted that the coaxial spring (13) of the modular mechanism 20 (2) is housed inside the annular outer chamber (16).
    The annular outer chamber (16) is complemented by an internal chamber (17) delimited by the inner faces of the lower tube (11) and upper tubular head (10). It has an upper trunk-conical mouth (18) in an inverted position.
    In some positions of the modular mechanism (2), as will be described later, the bottom of the lower recess (12b) of the annular support (12) abuts against the front disk (14), at least partially sealing the through holes ( 15) of the annular support (12), which will restrict or even cancel the passage of hydraulic fluid through the through holes (15) when the shock absorber moves to the position of maximum compression reducing its length. 30
    A part of the upper tubular head wall (10) has through slots (19) that allows the hydraulic fluid to pass between the outer annular chamber (16) and the inner chamber (17) in some relative positions between the upper tubular head (10) and the
    lower tube (11), reaching the maximum passage section when the shock absorber is in the position of maximum extension in which the coaxial spring (13) is at rest fully extended without tension.
    In contrast, in the position of maximum compression of the shock absorber, the entire length of the through grooves (19) are faced with the lower tube (11), whereby the section of passage of the hydraulic fluid through the grooves interns (19) is null. In this case the hydraulic fluid is restricted to the passage section of the through holes (15) of the annular support (12) with the limitation made by the front disc (14) when it stops against the bottom of the inner recess (12b) of the ring support (12).
    It should be noted that as the shock absorber approaches the position of maximum 10 compression, the section of fluid passage between the annular outer chamber (16) and the inner chamber (17) that flows into the upper space is progressively reduced (5) arranged above the plunger (4). This reduction of hydraulic fluid passage is achieved with a valve device determined by the combination of the through holes (15) of the annular support (12) and the frontal disk (14) faced with the lower recess (12b) of that annular support (12) where such through holes (15) flow.
    When the shock absorber reaches its maximum compression, the upper tubular head (10) stops at its lower edge against the annular support (12) which is in turn against the cover (7) that closes the lower end of the tubular housing (one). More specifically, the annular support (12) has an upper shoulder (20) against which the upper tubular head (10) stops in the position of maximum compression.
    On the other hand, the rod (3) has a lower extension (3a) that extends down below the piston (4), so that in the position of maximum compression of the shock absorber and also in positions close to maximum compression ( Figure 4), that lower extension (3a) of the rod (3) fits snugly into the lower tube (11), this clearance constituting an annular passage (21) of the hydraulic fluid passage that enhances the braking of the rod assembly (3) and piston (4) when the shock absorber approaches maximum compression.
    The maximum extension position of the shock absorber is shown in Figure 1 and also in Figures 2, 5 and 6.
    In figure 1 the plunger (4) is separated from the upper tubular head (10), while
    in figures 5 and 6 the upper head (10) is attached to the skirt (4a) of the plunger (4). In this case, when the shock absorber tends to recover its position of maximum extension, the upward movement of the piston (4) draws in the case shown in Figure 5 the assembly of the modular mechanism (2) separating from the cover (7) and also of the front disk (14). In other cases, the plunger (4) drags only the upper tubular head 5 (10).
    In accordance with what is shown in Figure 1, when the shock absorber tends to recover its position of maximum extension, the piston (4) does not drag to the modular mechanism (2), so that in this case the upper tubular head (10) recovers its position towards maximum extension by the action of the coaxial spring (13).) 10
    As the rod (3) and piston (4) assembly move down towards the position of maximum compression, the upper tubular head (10) descends against the resistance of the coaxial spring (13), gradually reducing the pitch of hydraulic fluid between the outer annular chamber (16) and the internal chamber (17) through the through slots (19) of the upper tubular head (10), the hydraulic fluid 15 finally flowing from the inner chamber (17) towards the first upper space (5) above the plunger (4). The passage of the fluid is also carried out through the through holes (15) of the annular support (12) that is part of the valve device (2) formed by the combination of those through holes (15) and front disc (14).
    In the final section of the plunger lowering (4) the lower extension (3a) of the rod (3) 20 is introduced into the lower tube (11) further restricting the passage of the hydraulic fluid, as previously mentioned.
    On the other hand, when the shock absorber moves towards the position of maximum extension, aided by the tension of the coaxial spring (13), there is a suction effect on the hydraulic fluid by running the hydraulic fluid from the first upper space (5) over 25 of piston (4) towards the second lower space (6) where the assembly of the modular mechanism (2), as well as the internal chamber (17) and annular outer chamber (16).
    The front disk (14) is fixed to the cover (7) by a central body (22).
    It should also be noted that the annular support (12) fits against the inner face of the tubular housing (1).
    According to the position of the modular mechanism (2) shown for example in Figure 1, the
    rod (3) descends during the compression stroke of the shock absorber. Therefore, in the instants prior to the entry into operation of the modular mechanism (2), the rod (3) is in a position such that the skirt (4a) of the piston (4) does not contact any element of the modular mechanism ( 2). That is, the skirt (4a) of the piston (4) is located in an area of the tubular housing (1) above an upper level (23) at the point 5 of entry into operation, so that that upper level (23 ) cited corresponds to the upper edge of the upper tubular head (10). In this situation, the coaxial spring (13) keeps the upper tubular head (10) and lower tube (11) to its maximum extent. The hydraulic fluid has freedom of movement from the piston (4) to the valve device that combines the front disk (14) and the through holes (15) 10 of the annular support (12). When the hydraulic device comes into operation, the sequence of events is as follows.
    The skirt (4a) of the piston (4) contacts the upper edge of the upper tubular head (10), so that the passage of hydraulic fluid out of that upper tubular head (10) is impeded and the lower space (6 ) is divided into two zones: 15
    The inner compression chamber (17) and the outer annular compression chamber (16) as well.
    The inner chamber (17) is defined superiorly by the inner area of the piston (4), inner diameter of the skirt (4a), the upper trunk-conical mouth (18) of the upper tubular head (10), the inner face of the lower tube (11), an inner region of the annular support 20 (12) and the front disk (14). In the inner chamber (17), the passage of hydraulic fluid from the piston (4) to the valve device remains unchanged, as is the normal operation of the shock absorber.
    The annular outer chamber (16) is defined superiorly by an outer and lower portion of the skirt (4a) of the plunger (4), outer surfaces of the upper part of the upper tubular head (10), the outer face of the lower tube (11), an outer region of the annular support (12) and the inner face of the tubular housing (1).
    In the outer annular chamber (16) the fluid passage is carried out towards the internal chamber (17) through the through slots (19) of the upper tubular head (10) and the through holes (15) of the annular support (12) ). Initially, the through holes (15) of the annular support 30 (12) are totally or partially closed by the front disk (14) fixed to the cover (7) that closes the lower end of the tubular housing (1).
    It may happen that, by construction, the perimeter skirt (4a) touches the upper edge of the upper tubular head (10) without interference between the inner diameter of said upper tubular head (10) and the outer diameter of the lower tube (11) . In this case, the perimeter skirt (4a) of the piston (4) comes into contact with the upper tubular head (10) when the rod (3) and piston (4) assembly descends. 5
    The skirt (4a) of the piston (4) pushes on the upper edge of the upper tubular head (10), forcing its descent and compressing the coaxial spring (13). The greater the compression of the shock absorber, the greater the descent of the upper tubular head (10) and, therefore, the greater the interference of the closure between the upper tubular head (10) and the lower tube (11), so that it progressively decreases the passage section through the 10 through slots (19) of the upper tubular head (10).
    Initially, the valve device almost completely seals the passage of hydraulic fluid through the through holes (15) of the annular support (12), whereby the evacuation of the volume of hydraulic fluid enclosed in the annular outer chamber (16) towards the Inner chamber (17) is made through the through slots (19). As the passage section decreases, the pressure in the annular outer chamber (16) increases.
    This control mode generates a soft damper start whose load depends on the position of the damper (greater or lesser section of passage through the through slots (19) and speed), which generates a force that is a quadratic function of the speed. twenty
    When the passage section of the through grooves (19) is small enough, the evacuation of the hydraulic fluid generates sufficient pressure to overcome the closing rigidity of the valve device, the through holes (15) of the annular support (12) opening in a manner Pressure controlled.
    This control mode, added to the previous one, means that the load does not increase excessively with increasing speed. The quadratic shape of the load curve is corrected. Thus, for the same position of the shock absorber within this zone, the load increases practically linear with the speed.
    When the bottom tube (11) completely seals the through slots (19), the only way out of the hydraulic fluid is the through holes (15) of the annular support (12). At this point, when the valvular device reaches its maximum opening, the load increase becomes quadratic again. However, the passage area or section is sufficiently
    wide enough for the quadratic effect to barely influence. In fact, the most noteworthy is that the point of maximum load is slightly ahead with speed, which generates an additional advantage when strong compression appears.
    If a block structure is formed (when the upper tubular head (10) by its lower edge contacts the annular support (12), the transmission of force is carried out through the following chain of elements: piston ( 4), upper tubular head (10) and annular support (12) The lower edge of the upper tubular head (10) rests on the annular support (12) by sealing the through holes (15) by means of the front disk (14), which generates a hydraulic block in the outer annular chamber (16) When this overpressure may be undesirable because it affects the piston (4) and the annular support (12), a conventional piece of mechanical stop is used.
    At the start of the traction stroke towards the maximum extension position of the shock absorber, the rod (3) rises so that the skirt (4a) of the piston (4) ceases the pressure on the upper tubular head (10). The annular outer chamber (16) stops decreasing and begins to grow, whereby the pressure drops and the hydraulic fluid flow is reversed, allowing the valve device to close the through holes (15). The pressure of the annular outer chamber (16) decreases to equalize with the pressure of the inner chamber (17) and the piston (4) separates from the upper tubular head (10), allowing the passage of hydraulic fluid between the outer surface of the upper tubular head (10) and the inner face of the tubular housing (1). twenty
    The coaxial spring (13) tends to decompress and return to its equilibrium position. Being assembled at its ends with interference to the upper tubular head (10) and the annular support (12) and, in turn, this annular support (12) to be with the tubular housing (1), the assembly reaches the position of rest and does not move.
    At the beginning of the traction or extension of the shock absorber, when the direction of the flow of hydraulic fluid 25 is reversed and the valve device is closed, the passage towards the annular outer chamber (16) is carried out through the through holes (15) of the annular support (12) and through the through slots (19) of the upper tubular head (10), unless these have been completely covered by the lower tube (11).
    Since the flow through these passages is insufficient to supply hydraulic fluid 30 from the inner chamber (17) to the annular outer chamber (16), the fact that the plunger (13) joins the action of the coaxial spring (13) 4) ascends faster than the upper tubular head (10) and sucks it, which causes a depression in the outer chamber
    annular (16), such that the upper tubular head (10) is braked and slightly separated from the plunger (4), allowing the entry of hydraulic fluid. The upper tubular head (10) follows the piston (4) until it reaches the rest position.
    It should be noted that, as illustrated in the perspective of Figures 7 and 8 by way of non-limiting example, the basic geometric shapes of the design tend to be generated by 5 revolution along the axis of the rod (3). However, this is not mandatory, since the final form will depend on the variation of the area you want to achieve, as well as other specifications such as weight, resistance, inertia, etc. One of the advantages of the present design is that the final finishing of the pieces can be done piece by piece to optimize the continuous control of the passage area. In this aspect the following is observed. 10
    The whole of the valve device is key in the invention, since the control of the braking pressure of the compression stop depends on its configuration, unlike in other inventions of a similar nature. In this sense, the geometry of the valve device is not tied exclusively to that illustrated in the figures.
    It can consist of one or more valve devices, whose accumulated stiffness 15 will mark the behavior of the stop.
    It can have different geometries of holes or windows for the passage or, in general, any kind of groove that contributes to the way in which the hydraulic fluid flows to the annular support (12).
    It can be manufactured by different methods, such as stamping, sintering, machining, etc. and in any material capable of withstanding the solicitations required during its operation, such as steel, bronze, aluminum, etc.
    The upper tubular head (10) fulfills the function of load variation depending on the position. Again, its geometry is not tied exclusively to that illustrated in the figures. 25
    The through grooves (19) of the upper tubular head (10) can be made by one or more grooves, holes or windows, and in general, any kind of groove that positively contributes to the way in which the passage section varies by increasing the area of interference between the upper tubular head (10) and the lower tube (11) to generate an input of greater or lesser abruptness. 30
    It can be manufactured in metallic, composite or plastic material, according to the requirements and
    complication of the slits or holes made.
    The lower tube (11) progressively covers the through slots (19) of the upper tubular head (10). However, its geometry does not have to be solid, being able to have grooves that communicate the inner chamber (17) and the outer annular chamber (16), so that the evolution of the load has a greater or lesser abruptness. 5
    The annular support (12) supports the valve device in combination with the front disk (14). Again, its geometry is not linked exclusively to that illustrated in the figures and can have a variety of grooves to control the variation in load when the pressure in the annular outer chamber (16) is such that the valve device opens the passage of hydraulic fluid . 10
    As shown in Figure 9, the versatility of the system of the invention allows the annular support (12) to rest directly on the cover (7) regardless of the front disk (14), counting the annular support (12) and the cover (7) with the grooves necessary to control the load. One could also dispense with part or all of the geometric elements between the annular support (12) and the cover (7) that are part of the valve device.
    The coaxial spring (13) is responsible for returning the assembly to its initial position, as well as providing load dependent on the position. To optimize the development of the load and the return of the assembly to its position, the coaxial spring (13) can have constant or variable stiffness and be composed of a thread with a section of free choice in terms of shape and size or by an accumulation of rings It can be fixed by interference or by an additional piece.
    However, an embodiment is also provided in which the coaxial spring (13) is dispensed with, as shown in Figure 6, where the upper head (10) is attached to the skirt (4a) of the plunger. 25
    Therefore, considering the embodiment in which the coaxial spring (13) is not included, the lower tube assembly (11) and annular support (12) are joined by interference with the tubular housing (1), where the annular support (12) is fixed to the tubular housing (1) immovably, so that in this case the coaxial spring (13) is not necessary to restore the original position of the hydraulic device after a duty cycle. 30 In this case, the upper tubular head (10) is attached to the perimeter skirt (4a) of the plunger (4).
    In line with what was said in the previous paragraph, the hydraulic device begins to function when an upper part of the lower tube (11) enters into a lower part of the upper tubular head (10), accompanying the movement of the piston (4) with the that said upper tubular head (10) is integral.
    Given the versatility and conjugability of the invention, the assembly can be used positioned for various applications. As regards the shock absorber, the invention can be applied as a hydraulic compression or hydraulic rebound stop. It is valid for any monotube or bitube technology and can be installed in the main body of the shock absorber or in neighboring bodies, for example, in hydraulic fluid reserve chambers. 10
    In general, the invention is applicable to any hydraulic device intended to be part of a structure, fixed or mobile, to provide a mechanical-hydraulic limit switch as in structures (solar panels, metal structures for buildings, etc.) or in motor vehicles.
    fifteen
    权利要求:
    Claims (15)
    [1]
    1.- VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE, where the hydraulic device comprises a tubular housing inside which a rod is located to which a piston that separates an upper space and a lower space filled with a hydraulic fluid is fixedly fixed , so that during the mobility of the piston and rod, these two elements move together in both directions of an axial direction through the interior of the tubular casing, passing the hydraulic fluid from one space to the other varying its volumes; where the piston advances towards a maximum compression position of the hydraulic device in which the displacement of the piston towards the maximum compression position progressively reduces the volume of the lower space; the hydraulic device also adopting a resting position of maximum extension;
    Characterized by:
    - comprises a modular mechanism (2) located inside the lower space (6) of the tubular housing (1) closed at its lower end by means of a cover (7); fifteen
    - the upper space (5) and the lower space (6) communicate with each other through through holes (8) established in the plunger (4);
    - the modular mechanism (2) comprises an upper tubular head (10) into which a lower tube (11) is fitted and guided at the lower end of which an annular support (12) is embedded, the upper tubular head (10) having mobility axial when moving 20 in a downward direction towards the maximum compression position of the hydraulic device, such as when moving in the opposite direction upward towards the position of maximum extension of the hydraulic device;
    - the upper tubular head (10) integrates through its wall through openings that communicate an internal chamber (17) delimited by the inner faces of the lower tube (11) 25 and upper tubular head (10), with an annular outer chamber (16 ) delimited by the inner face of the tubular housing (1) and the outer faces of the upper tubular head (10) and lower tube (11);
    - the annular support (12) has through holes (15) that communicate with the outer annular chamber (16).
    [ 2]
     2. VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE, according to claim 1, characterized in that the through holes (15) of the annular support (12) are faced with a front disk (14) fixed to the cover (7) ; 5 where the combination of the through holes (15) and the front disk (14) constitute a valve device that regulates the passage of hydraulic fluid through those through holes (15) when the annular support (12) rests on its lower face against the front disk (14).
    [3]
    3. VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE, according to claim 1, characterized in that the through holes (15) 10 of the annular support (12) face the cover (7); where the combination of the through holes (15) and the cover (7) constitute a valve device that regulates the passage of hydraulic fluid through those through holes (15) when the annular support (12) rests on its lower face against the cover ( 7).
    [4]
    4.- VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE, according to any one of the preceding claims, characterized in that the annular support (12) adjusts against the inner face of the tubular housing (1).
    [5]
    5. VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE, according to any one of the preceding claims, characterized in that a lower face of the annular support (12) comprises a lower recess (12b) where 20 through holes (15) flow .
    [6]
    6. VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE, according to any one of the preceding claims, characterized in that an upper face of the annular support (12) comprises an upper recess (12a) where a lower end of the lower tube is embedded (eleven). 25
    [7]
    7. VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE, according to any one of the preceding claims, characterized in that the through openings of the upper tubular head (10) comprise through slots (19) that reach a lower edge of the tubular head upper (10).
    [8]
    8.- VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE, according to any one of the preceding claims, characterized in that the upper tubular head (10) of the modular mechanism (2) is attached to the piston (4).
    [9]
    9.- VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE, according to any one of the preceding claims 1 to 7, 5 characterized in that the upper tubular head (10) of the modular mechanism (2) and the piston (4) are two independent elements that are separated from each other.
    [10]
    10.- VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE, according to any one of the preceding claims, characterized in that the modular mechanism (2) is complemented by a coaxial spring (13) that works at 10 compression and whose ends are abutted against the annular support (12) and also against radial extensions (10a) of the upper tubular head (10), which fit against the inner face of the tubular housing (1), the upper tubular head (10) having axial mobility both against the resistance of the coaxial spring (13) when it travels in a downward direction against the resistance of the coaxial spring (13) 15 towards the maximum compression position of the hydraulic device, such as when it travels in the opposite direction upwards towards the position of maximum extension of the hydraulic device in which the coaxial spring (13) tends to move the upper tubular head (10) axially upwards; the coaxial spring (13) being located inside the annular outer chamber (16). twenty
    [11]
    11. VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE, according to any one of the preceding claims, characterized in that the rod (3) integrates a lower extension (3a) that extends below the plunger (4); where in some positions of the damping device, that lower extension (3a) fits comfortably inside the lower tube (11), that clearance defining an annular passage (21) of the hydraulic fluid.
    [12]
    12.- VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE, according to any one of the preceding claims, characterized in that the upper tubular head (10) integrates a trunk-conical upper mouth (18).
    [13]
    13.- VARIABLE LOAD CONTROL SYSTEM IN A DEVICE 30
    HYDRAULIC, according to claim 9, characterized in that the upper head (10) of the annular mechanism (2) includes a region of lower surface hardness than the area of the piston with which it contacts; where the initial contact between a part of the plunger (4) and the upper tubular head (10) when they approach each other is a damped contact that is carried out by that region of less hardness 5
    [14]
    14.- VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE, according to claim 9, characterized in that the region of lower surface hardness is determined by an annular body (24) attached to an upper edge of the upper tubular head (10).
    [15]
    15.- VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE, according to claim 8, characterized in that the lower tube assembly (11) and annular support (12) are connected by interference with the tubular housing (1), wherein the annular support (12) is fixed to the tubular housing (1) immovably.
     fifteen
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    法律状态:
    2016-12-19| FG2A| Definitive protection|Ref document number: 2561132 Country of ref document: ES Kind code of ref document: B1 Effective date: 20161219 |
    2017-03-01| PC2A| Transfer of patent|Owner name: KYB EUROPE HEADQUARTERS, GMBH Effective date: 20170223 |
    优先权:
    申请号 | 申请日 | 专利标题
    ES201431107A|ES2561132B1|2014-07-23|2014-07-23|VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE|ES201431107A| ES2561132B1|2014-07-23|2014-07-23|VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE|
    JP2017503590A| JP6419303B2|2014-07-23|2015-06-25|Variable load control system for fluid pressure device|
    ES15824600T| ES2781112T3|2014-07-23|2015-06-25|Variable load control system in a hydraulic device|
    BR112017001405A| BR112017001405A2|2014-07-23|2015-06-25|variable load control system in a hydraulic device|
    CN201580051445.5A| CN107002811B|2014-07-23|2015-06-25|Changing load control system in hydraulic device|
    EP15824600.9A| EP3173655B8|2014-07-23|2015-06-25|Variable load control system in a hydraulic device|
    PCT/ES2015/070494| WO2016012642A1|2014-07-23|2015-06-25|Variable load control system in a hydraulic device|
    US14/797,208| US9982738B2|2014-07-23|2015-07-13|Variable load control system in a hydraulic device|
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