Chassis vibration damper valve and chassis vibration damper

Abstract

The invention relates to a chassis vibration damper valve (8) for a chassis vibration damper (1), comprising a valve body (11) which has a first side (12) and a second side (13) and is intended, when the chassis vibration damper valve (8) is installed in the chassis vibration damper (1), to separate a space of the chassis vibration damper (1) located on the first side (12) from a space of the chassis vibration damper (1) located on the second side (13). At least one flow opening (18) is introduced into the valve body (11), which opens on the one hand onto the first side (12) of the valve body (11) and on the other hand onto the second side (13) of the valve body (11).In order to realize the simplest possible construction of the chassis vibration damper valve (8), the at least one through-flow opening (18) is designed at least in sections as a Tesla valve (19) which opposes an increased flow resistance to a flow of fluid via the at least one through-flow opening (18) in a respective flow direction.

Description

The invention relates to a chassis vibration damper valve for a chassis vibration damper, comprising a valve body which has a first side and a second side and is provided for, in a state of the chassis vibration damper valve installed in the chassis vibration damper, dividing a space of the chassis vibration damper lying on the first side from a space of the chassis vibration damper lying on the second side, wherein at least one throughflow opening is introduced into the valve body, which opening in each case on the one hand on the first side of the valve body and on the other hand on the second side of the valve body. The invention further relates to a chassis vibration damper having at least one chassis vibration damper valve mentioned above.In chassis of motor vehicles, the use of chassis vibration dampers is known, which are usually present as telescopic dampers, single-tube or two-tube dampers being customary as designs. In this case, in the case of a chassis vibration damper, a damping effect is produced in that, when the chassis vibration damper is pulled apart (pull stage) and also when the chassis vibration damper is compressed (compression stage), a flow of fluid, usually in the form of oil, between spaces of the chassis vibration damper is in each case opposed by a resistance. For this purpose, a chassis vibration damper is usually equipped with at least one chassis vibration damper valve, by means of which the movement-dependent resistance is defined. A chassis vibration damper valve usually has a valve body with throttle bores, spring washers and partially helical springs, by whose interaction the movement-dependent flow resistance is defined.DE 10 2006 005 918 A1 discloses a chassis vibration damper valve which, in the case of a chassis vibration damper, is provided either as a piston valve or as a base valve. The chassis vibration damper valve comprises a valve body which, in the installed state of the chassis vibration damper valve, is provided for dividing two spaces in the chassis vibration damper. Flow openings are introduced into the valve body, which flow openings each open on one side of the valve body on the one side and on the other side of the valve body on the other side of the other space. In each case, associated spring disks are also provided on one of the openings in each case, which spring disks allow fluid to flow in a flow direction at the respective flow opening, in that the spring disks then lift off the respective opening, whereas the associated spring disks respectively prevent a flow direction of fluid opposite thereto by covering the respective opening.Proceeding from the prior art described above, it is now the object of the present invention to provide a chassis vibration damper valve having at least one throughflow opening via which a flow of fluid in a flow direction is permitted and is at least made more difficult in a flow direction opposite thereto, wherein the chassis vibration damper valve is intended to have the simplest possible structure in this case.This object is achieved on the basis of the preamble of claim 1 in conjunction with its characterizing features. The dependent claims which follow this represent advantageous further developments of the invention. A chassis vibration damper which has at least one chassis vibration damper valve according to the invention is furthermore subject matter of claims 6 to 8.According to the invention, a chassis vibration damper valve comprises a valve body which has a first side and a second side and is provided for dividing a space of the chassis vibration damper lying on the first side from a space of the chassis vibration damper lying on the second side in a state of the chassis vibration damper installed in the chassis vibration damper. At least one flow opening is introduced into the valve body, which opens on the one hand on the first side of the valve body and on the other hand on the second side of the valve body.The valve body of the chassis vibration damper valve according to the invention is therefore provided for dividing two spaces of the chassis vibration damper from one another, i.e. separating them from one another, in the installed state of the chassis vibration damper valve in a chassis vibration damper. This division or separation of the spaces is effected in this case by the valve body being placed lying between these spaces in the installed state of the chassis vibration damper valve. Depending on the arrangement of the chassis vibration damper valve and the position of the spaces to be divided off, the individual side of the valve body can be present as a respective axial side or as a respective radial side. Thus, the first side and the second side of the valve body can preferably be present as axially opposite sides of the valve body. Alternatively, in particular, the first side can be a radial outer side of the valve body and the second side can be an axial side of the valve body.In the valve body, at least one flow opening is configured, which in each case has, on the one hand, in each case one opening on the first side of the valve body and, on the other hand, in each case one opening on the second side of the valve body. Accordingly, the at least one throughflow opening runs between the first side and the second side, wherein the at least one throughflow opening is preferably formed in the form of a respective channel in the valve body. Depending on whether the individual side of the valve body is an axial side or a radial side, the at least one flow opening also has an axial course, a radial course or an axial and radial course.By "axial" is meant an orientation parallel to an axis which, in the installed state of the chassis vibration damper valve, is placed congruently on a longitudinal central axis of the chassis vibration damper. The chassis vibration damper valve is preferably designed to be substantially rotationally symmetrical, so that the axis is then a rotational axis of the chassis vibration damper valve. "Radial" means, in the sense of the invention, an orientation in the diameter direction with a center point lying on the axis.The invention now comprises the technical teaching that the at least one throughflow opening is configured at least in sections as a Tesla valve each, which opposes an increased flow resistance to a flow of fluid via the at least one throughflow opening in a flow direction each. In other words, at least one section of the at least one throughflow opening is thus present as a Tesla valve each, wherein the one Tesla valve each is aligned such that an increased flow resistance acts on the fluid in a flow direction of a fluid flowing between the sides of the valve body via the at least one throughflow opening each.Such a configuration of a chassis vibration damper valve has the advantage that a flow in one flow direction is made possible via the at least one flow opening, which is at least partially configured as a Tesla valve, whereas a high flow resistance is opposed to a flow in a flow direction opposite thereto, so that the flow in the opposite direction is impeded or even largely prevented. Since this is achieved by the mere configuration of the at least one throughflow opening, this can be realized with a small number of components. In this respect, the chassis vibration damper valve is characterized by a simple construction.For the purposes of the invention, a "Tesla valve" is understood to mean the passive fluidic valve which is generally known and developed by Nikaola Tesla. This valve works similar to a check valve in that a flow resistance in one flow direction is significantly lower than in the other flow direction. This increase in the flow resistance is achieved via loop-like bypasses which come into effect substantially only in the other flow direction. In this case, the flow in the other direction of flow is not completely interrupted, but is only impeded by a great increase in the flow resistance.In this respect, also in the case of the at least one flow opening, at least in a subsection, a plurality of loop-like bypasses emerge from a main channel running essentially in a straight line, which bypasses each merge into the main channel in such a way that they are flowed through essentially only in one flow direction and in the process each generate a flow counteracting a flow via the main channel.According to one embodiment of the invention, the one flow direction in each case, in which the increased flow resistance is effective, is assigned to a pressure stage of the chassis vibration damper. In this case, the currents occurring during a compression of the chassis vibration damper via the at least one flow opening are therefore made more difficult by the increased flow resistance. Alternatively, a flow restriction takes place via the increased flow resistance in a pull stage of the chassis vibration damper, i.e. when the chassis vibration damper is pulled apart. As a result, a flow of fluid via the chassis vibration damper valve can be influenced accordingly.In a further development of the invention, the chassis vibration damper valve is designed as a base valve. Alternatively, however, an embodiment as a piston rod guide is also possible. Within the scope of the invention, an embodiment as a piston valve would also be conceivable.According to a further possible embodiment of the invention, in addition to the at least one flow opening in the valve body, at least one throttle bore is also formed, which has in each case one orifice on the first side of the valve body and in each case one orifice on the second side of the valve body. At each of the respective orifices, at least one associated spring disk is provided, which covers the one orifice in a first flow direction of fluid flowing via the at least one throttle bore, and releases fluid flowing via the at least one throttle bore in a second, opposite flow direction.The invention also relates to a chassis vibration damper which has at least one chassis vibration damper valve according to one or more of the variants described above. In the context of the invention, a "chassis vibration damper" is understood to mean a vibration damper which is provided for use in a chassis of a motor vehicle. The chassis vibration damper is preferably designed as a telescopic damper.In a variant of the invention, a chassis vibration damper valve is used in a chassis vibration damper, in which a working cylinder is accommodated in a container and together with the container tube defines a compensating chamber. The at least one chassis vibration damper valve is accommodated on the working cylinder as a base valve and divides an interior of the working cylinder lying on the first side of the valve body from the compensation chamber lying on the second side of the valve body. As a result, with the aid of the at least one throughflow opening, which is designed at least in sections as a Tesla valve, a flow of fluid between the compensation chamber and the interior chamber can be influenced.Alternatively or additionally, a chassis vibration damper valve is used in a chassis vibration damper, in which a working cylinder is accommodated in a container and together with the container tube defines a compensating chamber. The at least one chassis vibration damper valve forms a piston rod guide, by means of which the working cylinder is connected to the container tube in the region of a piston rod being led out. The at least one chassis vibration damper valve divides an interior lying on the first side of the valve body from the compensation chamber lying on the second side of the valve body. In an advantageous manner, a stop damping for a piston of the chassis vibration damper can be realized in this way via the at least one flow opening.In both of the aforementioned cases, a two-tube damper can be realized in each case, which has a simpler structure due to the simpler structure of the chassis vibration damper valve according to the invention itself.Advantageous embodiments of the invention, which are explained below, are illustrated in the drawings. It shows: FIGS. 1 and 2 are sectional views of a part of a chassis vibration damper in the region of a chassis vibration damper valve according to a first embodiment of the invention, shown on the one hand in a pull stage and on the other hand in a compression stage of the chassis vibration damper; and FIGS. 3 and 4 show sectional views of a part of a chassis vibration damper in the region of a chassis vibration damper valve according to a second possible embodiment of the invention, shown firstly in a compression stage and secondly in a rebound stage of the chassis vibration damper.FIGS. 1 and 2 show sectional views of a part of a chassis vibration damper 1, which comprises a working cylinder 2, in which a piston-in the present case not visible in the region shown-is displaceably guided. The working cylinder 2 is surrounded by a container 3 which, together with the working cylinder 2, defines an intermediate compensating chamber 4. The container 3 is composed of a container tube 5 and a base section 6, by means of which the container tube 5 is closed at the end and additionally forms a connection point 7 of the chassis vibration damper 1, which connection point can be seen only partially in FIGS. 1 and 2. A further connection point of the chassis vibration damper 1 is designed in a manner known in principle to the person skilled in the art at one end of a piston rod connected to the piston, wherein the piston rod is led out of the working cylinder 2 and the container tube 5 with this end. In this respect, the chassis vibration damper 1 is designed in the present case as a telescopic damper in the form of a two-tube damper.A chassis vibration damper valve 8 in the form of a base valve 9 is fastened to the working cylinder 2 in the region of the base section 6, by means of which valve the compensating chamber 4 is divided from an interior 10 defined radially inside the working cylinder 2. The piston is also displaceably guided in the interior 10, wherein the interior 10 is completely filled with a fluid in the form of oil, whereas the compensating space 4 is partially filled with oil and partially filled with air or gas.The chassis vibration damper valve 8 is designed according to a first embodiment of the invention and comprises a valve body 11, via which the compartment of the compensating chamber 4 from the interior 10 is made. The interior 10 lies on a first side 12 of the valve body 11, while the compensating chamber 4 is provided on a second side 13 of the valve body 11. On the one hand, several bores 14 and several throttle bores-not located in the sectional views in FIGS. 1 and 2-are introduced into the valve body 11, which throttle bores each open in detail on the first side 12 and thus the interior 10 and on the second side 13 and thus the compensation chamber 4.At the openings of the bores 14 on the first side 12, a spring disk 15 is provided on the valve body 11, which is prestressed against the valve body 11 by means of a spring element 16. In a pull stage of the chassis vibration damper 1, i.e. when the chassis vibration damper 1 is pulled apart, an after-suction of oil from the compensation chamber 4 into the interior 10 via the bores 14 is made possible in that the spring washer 15 is at least partially lifted from the valve body 11 and thus opens up the openings of the bores 14 on the first side 12. On the other hand, the spring washer 15 covers the openings of the bores 14 on the first side 12 in a compression stage of the chassis vibration damper 1, i.e. when the chassis vibration damper 1 is compressed.This flow of oil from the interior 10 into the compensating chamber 4 in the pressure stage of the chassis vibration damper 1 is made possible via the throttle bores, not shown, at the mouths of which a plurality of spring washers 17 are provided on the second side 13, which form a spring washer pack. The flow of oil from the interior 10 into the compensating space 4 via the throttle bores is made possible by partially lifting the spring washers 17 from the valve body 11 and a concomitant release of the openings of the throttle bores on the second side 13, wherein the oil flow via the throttle bores is restricted and the flow is thus opposed by a resistance. In the pull stage, on the other hand, the spring washers 17 close the openings of the throttle bores located on the second side 13 and thus prevent oil from flowing over the throttle bores.As a special feature, in the chassis vibration damper valve 8, at least one flow opening 18 is also introduced into the valve body 11, wherein this at least one flow opening 18 also opens on the one hand on the first side 12 and on the other hand on the second side 13. The at least one flow opening 18 is configured as a Tesla valve 19 in each case, in that a plurality of bypasses 21 are provided in each case in a manner known in principle for a respective main channel 20 of the at least one flow opening 18, which bypasses each run in the manner of a loop to the respective one main channel 20. In the present case, the respective one Tesla valve 19 is oriented between the two sides 12 and 13 in such a way that in the rebound stage of the chassis vibration damper 1, a flow of oil indicated in FIG. 1 takes place via the main duct 20 in a flow direction from the second side 13 to the first side 12, whereas a flow of oil in a flow direction opposite thereto from the first side 12 to the second side 13 is opposed by an increased flow resistance. This flow resistance is caused by the generation of respective counter-currents via the respective bypasses 21, as is indicated in FIG. 2. As a result, in the pressure stage of the chassis vibration damper 1, the respective flow of oil from the interior 10 into the compensation chamber 4 via the at least one throughflow opening 18 is at least made more difficult.FIGS. 3 and 4 show sectional views of a part of a chassis vibration damper 22, wherein the chassis vibration damper 22 is shown in the region of a piston rod 23 being led out of a container tube 24. In addition, a working cylinder 25 is accommodated in the container tube 24, in which a piston connected to the piston rod 23 is displaceably guided. The chassis vibration damper 22 is designed in the present case as a two-tube damper. Apart from the region shown, the chassis vibration damper 22 can be designed in accordance with the chassis vibration damper 1 from FIGS. 1 and 2.A compensating chamber 26 of the chassis vibration damper 22 is defined in the present case by the container tube 24, the working cylinder 25 and a piston rod guide 27, via which the working cylinder 25 is connected to the container tube 24 in the region of the chassis vibration damper 22 shown. The piston rod guide 27 also accommodates a piston rod seal 28 together with the container tube 24, by means of which piston rod 23 is sealed from being guided out of the container tube 24.The piston rod guide 27 is formed in the present case by a chassis vibration damper valve 30 having a valve body 29, wherein the compensating chamber 26 is divided from an interior 31 via the valve body 29 which is defined by the working cylinder 25 and in which the piston is displaceably guided. The interior 31 lies on a first axial side 32 of the valve body 29, while the compensating chamber 26 is provided on a second axial side 33 of the valve body 29.At least one flow opening 34 is introduced into the valve body 29, which opens in each case on the one hand on the first axial side 32 of the valve body 29 and on the other hand on the second axial side 33. In the present case, the at least one throughflow opening 34 is in each case designed as a Tesla valve 35, for which purpose a plurality of loop-like bypasses 37 are respectively provided for in each case one main duct 36 of the at least one throughflow opening 34.The respective bypasses 37 of the Tesla valve 35 are connected to the main channel 36 in each case from their respective orientation in such a way that in the compression stage of the chassis vibration damper 22, i.e. a compression of the chassis vibration damper 22, a flow of oil indicated in FIG. 3 takes place in a flow direction from the second side 33 and thus from the compensation chamber 26 to the first side 32 and thus to the interior 31, wherein this flow in the first flow direction takes place substantially only via the main channel 36.In contrast, in a pull stage of the chassis vibration damper 22, i.e. a pulling apart of the chassis vibration damper 22, a flow in the opposite flow direction from the first side 32 to the second side 33 via the flow opening 34 is prevented, in that counter-flows to a flow via the main channel 36 are respectively produced via the respective bypasses 37 and the flow resistance with respect to the flow direction from the first side 32 to the second side 33 is thus significantly increased. This is indicated in FIG. 4.Overall, although in principle a flow of oil from the compensating chamber 26 into the interior 31 is permitted by the Tesla valve shown via the at least one flow opening 34, a flow opposite thereto from the interior 31 into the compensating chamber 26 is made more difficult. As a result, a tension stop damping for the piston of the chassis vibration damper 22 can be realized.By means of the embodiments according to the invention, a chassis vibration damper valve with at least one flow opening can be created in each case, via which a flow of fluid is permitted in a flow direction and is at least made more difficult in a flow direction opposite thereto, wherein the chassis vibration damper valve is distinguished by a simple design in this case.Reference numerals denote reference numerals1 Chassis vibration damper 2 Working cylinder 3 Container 4 Compensating chamber 5 Container tube 6 Base portion 7 Connection point 8 Chassis vibration damper valve 9 Base valve 10 Interior 11 Valve body 12 First side 13 Second side 14 Bores 15 Spring disk 16 Spring element 17 Spring disks 18 Throughflow opening 19 Tesla valve 20 Main channel 21 Bypasses 22 Chassis vibration damper 23 Piston rod 24 Container tube 25 Working cylinder 26 Compensating chamber 27 Piston rod guide 28 Piston rod seal 29 Valve body 30 Chassis vibration damper valve 31 Interior 32 First side 33 Second side 34 Throughflow opening 35 Tesla valve 36 Main channel 37 BypassesReferences included in the specificationThis list of documents cited by the applicant has been produced in an automated manner and is only included for the better information of the reader. The list is not part of the German patent application or utility model application. The DPMA does not take any adhesion for any faults or omissions.Patent Literature citedDE 10 2006 005 918 A1

[0003]

Claims

A chassis vibration damper valve (8; 30) for a chassis vibration damper (1; 22), comprising a valve body (11; 29) which has a first side (12; 32) and a second side (13; 33) and is provided for dividing a space of the chassis vibration damper (1; 22) lying on the first side (12; 32) from a space of the chassis vibration damper (1; 22) lying on the second side (13; 33) in a state of the chassis vibration damper (8; 30) installed in the chassis vibration damper (1; 22), wherein at least one throughflow opening (18; 34) is introduced into the valve body (11; 29), said throughflow opening in each case on the one hand on the first side (12; 32) of the valve body (11; 29) and on the other hand on the second side (13; 33) of the valve body (11; 29), characterized in that the at least one throughflow opening (18; 34) is configured at least in sections as a Tesla valve (19; 35) each, which opposes an increased flow resistance to a flow of fluid via the at least one flow opening (18; 34) in a flow direction each.The chassis vibration damper valve (8; 30) according to claim 1, characterized in that the one flow direction in which the increased flow resistance is effective is assigned to a compression stage of the chassis vibration damper (1; 22) or to a rebound stage of the chassis vibration damper.Chassis vibration damper valve (8) according to Claim 1 or 2, characterized bya design as a base valve (9).Chassis vibration damper valve (30) according to Claim 1 or 2, characterized bya design as a piston rod guide (27).The chassis vibration damper valve (8) according to any one of the preceding claims, characterized in that in addition to the at least one flow opening (18) in the valve body (11), at least one throttle bore is also formed, each of which has an orifice on the first side (12) of the valve body (11) and an orifice on the second side (13) of the valve body (11), wherein at least one associated spring disk (17) is provided on each of the respective orifices, which spring disk covers the respective one orifice in a first flow direction of fluid flowing via the at least one throttle bore and releases fluid flowing via the at least one throttle bore in a second, opposite flow direction in each case.A suspension vibration damper (1; 22) for a motor vehicle, comprising at least one suspension vibration damper valve (8; 30) according to any one of claims 1 to 5.The chassis vibration damper (1) according to claim 6, characterized in that a working cylinder (2) is accommodated in a container tube (3) and defines a compensation chamber (4) together with the container tube (3), wherein the at least one chassis vibration damper valve (8) is accommodated on the working cylinder (2) as a bottom valve (9) and in the process divides an interior (10) of the working cylinder (2) lying on the first side (12) of the valve body (11) from the compensation chamber (4) lying on the second side (13) of the valve body (11).The suspension vibration damper (22) according to claim 6 or 7, characterized in that a working cylinder (25) is accommodated in a container tube (24) and defines a compensation chamber (26) together with the container tube (24), wherein the at least one suspension vibration damper valve (30) forms a piston rod guide (27), via which the working cylinder (25) is connected to the container tube (24) in the region of a lead-out of a piston rod (23), and wherein the at least one suspension vibration damper valve (30) divides an interior (31) lying on the first side (32) of the valve body (29) from the compensation chamber (26) lying on the second side (33) of the valve body (29).

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