Hydraulic vibration damper and method for adjusting the damping effect of a hydraulic vibration damper

Abstract

Hydraulic vibration damper, which features: a first (5) and a second pressure chamber (6), each containing a hydraulic fluid, a mass (7) designed to move back and forth between the first (5) and the second pressure chamber (6) and thereby change the pressure in each of the individual pressure chambers (5, 6), a third chamber (12) in which the mass (7) moves and which also contains hydraulic fluid; and a first passage (9) which is designed to allow the hydraulic fluid to flow between the two pressure chambers (5, 6), wherein the hydraulic vibration damper (3, 21, 31) further comprises a first valve (15) which is designed to control a flow rate through the first passage (9), and wherein the mass (7) is hydraulically preloaded.

Description

TECHNICAL FIELD

[0001] The present invention relates to a hydraulic vibration damper and a method for adjusting the damping effect of a hydraulic vibration damper, with which the damping effect of the hydraulic vibration damper can be optimally adapted to the respective requirements or the respective application. BACKGROUND

[0002] Vibration dampers are special types of vibration absorbers that are not attached between two objects, but rather to one. Vibration dampers are an effective means of reducing excessive vibrations. They are used, for example, in long-span structures such as bridges, stages, and large staircases, as well as in slender, tall structures such as chimneys, antennas, masts, and buildings that are prone to excessive or disruptive natural vibrations caused by wind forces, machinery, traffic, or earthquakes. Vibration dampers are also used in combustion engines and vehicle construction, for example.

[0003] A vibration damper is a vibrating subsystem consisting of an abstract vibrating mass, an abstract spring, and an abstract damper, each of which need not be explicitly implemented as a concrete component. The abstract damper, in particular, is often not implemented as a concrete component and yet is effective due to friction and flow losses that practically always occur. A distinction is made between conventional passive vibration dampers, which are exclusively self-excited, and actively controlled vibration dampers.

[0004] From document EP 2 993 458 A1, a hydraulic vibration damper is known, which comprises a first and a second pressure chamber, each containing a hydraulic fluid, a mass configured to move back and forth between the first and second pressure chambers in a substantially airtight manner and thereby change the pressure in each of the individual pressure chambers, at least one spring configured to exert a position-dependent force on the mass, and a first passage configured to allow the hydraulic fluid to flow between the two pressure chambers. Document EP 3 636 465 A1 describes a vibration damper on the wheel suspension of a vehicle. Publication DE 38 27 905 A1 relates to a hydraulically damping rubber mount.

[0005] Vibration dampers must also be tuned to the frequency of the component to be damped. In particular, vibration dampers should preferably be designed to have a frequency that is almost identical to the frequency to be damped. However, conventional vibration dampers are preconfigured, which is why it is usually not possible to use a vibration damper for a different application or to adapt it during operation.

[0006] The object of the embodiments described here is to provide an improved vibration damper with which, in particular, different application purposes can be realized and the vibration damper can be adapted during operation. SUMMARY

[0007] The above-mentioned object is achieved by the hydraulic vibration damper according to claim 1 and the method according to claim 8. Various embodiments and further developments are the subject of the dependent claims.

[0008] According to one embodiment of the invention, this object is achieved by a hydraulic vibration damper comprising a first and a second pressure chamber, each containing a hydraulic fluid, a mass configured to reciprocate between the first and second pressure chambers in a substantially airtight manner and thereby vary the pressure in each of the individual pressure chambers, a first passage configured to allow the hydraulic fluid to flow between the two pressure chambers, and a first valve configured to regulate a flow rate through the first passage. The mass is hydraulically preloaded.

[0009] Compared to mechanical vibration dampers, hydraulic vibration dampers have the advantage that they can be designed and adjusted much more flexibly. The fact that the mass is designed to move between the first and second pressure chambers in a substantially airtight manner means that the mass is designed and arranged in such a way, for example, that when the mass moves, air can only flow through a narrow gap from a chamber in which the mass is arranged into the first or second pressure chamber. For example, a piston rod on which the mass is arranged and which is movably arranged in a bushing, which can be formed by a housing of the vibration damper, can be ground in such a way that the seal between the piston rod and the bushing is only achieved through narrow guide gaps.The gap size should also be selected so that resonant operation is possible. The first valve can also be used to direct a certain amount of hydraulic fluid from one pressure chamber to the other, creating a defined flow resistance and introducing defined damping. The first valve can in turn be controlled to adapt the hydraulic vibration damper to the corresponding requirements or the respective application. Furthermore, the hydraulic vibration damper is designed such that the hydraulic fluid always remains in the vibration damper, i.e. in a closed chamber, which means that the closed chamber does not need to be connected to an external hydraulic system. This means that it can be retrofitted to devices that require damping, or removed from them for maintenance and service purposes, particularly cost-effectively.

[0010] The fact that the mass is further hydraulically preloaded has the additional advantage that cavitation in the pressure chambers can be avoided during operation of the hydraulic vibration damper. For example, internal friction and inertia of the compressible liquid or hydraulic fluid can lead to cavitation phenomena in the pressure chamber, i.e., the formation and dissolution of vapor-filled cavities in the hydraulic fluid, particularly since hydraulic fluid is usually not replenished into the corresponding pressure chamber in a timely manner. Furthermore, the preload can be easily adjusted once depending on the application. In particular, the hydraulic vibration damper can be designed such that the higher the preload pressure generated by the hydraulic preload, the higher the resonance frequency of the hydraulic vibration damper.Overall, an improved vibration damper is thus specified, with which in particular different application purposes can be realized, i.e. the hydraulic vibration damper can be adapted to the respective requirements or the respective application.

[0011] The hydraulic preload can be achieved in particular by the hydraulic vibration damper having a third chamber in which the mass moves and which contains the hydraulic fluid. Since the hydraulic preload is also achieved by the hydraulic fluid flowing against the mass, the hydraulic preload can be implemented simply and cost-effectively. Furthermore, such a hydraulic preload can be easily adapted to the specific requirements or application.

[0012] The hydraulic preload can be adjusted or adapted to the respective requirements or the respective application by further comprising the hydraulic vibration damper with a second passage configured to allow the hydraulic fluid to flow between a reservoir containing the hydraulic fluid and the third chamber, and a second valve configured to regulate the flow rate through the second passage or the working pressure in the third chamber. Such a hydraulic supply also allows for optimal adaptation of the hydraulic preload to different operating frequencies.This adjustment is also possible directly to the specific application or location of the hydraulic vibration damper, without the need for external hydraulic fluid supply or connection to an external hydraulic system. Furthermore, the preload pressure should generally be selected so that the higher the vibrations to be damped, the higher the preload pressure, to avoid cavitation in the pressure chambers.

[0013] According to one embodiment, the hydraulic vibration damper further comprises a gas-filled hydraulic accumulator connected to the first pressure chamber and a gas-filled hydraulic accumulator connected to the second pressure chamber, wherein the hydraulic vibration damper is designed such that the hydraulic vibration damper can be adapted to different operating frequencies by means of the two gas-filled hydraulic accumulators. In this embodiment, the first and second chambers each have an additional gas spring, which is represented by the first and second chambers, respectively, and which each has a progressive spring characteristic. Changes in gas volume or gas pressure can be varied such that the gas spring can maintain a desired spring characteristic.Consequently, the progressive characteristic curve of the gas spring can be used to adjust the frequency of the vibration damper, i.e., to adapt it to the respective requirements or the specific application. In particular, the vibration damper can also be adjusted during operation, especially since the preload pressure can spread slowly into the two pressure chambers, for example, via the gap seals, compared to the operating frequency.

[0014] In addition, the hydraulic vibration damper can also have at least one mechanical centering spring. By using such a centering spring, or by selecting and designing the centering spring accordingly, the hydraulic vibration damper can be designed flexibly and easily adapted to the specific requirements or application.

[0015] According to another embodiment, the hydraulic vibration damper can also have two metal bellows to seal the working pressure in the first pressure chamber and the second pressure chamber from the third chamber. In particular, the metal bellows can be arranged between the first and the third chamber or between the second and the third chamber in such a way that the first and the second pressure chamber are each hermetically sealed from the third chamber. This can also prevent mass drift. The preload pressure in the third chamber can also be maintained and remain constant, so that no interventions to keep the resonance frequency constant are necessary. Furthermore, the guide gaps between the piston rod and the cylinder bushing, which are often difficult to implement, are not required.

[0016] In this embodiment, the hydraulic vibration damper can further comprise at least one compensating bore between the first and third chambers and the second and third chambers, through which the average preload pressure can be distributed. These compensating bores should be small compared to the effective piston diameter in order to achieve the greatest possible pressure for damping the vibrations on the device.

[0017] The hydraulic fluid can also be hydraulic oil. The use of hydraulic oil to achieve a pressure or damping effect is known, so the damping can be achieved simply using a known hydraulic fluid, without the need for costly and complex modifications. Furthermore, the hydraulic fluid can also be any other hydraulic fluid capable of producing a corresponding pressure or damping effect.

[0018] According to a further embodiment of the invention, a system is also provided which comprises a device and a hydraulic vibration damper as described above for damping disturbing vibrations of the device.

[0019] Such a system has the advantage that it has an improved vibration damper, with which in particular different application purposes can be realized, i.e. the system can be adapted to the respective requirements or the respective application.

[0020] Compared to mechanical vibration dampers, hydraulic vibration dampers have the advantage of being much more flexible in their design and adjustment. Furthermore, the hydraulic vibration damper is designed in such a way that the hydraulic fluid always remains within the vibration damper, i.e., within a closed chamber. This means that the closed chamber does not need to be connected to an external hydraulic system. This makes the vibration damper particularly cost-effective to retrofit to devices requiring damping, or to remove it for maintenance and service purposes.

[0021] The fact that the mass is further hydraulically preloaded has the additional advantage that cavitation in the pressure chambers can be avoided during operation of the hydraulic vibration damper. For example, internal friction and the inertia of the hydraulic fluid can lead to cavitation phenomena in the pressure chambers, i.e., the formation and dissolution of vapor-filled cavities in the hydraulic fluid, particularly since hydraulic fluid is usually not replenished into the corresponding pressure chamber in a timely manner. Furthermore, the preload can be easily adjusted once depending on the application. In particular, the hydraulic vibration damper can be designed such that the higher the preload pressure generated by the hydraulic preload, the higher the resonance frequency of the hydraulic vibration damper.

[0022] According to a further embodiment of the invention, a method for adjusting the damping effect of a hydraulic vibration damper is also provided, wherein first a mass is selected, wherein the weight of the mass is selected based on the weight of a device to be damped.Furthermore, a hydraulic vibration damper is attached to the device, wherein the hydraulic vibration damper has a first and a second pressure chamber, each containing a hydraulic fluid; the selected mass, which is configured to move back and forth between the first and second pressure chambers in a substantially airtight manner and thereby change the pressure in each of the individual pressure chambers; a first passage including a flow resistance well-defined with respect to the application, which is configured to allow the hydraulic fluid to flow between the two pressure chambers; and a first valve for regulating a flow rate through the first passage. Furthermore, the mass is hydraulically preloaded.

[0023] Such a method has the advantage that it can be used to realize an improved vibration damper, with which in particular different application purposes can be realized, i.e. the vibration damper can be adapted to the respective requirements or the respective application.

[0024] Compared to mechanical vibration dampers, hydraulic vibration dampers have the advantage that they can be designed and adjusted much more flexibly. The fact that the mass is designed to move between the first and second pressure chambers in a substantially airtight manner means that the mass is designed and arranged in such a way, for example, that when the mass moves, air can only flow through a narrow gap from a chamber in which the mass is arranged into the first or second pressure chamber. For example, a piston rod on which the mass is arranged and which is movably arranged in a bushing, which can be formed by a housing of the vibration damper, can be ground in such a way that the seal between the piston rod and the bushing is only achieved through narrow guide gaps.The gap size should also be selected to enable resonant operation. The first valve can then direct a certain amount of hydraulic fluid from one pressure chamber to the other, creating a defined flow resistance and introducing a defined damping effect. The first valve can, in turn, be controlled to adapt the hydraulic vibration damper to the specific requirements or application.

[0025] Furthermore, the hydraulic vibration damper is designed in such a way that the hydraulic fluid always remains within the vibration damper, i.e., in a closed chamber. This means that the closed chamber does not need to be connected to an external hydraulic system. This allows the vibration damper to be retrofitted to devices requiring damping, or removed from them for maintenance and service purposes, particularly cost-effectively.

[0026] The fact that the mass is further hydraulically preloaded has the additional advantage that cavitation in the pressure chambers can be avoided during operation of the hydraulic vibration damper. For example, internal friction and the inertia of the hydraulic fluid can lead to cavitation phenomena in the pressure chambers, i.e., the formation and dissolution of vapor-filled cavities in the hydraulic fluid, particularly since hydraulic fluid is usually not replenished into the corresponding pressure chamber in a timely manner. Furthermore, the preload can be easily adjusted once depending on the application. In particular, the hydraulic vibration damper can be designed such that the higher the preload pressure generated by the hydraulic preload, the higher the resonance frequency of the hydraulic vibration damper.

[0027] The hydraulic vibration damper can further comprise a third chamber in which the mass moves, and the step of hydraulically preloading the mass can involve introducing hydraulic fluid into the third chamber. Since the hydraulic preload is also achieved by the hydraulic fluid flowing against the mass, the hydraulic preload can be implemented simply and cost-effectively. Furthermore, such a hydraulic preload can be easily adapted to the specific requirements or application.

[0028] The hydraulic vibration damper can further comprise a second passage configured to allow the hydraulic fluid to flow between a reservoir containing the hydraulic fluid and the third chamber, and a second valve configured to regulate a flow rate through the second passage or a working pressure in the third chamber. The method comprises adjusting the hydraulic preload by adjusting the flow rate through the second passage. As a result, the hydraulic preload can be adapted or adjusted accordingly to the respective requirements or the respective application. Furthermore, such a hydraulic supply enables optimal adaptation of the hydraulic preload to different operating frequencies.This adjustment is also possible directly at the respective application or location of the hydraulic vibration absorber, without the need for external hydraulic fluid supply or a connection to an external hydraulic system.

[0029] According to one embodiment, the hydraulic vibration damper can further comprise a gas-filled hydraulic accumulator connected to the first pressure chamber and a gas-filled hydraulic accumulator connected to the second pressure chamber, wherein the method further comprises adapting the hydraulic vibration damper to different operating frequencies by means of the two gas-filled hydraulic accumulators. In this embodiment, the first and second pressure chambers each have an additional gas spring, which is represented by the first and second pressure chambers, respectively, and which each has a progressive spring characteristic. Changes in gas volume or gas pressure can be varied such that the gas spring can maintain a desired spring characteristic.Consequently, the progressive characteristic curve of the gas spring can be used to adjust the frequency of the vibration damper, i.e., to adapt it to the respective requirements or the specific application. In particular, the vibration damper can also be adjusted during operation, especially since the preload pressure can spread slowly into the two pressure chambers, for example, via the gap seals, compared to the operating frequency.

[0030] The hydraulic fluid can also be hydraulic oil. The use of hydraulic oil to achieve a pressure or damping effect is known, so the damping can be achieved simply using a known hydraulic fluid, without the need for costly and complex modifications. Furthermore, the hydraulic fluid can also be any other hydraulic fluid capable of producing a corresponding pressure or damping effect.

[0031] In summary, the present invention provides a hydraulic vibration damper which can be retrofitted cost-effectively to devices to be damped or removed from them for maintenance and service purposes.

[0032] By hydraulically preloading the mass, cavitation in the pressure chambers can be avoided during operation of the hydraulic vibration absorber. Furthermore, the preload can be easily adjusted depending on the application.

[0033] In addition, the progressive characteristic curve of a gas spring can be used to adjust the frequency of the vibration damper, i.e., to adapt it to the respective requirements or application. In particular, the vibration damper can also be adjusted during operation, especially since the preload pressure can spread slowly into the two pressure chambers, for example, via the gap seals, compared to the operating frequency. BRIEF DESCRIPTION OF THE ILLUSTRATIONS

[0034] The invention is explained in more detail below using the examples shown in the figures. The illustrations are not necessarily to scale, and the invention is not limited to the aspects shown. Rather, emphasis is placed on illustrating the principles underlying the invention. Fig. 1 shows a cross-sectional view of a system comprising a device and a hydraulic vibration damper for damping parasitic vibrations of the device, according to a first embodiment of the invention; Fig. 2 shows a cross-sectional view of a system comprising a device and a hydraulic vibration damper for damping parasitic vibrations of the device, according to a second embodiment of the invention; Fig. 3 shows a cross-sectional view of a system comprising a device and a hydraulic vibration damper for damping parasitic vibrations of the device, according to a third embodiment of the invention; Fig. 4 shows a flowchart of a method for adjusting the damping effect of a hydraulic vibration absorber according to an embodiment of the invention. DETAILED DESCRIPTION

[0035] Fig. 1 shows a cross-sectional view of a system 1 comprising a device 2 and a hydraulic vibration damper 3 for damping disturbing vibrations of the device 2, according to a first embodiment of the invention.

[0036] How Fig. As shown in Figure 1, the hydraulic vibration damper 3 has a housing 4 that is screwed to the device 2. Furthermore, the connection between the vibration damper and the device can also be made in other ways, for example, by means of form-fitting or gluing.

[0037] Vibration dampers must also be tuned to the frequency of the component to be damped. In particular, the vibration damper should be designed so that it has almost the same natural frequency as the frequency to be damped. However, common vibration dampers are preconfigured, which is why it is usually not possible to use a vibration damper once it has been provided for a different application.

[0038] The vibration damper 3 shown has a first 5 and a second pressure chamber 6, each containing a hydraulic fluid, a mass 7 which is designed to move back and forth between the first 5 and the second pressure chamber 6 in a substantially airtight manner and thereby to change the pressure in the individual pressure chambers 5, 6, at least one centering spring 8 which is designed to exert a position-dependent force on the mass 7, and a first passage 9 which is designed to allow the hydraulic fluid to flow between the two pressure chambers 5, 6.

[0039] In particular, Fig. 1, the housing 4 of the hydraulic vibration damper 3 forms a closed pressure chamber filled with hydraulic fluid, in which a piston rod 10 is displaceably arranged and axially divides this pressure chamber into two pressure chambers 5, 6. A damper mass 7 is also attached to the piston.

[0040] If a force F to be damped now strikes the housing 4 axially, it is transmitted hydraulically due to the inertia of the damper mass 7, whereby the piston rod 10 is pressed into the housing 4, so that the volume of the first pressure chamber 5 decreases, while the volume of the second pressure chamber 6 increases. As the piston rod 10 is retracted, hydraulic fluid is directed from the first pressure chamber 5 via the first passage 9 into the second pressure chamber 6, which is intended to generate flow resistance and an overall counterforce to the force F. The moment the force no longer acts on the piston rod 10, the piston rod 10 returns to its original or starting position. A centering spring 8 can also be seen, which is intended to prevent the piston rod 10 from drifting towards an end position during operation.

[0041] Such a system 1 has the advantage of having an improved vibration damper 3, which, in particular, can be used for various applications, meaning that the system 1 can be adapted to the specific application. Thus, the preload pressure can be adapted to the respective conditions, whereby the preload pressure must be higher the higher the vibrations to be damped.

[0042] Hydraulic vibration dampers 3 have the advantage over mechanical vibration dampers that they can be designed and adjusted much more flexibly. The fact that the mass is designed to move between the first and second pressure chambers in a substantially airtight manner means that the mass is designed and arranged, for example, in such a way that when the mass moves, air can only flow through a narrow gap from a chamber in which the mass is arranged into the first or second pressure chamber. For example, a piston rod on which the mass is arranged and which is movably arranged in a bushing, which can be formed by a housing of the vibration damper, can be ground in such a way that the seal between the piston rod and the bushing is only achieved through narrow guide gaps.The gap size should also be selected so that resonant operation is possible.

[0043] Furthermore, the hydraulic vibration damper 3 is designed such that the hydraulic fluid always remains within the vibration damper, i.e., in a closed chamber. This means that the closed chamber does not need to be connected to an external hydraulic system. This allows it to be retrofitted cost-effectively to devices 2 to be damped, or removed from them for maintenance and service purposes.

[0044] The fact that mass 7 is further hydraulically preloaded has the additional advantage of preventing cavitation in pressure chambers 5, 6 during operation of the hydraulic vibration damper 3. For example, cavitation phenomena can occur in pressure chambers 5, 6 due to internal friction and the inertia of the hydraulic fluid. This can lead to the formation and dissolution of vapor-filled cavities in the hydraulic fluid, particularly since hydraulic fluid is usually not refilled into the corresponding pressure chamber 5, 6 in a timely manner. Furthermore, the preload can be easily adjusted once, depending on the application.

[0045] According to the first embodiment, the hydraulic vibration damper 3 further comprises a third chamber 12 in which the mass 7 moves and which contains the hydraulic fluid to realize the preload. Fig. 1 shows, the third chamber 12 for adjusting the preload pressure is also connected to a reservoir 13 containing the hydraulic fluid.

[0046] Furthermore, the hydraulic fluid is hydraulic oil. Furthermore, the hydraulic fluid can also be any other hydraulic fluid that can produce a corresponding pressure or damping effect.

[0047] In addition, Fig. 1 a first valve 15, which is designed to regulate a flow rate through the first passage 9 and thus to generate a defined flow resistance, that is to say a defined damping.

[0048] Fig. Figure 2 shows a cross-sectional view of a system 20 comprising a device 2 and a hydraulic vibration damper 21 for damping disturbing vibrations of the device 2, according to a second embodiment of the invention. Components with the same function or construction as in Fig. 1 have the same reference numerals and are not discussed separately.

[0049] How Fig. 2, the hydraulic vibration damper 21 further comprises a second passage 22 which is designed to allow the hydraulic fluid to flow, in particular to pump, between a reservoir 23 containing the hydraulic fluid and the third chamber 12, and a second valve 24 which is designed to regulate a flow rate through the second passage 22.

[0050] The illustrated hydraulic vibration damper 21 according to the second embodiment also differs from that shown in Fig. 1 according to the first embodiment in that a gas-filled hydraulic accumulator 26 is arranged in each of the first pressure chambers 5 and 6, wherein the vibration damper 21 is designed such that the hydraulic vibration damper 21 can be adapted to different operating frequencies by means of the two gas-filled hydraulic accumulators. In particular, the first chamber 5 and the second chamber 6 each have an additional gas spring, which is represented by the first pressure chamber 5 and the second pressure chamber 6, respectively, and which each have a progressive spring characteristic. In this case, changes in gas volume or gas pressure can be varied such that the two gas springs can maintain a desired spring characteristic. The gas-filled hydraulic accumulators 26 are each pre-filled with a certain gas pressure.

[0051] Fig. Figure 3 shows a cross-sectional view of a system 30 comprising a device 2 and a hydraulic vibration damper 31 for damping disturbing vibrations of the device 2, according to a third embodiment of the invention. Components with the same function or construction as in Fig. 1 or Fig. 2 have the same reference numerals and are not discussed separately.

[0052] How Fig. As shown in Figure 3, the hydraulic vibration damper 31 according to the third embodiment does not have a centering spring, but rather has a metal bellows 32 between the first 5 and the third chamber 12, as well as between the second 6 and the third chamber 12. The two metal bellows 32 ensure that the first 5 and the second pressure chamber 6 are each hermetically sealed from the third chamber 12.

[0053] The hydraulic vibration damper further comprises a compensating bore 33 between the first chamber 5 and the third chamber 12, as well as between the second chamber 6 and the third chamber 12, through which the average preload pressure can spread into all chambers 5, 6, 12. Furthermore, more than one compensating bore can be provided between the first and third chambers and / or between the second and third chambers.

[0054] According to the third embodiment, two digital valves 34 are also provided instead of the second valve. The digital valves 34 can, for example, be designed such that the preload pressure can be adjusted by pulse width modulation (PWM) control.

[0055] Fig. 4 shows a flowchart of a method 40 for adjusting the damping effect of a hydraulic vibration damper according to an embodiment of the invention.

[0056] How Fig. As shown in Figure 4, the method first comprises the step of selecting a mass 41, wherein the weight of the mass is selected based on the weight of a device to be damped. In particular, the mass is generally freely selectable, although it should preferably be selected in a suitable ratio to the equivalent mass of the device to be damped.Furthermore, a hydraulic vibration damper is attached to the device 42, wherein the hydraulic vibration damper has a first and a second pressure chamber, each containing a hydraulic fluid, the selected mass configured to reciprocate between the first and second pressure chambers in a substantially airtight manner, thereby varying the pressure in each of the individual pressure chambers, a first passage configured to allow the hydraulic fluid to flow between the two pressure chambers, and a first valve for regulating a flow rate through the first passage. Furthermore, the mass is hydraulically preloaded 43.

[0057] According to the embodiments of the Fig. 4, the hydraulic vibration damper further comprises a third chamber in which the mass moves, wherein the step of hydraulically preloading the mass 43 comprises introducing the hydraulic fluid into the third chamber. In particular, the hydraulic vibration damper comprises a second passage configured to allow the hydraulic fluid to flow between a reservoir containing the hydraulic fluid and the third chamber, and a second valve configured to regulate a flow rate through the second passage. The method further comprises the step of adjusting the hydraulic preload by adjusting the flow rate through the second passage 44.

[0058] According to the embodiments of the Fig. 3, the hydraulic vibration damper further comprises a gas-filled hydraulic accumulator connected to the first pressure chamber and a gas-filled hydraulic accumulator connected to the second pressure chamber. The hydraulic preloading in steps 43 and 44 corresponds to the adjustment of the resonance frequency, with the hydraulic vibration damper being designed such that the hydraulic vibration damper can be adapted to different operating frequencies by means of the two gas-filled hydraulic accumulators. Fig. 3, the method also includes the step of adapting to an operating frequency by means of the gas-filled hydraulic accumulator 45.

[0059] It should be noted that in this embodiment, which has gas-filled hydraulic accumulators, after the hydraulic preloading of the system and thus the adjustment of the resonance frequency, the corresponding flow rate through the first valve should be adjusted in such a way that an optimal damping effect is achieved. List of reference symbols 1 system 2 Device 3 vibration absorbers 4 housings 5 first pressure chamber 6 second pressure chamber 7 Mass 8 centering spring 9 first round 10 Piston rod 12 third chamber 13 Reservoir 15 second valve 20 systems 21 vibration dampers 22 second round 23 Reservoir 24 first valve 26 hydraulic accumulators 30 systems 31 vibration absorbers 32 metal bellows 33 Compensation hole 34 Digital valve 40 procedures 41 Process step 42 process steps 43 Process step 44 Process step 45 Process step

Claims

[1] Hydraulic vibration damper, which has: a first (5) and a second pressure chamber (6), each containing a hydraulic fluid, a mass (7) which is designed to move back and forth between the first (5) and the second pressure chamber (6) and thereby to change the pressure in the individual pressure chambers (5, 6), a third chamber (12) in which the mass (7) moves and which also contains hydraulic fluid; and a first passage (9) designed to allow the hydraulic fluid to flow between the two pressure chambers (5, 6), wherein the hydraulic vibration damper (3, 21, 31) further comprises a first valve (15) designed to regulate a flow rate through the first passage (9), and wherein the mass (7) is hydraulically preloaded. [2] Hydraulic vibration damper according to claim 1, wherein the hydraulic vibration damper (21, 31) further comprises a second passage (22) adapted to allow the hydraulic fluid to flow between a reservoir (23) containing the hydraulic fluid and the third chamber (12), and a second valve (24, 34) adapted to regulate a working pressure in the third chamber (12). [3] Hydraulic vibration damper according to claim 1 or 2, wherein the hydraulic vibration damper (21, 31) further comprises a gas-filled hydraulic accumulator (26) connected to the first pressure chamber (5) and a gas-filled hydraulic accumulator (26) connected to the second pressure chamber (6), wherein the hydraulic vibration damper (21) is designed such that the hydraulic vibration damper (21) can be adapted to different operating frequencies by means of the two gas-filled hydraulic accumulators (26). [4] Hydraulic vibration damper according to one of claims 1 to 3, wherein the hydraulic vibration damper (31) further comprises two metal bellows (32) for respectively sealing the working pressure in the first pressure chamber (5) and in the second pressure chamber (6) from the third pressure chamber (12). [5] Hydraulic vibration damper according to claim 4, wherein the hydraulic vibration damper (31) further comprises at least one compensating bore (33) between the first (5) and the third pressure chamber (12) and between the second (6) and the third pressure chamber (12). [6] System comprising: a device (2) and a hydraulic vibration damper (3,21,31) according to one of claims 1 to 5 for damping disturbing vibrations of the device (1). [7] Method for adjusting the damping effect of a hydraulic vibration absorber, the method (40) comprising the following steps: Selecting a mass (41), the weight of the mass being selected based on the weight of a device to be damped; Attaching a hydraulic vibration damper to the device (42), the hydraulic vibration damper having a first and a second pressure chamber, each containing a hydraulic fluid, the selected mass being adapted to reciprocate between the first and second pressure chambers and thereby vary the pressure in each of the individual pressure chambers, and a first passage in communication with a first valve for regulating a flow rate through the first passage; and Hydraulic preloading of the mass (43). [8] The method of claim 8, wherein the hydraulic vibration damper further comprises a third chamber in which the mass moves, and wherein the step of hydraulically biasing the mass (43) comprises introducing the hydraulic fluid into the third chamber. [9] The method according to claim 8, wherein the hydraulic vibration damper further comprises a second passage configured to allow the hydraulic fluid to flow between a reservoir containing the hydraulic fluid and the third chamber, and a second valve configured to regulate a working pressure in the third chamber, and wherein the method further comprises the following step: Adjusting the hydraulic preload by adjusting the flow rate through the second passage (44). [10] Method according to claim 8 or 9, wherein the hydraulic vibration damper further comprises a gas-filled hydraulic accumulator connected to the first pressure chamber and a gas-filled hydraulic accumulator connected to the second pressure chamber, and wherein the method further comprises the following step: Adaptation of the hydraulic vibration damper to different operating frequencies using the two gas-filled hydraulic accumulators (45).

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