CN102803810A - Integrated hydraulic damping device - Google Patents

Abstract

Disclosed is a damping device for a fluid system wherein the damping device comprises an inner tube (205) and an outer tube (200). Fluid pressure waves entering the damping device are damped in an annular space (235) arranged between at least a portion of the inner tube (205) and the outer tube (200). At least part of the inner tube (205) is integrated in the outer tube (200) which is made of a rigid material. The outer tube (200) is preferably a tube part of the fluid system itself wherein the inner tube (205) is mounted within the outer tube (200) in a manner that one part of the inner tube (205) is orientated opposite to the flow direction of the fluid and that the other part of the inner tube (205) is orientated in the flow direction of the fluid.

Description

Integrated hydraulic shock absorber

technical field

The invention relates to a damping device for damping, damping or absorbing vibrations or pulsations in a fluid system, especially a hydraulic system, more particularly a hydraulic system for the automotive sector.

Background technique

In a fluid or hydraulic pipeline system, a driving source generates pressure pulsations or fluctuations during operation, which causes mechanical vibrations, thereby generating sound or noise. In various fields of application of such hydraulic systems, such as the motor vehicle field, such noises are to be reduced, for example, for reasons of user comfort.

In order to reduce or minimize such vibration or noise, U.S. Patent No. 7,017,610 B2, which has been assigned to the assignee of the present application, discloses inserting a damping device (resonator or tuner) between the two ends of the hydraulic circuit, which absorbs or Attenuates the aforementioned pulsations or pressure fluctuations. The damping device comprises a damping housing, which is preferably an expansion hose made of an elastic material, in which a damping tube extending into the interior of the hydraulic line is arranged opposite to the flow direction of the fluid. To achieve such damping, as described in more detail in US7017610B2, the damping tube is made of a material that is preferably less radially flexible than the damping housing, and is more preferably coated with a plastic such as polytetrafluoroethylene Metal or spiral tape of fluoroethylene (PTFE).

By using such a damping arrangement, forming a pressure-tight resonator wall, pressure pulsations or peaks entering the interior space move in the form of pressure waves between the outer wall of the damping housing and the damping tube. These pressure waves are reflected and damped in the annular space between the damper tube and the damper housing wall. As a result, pressure fluctuations or peaks reaching the outlet of the damper have only a small effect or even disappear.

For example in the automotive sector, for hydraulic systems, there is still a growing need to reduce the length of hoses used and to replace hoses with fittings. The main reason for these changes is the higher cost of hydraulic hoses compared to hydraulic fittings. Therefore, the applicable occasions for using the above-mentioned vibration damping device are reduced.

Contents of the invention

In a first aspect, the invention provides a damping device, wherein the aforementioned damping tube (=inner tube) or at least part of it is assembled or integrally integrated into a pipe (=outer tube) of a hydraulic line system ) to appear as an in-tube damping device. Thus, in contrast to known damping devices, the damping tube is arranged in a rigid tube instead of an elastic hose.

It is to be noted that the term "hydraulic line" is understood throughout this specification to mean hydraulic hoses, pipes, fittings or the like of any size, since the basic idea of the invention is not limited to a particular type or size of hydraulic line .

As in known damping devices, the damper tube acts as a resonator for damping the aforementioned pressure waves. It is also known that in a counter fluid flow configuration in which the open end of the damper tube is arranged opposite to the direction of fluid flow, especially low frequency pressure waves are attenuated, thereby advantageously reducing or minimizing low frequency noise. However, it is also well understood that mid and high frequencies can also be attenuated using the techniques described in this article.

But in contrast to known damping devices which use only elastic hose parts as outer tubes, the present invention makes it possible to arrange said damping devices in pipes of hydraulic pipeline systems and allows the use in such systems of more More fittings than hose sections. This advantageously increases the flexibility to design hydraulic lines containing both hoses and fittings, and helps reduce the cost of such systems due to the factor mentioned above that hoses are more expensive than pipe lines or pipe sections .

In addition, the mentioned reduction in hose length also reduces the hydraulic line space for arranging known damping devices which have to be installed in the hose instead of the pipe. The present invention overcomes this disadvantage of the known damping technique because pipes of the hydraulic system, rather than hose sections, are used to mount the damping device.

According to another variant, the in-line damping device can be mounted on a pipe arranged between two hose parts or between two pipe parts or between a hose part and a pipe part of a fluid or hydraulic line system middle.

In another variant, the damper tube can be oriented opposite to the direction of flow of the (hydraulic) fluid, or along the direction of flow.

According to another variant, the damper tube can be mounted (i.e. fastened or clamped) in the pipe in such a way that a part of the damper tube is oriented opposite to the flow direction (counter-flow) while the other part is oriented in the flow direction (down-flow), The damping device can thus calibrate or adjust its damping performance, preferably damping frequency and damping intensity, by changing the ratio of forward flow resonance/counterflow resonance, wherein the ratio can be greatly adjusted by changing the installation position along the length of the damping tube. easy to change. However, the mounting position can also vary depending on the sound and the desired damping effect.

According to another solution, the above-mentioned fixation or clamping of the damper tube in the (outer) tube may be tight (i.e. leak-free), or have a limited leak such that at least some fluid is able to pass not through the damper tube but through the The annular space between the damper tube and the (outer) tube wall flows from one side to the other. Such leakage can additionally or alternatively be used to calibrate and/or tune the damping performance of the damping device. However, such leakage has to be as small as possible or even reduced to zero in order to attenuate low frequencies, since low frequencies cause faster (liquid) flows than high frequencies.

In another aspect of said calibration or tuning, defined leakage can be provided by means of boreholes or holes preferably located in the inner pipe wall (perforations) and/or in a plurality of defined positions along said annulus, through which holes or The holes shorten the resonant length (ie, the resonator length), thereby changing the resonant frequency of the resonator.

According to another aspect of the present invention, the provided in-pipe damping device can be used in conjunction with known damping device technology using PTFE based resonators such as the FBS tuner described in US7017610B2. In such a combination, the in-tube damping portion can be along the flow direction, thereby acting as a downstream tuner, and the PTFE or FBS tuner can be arranged upstream, acting as a downstream tuner, or vice versa.

According to another solution, it should be emphasized that the inner tube (damping tube) and/or the (outer) tube can be produced from standard tube materials known from the prior art, but preferably from the material of the damping tube and (outer) tube Materials that are the same or different but chemically and/or physically matched for protection against galvanic corrosion.

Surprisingly, it has been found that the inner tube can be made of deformable metals such as aluminum or steel which are much cheaper than the above-mentioned PTFE, these materials should preferably include inherently high rigidity, but can be plastically deformed, so that the inner tube can pass through Plastic deformation of the outer tube to fix in the outer tube. These materials should also not include leak points along their length.

However, other elastically or plastically deformable materials can also be used, but when selecting the material for the damper tube, consideration must be given to a certain resistance to expansion pressure and to collapse under pressure.

Besides, the damping device proposed herein can advantageously be made of low-cost materials without the use of the aforementioned PTFE material. It is worth noting that the PTFE material has the additional disadvantage that the PTFE pipe may collapse if it is installed in the counter-flow direction. To reduce this risk, known damper tubes include pressure compensating bores or bores arranged near the fixing point of the PTFE to the damper housing.

Therefore according to yet another solution, the proposed damping device can be made with two pipes by inserting and fixing the first (inner) pipe (hereinafter referred to as the damping pipe) in the straight (outer) pipe and then inserting the outer pipe together with the formed The damper tube is manufactured by bending to a desired angle. Due to the aforementioned materials for the damper tube, this bending will neither damage the damper tube nor adversely affect the aforementioned surprising resonance effect of the damper tube. The reason for not affecting resonance performance is likely that the damper tube self-aligns within the outer tube when the outer tube is bent.

Hydraulic piping often combines hydraulic piping or fittings and hydraulic hoses, since hydraulic piping or fittings are generally much less expensive than hydraulic hoses. If such hydraulic lines are used to connect, for example, hydraulic sources and user loads that are movable relative to each other within a certain range, such as the air conditioning system and engine of a vehicle, such hydraulic hoses generally require a certain degree of flexibility. The in-line damping device proposed according to the invention is only provided in pipes in such hydraulic line arrangements, wherein the length of the pipe part itself can even be relatively short. The invention here does not so much limit the degree of freedom in designing the piping arrangement of the fluid or hydraulic system.

Other representative aspects and features of the invention are defined in the dependent claims, including but not limited to the following detailed description.

Description of drawings

The above and other aspects, features and advantages of the present invention will appear from the following detailed description of illustrative embodiments taken in conjunction with the accompanying drawings, in which:

Figures 1A and 1B are schematic longitudinal side views of two embodiments of an in-tube tuner according to the invention to illustrate the basic idea of the invention.

2 is a side sectional view of an in-tube tuner according to another embodiment of the present invention;

Figure 3 is a side sectional view of another embodiment according to the present invention incorporating an in-tube tuner and known vibration damping device technology.

4A-4D illustrate a preferred method of manufacturing an in-tube tuner according to the invention.

Detailed ways

Specific embodiments of the present invention will now be described with reference to the accompanying drawings. The drawings will illustrate the basic principles and various embodiments thereof, but should not be construed to scale, especially their absolute and relative dimensions and proportions. However, this invention may be embodied in many different forms and should not be construed as limited to the embodiments provided herein; Person fully infers the scope of the present invention. The terminology used in the detailed description of the particular embodiments shown in the drawings is not intended to be limiting of the invention. Like reference numerals are used in the drawings to refer to like elements.

With reference to FIGS. 1A and 1B , the basic idea of the invention is illustrated by two embodiments shown in schematic longitudinal side views of the inventive in-tube damping device (tuner). The damping device is integrally integrated into the hydraulic pipeline system, and Fig. 1 only shows a part of the hydraulic pipeline system (defined by severed or sheared ends 107 and 108) in which the damping device is arranged.

In the embodiment shown in FIG. 1A , the vibration damping device includes an outer tube 100 and an inner tube 105 , the inner tube 105 being substantially concentrically arranged or disposed within the outer tube 100 . The outer tube 100 includes an annular groove or opening 110 for securing the inner tube 105 therein. The unrevealed side of the groove is indicated by dashed line 115 .

The durable and reliable fixing or mounting structure 120 of the inner tube 105 in the outer tube 100 can be realized by a frictional or frictional mechanical connection or by gluing or welding. Concentric arrangement of tubes 100,105. As an alternative to using only a relatively wide groove 110, the mounting structure 120 may be realized by two or more (preferably narrow) annular grooves or openings spaced apart from each other along the longitudinal axis. However, when narrow slots are used, it is preferred to provide at least two such slots, in order to prevent the inner tube 105 from tipping inside the outer tube 100 and thus destroying the concentric arrangement described above.

In the embodiment shown in Figure IB, the outer tube 150 is not deformed or shaped as in the embodiment of Figure IA. The inner tube 155 is secured or mounted in the outer tube 150 by means of an annular sleeve 160 (the unrevealed side indicated by dashed line 165 ), which is arranged in the annular space between the two tubes 150 , 155 . Similar to the embodiment shown in FIG. 1A , the durable and reliable fixation or installation structure of the inner tube 155 in the outer tube 150 can be achieved through a mechanical mechanism of friction or force locking at the two joining surfaces (combining surfaces) 170, 175. Connection is achieved either by gluing, welding or rivets or similar structures at at least one of said joint surfaces. However, the durable fastening structure can also be achieved by locally deforming the inner tube 155 (for example expanding to assume an outer chime or flare), so that the described annular sleeve 160 can even be completely eliminated.

The functional aspects and modes of operation of the aforementioned damping device will be referred to in the following description of FIG. 2 .

Fig. 2 shows a side sectional view of a vibration damping device according to a first embodiment of the present invention. The damping device is mainly composed of two substantially concentric tubes, an outer tube 200 and an inner tube 205 . Due to such a configuration, the provided damping device may be understood as an "in-tube" damping device, since its calibration or tuning performance is described herein, may also be referred to as an "in-tube" tuner.

The inner tube 205 in this embodiment is secured within the outer tube 200 by a housing or sleeve 210 . However, it is also possible, without the shown sleeve 210, to assume the shown outer annular groove or annular groove 215, for example by gluing or by direct cold working (deformation) of the outer tube from the outside (see also Fig. 4A- 4D) to achieve said fixation by clamping or crimping the inner tube inside the outer tube, in particular preventing the inner tube from moving longitudinally relative to the outer tube.

The use of the shown sleeve 210 to secure the inner tube 205 in the outer tube 200 has the advantage that the inner tube 205 can be positioned properly and/or precisely. However, the sleeve 210 does not contribute at all to the damping performance in question and is therefore not essential. Additionally, in the embodiment of the elbow 200 (according to FIGS. 4A-4D ), the retaining or fastening effect of the sleeve 210 is virtually nil.

The vibration damping device of the present invention can be used to attenuate noise in hydraulic pipeline systems using hydraulic oil or other hydraulic fluids as fluids, especially in applications where user comfort is important, such as in the automotive sector, trucks, trains, utility vehicles or aviation tools. However, the damping device can also be used in other fluid systems with pressurized fluid flow, such as air conditioning systems or the like.

In the direction of the assumed fluid flow (arrow 220 ), the left-hand part 225 of the damper acts as a counter-flow resonator, while the right-hand part 230 acts as a down-flow resonator. Of course, by changing the flow direction 220 to the opposite direction, the damping device also works in the opposite direction. In this embodiment, however, the damping means preferably act on fluid flow in one direction only, left to right in this example, although the pressure wave itself will propagate in both directions as described below.

Of course, it is also well understood that the damping device described herein can also be used in cases where the fluid flows bidirectionally, for example in a cyclical fashion, since the tuning described enables calibration of the device even in the case of bidirectional fluid flow Or tune for good vibration damping.

With the illustrated flow direction 220 from left to right, at least part of the pressure fluctuations or pressure waves (such as noise from hydraulic pumps or similar devices) that propagate mainly from left to right will enter the outer wall of the inner tube 205 and the outer tube 200 The first annular space 235 between the inner walls also causes reflected waves and destructive interference between these reflected waves and the original waves, thereby reducing the amplitude or intensity of the pressure fluctuations.

In the right hand portion 230 of the damping device shown, any remaining pressure waves also do not enter the second annular space 240 between the outer wall of the inner tube 205 and the inner wall of the outer tube 200, providing only minimal pressure fluctuations. Or a "dead fluid" volume where vibrations exist, mainly due to destructive reflections and interference that exist in the second annular space 240.

It has surprisingly been found that the left-hand part 225 of the damping device, in which the aforementioned constructive/destructive interference mainly occurs, provides damping mainly for relatively low frequencies, while the right-hand part only provides damping mainly for mid-high frequencies The static fluid volume area.

It is emphasized that both effects contribute to the overall attenuation of the pressure wave propagating from left to right.

In this embodiment, the longitudinal position 245 for clamping or crimping the inner tube 205 in the outer tube 200 is asymmetrical, with the long portion of the inner tube disposed on the left hand side 225 and the short portion disposed on the right hand side 230 . However, this specific position can be adjusted for calibration or tuning purposes, and can even be located in the inner tube 205 to present a symmetrical damping arrangement, which then has the same damping effect in both directions, which has the following advantages One, that the damping device can work regardless of its installation orientation, which simplifies the installation of the device in, for example, a motor vehicle; or the device can advantageously be used to attenuate fluid flow alternating between two directions Noise in transformed fluid systems.

By changing or calibrating the longitudinal clamping position 245 of the inner tube 205, the resonant frequency v of the basic resonator can be adjusted almost arbitrarily or changed by Δv, so that the vibration damping performance of the device can be adjusted (tuned) over a wide frequency band .

In another embodiment, the sleeve 210 provides a defined leakage such that a portion of the fluid flows from the left hand side 225 to the right hand side 230 through the annular space 235 only. Such leakage may be provided by channels or holes provided in the housing/sleeve itself, or by some deformation of the housing/sleeve by the outer tube 200 . Via such leaks, the damping device can be calibrated (tuned).

Alternatively or additionally, such calibration or tuning may be accomplished by prescribed leakage, preferably using a drill located on the inner pipe wall (perforated) and/or at a number of prescribed locations along the annulus. Holes or apertures, whereby the resonant length (ie resonator length) can be shortened and thus the resonant frequency of the resonator can be changed.

Figure 3 shows an embodiment of the invention which combines the above described in-tube damping device (in-tube tuner) with a PTFE or FBS tuner known in the art. In this embodiment, the in-line damping device is provided in a hose-tubing connector or fitting assembly 300 that may be used to connect a hose 305 and a fitting 310 of a hydraulic line system. In both embodiments, fluid (not shown) flows from left to right as indicated by arrow 315 .

This embodiment includes the above-described in-tube tuner 320 with an outer tube 310 and an inner tube 323 as a right side portion 320 . The in-line tuner portion 320 is arranged or arranged along the flow direction 315, ie it acts as a downstream tuner as described above. The left end 330 of the in-tube tuner is inserted into the end 300 of the outer hose 305 of the PTFE or FBS tuner 335 described above. The PTFE or FBS tuner portion 335 acts as a countercurrent tuner, as described in US Pat. No. 7,017,610 B2.

The in-line tuner 320 is secured in the PTFE or FBS tuner 335 in this embodiment by a clamp 340 attached to the end 300 of the hose 305 . The clamping member 340 is preferably plastically deformable and/or a spring-actuated cap or cap to provide a constant and reliable inward force. It is emphasized that the connection between the two tuners 320, 335 must be tight to achieve the contemplated damping, since any uncontrolled leakage will detune the resonator. The clamp 340 is preferably realized by a flange or coupling integrally integrated to the end 300 of the hose 305 for the PTFE or FBS tuner 335 .

Clamping device 340 also includes in this embodiment a clamping region or annular profile 345 which is preferably created by deformation after in-tube tuner 320 has been inserted into PTFE or FBS tuner 335 . In this embodiment, the annular profile 345 is produced such that the outer tube 310 of the in-tube tuner 320 is deformed in a similar manner by means of which the inner tube 325 of the in-tube tuner 320 touches at least two lines or Clamped or fixed in the outer tube 310 at the contact area 350, this line of contact or contact area ensures that the inner tube 325 sits (or remains) substantially concentrically in the outer tube 310 and cannot spring back or even move radially .

In this embodiment, the PTFE or FBS tuner 335 is attached or mounted on the left end 360 of the inner tube 325 of the in-tube tuner 320 by a press-fit or shrink hose connection, and is preferably mounted on the left end 360 of the inner tube 325 of the in-tube tuner 320. Insert the PTFE or FBS tuner before the 335 is installed.

The damping device in the embodiment shown in FIG. 3 can also be installed in a counter-flow direction, thereby presenting a fluid inflow through the outer tube 310 and inner tube 325 instead of through the outer tube 305 and inner tube 355 . In such a "upstream installation", the in-line tuner 320 is used as the upstream tuner and the PTFE or FBS tuner 335 is used as the downstream tuner. Based on this, the function of the existing FBS or PTFE tuner can also be extended, so that it can provide the aforementioned vibration damping effect in both directions.

4A-4D illustrate the steps of a preferred manufacturing method for manufacturing the aforementioned vibration damping device.

The above vibration damping device can use two tubes and by inserting and fixing the first (inner) tube (hereinafter referred to as the vibration damping tube) in the straight (outer) tube and then bending the outer tube together with the built-in vibration damping tube to an ideal Made from the desired angle. Due to the aforementioned materials for the damper tube, this bending will neither destroy the damper tube nor adversely affect the aforementioned, surprising resonance effect of the damper tube. The reason for not affecting resonance performance is likely that the damper tube self-aligns within the outer tube when the outer tube is bent.

Referring to Figure 4A, an inner tube 400 of a given length "l" is made of metal or other tubing. The sleeve or housing 405 is then slid or fitted over the inner tube 400 (the unrevealed side of the sleeve is indicated by dashed line 410). According to FIG. 4B , the inner tube 400 including the sleeve 405 is inserted into the outer tube 415 from one end. As previously mentioned, this outer tube 415 is preferably part of the hydraulic line system, thereby presenting an in-tube damping device (or tuner). As an intermediate, this sleeve/housing is arranged in the annular space between the inner tube 400 and the outer tube 415 .

It is emphasized that the above-mentioned housing or sleeve 405 can be mounted first on the inner tube 400 or inside the outer tube 415 as in the above-described embodiments. In both cases, the housing or sleeve 405 can be secured by gluing, welding or using a friction or force-lock mechanical connection.

After inserting the inner tube 400 into the outer tube 415, the inner tube 400 will be fixed inside the outer tube 415 by annular deformation or extrusion of the outer tube 415 from the outside, as shown in FIG. 4C. This deformation is preferably formed near the middle of the position of the housing/sleeve along the longitudinal axis of the outer tube 415 , for example by cold forming from the outside of the outer tube 415 . Through this process, the housing or sleeve 405 is also deformed or squeezed, which increases the frictional force against the inner tube 400 so that the inner tube 400 is securely fixed in the outer tube 415 .

As already mentioned, the use of a sleeve/housing to fix the inner tube in the outer tube is only preferred, while such fixing can also be achieved without such a sleeve/housing, wherein in this case the inner The tube is held in place only by the deformed outer tube. Such a fixation can be durable and reliable, even leak-proof, without the use of a sleeve/housing.

The action of a straight in-tube damper as shown in FIG. 4C when being bent is shown in FIG. 4D. Such bending of the pipes of the hydraulic line system at the location where the in-pipe damping device is provided is only optional, but it increases the degree of freedom in designing the line system or piping arrangement of such a hydraulic system. Figure 4D shows how the possibility of leakage of the housing/sleeve 405 can be reduced by using a resilient material such as aluminum or polymer for the housing/sleeve 405 after the outer tube 415 has been bent. It is also shown that the inner tube 400 is not arranged concentrically within the outer tube 415 after bending, in particular the ends 425 , 430 of the inner tube 400 . Surprisingly, however, it has been found that such uncalibrated resonators do not have a significant negative effect on the damping performance of the in-tube damper.

The above-mentioned damping device can be made of standard pipes known in the prior art, but preferably the materials of the damping pipe and the (outer) pipe are the same or different but chemically and/or physically compatible materials to prevent contact corrosion. Such matching materials are well known in the chemical/physical literature and suitable types can be selected for different fields of application. Contact corrosion itself is a well-known phenomenon, and one of ordinary skill in the art will furthermore be able to find suitable material combinations.

However, other elastically or plastically deformable materials can also be used, but when selecting the material for the damper tube, consideration must be given to a certain resistance to expansion pressure and to collapse under pressure. In addition, the damping device proposed herein can advantageously be made of low cost materials without the use of the aforementioned PTFE material.

Hydraulic lines incorporating the damping devices provided herein are capable of bending without damaging the internal structure of the pipe, in contrast to existing damping devices using plastics such as PTFE, which collapse when bent at small bend radii , or even completely damaged.

Furthermore, the use of PTFE tubing would require pressure compensating drilling or perforations to prevent the tubing from collapsing. These drillings or holes will adversely affect the vibration damping performance of the vibration damping device. The damping device (in-tube tuner) of the invention preferably uses metal tubes, which do not require such pressure-compensating bores or holes. Of course, the flexible FBS tuner does not need such pressure compensation, but its cost is much more expensive than the vibration damping device of the present invention. In addition, there is no need to worry about the inflexibility of the damping device according to the invention, since there is sufficient space for arranging a rigid in-tube tuner according to the invention in the relevant field of application.

The in-line tuner described above can be arranged in a pipe between two hose parts or between two pipes or between a hose part and a pipe of a fluid or pipeline system.

While illustrative/specific embodiments of the present invention have been described in detail in the foregoing specification, it will be understood that the above-described Many modifications or variations of these details may be made in light of the overall teaching of the disclosure. Accordingly, the particular arrangements disclosed are intended to be illustrative only and are not intended to limit the scope of the invention which is to be defined by the full scope of the appended claims and any and all equivalents thereof.

Claims (19)

1. vibration damping equipment that is used for fluid system; Pipe and outer tube in this vibration damping equipment comprises; The hydrodynamic pressure ripple that wherein gets into this vibration damping equipment be arranged in part at least should in be attenuated in the annular space between pipe and this outer tube, at least part should in pipe and the outer tube one processed by rigid material constitute.

2. vibration damping equipment according to claim 1 is characterized in that, this outer tube is the part of this fluid system.

3. vibration damping equipment according to claim 1 and 2 is characterized in that, pipe is installed in this outer tube by this way in this, that is, the part of pipe and the flow direction of fluid are orientated on the contrary in this, and another part of pipe flows to orientation along this in being somebody's turn to do.

4. vibration damping equipment according to claim 3 is characterized in that, calibrates vibration damping frequency and/or vibration damping intensity through changing to manage in this along the mounting point longitudinally of this outer tube.

5. according to each described vibration damping equipment in the claim 1 to 4, it is characterized in that pipe installation in this outer tube is leak free basically in this, thereby have basically no fluid this annular space process between pipe and this outer tube in this.

6. according to each described vibration damping equipment in the claim 1 to 4, it is characterized in that the installation of pipe in this outer tube provides the leakage of qualification in this, thus segment fluid flow this annular space process between pipe and this outer tube in this at least.

7. vibration damping equipment according to claim 6 is characterized in that, said leakage is reduced the decay with enhance fluid low frequency pressure wave as far as possible.

8. according to claim 6 or 7 described vibration damping equipments, it is characterized in that the leakage of this qualification is provided by the boring or the eyelet that are positioned on the inner tubal wall.

9. according to claim 6 or 7 described vibration damping equipments, it is characterized in that the leakage of this qualification is provided by the boring or the eyelet at the assigned position place of the annular space between managing along this outer tube with in being somebody's turn to do.

10. according to each described vibration damping equipment in the claim 1 to 9; It is characterized in that; To combine with PTFE or FBS tuner according to the described vibration damping equipment of aforementioned arbitrary claim, wherein said interior pipe longshore current direction of flow arranges that the FBS tuner and the flow direction be layout on the contrary.

11. vibration damping equipment according to claim 10 is characterized in that, this vibration damping equipment is arranged in the flexible pipe-Tube jointer or adapter assembly of the pipe fitting that can be used for connecting flexible pipe and hydraulic line system.

12. vibration damping equipment according to claim 11 is characterized in that, the end of this vibration damping equipment is inserted in the end of outside flexible pipe of this PTFE or FBS tuner.

13. vibration damping equipment according to claim 12; It is characterized in that; This vibration damping equipment is through using elastically deformable or plastic deformation or being fixed to this PTFE or FBS tuner by spring-actuated clamping element, and this clamping element is attached to the said end of this outside flexible pipe.

14. vibration damping equipment according to claim 13 is characterized in that, this clamping element is cap, flange or the connecting sleeve of said end that integrates the outside flexible pipe of this PTFE or FBS tuner.

15., it is characterized in that pipe and/or this outer tube are processed by material identical or different but that chemistry and/or physics are complementary in this according to each described vibration damping equipment in the claim 1 to 14.

16., it is characterized in that pipe is by intrinsic high rigidity but still the material of plastically deformable is processed preferably aluminium or steel in this according to each described vibration damping equipment in the claim 1 to 15.

17. a manufacturing according to the method for each described vibration damping equipment in the claim 1 to 16, comprise with interior pipe insert the outer tube neutralization through the position that makes said outer tube and in this is housed, manage at least partly along longitudinal axis deform with should in manage and be fixed in this outer tube.

18. method according to claim 17; It is characterized in that; Sleeve or housing are installed to the outside of managing in this or the inboard of this outer tube; Should in pipe insert in this outer tube and make this outer tube the position that tube/housing is housed deform along longitudinal axis at least partly with should in manage and be fixed in this outer tube.

19. according to claim 17 or 18 described methods, it is characterized in that, also comprise this outer tube is somebody's turn to do interior canal curvature to predetermined angular together with fixing.

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