EP2369152A1 - Dispositif de retenue - Google Patents

Dispositif de retenue Download PDF

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Publication number
EP2369152A1
EP2369152A1 EP11154285A EP11154285A EP2369152A1 EP 2369152 A1 EP2369152 A1 EP 2369152A1 EP 11154285 A EP11154285 A EP 11154285A EP 11154285 A EP11154285 A EP 11154285A EP 2369152 A1 EP2369152 A1 EP 2369152A1
Authority
EP
European Patent Office
Prior art keywords
holding device
component
exhaust system
coupling device
frequency
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP11154285A
Other languages
German (de)
English (en)
Other versions
EP2369152B1 (fr
Inventor
Thomas Nording
Joachim Hildebrand
Arnulf Spieth
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Eberspaecher Exhaust Technology GmbH and Co KG
Original Assignee
J Eberspaecher GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by J Eberspaecher GmbH and Co KG filed Critical J Eberspaecher GmbH and Co KG
Priority to EP15166890.2A priority Critical patent/EP2949899B1/fr
Publication of EP2369152A1 publication Critical patent/EP2369152A1/fr
Application granted granted Critical
Publication of EP2369152B1 publication Critical patent/EP2369152B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/18—Construction facilitating manufacture, assembly, or disassembly
    • F01N13/1805—Fixing exhaust manifolds, exhaust pipes or pipe sections to each other, to engine or to vehicle body
    • F01N13/1811—Fixing exhaust manifolds, exhaust pipes or pipe sections to each other, to engine or to vehicle body with means permitting relative movement, e.g. compensation of thermal expansion or vibration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/18—Construction facilitating manufacture, assembly, or disassembly
    • F01N13/1805—Fixing exhaust manifolds, exhaust pipes or pipe sections to each other, to engine or to vehicle body
    • F01N13/1811—Fixing exhaust manifolds, exhaust pipes or pipe sections to each other, to engine or to vehicle body with means permitting relative movement, e.g. compensation of thermal expansion or vibration
    • F01N13/1822—Fixing exhaust manifolds, exhaust pipes or pipe sections to each other, to engine or to vehicle body with means permitting relative movement, e.g. compensation of thermal expansion or vibration for fixing exhaust pipes or devices to vehicle body

Definitions

  • the present invention relates to a holding device for holding a component of an exhaust system to a peripheral structure, in particular a vehicle equipped with the exhaust system. Moreover, the present invention relates to an exhaust system provided with such a holding device.
  • vibrations may occur in an exhaust system.
  • Such vibrations can be excited, for example, by the internal combustion engine or by road bumps.
  • so-called motor excitations and road excitations are distinguished from each other.
  • heavier components of the exhaust system such as a catalyst or a particulate filter, crucial for the vibration behavior due to their larger mass.
  • the engine-induced vibration excitation via on the internal combustion engine of the vehicle, eg the motor housing and / or the transmission housing, fixed components in the vibration system, so the exhaust system registered, so that close to the engine components of the exhaust system are exposed to a much stronger vibration excitation than remote engine components.
  • a holding device of the type mentioned can be used. This can be attached by means of a first connection point to a component of the exhaust system and with a second connection point to the respective structure of the vehicle.
  • the problem with the use of such a holding device is the fact that the respective component of the exhaust system must be able to move relative to the adjacent structure of the vehicle in order to be able to compensate for thermal expansion effects. Will one Holding device used, which has sufficient elasticity to compensate for such thermal expansion, it also regularly allows undesirable component vibrations.
  • Such oscillations or relative movements represent a large mechanical load on the affected components, ie in particular the exhaust system, the vehicle structure and the holding device.
  • the present invention is concerned with the problem of specifying an improved embodiment for a holding device of the type mentioned at the outset or for an exhaust system equipped therewith, which is characterized in particular by the fact that the risk of damage to the respective component or component or the respective structure or The holding device is reduced.
  • the invention is based on the general idea of equipping the holding device with a coupling device which permits reversible relative movements between the two connection points of the holding device, but has a rigidity which depends on the speed or on the frequency of the relative movements.
  • the coupling device For slow or low-frequency relative movements, the coupling device has a relatively low rigidity.
  • the coupling device For faster or high-frequency relative movements, however, the coupling device has a relatively high rigidity.
  • a slow relative motion occurs when the component moves relative to the structure at less than 1 cm / sec.
  • Low frequency relative movements are oscillations with an oscillation frequency of less than 1 Hz.
  • rapid relative movements are given when the component moves relative to the structure with more than 1 cm / s.
  • the construction presented here makes possible slower or low-frequency movements, as occur, for example, due to thermal expansion effects.
  • the holding device obstructs or dampens faster or high-frequency relative movements which, for example, occur during operation of the vehicle due to the engine-induced and / or road-induced vibration excitation of the respective component of the exhaust system.
  • the coupling device has at least two coupling elements acting in series, of which the one slower or low-frequency relative movements substantially without force permits, while the other counteracts faster or high-frequency relative movements.
  • the slower or low-frequency relative movements are triggered by thermal expansion effects and are force-free enabled by the one coupling element, so that there are essentially no distortions within the exhaust system.
  • the motor-induced or road-induced vibration excitations lead in comparison to thermal expansion effects to faster or high-frequency relative movements, which then counteracts the other coupling element with corresponding forces.
  • the other coupling element then acts, for example as a damper and / or spring. It is also conceivable an active coupling element, which counteracts the faster or high-frequency relative movements as absorbers, so with backlashes.
  • the coupling device may comprise at least one hydraulic or pneumatic damper or be formed by such.
  • the damper includes a damping fluid which is displaced in a relative movement between the two connection points of a first chamber of the damper in a second chamber of the damper.
  • the two chambers are connected via a throttle point with each other.
  • the passage of fluid from one chamber into the other chamber is almost without resistance possible at low flow rates, while at high flow rates, the throttle unfolds its effect and thus slows or throttles the flow of fluid. Accordingly, such a damped damper acts softly for slow movements while being hard against fast movements.
  • the coupling device may comprise at least one elastomeric body, which consists of an electroactive polymer whose elasticity is variable by applying an electrical voltage, and which is connected to an electrical control circuit having a vibration sensor for detecting vibrations of the component or component and a controller for changing the elasticity of the elastomeric body depending on the oscillation frequency.
  • an elastomeric body is used whose elasticity depends on a thereto applied electrical voltage can be changed. This makes it possible, for example, in component vibrations whose vibration frequency is below a predetermined switching frequency to leave the elastomer body energized, whereby it has a comparatively high elasticity and has a soft damping characteristic.
  • a predetermined electrical voltage is applied to the elastomer body, whereby its elasticity is changed, namely reduced. As a result, a harder damping characteristic results.
  • the controller does not work with a vibration sensor, but with a map in which the elasticity to be set is stored depending on the speed of the internal combustion engine.
  • the controller can communicate with a corresponding engine control unit of the internal combustion engine.
  • the speed of the internal combustion engine correlates with the engine-induced vibration excitation, so that the setting of the frequency-dependent elasticity can be realized here with a simplified control effort.
  • the controller may switch the two above-described states, namely, turning off the predetermined voltage and turning on the predetermined voltage.
  • it may be provided to vary the tension on the elastomer body in several stages so as to be able to change the elasticity of the elastomer body in a stepped manner.
  • several different switching frequencies can be predetermined for this purpose, which trigger a stepwise increase in the voltage applied to the elastomer body.
  • the coupling device may have a dilatant material for transmitting motion between the two connection points.
  • a dilatant material is characterized by a dependent on the speed of the force application elasticity, in a solid, or viscosity, in a liquid.
  • there is a malleable dilatant mass that, when thrown onto the ground, springs back like a rubber ball and, when hit with a hammer, breaks like a ceramic body.
  • the Applicant has recognized that such a dilatant material is highly suitable for realizing a speed-dependent or frequency-dependent stiffness in a coupling device. In high-frequency disturbances, the dilatant material reacts hard and shows a high rigidity. In case of slow disturbances it reacts softly and can be deformed be, depending on the embodiment - elastic or plastic, but in particular reversible.
  • At least one spring element may be provided to produce a corresponding restoring force in the case of a change in shape of the dilatant material.
  • this arrangement of dilatant material and at least one spring element acts as a spring.
  • this arrangement of dilatant material and at least one spring element acts as a solid.
  • the coupling device may comprise a piston-cylinder unit whose cylinder is firmly connected to the one connection point and the piston fixed to the other connection point.
  • the cylinder contains a chamber in which the piston is movable. This chamber is filled with the dilatant material, which may be a liquid or pasty or solid dilatant material.
  • the dilatant material which may be a liquid or pasty or solid dilatant material.
  • the coupling device may comprise a flexurally elastic sheet metal part or be formed by such.
  • This sheet metal part has at least one closed cavity, in which a free-flowing granules is arranged.
  • the volume filled by the granulate is smaller than the total volume of the cavity.
  • relative movements between the connection points lead to elastic deformations of the sheet metal part. With low-frequency relative movements, the granules can follow the movements of the sheet metal part.
  • a movement excitation which absorbs energy from the vibration system, that converts into heat and thereby causes a damping of the vibration.
  • the general idea of the invention is based on the idea of realizing the coupling device by means of at least one electric actuator.
  • An associated electrical control circuit comprises the respective actuator, at least one vibration sensor for detecting vibrations of the component and at least one controller for actuating the actuator as a function of the vibration frequency.
  • the actuator can now change a distance between the connection points depending on its operation.
  • the coupling device can counteract relative movements between component and structure more or less strongly. For example, low-frequency relative movements can be realized with little resistance, while high-frequency relative movements are realized only against increased resistance and even against oppositely directed movements.
  • the controller can excite the respective actuator with the oscillation frequency at which vibrates the component to oscillate. It is particularly expedient to realize the Aktuatorschwingungen compared to the component vibrations with a phase shift, which is chosen so that adjusts a reduction of the vibration amplitudes on the component.
  • the coupling device works like an anti-vibration generator, which effectively reduces the vibration amplitudes of the component. Ideally, even a vibration cancellation can be realized.
  • the coupling device is analogous to an anti-noise generator operated, which extinguishes or reduces Schwindungsamplituden of sound to be damped in an active silencing system by means of phase-shifted anti-sound.
  • the actuator is equipped with an electroactive polymer that changes its shape by applying an electrical voltage.
  • the actuator can be realized particularly inexpensively.
  • the electroactive polymer can be realized in a wide variety of geometric shapes.
  • a piezo actuator can also be used.
  • FIG. 1 an internal combustion engine 1 in a conventional manner an exhaust system 2, which is connected for example via an exhaust manifold 3 or manifold 3 to the internal combustion engine 1.
  • the exhaust system 2 comprises an exhaust pipe 4, which is connected to the manifold 3 and leads away the exhaust gas collected there.
  • the exhaust system 2 has in the usual way at least one exhaust gas treatment device 5, which is integrated into the exhaust pipe 4. in the Example of Fig. 1 only one such exhaust treatment device 5 is shown, which is integrated into the exhaust pipe 4 relatively close to the internal combustion engine 1.
  • the exhaust gas treatment device 5 is a catalyst. Likewise, it may be a particulate filter.
  • the exhaust system 2 is held or positioned or supported by means of a holding device 6 at its periphery.
  • the holding device 6 cooperates with a peripheral structure 7 of a vehicle, in which the internal combustion engine 1 is arranged.
  • the peripheral structure 7 is in the example of Fig. 1 to a transmission housing 8 of a transmission which is connected to the internal combustion engine 8.
  • the holding device 6 may be connected to an engine block 9 of the internal combustion engine 1.
  • a body of the vehicle can serve as a support for the holding device 6.
  • a component 10 or component 10 of the exhaust system 2 can now be held on said structure 7.
  • Fig. 1 is the component 10 and the component 10 is formed by a portion of the exhaust pipe 4, which is fixed by means of the holding device 6 on the vehicle side.
  • Said pipe section 10 is positioned downstream of the exhaust gas treatment device 5.
  • the connection points mentioned are purely exemplary.
  • the respective holding device 6 has a first connection point 11, by means of which the holding device 6 can be fastened to the respective component 10 of the exhaust system 2, and a second connection point 12, with which the holding device 6 can be attached to the respective peripheral structure 7. Furthermore, the holding device 6 has a coupling device 13 arranged between the connection points 11, 12. This coupling device 13 is designed so that it allows reversible relative movements between the connection points 11,12. Such relative movements For example, in one of the Fig. 2 and 3 effected by a double arrow indicated direction of action 14.
  • the exhaust system 2 can be excited in the region of the first connection point 11 in the operation of the internal combustion engine 1 to vibrations whose vibration directions in Fig. 1 indicated by double arrows and denoted by 15. Shown are longitudinal vibrations and transverse vibrations. Likewise, rotational vibrations are conceivable. In addition to these high-frequency or rapid relative movements between the respective component 10 of the exhaust system 2 and the stationary structure 7 in this regard, there may also be slow or low-frequency relative movements between said components. For example, the thermal expansion of the exhaust system 2 during operation leads to a displacement of the first connection point 11 relative to the internal combustion engine 1 and thus relative to the structure 7. A direction of action of the thermal expansion is in Fig. 1 indicated by a double arrow and designated 16.
  • the coupling device 13 may be configured so that it has a speed-dependent and / or frequency-dependent stiffness at least in its effective direction 14. This has the consequence that the stiffness of the coupling device 13 at slow relative movements between the connection points 11,12 or at low-frequency relative movements between the connection points 11,12 has a comparatively small stiffness, while at faster or high-frequency relative movements between the connection points 11,12 has a relatively high rigidity.
  • the slow or low-frequency relative movements are usually triggered by the thermal expansion 16 relative movements.
  • the faster or high-frequency relative movements are vibrations 15 of the exhaust system 2, which in the Operation of the internal combustion engine 1 in the region of the respective component 10 of the exhaust system 2 occur.
  • the stiffness in the present context is understood to be reciprocal to the elasticity, so that a high rigidity is associated with a small elasticity, while a large elasticity leads to a low rigidity.
  • Such a coupling device 13 with speed-dependent and / or frequency-dependent stiffness can be realized in different ways.
  • Fig. 2 a solution in which the coupling device 13 has a hydraulic or pneumatic damper 17 or is formed by such a damper 17.
  • said damper 17 in the example by a piston-cylinder unit 18, which has a cylinder 19 and a piston 20 which is led out by means of a piston rod 21 from the cylinder 19.
  • the piston 20 separates in the cylinder 19 two spaces 22, 23, which are connected by a throttle point 24 with each other. Through this throttle point 24 fluid can flow from one chamber 22 into the other chamber 23 in a piston movement in the cylinder 19.
  • the hydraulic fluid may be liquid or gaseous or pasty.
  • cylinder 19 and piston 20 and the chambers 22 and 23 may have basically any cross-sections.
  • round cross-sections such as circular, elliptical or oval cross-sections, come into consideration as well as angular cross-sections, such as triangular, quadrangular, hexagonal and octagonal cross-sections.
  • Fig. 3 shows another embodiment of the coupling device 13, which has at least one elastomeric body 25 which consists of an electroactive polymer.
  • an electroactive polymer changes its elasticity by applying an electrical voltage.
  • the holding device 6 additionally comprises an electrical control circuit 26 for actuating the elastomer body 25.
  • the control circuit 26 comprises a controller 27 and a vibration sensor 28 for this purpose.
  • the vibration sensor 28 can detect vibrations of the component 10 of the exhaust system 2 and transmit them via a signal line 29 of FIG Feed control 27.
  • the controller 27 is connected via control lines 30 to the elastomer body 25 and to the electroactive polymer.
  • the elastomeric body 25 is disposed between two plates 31, in particular fixedly connected thereto, for example glued or vulcanized.
  • the plates 30, 31 are connected via connecting element 32 with the connection points 11, 12 in connection.
  • the connecting elements 32 and the plates 31 serve here as connection electrodes in order to connect the control lines 30 to the elastomer body 25 or to the electroactive polymer.
  • the controller 27 can now change the elasticity of the elastomeric body 25 depending on the detected vibration frequency.
  • the change in the elasticity of the elastomer body 25 can be varied, for example, in at least two stages. Likewise, a continuous adaptation of the elasticity to the oscillation frequency can be realized.
  • the controller 27 may be configured or programmed to vary the elasticity of the elastomeric body 25 at the detected vibration frequency. In particular, it is possible to shift the elasticity oscillations with respect to the component vibrations with respect to their phase, in particular in such a way that this results in a reduction of the vibration amplitudes on the respective component 10.
  • the respective component 10 is the component 10, which by means of the holding device 6 is supported. In the example of Fig. 1 is the component 10, the exhaust pipe 4 and the pipe section 10th
  • the controller 27 operates with a low-pass filter, so that the slow, low-frequency thermal expansions trigger no reaction by the controller 27, namely a driving of the elastomer body 25.
  • the controller 27 takes into account thermally induced expansion effects, which likewise lead to relative movements, by means of a special characteristic in which the thermally induced relative movements are plotted as a function of the current component temperature.
  • the controller 27 can interact with a corresponding temperature sensor. In this way, the slow relative movements can be superimposed on the fast relative movements.
  • the thermally induced relative movements on the one hand and the relative movements generated by the component vibrations on the other hand within the coupling device 13 at least two separate coupling elements are provided which act in series.
  • two elastomeric bodies 25 are then provided whose elasticities can be changed independently of each other with the aid of the control 27.
  • the thermally induced strain can be allowed almost force-free, while with the aid of the second elastomer body 25 of the vibration excitation can be counteracted frequency-dependent with corresponding counter forces.
  • the coupling device 13 may include at least one electric actuator 33 and be formed by such.
  • the holding device 6 in this case comprises an electrical control circuit 34 for actuating the actuator 33.
  • This control circuit 34 has a vibration sensor 35, with the aid thereof Vibrations of the respective component 10 can be detected.
  • a signal line 36 supplies the detected vibrations to a controller 37.
  • Control lines 38 connect the controller 37 with the actuator 33.
  • the actuator 33 has in the example two plates 31, which are each connected via a connecting element 32 with the two connection points 11,12. An actuation of the actuator 33 leads to a change in the distance between the two connection points 11, 12.
  • the controller 37 depending on the determined oscillation frequency, the actuator 33 for changing the distance between the connection points 11,12 drive.
  • the actuator 33 is equipped with an electroactive polymer which changes its shape by applying an electrical voltage.
  • the shape of the polymer can be selectively changed by applying an electrical voltage and thus in particular the distance between the connection points 11, 12 can be varied.
  • the controller 37 may preferably be configured or programmed such that it excites the actuator 33 with a frequency to oscillations, which corresponds to the determined by means of the vibration sensor 35 frequency. It is now particularly advantageous to shift the actuator oscillations in terms of their vibration amplitudes in relation to the determined component vibrations in their phase. This phase shift is carried out in a targeted manner so that a reduction of the oscillation amplitudes is established on the respective component.
  • the actuator 33 is operated in this case as an active silencer for structure-borne noise. He works with quasi anti-vibration or counter-vibrations, which at least partially extinguish the vibrations of the component 10 to be damped.
  • the controller 37 operates with a low-pass filter, so that the slow, low-frequency thermal expansions no reaction of the controller 37, namely a Activation of the actuator 33 trigger.
  • the controller 37 takes into account thermally induced expansion effects, which likewise lead to relative movements, by means of a special characteristic in which the thermally induced relative movements are plotted as a function of the current component temperature.
  • the controller 37 may be coupled to a corresponding temperature sensor. In this way, the slow relative movements can be superimposed on the fast relative movements.
  • the thermally induced relative movements on the one hand and the relative movements generated by the component vibrations on the other hand within the coupling device 13 at least two separate coupling element are provided, which act in series.
  • two actuators 33 are then provided, whose actuating movements can be changed independently with the aid of the controller 37.
  • the thermally induced strain can be allowed almost force-free, while using the second actuator 33der the vibration excitation can be counteracted frequency-dependent with corresponding counter forces.
  • Fig. 5 can be realized for the holding device 6 preferably a mounting, which causes the effective direction 14 of the holding device 6 and the coupling device 13 is substantially parallel to the thermal expansion direction 16, in which the respective component of the exhaust system 2, here the exhaust pipe 4 or the pipe section 10 moves relative to the structure 7.
  • the design of the coupling device 13 with frequency-dependent stiffness or as an actuator is of particular interest.
  • Fig. 6 shows a further embodiment of a coupling device 13 with frequency-dependent or speed-dependent stiffness.
  • the coupling device 13 has a dilatant material 39.
  • This dilatant material 39 may be a liquid or a solid.
  • the viscosity changes with the force introduction velocity.
  • a solid dilatant material changes with the force introduction speed, the elasticity.
  • the dilatant material is low viscosity or highly elastic. With a fast introduction of force, its viscosity increases strongly or has an extremely high rigidity.
  • the dilatant material 39 is arranged within the coupling device 13 so that it serves for the transmission of movement between the two connection points 11,12. In other words, a relative movement between the two connection points 11, 12 is only possible if within the coupling device 13, the dilatant material 39 is deformed or displaced.
  • the coupling device 13 again has a piston-cylinder unit 40, which has a cylinder 41, a piston 42 and a piston rod 43, which is connected to the piston 42 and leads out of the cylinder 41.
  • One connection point 11 is fixedly connected to the cylinder 41, while the other connection point 12 is fixedly connected to the piston 42 via the piston rod 43.
  • the piston 42 is adjustable in a working chamber 44 of the cylinder 41, in which the dilatant material 39 is located.
  • the piston 42 does not have to be guided laterally in the cylinder 41.
  • the piston 42 can be embedded in the dilatant material 39.
  • the piston 42 may be within the dilatant material 39 relative to the cylinder 41st to be moved. However, if fast movements are to be performed, the dilatant material 39 is extremely counteracting.
  • the dilatant material 39 may also be formed into an elastomeric body. Then basically a structure like in Fig. 3 feasible without then a control circuit 26 is required.
  • the dilatant material 39 is in the form of an elastomeric body, optionally at least one spring element can be arranged so that it acts parallel to the elastomeric body.
  • such a spring element can be integrated into the elastomer body or embedded therein.
  • slow relative movements essentially only the spring force then acts, which drives the components coupled to one another with the aid of the coupling device 13 into a starting position.
  • rapid relative movements leads the dilatant material 39 to block the movement or to a strong damping, which superimposes the spring force.
  • Fig. 7 shows a further embodiment for a coupling device 13, which has a plurality of elastomer body 45, 46 and 47.
  • elastomer bodies 45, 46, 47 may consist of an electroactive polymer, but may be arranged differently with respect to their direction of action.
  • the direction of action of the central elastomer body 45 is perpendicular to the effective directions of the two outer elastomeric bodies 46, 47.
  • electric actuators can also be provided here.
  • FIG. 8 and 9 show a first design while the 10 and 11 play a second design.
  • Fig. 12 shows a sectional view, which in principle for both types of 8 to 11 Has validity.
  • the coupling device 13 comprises a bending elastic sheet metal part 48.
  • Said sheet metal part 48 has at least one closed cavity 49 in which Fig. 12 a free-flowing granules 50 is arranged. Visible here is the volume filled by the granules 50 smaller than the total volume of the respective cavity 49. This has the consequence that the granules 50 can move in the cavity 49.
  • a plurality of chambers 51 are formed in the cavity 49, on the one hand restrict the movement of the granules 50 within the cavity 49 to the individual chambers 51 and on the other hand cause a transverse stiffening of the sheet metal body 48.
  • the chambers 51 may be configured honeycomb-shaped.
  • the hollow chambers 49 can be realized in the sheet metal part 48, for example, by the fact that the respective sheet metal part 48 is formed at least in the region of the respective cavity 49 as a double sheet structure 52, which again in Fig. 12 is indicated. Within the respective double sheet structure 52, two individual sheets 53, 54 are provided, each having a recess 55 and 56, which complement each other in the assembled state mirror symmetry to the respective cavity 49.
  • the sheet metal parts 48 have in the examples shown here at their remote ends, the connection points 11 and 12th

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Vibration Prevention Devices (AREA)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
  • Exhaust Gas After Treatment (AREA)
  • Exhaust Silencers (AREA)
EP11154285.8A 2010-03-24 2011-02-14 Dispositif de retenue Active EP2369152B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP15166890.2A EP2949899B1 (fr) 2010-03-24 2011-02-14 Dispositif de retenue

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010012663 2010-03-24
DE102010034313A DE102010034313A1 (de) 2010-03-24 2010-08-13 Haltevorrichtung

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP15166890.2A Division-Into EP2949899B1 (fr) 2010-03-24 2011-02-14 Dispositif de retenue
EP15166890.2A Division EP2949899B1 (fr) 2010-03-24 2011-02-14 Dispositif de retenue

Publications (2)

Publication Number Publication Date
EP2369152A1 true EP2369152A1 (fr) 2011-09-28
EP2369152B1 EP2369152B1 (fr) 2015-07-15

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EP15166890.2A Active EP2949899B1 (fr) 2010-03-24 2011-02-14 Dispositif de retenue
EP11154285.8A Active EP2369152B1 (fr) 2010-03-24 2011-02-14 Dispositif de retenue

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US (1) US8485302B2 (fr)
EP (2) EP2949899B1 (fr)
JP (1) JP5725920B2 (fr)
CN (1) CN102200045B (fr)
DE (1) DE102010034313A1 (fr)

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DE102009015420A1 (de) * 2009-03-27 2010-09-30 Emitec Gesellschaft Für Emissionstechnologie Mbh Wabenkörper für ein Abgasreinigungssystem
DE102010020032A1 (de) * 2010-05-11 2011-11-17 J. Eberspächer GmbH & Co. KG Schwingungstilger
DE102012219373A1 (de) * 2011-10-27 2013-05-02 Schaeffler Technologies AG & Co. KG Ausrücksystem
CN103217331A (zh) * 2013-04-27 2013-07-24 江苏大学 一种金相镶嵌机镶嵌薄板试样的方法和夹片辅助装置
CN109112503B (zh) * 2017-06-23 2021-01-08 北京北方华创微电子装备有限公司 反应腔室的排气装置及反应腔室
US11242934B2 (en) 2018-03-09 2022-02-08 Fujikin Incorporated Valve device
CN113423987A (zh) * 2019-01-31 2021-09-21 株式会社富士金 阀装置、流量控制方法、流体控制装置、半导体制造方法以及半导体制造装置
KR102605036B1 (ko) * 2019-09-04 2023-11-22 삼성중공업 주식회사 스크러버
CN113685473B (zh) * 2021-08-19 2022-09-16 奇瑞汽车股份有限公司 减振结构

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US5082252A (en) * 1987-11-25 1992-01-21 Honda Giken Kogyo Kabushiki Kaisha Fluid-filled mount
DE19734499A1 (de) * 1997-08-08 1999-02-18 Daimler Benz Ag Elastische Aufhängevorrichtung für eine Auspuffanlage
EP1160428A2 (fr) * 2000-05-27 2001-12-05 Eras Entwicklung und Realisation adaptiver Systeme GmbH Support élastique pour une fixation vibratoirement isolée d'un sytème d'échappement à un plancher de véhicule
US20020109280A1 (en) * 2001-02-15 2002-08-15 Baudendistel Thomas A. Active decoupler hydraulic mount
US20020175594A1 (en) * 2001-05-22 2002-11-28 Sri International Variable stiffness electroactive polymer systems

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EP2369152B1 (fr) 2015-07-15
CN102200045B (zh) 2014-12-10
US20110232986A1 (en) 2011-09-29
EP2949899A1 (fr) 2015-12-02
EP2949899B1 (fr) 2016-11-02
JP5725920B2 (ja) 2015-05-27
US8485302B2 (en) 2013-07-16
DE102010034313A1 (de) 2011-09-29
CN102200045A (zh) 2011-09-28
JP2011201531A (ja) 2011-10-13

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