EP2369152B1 - Clamping device - Google Patents
Clamping device Download PDFInfo
- Publication number
- EP2369152B1 EP2369152B1 EP11154285.8A EP11154285A EP2369152B1 EP 2369152 B1 EP2369152 B1 EP 2369152B1 EP 11154285 A EP11154285 A EP 11154285A EP 2369152 B1 EP2369152 B1 EP 2369152B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- holding device
- component
- coupling device
- frequency
- vibrations
- 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.)
- Active
Links
- 230000033001 locomotion Effects 0.000 claims description 78
- 230000008878 coupling Effects 0.000 claims description 60
- 238000010168 coupling process Methods 0.000 claims description 60
- 238000005859 coupling reaction Methods 0.000 claims description 60
- 239000000463 material Substances 0.000 claims description 30
- 229920001971 elastomer Polymers 0.000 claims description 29
- 239000000806 elastomer Substances 0.000 claims description 28
- 230000001419 dependent effect Effects 0.000 claims description 20
- 238000002485 combustion reaction Methods 0.000 claims description 16
- 239000002184 metal Substances 0.000 claims description 16
- 229920001746 electroactive polymer Polymers 0.000 claims description 12
- 239000008187 granular material Substances 0.000 claims description 10
- 230000009471 action Effects 0.000 claims description 7
- 230000002093 peripheral effect Effects 0.000 claims description 7
- 230000009467 reduction Effects 0.000 claims description 6
- 230000002441 reversible effect Effects 0.000 claims description 5
- 230000006978 adaptation Effects 0.000 claims description 2
- 230000010355 oscillation Effects 0.000 description 16
- 230000005284 excitation Effects 0.000 description 10
- 230000000694 effects Effects 0.000 description 8
- 230000008859 change Effects 0.000 description 6
- 238000013016 damping Methods 0.000 description 6
- 239000007787 solid Substances 0.000 description 6
- 239000012530 fluid Substances 0.000 description 5
- 239000007788 liquid Substances 0.000 description 5
- 230000005540 biological transmission Effects 0.000 description 4
- 230000010363 phase shift Effects 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 239000003054 catalyst Substances 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 235000011837 pasties Nutrition 0.000 description 2
- 230000001960 triggered effect Effects 0.000 description 2
- 239000006096 absorbing agent Substances 0.000 description 1
- 230000004913 activation Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 239000000919 ceramic Substances 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 230000030279 gene silencing Effects 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 229920000642 polymer Polymers 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 230000003584 silencer Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Images
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, having the features of the preamble of claim 1. Furthermore, 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, for example on the motor housing and / or the transmission housing, fixed components in the vibration system, so the exhaust system registered, so that close-coupled components of the exhaust system are exposed to a much stronger vibration excitation than motorfeme 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 holding device comprises a first connection point for fastening the holding device to the tube of the exhaust system, a second connection point for fixing the holding device to the support frame and a coupling device arranged between the connection points, which allows reversible relative movements between the connection points, wherein the coupling device is designed such that it at least in a direction of action has a speed-dependent and / or frequency-dependent stiffness, such that the coupling device with slower or low-frequency relative movements a lower stiffness than in faster or high-frequency relative movements.
- the coupling device has a hydraulic damper.
- the present invention is concerned with the problem of providing for a holding device of the type mentioned or for an exhaust system equipped therewith an improved embodiment, 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 to provide the holding device with a coupling device that allows reversible relative movements between the two connection points of the holding device, but it has a stiffness that is dependent on the speed or 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 now has at least two coupling elements which act in series, of which the one permits slower or lower-frequency relative movements substantially without force, 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 via a throttle point with each other in Connection.
- 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 elastomer body is thus used, the elasticity of which can be changed depending on an electrical voltage applied thereto. 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. However, as soon as the component vibrations reach an oscillation frequency above the predetermined switching frequency, 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 with a corresponding engine control unit of Internal combustion engine communicate.
- 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 slow disturbances, it reacts softly and can be deformed, depending on the embodiment - elastic or plastic, but especially 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.
- a chamber In the cylinder is a chamber contain, 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.
- An alternative embodiment is based on the general idea to realize 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. With the help of such an actuator, the coupling device relative movements between Counteract 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 operated analogously to an anti-sound generator, 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 also 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 coupling device 13 it is necessary for separate consideration of 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 help of the second elastomeric 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.
- At least two separate coupling elements are provided within the coupling device 13, 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
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Vibration Prevention Devices (AREA)
- Exhaust Gas After Treatment (AREA)
- Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
- Exhaust Silencers (AREA)
Description
Die vorliegende Erfindung betrifft eine Haltevorrichtung zum Halten eines Bestandteils einer Abgasanlage an einer dazu peripheren Struktur, insbesondere eines mit der Abgasanlage ausgestatteten Fahrzeugs, mit den Merkmalen des Oberbegriffs des Anspruchs 1. Außerdem betrifft die vorliegende Erfindung eine mit einer derartigen Haltevorrichtung versehene Abgasanlage.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, having the features of the preamble of
Im Betrieb eines Kraftfahrzeugs kann es in einer Abgasanlage zu Schwingungen kommen. Derartige Schwingungen können z.B. durch die Brennkraftmaschine oder durch Fahrbahnunebenheiten angeregt werden. Dementsprechend werden sogenannte Motoranregungen und Fahrbahnanregungen voneinander unterschieden. Hierbei sind insbesondere schwerere Bauteile der Abgasanlage, wie z.B. ein Katalysator oder ein Partikelfilter, aufgrund ihrer größeren Masse für das Schwingungsverhalten entscheidend. Des Weiteren wird die motorinduzierte Schwingungsanregung über an der Brennkraftmaschine des Fahrzeugs, z.B. am Motorgehäuse und/oder am Getriebegehäuse, fixierte Komponenten in das Schwingungssystem, also die Abgasanlage, eingetragen, so dass motornahe Bauteile der Abgasanlage einer deutlich stärkeren Schwingungsanregung ausgesetzt sind als motorfeme Bauteile. Um nun ein derartiges Bauteil an der Peripherie der Abgasanlage, also an einer peripheren Struktur des Fahrzeugs abzustützen, kann eine Haltevorrichtung der eingangs genannten Art zum Einsatz kommen. Diese kann mit Hilfe einer ersten Anschlussstelle an einem Bestandteil der Abgasanlage und mit einer zweiten Anschlussstelle an der jeweiligen Struktur des Fahrzeugs befestigt werden. Problematisch ist bei der Verwendung einer derartigen Haltevorrichtung der Umstand, dass sich der jeweilige Bestandteil der Abgasanlage gegenüber der benachbarten Struktur des Fahrzeugs bewegen können muss, um thermische Dehnungseffekte ausgleichen zu können. Wird eine Haltevorrichtung verwendet, die zum Ausgleich derartiger thermischer Wärmedehnungen eine ausreichende Elastizität besitzt, lässt sie regelmäßig auch unerwünschte Bauteilschwingungen zu.During operation of a motor vehicle, vibrations may occur in an exhaust system. Such vibrations can be excited, for example, by the internal combustion engine or by road bumps. Accordingly, so-called motor excitations and road excitations are distinguished from each other. In this case, in particular heavier components of the exhaust system, such as a catalyst or a particulate filter, crucial for the vibration behavior due to their larger mass. Furthermore, the engine-induced vibration excitation via on the internal combustion engine of the vehicle, for example on the motor housing and / or the transmission housing, fixed components in the vibration system, so the exhaust system registered, so that close-coupled components of the exhaust system are exposed to a much stronger vibration excitation than motorfeme components. In order to support such a component on the periphery of the exhaust system, ie on a peripheral structure of the vehicle, 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.
Derartige Schwingungen oder Relativbewegungen stellen eine große mechanische Belastung der betroffenen Bauteile, also insbesondere der Abgasanlage, der Fahrzeugstruktur und der Haltevorrichtung dar.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.
Aus der
Weitere Haltevorrichtungen mit hydraulisch gedämpfter Kopplungseinrichtung sind aus der
Die vorliegende Erfindung beschäftigt sich mit dem Problem, für eine Haltevorrichtung der eingangs genannten Art bzw. für eine damit ausgestattete Abgasanlage eine verbesserte Ausführungsform anzugeben, die sich insbesondere dadurch auszeichnet, dass die Gefahr einer Beschädigung des jeweiligen Bauteils oder Bestandteils bzw. der jeweiligen Struktur bzw. der Haltevorrichtung reduziert ist.The present invention is concerned with the problem of providing for a holding device of the type mentioned or for an exhaust system equipped therewith an improved embodiment, 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.
Dieses Problem wird erfindungsgemäß durch die Gegenstände der unabhängigen Ansprüche gelöst. Vorteilhafte Ausführungsformen sind Gegenstand der abhängigen Ansprüche.This problem is solved according to the invention by the subject matters of the independent claims. Advantageous embodiments are the subject of the dependent claims.
Die Erfindung beruht auf dem allgemeinen Gedanken, die Haltevorrichtung mit einer Kopplungseinrichtung auszustatten, die reversible Relativbewegungen zwischen den beiden Anschlussstellen der Haltevorrichtung zulässt, dabei jedoch eine Steifigkeit aufweist, die von der Geschwindigkeit bzw. von der Frequenz der Relativbewegungen abhängig ist. Bei langsamen oder niederfrequenten Relativbewegungen weist die Kopplungseinrichtung eine relativ kleine Steifigkeit auf. Bei schnelleren oder hochfrequenten Relativbewegungen weist die Kopplungseinrichtung dagegen eine relativ hohe Steifigkeit auf. Eine langsame Relativbewegung liegt beispielsweise vor, wenn sich das Bauteil relativ zur Struktur mit weniger als 1 cm/s bewegt. Niederfrequente Relativbewegungen sind Schwingungen mit einer Schwingungsfrequenz von weniger als 1 Hz. Diesbezüglich sind schnelle Relativbewegungen gegeben, wenn sich das Bauteil relativ zur Struktur mit mehr als 1 cm/s bewegt. Ebenso liegen diesbezüglich hochfrequente Schwingungen vor, wenn das Bauteil relativ zur Struktur mit einer Schwingungsfrequenz von mehr als 1 Hz schwingt. Die Begriffe "langsam", "schnell", "niederfrequent" und "hochfrequent" sind vorwiegend relativ zueinander zu verstehen. Außerdem können sie entsprechend den vorstehenden Zahlenangaben auch absolut verstanden werden. Des Weiteren sind die Begriffe "kleinere Steifigkeit" und "größere Steifigkeit" relativ zueinander zu verstehen. Bei einer kleineren Steifigkeit wirkt die Haltevorrichtung der Relativbewegung mit vergleichsweise kleinen Kräften entgegen. Bei einer größeren Steifigkeit wirkt die Haltevorrichtung der Relativbewegung mit vergleichsweise großen Gegenkräften entgegen.The invention is based on the general idea to provide the holding device with a coupling device that allows reversible relative movements between the two connection points of the holding device, but it has a stiffness that is dependent on the speed or the frequency of the relative movements. For slow or low-frequency relative movements, the coupling device has a relatively low rigidity. For faster or high-frequency relative movements, however, the coupling device has a relatively high rigidity. For example, 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. In this regard, rapid relative movements are given when the component moves relative to the structure with more than 1 cm / s. Likewise, in this regard, there are high-frequency vibrations when the component oscillates relative to the structure with an oscillation frequency of more than 1 Hz. The terms "slow", "fast", "low frequency" and "high frequency" are to be understood primarily relative to one another. In addition, they can be understood absolutely according to the above figures. Furthermore, the terms "lower stiffness" and "greater stiffness" are to be understood relative to one another. With a smaller rigidity, the holding device counteracts the relative movement with comparatively small forces. With a greater rigidity, the holding device counteracts the relative movement with comparatively large opposing forces.
Die hier vorgestellte Bauweise ermöglicht einerseits langsamere bzw. niederfrequente Bewegungen, wie sie beispielsweise aufgrund thermischer Dehnungseffekte auftreten. Andererseits behindert bzw. dämpft die Haltevorrichtung schnellere bzw. hochfrequente Relativbewegungen, die beispielsweise im Betrieb des Fahrzeugs durch die motorinduzierte und/oder fahrbahninduzierte Schwingungsanregung des jeweiligen Bestandteils der Abgasanlage entstehen.On the one hand, the construction presented here makes possible slower or low-frequency movements, as occur, for example, due to thermal expansion effects. On the other hand, 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.
Erfindungsgemäß weist die Kopplungseinrichtung nun zumindest zwei in Reihe wirkende Kopplungselemente auf, von denen das eine langsamere oder niederfrequente Relativbewegungen im Wesentlichen kraftfrei zulässt, während das andere schnelleren oder hochfrequenten Relativbewegungen entgegenwirkt. Die langsameren oder niederfrequenten Relativbewegungen werden durch thermische Dehnungseffekte ausgelöst und werden durch das eine Kopplungselement kraftfrei ermöglicht, so dass im Wesentlichen keine Verspannungen innerhalb der Abgasanlage entstehen. Die motorinduzierten bzw. fahrbahninduzierten Schwingungsanregungen führen im Vergleich zu thermischen Dehnungseffekten zu schnelleren bzw. hochfrequenten Relativbewegungen, denen dann das andere Kopplungselement mit entsprechenden Kräften entgegenwirkt. Das andere Kopplungselement wirkt dann beispielsweise als Dämpfer und/oder Feder. Denkbar ist auch ein aktives Kopplungselement, das den schnelleren oder hochfrequenten Relativbewegungen als Tilger entgegenwirkt, also mit Gegenschwingungen.According to the invention, the coupling device now has at least two coupling elements which act in series, of which the one permits slower or lower-frequency relative movements substantially without force, 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.
Entsprechend einer vorteilhaften Ausführungsform kann die Kopplungseinrichtung zumindest einen hydraulischen oder pneumatischen Dämpfer aufweisen oder durch einen solchen gebildet sein. Der Dämpfer enthält ein Dämpfungsfluid, das bei einer Relativbewegung zwischen den beiden Anschlussstellen von einer ersten Kammer des Dämpfers in eine zweite Kammer des Dämpfers verdrängt wird. Hierzu stehen die beiden Kammern über eine Drosselstelle miteinander in Verbindung. Der Fluidübertritt von der einen Kammer in die andere Kammer ist bei geringen Volumenströmen nahezu widerstandsfrei möglich, während bei großen Volumenströmen die Drossel ihre Wirkung entfaltet und so den Fluidstrom bremst bzw. drosselt. Dementsprechend wirkt ein derartiger gedrosselter Dämpfer für langsame Bewegungen weich, während er gegenüber schnellen Bewegungen hart ist.According to an advantageous embodiment, 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. For this purpose, the two chambers via a throttle point with each other in Connection. 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.
Bei einer alternativen Ausgestaltung kann die Kopplungseinrichtung zumindest einen Elastomerkörper aufweisen, der aus einem elektroaktiven Polymer besteht, dessen Elastizität durch Anlegen einer elektrischen Spannung veränderbar ist, und der an einen elektrischen Steuerkreis angeschlossen ist, der einen Schwingungssensor zur Erfassung von Schwingungen des Bauteils oder Bestandteils und eine Steuerung zum Verändern der Elastizität des Elastomerkörpers abhängig von der Schwingungsfrequenz aufweist. Bei dieser Ausführungsform wird somit ein Elastomerkörper verwendet, dessen Elastizität abhängig von einer daran angelegten elektrischen Spannung verändert werden kann. Hierdurch ist es beispielsweise möglich, bei Bauteilschwingungen, deren Schwingungsfrequenz unterhalb einer vorbestimmten Schaltfrequenz liegen, den Elastomerkörper unbestromt zu lassen, wodurch er eine vergleichsweise hohe Elastizität besitzt und eine weiche Dämpfungscharakteristik aufweist. Sobald jedoch die Bauteilschwingungen eine Schwingungsfrequenz oberhalb der vorgegebenen Schaltfrequenz erreichen, wird an den Elastomerkörper eine vorbestimmte elektrische Spannung angelegt, wodurch sich dessen Elastizität verändert, nämlich reduziert. In der Folge ergibt sich eine härtere Dämpfungscharakteristik.In an alternative embodiment, 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. In this embodiment, an elastomer body is thus used, the elasticity of which can be changed depending on an electrical voltage applied thereto. 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. However, as soon as the component vibrations reach an oscillation frequency above the predetermined switching frequency, 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.
Bei einer vereinfachten Ausführungsform arbeitet die Steuerung nicht mit einem Schwingungssensor zusammen, sondern mit einem Kennfeld, in dem die einzustellende Elastizität abhängig von der Drehzahl der Brennkraftmaschine abgelegt ist. Hierzu kann die Steuerung mit einem entsprechenden Motorsteuergerät der Brennkraftmaschine kommunizieren. Die Drehzahl der Brennkraftmaschine korreliert mit der motorinduzierten Schwingungsanregung, so dass die Einstellung der frequenzabhängigen Elastizität hier mit einem vereinfachten Steuerungsaufwand realisiert werden kann.In a simplified embodiment, 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. For this purpose, the controller with a corresponding engine control unit of Internal combustion engine communicate. 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.
Bei einer einfachen Ausführungsform kann die Steuerung die zwei vorbeschriebenen Zustände schalten, nämlich Ausschalten der vorgegebenen Spannung und Einschalten der vorgegebenen Spannung. Bei einer komfortableren Ausführungsform kann vorgesehen sein, die Spannung am Elastomerkörper in mehreren Stufen zu variieren, um so die Elastizität des Elastomerkörpers gestuft verändern zu können. Beispielsweise können hierzu mehrere verschiedene Schaltfrequenzen vorgegeben werden, die eine stufenweise Erhöhung der am Elastomerkörper anliegenden Spannung auslösen. Darüber hinaus ist es ebenso möglich, die Spannung am Elastomerkörper abhängig von der gemessenen Bauteilschwingungsfrequenz stufenlos zu variieren, wodurch eine proportionale Zuordnung zwischen Bauteilfrequenz und Elastizität des Elastomerkörpers und letztlich Steifigkeit der Kopplungseinrichtung realisierbar ist. Die Proportionalität kann dabei degressiv oder progressiv oder linear konzipiert werden.In a simple embodiment, the controller may switch the two above-described states, namely, turning off the predetermined voltage and turning on the predetermined voltage. In a more comfortable embodiment, 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. For example, several different switching frequencies can be predetermined for this purpose, which trigger a stepwise increase in the voltage applied to the elastomer body. In addition, it is also possible to vary the voltage on the elastomer body depending on the measured component vibration frequency continuously, whereby a proportional relationship between component frequency and elasticity of the elastomer body and ultimately rigidity of the coupling device can be realized. Proportionality can be designed degressive or progressive or linear.
Alternativ ist es ebenso möglich, die Elastizität des Elastomerkörpers mit der Schwingungsfrequenz zu variieren, so dass im Elastomerkörper Elastizitätsschwingungen entstehen. Dabei wird also nicht statisch zwischen zwei oder mehr Zuständen des Elastomerkörpers gewechselt, sondern dynamisch, eben mit der Frequenz der Bauteilschwingungen. Besonders vorteilhaft kann es dabei sein, zwischen den Betätigungsschwingungen, die im Elastomerkörper mit Hilfe der Steuerung erregt werden, eine Phasenverschiebung gegenüber den Bauteilschwingungen vorzusehen, derart, dass sich eine Reduzierung der Schwingungsamplituden am Bauteil einstellt. Hierdurch werden an der Haltevorrichtung quasi Antischwingungen generiert, die zu einer effektiven Dämpfung der Bauteilschwingungen führen.Alternatively, it is also possible to vary the elasticity of the elastomer body with the oscillation frequency, so that elastic oscillations occur in the elastomer body. It is therefore not static switched between two or more states of the elastomer body, but dynamically, just with the frequency of component vibrations. It may be particularly advantageous to provide a phase shift relative to the component vibrations between the actuation vibrations which are excited in the elastomer body by means of the control, such that a reduction of the oscillation amplitudes on the component occurs. This will be on the fixture generates quasi anti-vibrations, which lead to an effective damping of the component vibrations.
Entsprechend einer anderen vorteilhaften Ausführungsform kann die Kopplungseinrichtung ein dilatantes Material zur Bewegungsübertragung zwischen den beiden Anschlussstellen aufweisen. Ein dilatantes Material charakterisiert sich durch eine von der Geschwindigkeit der Krafteinleitung abhängige Elastizität, bei einem Festkörper, bzw. Viskosität, bei einer Flüssigkeit. Beispielsweise existiert eine knetbare dilatante Masse, die, wenn man sie auf den Boden wirft, wie ein Gummiball zurückspringt und die, wenn man mit einem Hammer daraufschlägt, wie ein Keramikkörper zerbricht. Die Anmelderin hat erkannt, dass ein derartiges dilatantes Material in hohem Maße geeignet ist, um bei einer Kupplungseinrichtung eine geschwindigkeitsabhängige bzw. frequenzabhängige Steifigkeit zu realisieren. Bei hochfrequenten Störungen reagiert das dilatante Material hart und zeigt eine hohe Steifigkeit. Bei langsamen Störungen reagiert es weich und kann verformt werden, und zwar - je nach Ausführungsform - elastisch oder plastisch, insbesondere jedoch reversibel.According to another advantageous embodiment, 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. For example, 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 slow disturbances, it reacts softly and can be deformed, depending on the embodiment - elastic or plastic, but especially reversible.
Parallel wirkend zum dilatanten Material kann zumindest ein Federelement vorgesehen sein, um im Falle einer Formänderung des dilatanten Materials eine entsprechende Rückstellkraft zu erzeugen. Bei niederfrequenten oder langsamen Verstellbewegungen wirkt diese Anordnung aus dilatantem Material und wenigstens einem Federelement wie eine Feder. Bei schnellen oder hochfrequenten Verstellbewegungen wirkt diese Anordnung aus dilatantem Material und wenigstens einem Federelement wie ein Festkörper.Parallel acting to the dilatant material, 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. For low-frequency or slow adjustment movements, this arrangement of dilatant material and at least one spring element acts as a spring. In fast or high-frequency adjustment movements, this arrangement of dilatant material and at least one spring element acts as a solid.
Beispielsweise kann die Kopplungseinrichtung ein Kolben-Zylinder-Aggregat aufweisen, dessen Zylinder fest mit der einen Anschlussstelle und dessen Kolben fest mit der anderen Anschlussstelle verbunden ist. Im Zylinder ist eine Kammer enthalten, in welcher der Kolben bewegbar ist. Diese Kammer ist mit dem dilatanten Material befüllt, wobei es sich hierbei um ein flüssiges oder pastöses oder festes dilatantes Material handeln kann. Bei langsamen Bewegungen des Kolbens im Zylinder liegt eine vergleichsweise niedrige Viskosität bzw. Steifigkeit vor, so dass sich der Kolben nahezu widerstandsfrei im Zylinder bewegen kann. Bei raschen Bewegungen erhöht sich die Viskosität bzw. Steifigkeit, wodurch der Widerstand, den das dilatante Material der Relativbewegung zwischen Zylinder und Kolben entgegensetzt, entsprechend zunimmt.For example, 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. In the cylinder is a chamber contain, 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. With slow movements of the piston in the cylinder is a comparatively low viscosity or stiffness, so that the piston can move almost without resistance in the cylinder. With rapid movements, the viscosity or rigidity increases, whereby the resistance, which opposes the dilatant material of the relative movement between the cylinder and the piston, increases accordingly.
Bei einer anderen Ausführungsform kann die Kopplungseinrichtung ein biegeelastisches Blechteil aufweisen oder durch ein solches gebildet sein. Dieses Blechteil weist zumindest einen geschlossenen Hohlraum auf, in dem ein rieselfähiges Granulat angeordnet ist. Dabei ist das vom Granulat befüllte Volumen kleiner als das Gesamtvolumen des Hohlraums. Bei dieser Ausführungsform führen Relativbewegungen zwischen den Anschlussstellen zu elastischen Verformungen des Blechteils. Bei niederfrequenten Relativbewegungen kann das Granulat den Bewegungen des Blechteils folgen. Bei hochfrequenten Relativbewegungen erfolgt auch im Granulat eine Bewegungsanregung, die Energie aus dem Schwingungssystem absorbiert, also in Wärme umwandelt und dadurch eine Dämpfung der Schwingung bewirkt.In another embodiment, 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. In this embodiment, 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. In high-frequency relative motions also in the granules, a movement excitation, which absorbs energy from the vibration system, that converts into heat and thereby causes a damping of the vibration.
Eine alternative Ausführungsform beruht auf dem allgemeinen Gedanken, die Kopplungseinrichtung mittels wenigstens eines elektrischen Aktuators zu realisieren. Ein zugehöriger elektrischer Steuerkreis umfasst den jeweiligen Aktuator, zumindest einen Schwingungssensor zur Erfassung von Schwingungen des Bauteils sowie zumindest eine Steuerung zum Betätigen des Aktuators in Abhängigkeit der Schwingungsfrequenz. Der Aktuator kann nun in Abhängigkeit seiner Betätigung einen Abstand zwischen den Anschlussstellen verändern. Mit Hilfe eines derartigen Aktuators kann die Kopplungseinrichtung Relativbewegungen zwischen Bauteil und Struktur mehr oder weniger stark entgegenwirken. Beispielsweise können niederfrequente Relativbewegungen mit wenig Widerstand realisiert werden, während hochfrequente Relativbewegungen nur gegen erhöhten Widerstand und sogar gegen entgegengesetzt gerichtete Bewegungen realisiert werden.An alternative embodiment is based on the general idea to realize 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. With the help of such an actuator, the coupling device relative movements between Counteract 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.
Entsprechend einer vorteilhaften Ausführungsform kann die Steuerung den jeweiligen Aktuator mit der Schwingungsfrequenz, mit welcher das Bauteil schwingt, zu Schwingungen anregen. Besonders zweckmäßig ist es dabei, die Aktuatorschwingungen gegenüber den Bauteilschwingungen mit einer Phasenverschiebung zu realisieren, die so gewählt ist, dass sich eine Reduzierung der Schwingungsamplituden am Bauteil einstellt. Die Kopplungseinrichtung arbeitet dabei wie ein Antischwingungserzeuger, der die Schwingungsamplituden des Bauteils effektiv reduziert. Im Idealfall kann sogar eine Schwingungsauslöschung realisiert werden. Die Kopplungseinrichtung wird hierbei analog zu einem Antischallgenerator betrieben, der in einem aktiven Schalldämpfungssystem mittels phasenverschobenem Antischall Schwindungsamplituden von zu bedämpfendem Schall auslöscht oder reduziert.According to an advantageous embodiment, 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 operated analogously to an anti-sound generator, which extinguishes or reduces Schwindungsamplituden of sound to be damped in an active silencing system by means of phase-shifted anti-sound.
Besonders vorteilhaft ist es dabei, wenn der Aktuator mit einem elektroaktiven Polymer ausgestattet ist, das durch Anlegen einer elektrischen Spannung seine Form ändert. Hierdurch lässt sich der Aktuator besonders preiswert realisieren. Insbesondere lässt sich das elektroaktive Polymer in unterschiedlichsten geometrischen Formen realisieren. Alternativ kann auch ein Piezoaktuator verwendet werden.It is particularly advantageous if the actuator is equipped with an electroactive polymer that changes its shape by applying an electrical voltage. As a result, the actuator can be realized particularly inexpensively. In particular, the electroactive polymer can be realized in a wide variety of geometric shapes. Alternatively, a piezo actuator can also be used.
Weitere wichtige Merkmale und Vorteile der Erfindung ergeben sich aus den Unteransprüchen, aus den Zeichnungen und aus der zugehörigen Figurenbeschreibung anhand der Zeichnungen.Other important features and advantages of the invention will become apparent from the dependent claims, from the drawings and from the associated figure description with reference to the drawings.
Es versteht sich, dass die vorstehend genannten und die nachstehend noch zu erläuternden Merkmale nicht nur in der jeweils angegebenen Kombination, sondern auch in anderen Kombinationen oder in Alleinstellung verwendbar sind, ohne den Rahmen der vorliegenden Erfindung zu verlassen.It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.
Bevorzugte Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden in der nachfolgenden Beschreibung näher erläutert, wobei sich gleiche Bezugszeichen auf gleiche oder ähnliche oder funktional gleiche Bauteile beziehen.Preferred embodiments of the invention are illustrated in the drawings and will be described in more detail in the following description, wherein like reference numerals refer to the same or similar or functionally identical components.
Es zeigen, jeweils schematisch
- Fig. 1
- eine stark vereinfachte, schaltplanartige Prinzipdarstellung einer Brennkraftmaschine mit Abgasanlage,
- Fig. 2
- eine stark vereinfachte, prinzipielle Darstellung einer Haltevorrichtung,
- Fig. 3
- eine Ansicht wie in
Fig. 2 , jedoch bei einer anderen Ausführungsform, - Fig. 4
- eine Ansicht wie in
Fig. 3 , jedoch einer alternativen Ausführungsform, - Fig. 5
- eine Ansicht wie in
Fig. 1 mit einer Haltevorrichtung einer weiteren Ausführungsform, - Fig. 6 und 7
- weitere Ausführungsformen von Haltevorrichtungen,
- Fig. 8 und 9
- verschiedene Ansichten einer weiteren Haltevorrichtung,
- Fig. 10
und 11 - verschiedene Ansicht einer weiteren Haltevorrichtung wie in den
Fig. 8 und 9 , jedoch bei einer anderen Bauform, - Fig. 12
- einen Querschnitt der Haltevorrichtung der
Fig. 8 im Bereich eines Hohlraums.bis 11
- Fig. 1
- a greatly simplified, schematics-like schematic representation of an internal combustion engine with exhaust system,
- Fig. 2
- a greatly simplified, schematic representation of a holding device,
- Fig. 3
- a view like in
Fig. 2 but in another embodiment, - Fig. 4
- a view like in
Fig. 3 but an alternative embodiment, - Fig. 5
- a view like in
Fig. 1 with a holding device of a further embodiment, - 6 and 7
- further embodiments of holding devices,
- 8 and 9
- different views of another holding device,
- 10 and 11
- different view of another holding device as in the
8 and 9 but in another design, - Fig. 12
- a cross section of the holding device of
8 to 11 in the area of a cavity.
Entsprechend
Die Abgasanlage 2 ist mit Hilfe einer Haltevorrichtung 6 an ihrer Peripherie festgehalten bzw. positioniert oder abgestützt. Beispielsweise wirkt die Haltevorrichtung 6 hierzu mit einer peripheren Struktur 7 eines Fahrzeugs zusammen, in dem die Brennkraftmaschine 1 angeordnet ist. Bei der peripheren Struktur 7 handelt es sich im Beispiel der
Entsprechend den
Gemäß
Gemäß einer ersten erfindungsgemäßen Lösung kann die Kopplungseinrichtung 13 so ausgestaltet sein, dass sie zumindest in ihrer Wirkrichtung 14 eine geschwindigkeitsabhängige und/oder frequenzabhängige Steifigkeit aufweist. Dies hat zur Folge, dass die Steifigkeit der Kopplungseinrichtung 13 bei langsamen Relativbewegungen zwischen den Anschlussstellen 11,12 bzw. bei niederfrequenten Relativbewegungen zwischen den Anschlussstellen 11,12 eine vergleichsweise kleine Steifigkeit aufweist, während sie bei schnelleren oder hochfrequenten Relativbewegungen zwischen den Anschlussstellen 11,12 eine relativ große Steifigkeit aufweist. Die langsamen bzw. niederfrequenten Relativbewegungen sind in der Regel die durch die thermische Wärmedehnung 16 ausgelösten Relativbewegungen. Im Unterschied dazu sind die schnelleren oder hochfrequenten Relativbewegungen Schwingungen 15 der Abgasanlage 2, die im Betrieb der Brennkraftmaschine 1 im Bereich des jeweiligen Bestandteils 10 der Abgasanlage 2 auftreten.According to a first inventive solution, the
Die Steifigkeit wird im vorliegenden Zusammenhang reziprok zur Elastizität verstanden, so dass eine hohe Steifigkeit mit einer kleinen Elastizität einhergeht, während eine große Elastizität zu einer niedrigen Steifigkeit führt.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.
Eine derartige Kopplungseinrichtung 13 mit geschwindigkeitsabhängiger und/oder frequenzabhängiger Steifigkeit kann auf unterschiedliche Weise realisiert werden. Beispielsweise zeigt
Innerhalb des Kolben-Zylinder-Aggregats 18 können Zylinder 19 und Kolben 20 sowie die Kammern 22 und 23 grundsätzlich beliebige Querschnitte aufweisen. Beispielsweise kommen runde Querschnitte, wie z.B. kreisförmige, eliptische oder ovale Querschnitte, ebenso in Betracht wie eckige Querschnitte, wie z.B. dreieckige, viereckige, sechseckige und achteckige Querschnitte. Bevorzugt sind jedoch kreisförmige Querschnitte.Within the piston-cylinder unit 18
Die Steuerung 27 kann nun die Elastizität des Elastomerkörper 25 abhängig von der erfassten Schwingungsfrequenz verändern. Die Veränderung der Elastizität des Elastomerkörpers 25 kann beispielsweise in wenigstens zwei Stufen variiert werden. Ebenso ist eine stufenlose Adaption der Elastizität an die Schwingungsfrequenz realisierbar. Des Weiteren kann die Steuerung 27 so ausgestaltet bzw. programmiert sein, dass sie die Elastizität des Elastomerkörpers 25 mit der erfassten Schwingungsfrequenz variiert. Insbesondere ist es dabei möglich, die Elastizitätsschwingungen gegenüber den Bauteilschwingungen hinsichtlich ihrer Phase zu verschieben, und zwar insbesondere derart, dass sich dadurch eine Reduzierung der Schwingungsamplituden am jeweiligen Bauteil 10 einstellt. Beim jeweiligen Bauteil 10 handelt es sich um den Bestandteil 10, der mit Hilfe der Haltevorrichtung 6 abgestützt ist. Im Beispiel der
Die Steuerung 27 arbeitet mit einem Tiefpassfilter, so dass die langsamen, niederfrequenten Wärmedehnungen keine Reaktion durch die Steuerung 27, nämlich ein Ansteuern des Elastomerkörpers 25 auslösen. Optional kann außerdem vorgesehen sein, dass die Steuerung 27 thermisch bedingte Dehnungseffekte, die ebenfalls zu Relativbewegungen führen, mittels einer speziellen Kennlinie berücksichtigt, in welcher die thermisch bedingten Relativbewegungen abhängig von der aktuellen Bauteiltemperatur aufgetragen sind. Hierzu kann die Steuerung 27 mit einem entsprechenden Temperatursensor zusammenwirken. Auf diese Weise können die langsamen Relativbewegungen den schnellen Relativbewegungen überlagert werden. Erfindungsgemäß ist es notwendig, dass zur getrennten Berücksichtigung der thermisch bedingten Relativbewegungen einerseits und der durch die Bauteilschwingungen erzeugten Relativbewegungen andererseits innerhalb der Kopplungseinrichtung 13 zumindest zwei separate Kopplungselemente vorgesehen sind, die in Reihe wirken. Beispielsweise sind dann zwei Elastomerkörper 25 vorgesehen, deren Elastizitäten unabhängig voneinander mit Hilfe der Steuerung 27 verändert werden können. Somit kann dann insbesondere über eine entsprechende Ansteuerung des einen Elastomerkörpers 25 die thermisch bedingte Dehnung nahezu kraftfrei zugelassen werden, während mit Hilfe des zweiten Elastomerkörpers 25 der Schwingungsanregung mit entsprechenden Gegenkräften frequenzabhängig entgegengewirkt werden kann.The
Bei einer zweiten erfindungsgemäßen Lösung, die in
Die Steuerung 37 kann vorzugsweise so ausgestaltet bzw. programmiert sein, dass sie den Aktuator 33 mit einer Frequenz zu Schwingungen anregt, welche der mit Hilfe des Schwingungssensors 35 ermittelten Frequenz entspricht. Besonders vorteilhaft ist es nun, die Aktuatorschwingungen hinsichtlich ihrer Schwingungsamplituden gegenüber den ermittelten Bauteilschwingungen in ihrer Phase zu verschieben. Diese Phasenverschiebung wird gezielt so durchgeführt, dass sich am jeweiligen Bauteil eine Reduzierung der Schwingungsamplituden einstellt. Der Aktuator 33 wird in diesem Fall wie ein aktiver Schalldämpfer für Körperschall betrieben. Er arbeitet quasi mit Antischwingungen oder Gegenschwingungen, welche die zu bedämpfenden Schwingungen des Bauteils 10 zumindest teilweise auslöschen.The controller 37 may preferably be configured or programmed such that it excites the
Die Steuerung 37 arbeitet mit einem Tiefpassfilter, so dass die langsamen, niederfrequenten Wärmedehnungen keine Reaktion der Steuerung 37, nämlich eine Ansteuerung des Aktuators 33 auslösen. Optional kann außerdem vorgesehen sein, dass die Steuerung 37 thermisch bedingte Dehnungseffekte, die ebenfalls zu Relativbewegungen führen, mittels einer speziellen Kennlinie berücksichtigt, in welcher die thermisch bedingten Relativbewegungen abhängig von der aktuellen Bauteiltemperatur aufgetragen sind. Hierzu kann die Steuerung 37 mit einem entsprechenden Temperatursensor gekoppelt sein. Auf diese Weise können die langsamen Relativbewegungen den schnellen Relativbewegungen überlagert werden. Erfindungsgemäß ist es notwendig, dass zur getrennten Berücksichtigung der thermisch bedingten Relativbewegungen einerseits und der durch die Bauteilschwingungen erzeugten Relativbewegungen andererseits innerhalb der Kopplungseinrichtung 13 zumindest zwei separate Kopplungselement vorgesehen sind, die in Reihe wirken. Beispielsweise sind dann zwei Aktuatoren 33 vorgesehen, deren Stellbewegungen unabhängig voneinander mit Hilfe der Steuerung 37 verändert werden können. Somit kann dann insbesondere über eine entsprechende Ansteuerung des einen Aktuators 33 die thermisch bedingte Dehnung nahezu kraftfrei zugelassen werden, während mit Hilfe des zweiten Aktuator 33der Schwingungsanregung mit entsprechenden Gegenkräften frequenzabhängig entgegengewirkt werden kann.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
Gemäß
Das dilatante Material 39 ist dabei innerhalb der Kopplungseinrichtung 13 so angeordnet, dass es zur Bewegungsübertragung zwischen den beiden Anschlussstellen 11,12 dient. Mit anderen Worten, eine Relativbewegung zwischen den beiden Anschlussstellen 11, 12 ist nur dann möglich, wenn innerhalb der Kopplungseinrichtung 13 das dilatante Material 39 deformiert oder verdrängt wird.The
Im Beispiel der
Bei einer anderen Ausführungsform kann das dilatante Material 39 auch zu einem Elastomerkörper geformt sein. Dann ist grundsätzlich ein Aufbau wie in
Mit Bezug auf die
Entsprechend den
Die Hohlkammern 49 können im Blechteil 48 beispielsweise dadurch realisiert werden, dass das jeweilige Blechteil 48 zumindest im Bereich des jeweiligen Hohlraums 49 als Doppelblechstruktur 52 ausgebildet ist, was wieder in
Claims (14)
- Holding device for holding a component (10) of an exhaust system (2) on a peripheral structure (7) belonging particularly to a vehicle equipped with the exhaust system (2), comprising:- a first connecting point (11) for attaching the holding device (6) to the component (10) of the exhaust system (2);- a second connecting point (12) for attaching the holding device (6) to the structure (7);- a coupling device (13) arranged between the connecting points (11, 12), which enables reversible relative movements to take place between the connecting points (11, 12),- the coupling device (13) being configured so that it has a speed-dependent and/or frequency-dependent stiffness in at least one direction of action (14) such that the coupling device (13) has less stiffness with slower or low-frequency relative movements than with faster or high-frequency relative movements,characterised in that
the coupling device (13) comprises at least two coupling elements acting in series, one of which permits slower or low-frequency relative movements substantially free from force, while the other counteracts faster or high-frequency relative movements. - Holding device according to claim 1,
characterised in that the coupling device (13) comprises, or is formed by, at least one hydraulic or pneumatic damper (17). - Holding device according to claim 1,
characterised in that
the coupling device (13) comprises at least one elastomer body (25) consisting of an electroactive polymer, the elasticity of which can be varied by the application of an electric voltage and which is connected to an electric control circuit (26) comprising a controller (27) for varying the elasticity of the elastomer body (25) as a function of the vibration frequency, while the controller (27) may be configured and/or programmed so as to vary the elasticity of the elastomer body (25) in at least two steps or to allow smooth adaptation of the elasticity to the vibration frequency. - Holding device according to claim 3,
characterised in that
the controller (27) is configured and/or programmed so as to vary the elasticity of the elastomer body (25) with the vibration frequency, while the controller (27) may, in particular, be configured and/or programmed so that the elasticity vibrations are phaseshifted relative to the component vibrations such that there is a reduction in the amplitudes of the vibrations on the component (10). - Holding device according to claim 1,
characterised in that
the coupling device (13) comprises at least one dilatant material (39) for transmitting movement between the connecting points (11). - Holding device according to claim 5,
characterised in that
the coupling device (13) comprises a piston-cylinder unit (40), the cylinder (41) of which is fixedly connected to one connecting point (11) and the piston (42) of which is fixedly connected to the other connecting point (12), the dilatant material (39) being arranged in a working chamber (44) of the cylinder (41) within which the piston (42) is movable. - Holding device according to claim 5 or 6,
characterised in that
the dilatant material (39) is formed into an elastomer body, while, in particular, at least one spring element acting in parallel to the dilatant material (39) may be arranged particularly in the elastomer body. - Holding device according to claim 1,
characterised in that
the coupling device (13) comprises, or is formed by, at least one flexurally elastic sheet metal part (48), the sheet metal part (48) comprising at least one closed cavity (49) in which a free-flowing granulate (50) is arranged, the volume filled by the granulate being smaller than the total volume of the cavity (49). - Holding device according to claim 8,
characterised in that
the sheet metal part (48) is configured as a double sheet metal structure (52) at least in the region of the respective cavity (49), each individual sheet (53, 54) of the double sheet metal structure (52) having a depression (55, 56), these depressions (55, 56) complementing one another mirror-symmetrically to form the respective cavity (49). - Holding device according to one of claims 1 to 9,
characterised in that
the coupling device (13) comprises, or is formed by, at least one electric actuator (33), while an electric control circuit (34) is provided to which the electrical actuator (33) is connected, which comprises a vibration sensor (35) for detecting vibrations of the component (10), and a controller (37) for operating the actuator (33) as a function of the vibration frequency, the operation of the actuator (33) causing it to vary a distance between the connecting points (11, 12). - Holding device according to claim 10,
characterised in that
the controller (37) is configured and/or programmed so as to excite the actuator (33) with the vibration frequency to vibrate, the actuator vibrations being phase-shifted, particularly relative to the component vibrations, such that there is a reduction in the amplitude of the vibrations on the component (10). - Holding device according to claim 10 or 11,
characterised in that
the actuator (33) is provided with an electroactive polymer which changes its shape as a result of the application of an electric voltage. - Holding device according to one of claims 1 to 12,
characterised in that
the direction of action (14) of the coupling device (13) is oriented parallel to a direction (16) of thermal expansion in which the respective component (10) moves relative to the structure (7) as a result of thermal expansion. - Exhaust system for an internal combustion engine (1), wherein a component (10) of the exhaust system (2) is held on a peripheral structure (7) of the exhaust system (2) by at least one holding device (6) according to one of claims 1 to 13.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP15166890.2A EP2949899B1 (en) | 2010-03-24 | 2011-02-14 | Holding device |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102010012663 | 2010-03-24 | ||
DE102010034313A DE102010034313A1 (en) | 2010-03-24 | 2010-08-13 | holder |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15166890.2A Division EP2949899B1 (en) | 2010-03-24 | 2011-02-14 | Holding device |
EP15166890.2A Division-Into EP2949899B1 (en) | 2010-03-24 | 2011-02-14 | Holding device |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2369152A1 EP2369152A1 (en) | 2011-09-28 |
EP2369152B1 true EP2369152B1 (en) | 2015-07-15 |
Family
ID=44170196
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15166890.2A Active EP2949899B1 (en) | 2010-03-24 | 2011-02-14 | Holding device |
EP11154285.8A Active EP2369152B1 (en) | 2010-03-24 | 2011-02-14 | Clamping device |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15166890.2A Active EP2949899B1 (en) | 2010-03-24 | 2011-02-14 | Holding device |
Country Status (5)
Country | Link |
---|---|
US (1) | US8485302B2 (en) |
EP (2) | EP2949899B1 (en) |
JP (1) | JP5725920B2 (en) |
CN (1) | CN102200045B (en) |
DE (1) | DE102010034313A1 (en) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009015420A1 (en) * | 2009-03-27 | 2010-09-30 | Emitec Gesellschaft Für Emissionstechnologie Mbh | Honeycomb body for an exhaust gas purification system |
DE102010020032A1 (en) * | 2010-05-11 | 2011-11-17 | J. Eberspächer GmbH & Co. KG | vibration absorber |
DE102012219373A1 (en) * | 2011-10-27 | 2013-05-02 | Schaeffler Technologies AG & Co. KG | Disengaging system for operating friction clutch of vehicle, has friction unit in region facing toward another friction unit provided with electro-active polymers |
CN103217331A (en) * | 2013-04-27 | 2013-07-24 | 江苏大学 | Method for embedding thin plate samples by adopting metallographic embedding machine and piece clamping auxiliary device |
CN109112503B (en) * | 2017-06-23 | 2021-01-08 | 北京北方华创微电子装备有限公司 | Exhaust device of reaction chamber and reaction chamber |
US11242934B2 (en) | 2018-03-09 | 2022-02-08 | Fujikin Incorporated | Valve device |
JP7352971B2 (en) * | 2019-01-31 | 2023-09-29 | 株式会社フジキン | Valve devices, flow rate control methods, fluid control devices, semiconductor manufacturing methods, and semiconductor manufacturing equipment |
KR102605036B1 (en) * | 2019-09-04 | 2023-11-22 | 삼성중공업 주식회사 | Scrubber |
CN113685473B (en) * | 2021-08-19 | 2022-09-16 | 奇瑞汽车股份有限公司 | Vibration damping structure |
Family Cites Families (23)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5643028A (en) | 1979-09-18 | 1981-04-21 | Nissan Motor Co Ltd | Low noise vehicle |
JPS5820U (en) * | 1981-06-25 | 1983-01-05 | カヤバ工業株式会社 | Suspension devices for automobile mufflers, etc. |
US4746104A (en) | 1986-12-08 | 1988-05-24 | General Motors Corporation | Hydraulic exhaust pipe hanger mount |
JPH0183944U (en) * | 1987-11-25 | 1989-06-05 | ||
JPH02179738A (en) * | 1988-12-30 | 1990-07-12 | Aichi Steel Works Ltd | Vibration damping composite metal sheet |
DE4116270C2 (en) | 1990-05-18 | 2002-01-17 | Toyo Tire & Rubber Co | attenuator |
FR2674800B1 (en) | 1991-04-08 | 1993-07-30 | Hutchinson | EXHAUST TUBING SUSPENSION DEVICE FOR VEHICLE. |
JPH05820U (en) * | 1991-06-20 | 1993-01-08 | ミサワホーム株式会社 | Makeup purlin with attic ventilation |
FR2678221A1 (en) | 1991-06-27 | 1992-12-31 | Hutchinson | Device for suspension of an exhaust pipe from the body of a vehicle |
JPH06109068A (en) * | 1992-09-28 | 1994-04-19 | Mazda Motor Corp | Vibration reducing device for vehicle |
JPH06129462A (en) * | 1992-10-13 | 1994-05-10 | Bridgestone Corp | Vibration isolator |
DE4340034C1 (en) * | 1993-11-24 | 1995-02-02 | Freudenberg Carl Fa | Mounting arrangement |
DE19621271A1 (en) | 1995-06-21 | 1997-01-09 | Witzenmann Metallschlauchfab | Device to form flexible vibration=damping connection on exhaust pipes - comprises at least partly flexible pipe section to guide exhaust gases, and has supporting element with longitudinal and transverse springing |
US6882086B2 (en) * | 2001-05-22 | 2005-04-19 | Sri International | Variable stiffness electroactive polymer systems |
DE19734499C2 (en) * | 1997-08-08 | 2002-02-14 | Daimler Chrysler Ag | Elastic suspension device for an exhaust system |
DE19812699A1 (en) | 1998-03-23 | 1999-09-30 | Volkswagen Ag | Exhaust system for a motor vehicle |
ATE381116T1 (en) | 1999-07-20 | 2007-12-15 | Stanford Res Inst Int | ELECTROACTIVE POLYMER GENERATORS |
JP2001187534A (en) | 1999-12-28 | 2001-07-10 | Isuzu Motors Ltd | Active mount device for engine |
DE10026527B4 (en) * | 2000-05-27 | 2008-08-28 | Eras Entwicklung Und Realisation Adaptiver Systeme Gmbh | Use of an elastic bearing for a vibration-insulated mounting of an exhaust system on a vehicle floor |
US6439556B1 (en) * | 2001-02-15 | 2002-08-27 | Delphi Technologies, Inc. | Active decoupler hydraulic mount |
DE102004001060A1 (en) | 2004-01-02 | 2005-08-04 | Wilhelm Karmann Gmbh | motor vehicle |
DE102005029234B4 (en) | 2005-06-23 | 2012-09-20 | Anvis Deutschland Gmbh | System for damping and / or compensating bearing of an assembly and method for damping and / or compensating bearings |
DE102006021641B4 (en) | 2006-05-08 | 2013-05-16 | J. Eberspächer GmbH & Co. KG | fastening device |
-
2010
- 2010-08-13 DE DE102010034313A patent/DE102010034313A1/en not_active Withdrawn
-
2011
- 2011-02-14 EP EP15166890.2A patent/EP2949899B1/en active Active
- 2011-02-14 EP EP11154285.8A patent/EP2369152B1/en active Active
- 2011-03-22 US US13/053,852 patent/US8485302B2/en active Active
- 2011-03-24 CN CN201110071618.3A patent/CN102200045B/en active Active
- 2011-03-24 JP JP2011065971A patent/JP5725920B2/en active Active
Also Published As
Publication number | Publication date |
---|---|
CN102200045A (en) | 2011-09-28 |
EP2949899A1 (en) | 2015-12-02 |
US20110232986A1 (en) | 2011-09-29 |
US8485302B2 (en) | 2013-07-16 |
CN102200045B (en) | 2014-12-10 |
JP2011201531A (en) | 2011-10-13 |
JP5725920B2 (en) | 2015-05-27 |
EP2949899B1 (en) | 2016-11-02 |
EP2369152A1 (en) | 2011-09-28 |
DE102010034313A1 (en) | 2011-09-29 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2369152B1 (en) | Clamping device | |
EP1975455B1 (en) | Device for vibration damping | |
DE3034246C2 (en) | Vibration damper for a vehicle internal combustion engine | |
DE102011000656B4 (en) | Vibration-free mounting of an object on a vibrating structure | |
DE19642827B4 (en) | Actuator for vibration damping | |
DE102015211891B4 (en) | Frequency-dependent damping valve arrangement | |
WO2005100816A1 (en) | Pushing force deviating interface for damping mechanical vibrations | |
DE102008045492A1 (en) | Vehicle oscillation damping system for two vehicle units, has two throttle controls connected with gas line, where gas line has adjustable passage valve | |
DE102009021994B4 (en) | hydromount | |
EP1160483A2 (en) | Hydraulic support | |
EP2615325A1 (en) | Active bearing | |
DE4209610C1 (en) | ||
EP1528281B1 (en) | Adaptive vibration damper | |
DE102011120095A1 (en) | Shaft arrangement and method for forwarding acting around a rotational axis torques | |
DE102011112405B4 (en) | Damper bearing for supporting a chassis component on a motor vehicle body | |
DE102004001098A1 (en) | Piezoelectric material for dampening vibrations of a dashboard and / or a steering column | |
DE102005033528B3 (en) | Switchable shock absorber to absorb vibrations has shock absorbing devices which can be used together or separately | |
DE202006008811U1 (en) | Vibration damper for motor vehicle exhaust unit, has frame supported by springy wire-element against exhaust component being damped | |
EP2153079B1 (en) | Elastic shaft coupling with adaptive characteristics | |
DE102008052424B4 (en) | Vibrationstilgersystem | |
DE10330877A1 (en) | chassis mounts | |
DE102008050192A1 (en) | Vehicle vibration damping system for tractor, has inertia element whose inertia force works during arising of vibratory movements from upper part on actuators for readjusting of parameter of suspension element to change transfer function | |
DE4230799C1 (en) | Active vibration absorber | |
EP0462510B1 (en) | Damping unit, for wheel suspension systems in motor cars | |
DE102018205737B4 (en) | Unit mounting for a drive unit of a vehicle |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
17P | Request for examination filed |
Effective date: 20120328 |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: EBERSPAECHER EXHAUST TECHNOLOGY GMBH & CO. KG |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20150313 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 736931 Country of ref document: AT Kind code of ref document: T Effective date: 20150815 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502011007320 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: SE Ref legal event code: TRGR |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20150715 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151016 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151015 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 6 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151116 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502011007320 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160229 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 |
|
26N | No opposition filed |
Effective date: 20160418 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160214 Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160229 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160229 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160214 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 7 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 736931 Country of ref document: AT Kind code of ref document: T Effective date: 20160214 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160214 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 8 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20110214 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20180221 Year of fee payment: 8 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150715 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190214 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R081 Ref document number: 502011007320 Country of ref document: DE Owner name: PUREM GMBH, DE Free format text: FORMER OWNER: EBERSPAECHER EXHAUST TECHNOLOGY GMBH & CO. KG, 66539 NEUNKIRCHEN, DE |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: SE Payment date: 20220221 Year of fee payment: 12 |
|
REG | Reference to a national code |
Ref country code: SE Ref legal event code: EUG |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230215 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20240216 Year of fee payment: 14 Ref country code: GB Payment date: 20240222 Year of fee payment: 14 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20240221 Year of fee payment: 14 |