WO2012069142A2 - Dispositif de stockage pour système d'échappement - Google Patents

Dispositif de stockage pour système d'échappement Download PDF

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Publication number
WO2012069142A2
WO2012069142A2 PCT/EP2011/005658 EP2011005658W WO2012069142A2 WO 2012069142 A2 WO2012069142 A2 WO 2012069142A2 EP 2011005658 W EP2011005658 W EP 2011005658W WO 2012069142 A2 WO2012069142 A2 WO 2012069142A2
Authority
WO
WIPO (PCT)
Prior art keywords
damping
bearing device
arms
abutment
counter
Prior art date
Application number
PCT/EP2011/005658
Other languages
German (de)
English (en)
Other versions
WO2012069142A3 (fr
Inventor
Klaus Steinmaier
Thomas Burkhard
Original Assignee
Sgf Sueddeutsche Gelenkscheibenfabrik Gmbh & Co. Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sgf Sueddeutsche Gelenkscheibenfabrik Gmbh & Co. Kg filed Critical Sgf Sueddeutsche Gelenkscheibenfabrik Gmbh & Co. Kg
Publication of WO2012069142A2 publication Critical patent/WO2012069142A2/fr
Publication of WO2012069142A3 publication Critical patent/WO2012069142A3/fr

Links

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
    • F01N13/16—Selection of particular materials
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K13/00—Arrangement in connection with combustion air intake or gas exhaust of propulsion units
    • B60K13/04—Arrangement in connection with combustion air intake or gas exhaust of propulsion units concerning exhaust
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/373—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by having a particular shape
    • F16F1/377—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by having a particular shape having holes or openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/38—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type
    • F16F1/3842—Method of assembly, production or treatment; Mounting thereof
    • F16F1/3849—Mounting brackets therefor, e.g. stamped steel brackets; Restraining links
    • 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
    • F01N2530/00—Selection of materials for tubes, chambers or housings
    • F01N2530/22—Flexible elastomeric material

Definitions

  • the present invention relates to a bearing device for an exhaust system with at least one fastening device for vehicle-mounted mounting of the bearing device and at least one fastening device for abgasanlagensei- term attachment of the bearing device and at least one extending between the fastening devices damping body.
  • the document DE 100 23 781 AI discloses a fastening device for a vibratory component, which has a holder and a damping element arranged thereon.
  • the bracket has holes to accommodate screws can, with which the bracket is screwed to a vehicle floor.
  • the damping element is cone-shaped. In the damping element, a bore for receiving a retaining clip for attachment to the exhaust system is arranged centrally.
  • suspension devices for exhaust systems are known from the prior art.
  • Such a suspension device is described, for example, in the document EP 0 839 680 B1.
  • the suspension device comprises an outer ring and an inner ring, wherein the outer ring crosses the inner ring at 90 °.
  • the inner ring and the outer ring are connected to bent end portions, each having a screw. By means of these screws, the suspension device can be attached to the vehicle body and the exhaust system.
  • ge device meets, and in particular in the case of load has increased rigidity.
  • the damping body has at least one damping arm which extends between the fastening devices in such a way that it has a predetermined distance to a counterpart bearing section of at least one opposing bearing body with an abutment section in the unloaded state of the damping body, wherein the at least one damping arm buckles to reach a progressive damping characteristic as a result of a compressive load and under
  • the bearing device has a relatively low rigidity in the static load case.
  • a low stiffness in the static load case is necessary in order to meet today's very high demands on the vehicle acoustics.
  • the at least one damping arm engages the counter abutment portion of a counter abutment body, whereby the rigidity of the bearing device relative greatly increased and progressively increases. With such a progressively stiffened bearing device, movements or vibrations of the exhaust system relative to the vehicle can be effectively limited.
  • the damping arm already in its basic form or even under pressure to the at least one counter-investment body bulges out and extends between the fasteners such that it with a vertex of the curvature comprehensive investment section in the unloaded state the damping body has a predetermined distance to a counter-bearing portion of the counter-abutment body.
  • the at least one damping arm initially deforms freely to achieve a progressive damping characteristic as a result of a compressive load, increasing the curvature, and then abuts with the abutment portion against the countersection section.
  • the damping arm in this embodiment of the invention even in the unloaded state, a curvature which increases in the loaded state with pressure and comes into abutment with a mating abutment portion of the opposing abutment body.
  • the damping body of the bearing device has at least two, preferably curved, damping arms.
  • the at least two damping arms face each other and are preferably curved in the direction of the respective other damping arm.
  • one of the two mutually opposite damping arms forms the counter-body, which is arched to the respective other damping body and has a vertex of the buckling comprehensive Gegenstromabites.
  • a predetermined distance between the abutment portion and the mating abutment portion is given.
  • the damping arms deform to achieve a progressive damping characteristic such that the curvature of the two damping body in the direction of the respective other damping body increases and the abutment portion and the mating abutment abut each other.
  • the rigidity of the bearing device increases in the direction of the vehicle vertical axis, as soon as the two damping arms overcome the predetermined distance between them and the abutment portion of the one damping arm with the mating abutment portion of the respective other damping arm comes into abutment.
  • the bearing device is designed such that the at least one attachment means for vehicle-mounted mounting of the bearing device and the at least one attachment means for Abgasanlagen disorderen attachment of the bearing device are provided at opposite end portions of the at least one damping arm.
  • the fastening devices can be formed in the form of openings, locking devices or provided with screws surfaces.
  • the bearing device is further stiffened transversely to the vehicle longitudinal axis and can contribute to the rigidity of the bearing device even in the case of tensile stresses occurring in the direction of the vehicle vertical axis.
  • the rigidity also increases in the case of tensile loads, since the textile insert has a very high rigidity when stretched.
  • the two damping bodies are curved in opposite directions.
  • the damping bodies are each curved in the direction of a counter bearing body.
  • the bearing device according to the invention can also be designed such that the two curved damping arms do not move toward each other under a compressive load under an increase in the curvature, but increase the curvature in opposite directions.
  • the damping arms approach under pressure load with their curvature to a counter-investment body until they rest against a mating abutment portion of the opposing investment body. If the damping arms with their curvature on the counter-investment body, the rigidity of the bearing device increases progressively.
  • the counter-abutment body may also be arranged between the at least two opposing damping arms, wherein the two opposing damping arms are arched towards the counter-abutment body according to a further preferred embodiment of the present invention.
  • the damping body has, according to a preferred embodiment of the invention, at least four damping arms, two of which are opposed in pairs. Overall, results in this embodiment in plan view, a cross-like arrangement.
  • the four damping arms preferably each have a predetermined distance from the at least one mating abutment section.
  • the at least four damping arms initially deform freely and attach themselves to the opposing abutment section of the at least one opposing abutment body, increasing their respective curvature.
  • the bearing device is configured such that the vehicle-side fastening device has at least one receiving opening, which holds the damping body and the exhaust-gas-side fastening devices. takes up.
  • the exhaust gas-side fastening device is preferably formed bolt-shaped.
  • a plate-shaped element can be provided, which is in communication with the damping body and can transmit a force in the direction of the vehicle longitudinal axis to the bearing device.
  • the at least one counter-abutment body is provided on the at least one receiving opening.
  • the opposing abutment body arranged between the at least two damping arms is the exhaust-gas-side fastening device.
  • the fastening device preferably has a counter abutment section against which the abutment section of the damping arms can rest as a result of a pressure load.
  • the present invention relates to a vehicle exhaust system with a Lagerervor ⁇ direction of the type described above.
  • Figure 1 is a perspective view of the bearing device according to a first
  • Figure 2 is a sectional view of the bearing device according to the first embodiment of the invention.
  • FIG. 3 shows a perspective view of a bearing apparatus according to a two ⁇ th embodiment of the invention
  • Figure 4 is a sectional view of the bearing device according to the second embodiment of the invention.
  • Figure 5 is a perspective view of a bearing device according to a third
  • Figure 6 is a sectional view of the bearing device according to the third embodiment of the invention.
  • Figs. 7 and 8 are a perspective view and a sectional view of the damper arms according to a fourth embodiment of the invention.
  • Figure 9 is a perspective view of a bearing device according to a fifth embodiment of the invention.
  • Figure 10 is a sectional view of the bearing device according to the fifth embodiment of the invention.
  • Figure 11 is a perspective view of a bearing device according to a sixth embodiment of the invention.
  • Figure 12 is a sectional view of the bearing device according to the sixth embodiment of the invention.
  • Figure 13 is a perspective view of a bearing device according to a seventh embodiment of the invention.
  • Figures 14a-14c are partial views of the bearing device according to the seventh embodiment of the invention.
  • FIG. 15 is a perspective view of a bearing device according to an eighth embodiment
  • Figures 16a-6c are partial views of the bearing device according to the eighth embodiment of the invention.
  • FIG. 17 is a perspective view of a bearing device according to a ninth embodiment.
  • Figures 18a-18c are the partial views of the storage devices according to the ninth
  • FIG. 19 is a perspective view of a bearing device according to a tenth embodiment
  • Figures 20a-20c are the partial views of the storage devices according to the tenth
  • Figure 21 is a perspective view of a bearing device according to an eleventh
  • Figures 22a-22c are partial views of a bearing device according to the eleventh embodiment of the invention.
  • Figure 1 shows a perspective view of the bearing device according to the first embodiment, which is generally designated 10.
  • the bearing device 10 has fastening devices 12 and 14, between which a damping body 16 extends.
  • the fastening devices 12 and 14 are formed according to this embodiment of openings 12a, 12b and 14a and 14b, in the fastening bolts can be inserted.
  • the fastening devices 12, 14 are not limited to a design with two openings, for example, can also have an opening in the form of a slot.
  • the damping body 16 comprises two arched damping arms 18 and 20, wherein the damping arm 18 is curved in the direction of the damping arm 20 and the damping arm 20 is correspondingly curved in the direction of the damping arm 18.
  • the damping arm 18 has an abutment portion 18b comprising the apex of the arch 18a.
  • the damping arm 20 acts according to this embodiment as a counter-abutment body and forms at its curvature 20a a vertex of the vault comprehensive Schmidtabites 20b ( Figure 2).
  • Z denotes the direction of the vehicle vertical axis
  • X the traveling direction of the vehicle
  • Y the transverse direction of the vehicle when the bearing device is installed in the vehicle.
  • the damping arms 18 and 20 of the bearing device 10 have a predetermined distance d from each other.
  • a pressure load ie the fastening devices 12 and 14 approach each other due to this pressure load, the damping arms 18 and 20 and their bulges 18a and 20a move toward each other until they mitei- get in contact with each other.
  • the rigidity of the bearing device 10 increases abruptly, ie progressively, further.
  • the damping arms 18 and 20 deform as a result of a compressive load such that their bulges 18a and 20a initially increase in size until the abutment portion 18b and the abutment portion 20b abut each other. A further deformation is opposed as a result of the plant greater resistance.
  • the bearing device 10 has a reinforcing insert 22 in the form of a textile insert.
  • the textile insert 22 extends along the bulges 18a and 20a and around the circumference of the openings 12a, 12b and 14a, 14b of the fastening devices 12 and 14, respectively.
  • the textile insert 22 serves to further stiffen the bearing device 10, in particular transversely to the vehicle longitudinal axis (not shown). In the operation of the vehicle also tensile loads in the direction of the vehicle vertical axis on the
  • the reinforcing insert 22 further increases the rigidity, since the reinforcing insert 22 has a very high rigidity when stretched.
  • Figures 3 and 4 show a perspective view and a sectional view of the second embodiment.
  • the bearing device 110 includes the fastener 112 having the openings 112a and 112b. Between the openings 112a and 112b, according to this embodiment, a relatively thin web 112c extends. Starting from the fastening device 112, the damping arms 118 and 120 extend in the direction of the second fastening device 114, which are formed here in the form of latching devices 114a and 114b.
  • the reinforcing insert 122 completely extends around the space between the damper arms 118 and 120 from the detents 114a and 114b.
  • the reinforcing insert 122 extends from the locking device 114a in the direction of the bulge 118a of the damping arm 118 and then along the curvature 118a, of the web 112c of the fastening device 112 and along the curvature 120a until it runs out into the locking device 114b.
  • the locking devices 114a and 114b can each be designed with two individual locking elements 115 made of plastic, between which the reinforcing insert 122 expires.
  • the bearing device 110 can be attached to a vehicle floor (not shown) via the latching devices 114a and 114b, whereas the openings 112a, 112b of the fastening device 112 serve for fastening the bearing device to an exhaust system (not shown).
  • Figure 5 shows a perspective view and Figure 6 is a sectional view of the bearing device 210 according to a third embodiment.
  • FIG. 5 again shows the fastening device 222 with its two openings 212a and 212b, between which the web 212c extends.
  • the arched damping arms 218 and 220 extend in the direction of the fastening device 214.
  • the fastening device 214 is formed by a strip-shaped element 214a, preferably made of sheet metal. From the strip-shaped element 214a, a threaded pin 214b projects.
  • the fastening device 214 or the strip-shaped sheet metal element 214a is preferably connected by vulcanization to the rubber damping arms 218 and 220.
  • the damping body 216 has, as Figure 6 can be seen, no reinforcing insert.
  • FIGS. 7 and 8 respectively show a perspective view and a sectional view of a fourth embodiment of the invention.
  • damping arms 318 and 320 are designed in such a way that the two damping arms 318 and 320 can each be provided at their ends with a fastening device labeled 214 in the above-described embodiment, ie with one strip-shaped sheet metal element having a threaded pin.
  • damping arms 318 and 320 may be combined with various fastening devices suitable for mounting the bearing assembly to the exhaust system and the vehicle.
  • the damping arms 318 and 320 are provided at their bulges 318a and 320a with a reinforcing insert 322, ie the reinforcing insert 22 extends completely over the bulge 318a and 320a of the damping arms 318 and 320.
  • Figures 9 and 10 show a perspective view and a sectional view of a bearing device according to a fifth embodiment.
  • FIG. 9 shows the schematically illustrated fastening devices 412 and 414, between which the damping arms 418 and 420 of the damping body 416 extend.
  • Fasteners 412 and 414 are in the form of strip-like elements and are preferably connected to damper arms 418 and 420 via vulcanization.
  • FIGS. 9 and 10 show that the damping arms 418 and 420 each again have a bulge 418a and 420a in the direction of the respective other damping arm 418 or 420.
  • a rigid counter abutment body 424 extends between the arched damper arms 418 and 420, i. the opposing abutment body 424 extends in the direction of the fastening device 414, which ends in a region after the bulges 418a and 420a and has a predetermined distance from the counter abutment body.
  • the cambers 418a and 420a of the damper arms 418 and 420 increase until they abut against the mating abutment portions 424a and 424b of the countermesh body 424 due to the compressive load.
  • the two damping arms 418 and 420 do not abut on each other as a result of a compressive load, as in the embodiments described above, but they abut against the abutting portions 424a and 424b of the opposing abutment body 424.
  • Figures 11 and 12 show a perspective view and a sectional view of a bearing device according to a fifth embodiment.
  • the damper arms 518 and 520 are in opposite directions however, as in the embodiments described above, they extend between the fasteners 512 and 514.
  • the fastener 514 here has opposing abutment bodies 524 at the
  • FIG. 12 it can be seen that a predetermined distance is provided between the bulges 518a and 520a of the damping arms 518 and 520 in the unloaded state.
  • a pressure load d. H. the fasteners 512 and 514 move toward each other, the bulges 518a and 520a increase toward the mating abutment portions 524a and 524b until they abut the corresponding mating abutment portions 524a and 524b.
  • the rigidity of the bearing apparatus 510 progressively increases.
  • FIG. 13 shows a perspective view according to a seventh embodiment of the invention.
  • the fastening device 612 has receiving openings 626 in which the damping bodies 616 are accommodated.
  • the damper body 616 further receives the fastener 614.
  • Damping body 616 according to this embodiment comprises four damping arms 628, 630, 632 and 634 extending between the fastening means 612 and the fastening means 614.
  • the fastening device 612 is provided for fastening the bearing device 610 to a vehicle underbody or to a cross member on the vehicle underbody, whereas the fastening device 614 is designed to attach a vehicle exhaust system to the bearing device.
  • FIG. 13 it can further be seen that the four damping arms 628, 630, 632 and 634 act as mutually independent pressure rods, which are connected to one another only at their connection points to the fastening devices 612, 614, in particular to receive the fastening device 614 between them can.
  • FIGS. 14a to 14c show the partial views of the bearing device 610.
  • FIG. 14 a shows a section of the fastening device 612 with the receiving openings 626, in which the damping bodies 616 are accommodated with the fastening devices 614, wherein the individual points in the direction of the
  • FIG. 14b shows an axis-containing sectional view of the receiving opening 626 of the fastening device 612 according to FIG. 14a.
  • damping arms 628 and 632 shown in FIG. 14b which extend from the fastening device 612 in the direction of the fastening device 614.
  • the damping arms 628 and 632 are opposite each other and are curved in the direction of the respective other damping arm 628 and 632.
  • the fastening device 614 which acts according to this embodiment as a counter-investment body.
  • the fastening device 614 is bolt-shaped and has a
  • the damping arms 628 and 632 overcome the predetermined distance between them and the mating abutment portion 614a of the fastening device 614 under an increase of their bulges 628a and 632a to the counter abutment portion 614a.
  • the damping arms 628 and 632 deform such that they initially deform freely and increase their bulge 628a and 628b in the direction of the mating abutment portion 614a of the fastening device 614.
  • FIG. 14b two circumferential projections 614b and 614c can be seen on the bolt-shaped fastening device 614, wherein the opposing abutment portion 614a begins after the projection 614b and continues in the axial direction to the left.
  • FIG. 14c shows a view of the receiving opening 626 in the fastening device 614, viewed from the right in the axial direction in FIG. 14b.
  • Figure 15 is a perspective view of an eighth embodiment of the invention.
  • FIG. 15 shows the counterbearing bodies 724 formed on the fastening device 712.
  • the counterbearing bodies 724 are connected to the receiving openings 726 (FIG. 16b).
  • the four damping arms 728, 730, 732 and 734 of the damping body 716 which receives the fastening device 714.
  • FIG. 16a shows a detailed view of the receiving opening 726 of the fastening device 712 with the four damping arms 728, 730, 732 and 734 extending between the damping device 712 and the damping device 714.
  • FIG. 16b shows an axis-containing sectional view of the view according to FIG. 16a.
  • FIG. 16b shows the damping arms 728 and 732, which extend from the fastening device 712 to the fastening device 714.
  • the damper arms 728 and 730 according to this embodiment are curved in the direction of the countermember 724 provided at the receiving openings 726.
  • the fastening device 714 does not act as a counter-abutment body in this embodiment.
  • the counter-abutment body 724 is here tubular and can be integrally connected to the fastening device 712.
  • the predetermined distance between the bulge 728a, 732a and the opposing abutment body 724 can be seen in the resting state of the bearing device 710.
  • the fastening device 714 moves axially in the axial direction to the left and the bulges 728a and 732a of the damping arms 728 and 732 or the abutment sections 728b and 730b shift in the direction of the opposing abutment body 724 until the damping arms 728 and 732 with their enlarged bulges 728a and 732b abut against the mating abutment portion 724a of the opposing abutment body 724, whereby the bearing device 710 stiffens.
  • the damping arms 728 and 732 first deform freely until they abut with their abutment portions 728b and 732b against the mating abutment portion 724a of the tub
  • FIG. 16c shows a view from the right in the axial direction in FIG. 16b of the bearing device 710.
  • Figures 17 to 18c show views of a ninth embodiment of the bearing device, which largely coincides with the embodiment described above.
  • This embodiment differs from the previous embodiment only in that an elastomer layer 836 is arranged on the counter-abutment body 824 at its mating abutment portion 824a.
  • FIGS. 19 to 20 c show a tenth embodiment of the invention which differs from the embodiment described with reference to FIGS. 15 to 16 c only in that the receiving openings 926 are rectangular in shape.
  • FIGs 21 to 22c show a tenth embodiment of the invention, wherein it can be seen in particular from Figure 22b that the damping arms 1028 and 1030 are rectilinear, i. without buckling, between the fastener 1012 and the fastener 1014 extend.
  • the damping arms 1028 and 1030 act as mutually independent push rods, which are interconnected only at their junctions with the fasteners 1012 and 1014, in particular to accommodate the fastener 1014 between them can.
  • the rectilinear damper arms 1028 and 1032 overcome the predetermined distance therebetween at a pressure load in the axial direction from the right in FIG. 22c Counter abutment body 1024 under a free deformation, bulge and attach with an increased curvature at the mating abutment portion 1024 a of the counter abutment body 1024.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Manufacturing & Machinery (AREA)
  • Transportation (AREA)
  • Vibration Prevention Devices (AREA)
  • Exhaust Silencers (AREA)

Abstract

L'invention concerne un dispositif de stockage (10) pour un système d'échappement de véhicule doté d'au moins un dispositif de fixation (12, 14) destiné à la disposition côté véhicule du dispositif de stockage (10), d'au moins un dispositif de fixation (12, 14) destiné à la disposition côté système d'échappement du dispositif de stockage (10) et d'au moins un corps d'amortissement (16) s'étendant entre les dispositifs de fixation (12, 14). Selon l'invention, le corps d'amortissement (16) peut comporter au moins un bras d'amortissement (18, 20) s'étendant entre les dispositifs de fixation (12, 14) de telle manière qu'il présente dans l'état à vide du corps d'amortissement (16) avec une section d'appui (18b) une distance prédéfinie par rapport à une section de contre-appui (20b) d'au moins un corps de contre-appui (20). Le ou les bras d'amortissement (18, 20) se courbent après avoir été soumis à l'action d'une pression pour atteindre une courbe caractéristique d'amortissement progressive et, lorsque la courbure (18a, 20a) augmente, se déforment tout d'abord librement puis s'appliquent avec la section d'appui (18b) contre la section de contre-appui (20b).
PCT/EP2011/005658 2010-11-26 2011-11-10 Dispositif de stockage pour système d'échappement WO2012069142A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010052718 DE102010052718A1 (de) 2010-11-26 2010-11-26 Lagervorrichtung für eine Abgasanlage
DE102010052718.1 2010-11-26

Publications (2)

Publication Number Publication Date
WO2012069142A2 true WO2012069142A2 (fr) 2012-05-31
WO2012069142A3 WO2012069142A3 (fr) 2012-08-09

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WO (1) WO2012069142A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2666988A1 (fr) * 2012-05-21 2013-11-27 Nissan Motor Manufacturing (UK) Ltd. Suspension d'échappement

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019000694A1 (de) * 2019-01-31 2020-08-06 Süddeutsche Gelenkscheibenfabrik GmbH & Co. KG Elastisches Lager
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