EP1186781B2 - Filter silencer mounting device for turbo charger inlet - Google Patents

Filter silencer mounting device for turbo charger inlet Download PDF

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Publication number
EP1186781B2
EP1186781B2 EP00810814A EP00810814A EP1186781B2 EP 1186781 B2 EP1186781 B2 EP 1186781B2 EP 00810814 A EP00810814 A EP 00810814A EP 00810814 A EP00810814 A EP 00810814A EP 1186781 B2 EP1186781 B2 EP 1186781B2
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EP
European Patent Office
Prior art keywords
compressor
vibration
uncoupler
casing part
turbocharger
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.)
Expired - Lifetime
Application number
EP00810814A
Other languages
German (de)
French (fr)
Other versions
EP1186781B1 (en
EP1186781A1 (en
Inventor
Josef Bättig
Alfons Tröndle
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Accelleron Industries AG
Original Assignee
ABB Turbo Systems AG
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.)
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Publication date
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=8174898&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1186781(B2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by ABB Turbo Systems AG filed Critical ABB Turbo Systems AG
Priority to EP00810814A priority Critical patent/EP1186781B2/en
Priority to DE50013694T priority patent/DE50013694D1/en
Priority to TW090101395A priority patent/TW576899B/en
Priority to AU2001281644A priority patent/AU2001281644A1/en
Priority to PCT/CH2001/000511 priority patent/WO2002020996A1/en
Priority to KR1020037003374A priority patent/KR100812585B1/en
Priority to CNB018185827A priority patent/CN1242179C/en
Priority to JP2002525376A priority patent/JP4681211B2/en
Publication of EP1186781A1 publication Critical patent/EP1186781A1/en
Publication of EP1186781B1 publication Critical patent/EP1186781B1/en
Application granted granted Critical
Publication of EP1186781B2 publication Critical patent/EP1186781B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
    • F04D29/701—Suction grids; Strainers; Dust separation; Cleaning especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/024—Units comprising pumps and their driving means the driving means being assisted by a power recovery turbine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers

Definitions

  • the invention relates to a fastening device for releasably attaching a filter silencer to a housing part of a belonging to a turbocharger for internal combustion engines compressor according to the preamble of claim 1.
  • a turbocharger is in EP 0 574 605 A1 disclosed.
  • a filter silencer is usually arranged at the compressor inlet, which reduces these noise emissions. Since the filter muffler is rigidly connected to a housing part of the compressor and this vibration technology is not decoupled from the turbocharger, the vibrations of the turbocharger transmitted to the filter muffler.
  • the turbocharger is in turn usually attached either directly or via a mounting foot on a console of an internal combustion engine. The axial distance between mounting foot and filter silencer is usually very large. If the turbocharger is excited by engine vibrations and / or gets into natural frequency oscillations, the oscillation amplitude is greatest due to the geometry of the filter silencer. This is undesirable, inter alia, because of the resulting large material load. In countries with appropriate provisions, this vibration problem can lead to rejection of the technical approval.
  • the fastening device has a vibration decoupler for connecting a filter silencer to a housing part of a compressor at the compressor inlet between the filter silencer and the housing part of the compressor.
  • the filter silencer is largely isolated from the compressor housing part and thus from the turbocharger.
  • large vibration amplitudes are avoided at the filter muffler and premature fatigue due to high, vibration-induced material stress is counteracted.
  • vibration decoupler As a vibration decoupler is best used a temperature and oil resistant and wear-resistant, rubber-elastic element. In this way, the vibration decoupler is perfectly adapted to the conditions of use, which ensures a long service life of the vibration decoupler. It has been found that rubber-elastic elements made of an elastomer (such as Viton® from Du Pont or from silicone) are very well suited as vibration isolators.
  • an elastomer such as Viton® from Du Pont or from silicone
  • the vibration decoupler viewed in the installed state, a low rigidity in the axial direction and transversely to the axial direction of the turbocharger on.
  • the stiffnesses in the axial direction and transversely to the axial direction can be chosen differently.
  • the low rigidity ensures a sufficient vibration decoupling between the filter silencer and the housing part of the compressor.
  • the vibration decoupler is chosen as soft as possible. But at least the stiffness is chosen so that taking into account the weight of the components and their geometry and taking into account the geometry of the connection between the filter muffler and the housing part of the compressor, the filter muffler finally a natural frequency of about 25% to 50%, preferably 40% at least the lowest having the natural frequencies of the turbocharger.
  • the filter silencer Upon excitation of the turbocharger in the natural frequency range, for example by engine vibrations, the filter silencer then oscillates in the supercritical range.
  • the vibration decoupler is under prestressing. In this way it can be prevented that the contact between the vibration isolator and a component is lost and abrasion and wear occur on the vibration isolator.
  • the formation of the vibration decoupler in the form of an O-ring is particularly advantageous because in this embodiment, the forces to be absorbed by the compound are distributed over the entire circumference of the O-ring.
  • FIG. 1 shows in section to its longitudinal axis 10 a turbocharger 12 and a portion of a compressor inlet 14 attached to the turbocharger 12 filter muffler 16.
  • the turbocharger 12 has a typical structure, ie it comprises a compressor 18 and a turbine 20 whose wheels 22, 24 on a common Shaft 26 are spaced from each other.
  • the turbocharger 12 has a turbocharger housing 28, which comprises a plurality of housing parts, such as a turbine housing 29, a bearing housing 30 and a compressor housing 27, which themselves may consist of several housing parts.
  • the shaft 26 is mounted between the turbine runner 24 and the compressor wheel 22.
  • the turbocharger 12 is mounted on a bracket 34 of the engine (not shown).
  • the filter silencer 16 is fastened to the compressor inlet 14 on a housing part 32 of the compressor 18.
  • Filter silencer 16 and housing part 32 of the compressor 18 are connected via a fastening device 36 rigidly together.
  • the fastening device 36 comprises in this example on a circular line around the turbocharger axis 10 arranged, first mounting holes 38 which are provided in the housing part 32 of the compressor 18.
  • the first attachment openings 38 are threaded.
  • the fastening device 36 comprises second fastening openings 42, which are arranged in a flange 40 of the filter silencer 16 and can be coaxially brought into coincidence with the first fastening openings 38.
  • fasteners 44 which are formed in this example as screws, and are screwed through the second mounting holes 42 in the first mounting holes 38, and so connect the filter muffler 16 rigidly with the housing part 32 of the compressor 18.
  • FIG. 1 it can be seen that the distance between the mounting foot 31 and the filter muffler 16 is quite large. Vibrations transmitted to the turbocharger 12 via the bracket 34 and the mounting leg 31 from the engine (not shown), and natural vibrations of the turbocharger 12 are transmitted to the filter muffler 16 via the rigid attachment device 36. Due to the large distance between the mounting foot 31 and filter muffler 16, the vibration amplitude at the filter muffler 16 is the largest. What brings the already mentioned disadvantages.
  • Each one of these fastening devices 36 comprises, in the housing part 32 of the compressor 18, arranged first mounting holes 38 with thread and fasteners 44 in the form of screws which are screwed into the first mounting holes 38.
  • the attachment openings 38 are preferably arranged in a plane perpendicular to the turbocharger axis 10, arranged on a ring around the turbocharger axis 10.
  • the direction in which the turbocharger axle (10) lies is in each case marked by an arrow a.
  • the ring is ideally a circular ring and the mounting holes 38 are evenly distributed on the ring.
  • the inventive fastening device 36 comprises a vibration decoupler 46, which is arranged between the filter silencer 16 and the housing part 32 of the compressor 18.
  • the vibration isolator 46 is made of an elastomer having low rigidity in the axial direction and transverse to the axial direction of the turbocharger 12.
  • the stiffness is selected so that the natural frequencies of the filter silencer 16 is about 40% of at least the lowest of the natural frequencies of the turbocharger 12.
  • the rigidity depends inter alia on the geometry of the components and their weight, as well as on the design of the fastening device 36.
  • fastening device 36 shown comprises in addition to the above-mentioned elements an O-ring vibration isolator 46, a radially outwardly open annular groove 62 disposed in an element 60 of the filter silencer 62 for supporting the vibration isolator 46 and two fastening rings 64, 66.
  • the two fastening rings 64, 66 have holes 68 which can be brought into coincidence with the first fastening openings 38 in the housing part 32 of the compressor 18 for accommodating the fastening elements 44. They are coaxial with each other and one behind the other in the axial direction, then arranged on the housing part 32 of the compressor 18. Via the helical fastening elements 44, the fastening rings 64, 66 are fixed to the housing part 32 of the compressor 18.
  • the mounting rings 64, 66 support surfaces 67, which support the O-ring 46 at an angle of about + 30 ° to + 50 ° or -30 ° to -50 °.
  • the support surfaces 67 together again form a kind of annular groove which is radially open towards the inside and spaced from the annular groove 62 in the element 60 extends parallel to this.
  • the diameter on the radially inner side of the mounting rings 64, 66 and the diameter of the annular groove 62 in the element 60 of the filter muffler 16 are selected so that the arranged between them O-ring vibration isolator 46 is in the mounted state under bias.
  • a natural frequency of the filter muffler 16 is obtained from about 40% of the turbocharger 12 having an axial rigidity of 7000 N / mm to 14000 N / mm and a radial rigidity of 15000 to 40,000 N / mm.
  • a further embodiment is shown, which is analogous to that in Fig.2 shown is constructed.
  • a securing element 68 still belongs to the fastening device 36.
  • the securing element 68 is then arranged axially adjacent to the fastening ring 66 adjacent to the filter muffler 16 and fastened to the housing part 32 together with the fastening rings 64, 66 with the aid of the fastening means 44. It protrudes radially both inwards as well as outward on the mounting rings 64, 66 addition.
  • the securing element like the mounting ring 64, 66, be configured annular or, as in the example shown, consist of Ringsegment Swissen.
  • the housing part 32 of the compressor 18 adjacent mounting ring 64 is integrally formed with the housing part 32.
  • FIG Fig. 4 shows a further variant of Fig. 2 known embodiment.
  • the fastening device 36 comprises fastening elements 44 in the form of clamping elements 72.
  • the housing part 32 of the compressor 18 therefore has a fastening flange 70 instead of first fastening openings 38.
  • the fastening rings 64, 66 have no attachment opening 38.
  • the fixation of the mounting rings 64, 66 on the housing part 32 of the compressor 18 takes place instead of helical fasteners 44 with the clamping brackets 72, distributed over the circumference provide a firm connection between the components.
  • the O-ring vibration isolator 46 and the mounting rings 64, 66 - which are e.g. can be connected to each other by means of Spannklammem or by means of introduced into them auxiliary holes and auxiliary screws - pre-assembled on the filter muffler 16. Then the filter muffler 16 is fastened via the fastening rings 64, 66 by means of the fastening elements 44 to the housing part 32 of the compressor 18 and thus to the turbocharger 12.
  • a natural frequency of the filter muffler 16 is from about 40% of the turbocharger 12 having an axial stiffness of 7000 N / mm to 14000 N / mm of the vibration isolator 46 and a radial stiffness of 15,000 to 40,000 N / mm of the vibration isolator 46 reached.
  • attachment device 36 Various other variations and combinations of said attachment device 36 are conceivable.
  • clamping brackets 72 and helical fastening elements 44 may be used in combination.
  • the second attachment openings 42 may instead be arranged in a flange 40 of the filter silencer 16 in another of the compressor inlet 14 adjacent element of the filter silencer 16.
  • the second attachment openings 42 may be provided in the filter muffler 16 with a thread.
  • the first attachment openings 38 in the housing part 32 of the compressor 18 may be arranged in a flange of the housing part 32.
  • the helical fasteners 44 may then be threaded from the compressor side rather than from the side of the filter muffler 16.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Description

Technisches GebietTechnical area

Die Erfindung bezieht sich auf eine Befestigungsvorrichtung zum lösbaren Befestigen eines Filterschalldämpfers an einem Gehäuseteil eines zu einem Turbolader für Verbrennungsmotoren gehörenden Verdichters gemäss dem Oberbegriff des Patentanspruches 1. Ein solcher Turbolader ist in EP 0 574 605 A1 offenbart.The invention relates to a fastening device for releasably attaching a filter silencer to a housing part of a belonging to a turbocharger for internal combustion engines compressor according to the preamble of claim 1. Such a turbocharger is in EP 0 574 605 A1 disclosed.

Stand der TechnikState of the art

Am Verdichtereingang von Turboladern gibt es hohe Geräuschemissionen. Daher ist am Verdichtereingang meist ein Filterschalldämpfer angeordnet, der diese Geräuschemissionen vermindert. Da der Filterschalldämpfer starr mit einem Gehäuseteil des Verdichters verbunden ist und dies schwingungstechnisch nicht vom Turbolader entkoppelt ist, übertragen sich die Schwingungen des Turboladers auf den Filterschalldämpfer. Der Turbolader ist seinerseits in der Regel entweder direkt oder via einen Befestigungsfuss auf einer Konsole eines Verbrennungsmotors befestigt. Die axiale Distanz zwischen Befestigungsfuss und Filterschalldämpfer ist in der Regel sehr gross. Wird der Turbolader durch Motorvibrationen angeregt und/oder gerät in Eigenfrequenzschwingungen, so ist die Schwingungsamplitude aufgrund der Geometrie am Filterschalldämpfer am grössten. Dies ist unter anderem wegen der daraus resultierenden grossen Materialbelastung unerwünscht. In Ländern mit entsprechenden Bestimmungen kann dieses Schwingungsproblem bis zur Zurückweisung bei der technischen Zulassung führen.There are high noise emissions at the compressor inlet of turbochargers. Therefore, a filter silencer is usually arranged at the compressor inlet, which reduces these noise emissions. Since the filter muffler is rigidly connected to a housing part of the compressor and this vibration technology is not decoupled from the turbocharger, the vibrations of the turbocharger transmitted to the filter muffler. The turbocharger is in turn usually attached either directly or via a mounting foot on a console of an internal combustion engine. The axial distance between mounting foot and filter silencer is usually very large. If the turbocharger is excited by engine vibrations and / or gets into natural frequency oscillations, the oscillation amplitude is greatest due to the geometry of the filter silencer. This is undesirable, inter alia, because of the resulting large material load. In countries with appropriate provisions, this vibration problem can lead to rejection of the technical approval.

Aus der DE-U-1807288 ist eine Aufhängung für einen Filterschalldämpfer bekannt, wobei das Filtergehäuse mit seiner Halterung ausschliesslich durch elastische Formteile aus Gummi oder gummiähnlichen Werkstoffen verbunden ist.From the DE-U-1807288 a suspension for a filter muffler is known, wherein the filter housing is connected to its holder exclusively by elastic molded parts made of rubber or rubber-like materials.

Darstellung der ErfindungPresentation of the invention

Es ist deshalb Aufgabe der Erfindung, eine Befestigungsvorrichtung der eingangs genannten Art zu schaffen, welche die oben genannten Nachteile einfach und kostengünstig behebt.It is therefore an object of the invention to provide a fastening device of the type mentioned, which solves the above-mentioned disadvantages easily and inexpensively.

Diese Aufgabe löst eine Befestigungsvorrichtung mit den Merkmalen des Patentanspruches 1.This object is achieved by a fastening device having the features of patent claim 1.

Die erfindungsgemässe Befestigungsvorrichtung weist zum Verbinden eines Filterschalldämpfers mit einem Gehäuseteil eines Verdichters am Verdichtereingang zwischen dem Filterschalldämpfer und dem Gehäuseteil des Verdichters einen Schwingungsentkoppler auf. Mit Hilfe des Schwingungsentkopplers ist der Filterschalldämpfer schwingungstechnisch weitgehend von dem Verdichtergehäuseteil und damit vom Turbolader getrennt. Bei der Übertragung von Schwingungen vom Turbolader bzw. vom Verdichter auf den Filterschalldämpfer werden grosse Schwingungsamplituden am Filterschalldämpfer vermieden und einer vorzeitige Materialermüdung durch eine hohe, schwingungsbedingte Materialbeanspruchung wird entgegengewirkt.The fastening device according to the invention has a vibration decoupler for connecting a filter silencer to a housing part of a compressor at the compressor inlet between the filter silencer and the housing part of the compressor. With the help of the vibration decoupler, the filter silencer is largely isolated from the compressor housing part and thus from the turbocharger. In the transmission of vibrations from the turbocharger or the compressor to the filter muffler large vibration amplitudes are avoided at the filter muffler and premature fatigue due to high, vibration-induced material stress is counteracted.

Als Schwingungsentkoppler wird am besten ein temperatur- und ölbeständiges sowie verschleissfestes, gummielastisches Element eingesetzt. Auf diese Weise ist der Schwingungsentkoppler den Einsatzbedingungen bestens angepasst, was eine hohe Standzeit des Schwingungsentkopplers gewährleistet. Es hat sich gezeigt, dass aus einem Elastomer (wie z.B. aus Viton ® von der Firma du Pont oder aus Silikon) gefertigte gummielastische Elemente sehr gut als Schwingungsentkoppler geeignet sind.As a vibration decoupler is best used a temperature and oil resistant and wear-resistant, rubber-elastic element. In this way, the vibration decoupler is perfectly adapted to the conditions of use, which ensures a long service life of the vibration decoupler. It has been found that rubber-elastic elements made of an elastomer (such as Viton® from Du Pont or from silicone) are very well suited as vibration isolators.

Vorteilhafterweise weist der Schwingungsentkoppler, im eingebauten Zustand betrachtet, eine geringe Steifigkeit in Achsrichtung sowie quer zur Achsrichtung des Turboladers auf. Abhängig von den sechs Eigenfrequenzen des Turboladers können die Steifigkeiten in Achsrichtung und quer zur Achsrichtung unterschiedlich gewählt werden. Die geringe Steifigkeit sorgt für eine ausreichende schwingungsmässige Entkopplung zwischen Filterschalldämpfer und Gehäuseteil des Verdichters.Advantageously, the vibration decoupler, viewed in the installed state, a low rigidity in the axial direction and transversely to the axial direction of the turbocharger on. Depending on the six natural frequencies of the turbocharger, the stiffnesses in the axial direction and transversely to the axial direction can be chosen differently. The low rigidity ensures a sufficient vibration decoupling between the filter silencer and the housing part of the compressor.

Unter Berücksichtigung der konstruktiven Bedingungen wir der Schwingungsentkoppler so weich wie möglich gewählt. Mindestens aber wird die Steifigkeit so gewählt, dass unter Berücksichtung des Gewichtes der Bauteile und ihrer Geometrie sowie unter Berücksichtigung der Geometrie der Verbindung zwischen Filterschalldämpfer und Gehäuseteil des Verdichters der Filterschalldämpfer schliesslich eine Eigenfrequenz von etwa 25% bis 50%, vorzugsweise 40% zumindest der tiefsten der Eigenfrequenzen des Turboladers aufweist. Bei Erregung des Turboladers im Eigenfrequenzbereich, beispielsweise durch Motorschwingungen, schwingt der Filterschalldämpfer dann im überkritischen Bereich.Taking into account the constructive conditions, the vibration decoupler is chosen as soft as possible. But at least the stiffness is chosen so that taking into account the weight of the components and their geometry and taking into account the geometry of the connection between the filter muffler and the housing part of the compressor, the filter muffler finally a natural frequency of about 25% to 50%, preferably 40% at least the lowest having the natural frequencies of the turbocharger. Upon excitation of the turbocharger in the natural frequency range, for example by engine vibrations, the filter silencer then oscillates in the supercritical range.

Besonders vorteilhaft ist es, wenn der Schwingungsentkoppler unter Vorspannung steht. Auf diese Weise kann verhindert werden, dass der Kontakt zwischen Schwingungsentkoppler und einem Bauteil verloren geht und Abrieb und Verschleiss am Schwingungsentkoppler auftreten.It is particularly advantageous if the vibration decoupler is under prestressing. In this way it can be prevented that the contact between the vibration isolator and a component is lost and abrasion and wear occur on the vibration isolator.

Die Ausbildung des Schwingungsentkopplers in Form eines O-Ringes ist besonders vorteilhaft, da bei dieser Ausführungsform die von der Verbindung aufzunehmenden Kräfte auf den ganzen Umfang des O-Ringes verteilt werden.The formation of the vibration decoupler in the form of an O-ring is particularly advantageous because in this embodiment, the forces to be absorbed by the compound are distributed over the entire circumference of the O-ring.

Vorteilhaft ist es ein Sicherungselement vorzusehen, welches bei einem Versagen des O-ringförmigen Schwingungsentkopplers einer Auflösung der Verbindung zwischen Filterschalldämpfer und Gehäuseteil des Verdichters entgegenwirkt.It is advantageous to provide a securing element, which counteracts a resolution of the connection between the filter silencer and the housing part of the compressor in case of failure of the O-ring vibration decoupler.

Weitere bevorzugte Ausführungsformen sind Gegenstand weiterer abhängigen Patentansprüche.Further preferred embodiments are the subject of further dependent claims.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Im folgenden wird der Erfindungsgegenstand anhand von bevorzugten Ausführungsbeispielen, welche in den beiliegenden Figuren 1 bis 4 dargestellt sind, näher erläutert. Es zeigen rein schematisch:

Fig. 1
im Schnitt längs der Turboladerachse einen Turbolader mit einem am Verdichtereingang angeordneten Filterschalldämpfer mit einer Befestigungsvorrichtung gemäss dem Stand der Technik.
Fig. 2
in analoger Darstellungsweise wie in Figur 2 einen Teil einer zweiten Ausführungsform der erfindungsgemässen Befestigungsvorrichtung;
Fig. 3
die Befestigungsvorrichtung aus Fig. 3 mit einem Sicherungselement; und
Fig. 4
in analoger Darstellungsweise wie in Figur 2 einen Teil einer dritten Ausführungsform der erfindungsgemässen Befestigungsvorrichtung;
In the following the subject invention is based on preferred embodiments, which in the accompanying FIGS. 1 to 4 are illustrated, explained in more detail. It shows purely schematically:
Fig. 1
in section along the turbocharger axis, a turbocharger with a compressor inlet arranged on the filter silencer with a fastening device according to the prior art.
Fig. 2
in analog representation as in FIG. 2 a part of a second embodiment of the inventive fastening device;
Fig. 3
the fastening device Fig. 3 with a securing element; and
Fig. 4
in analog representation as in FIG. 2 a part of a third embodiment of the inventive fastening device;

Die in den Zeichnungen verwendeten Bezugszeichen und deren Bedeutung sind in der Bezugszeichenliste zusammengefasst aufgelistet. Grundsätzlich sind in den Figuren gleiche Teile mit gleichen Bezugszeichen versehen. Die beschriebenen Ausführungsformen stehen beispielhaft für den Erfindungsgegenstand und haben keine beschränkende Wirkung.The reference numerals used in the drawings and their meaning are listed in the list of reference numerals. Basically, the same parts are provided with the same reference numerals in the figures. The described embodiments are exemplary of the subject invention and have no limiting effect.

Wege zur Ausführung der ErfindungWays to carry out the invention

Figur 1 zeigt im Schnitt zu seiner Längsachse 10 einen Turbolader 12 und einen Teil eines am Verdichtereingang 14 des Turboladers 12 befestigten Filterschalldämpfers 16. Der Turbolader 12 hat einen typischen Aufbau, d.h. er umfasst einen Verdichter 18 und eine Turbine 20 deren Laufräder 22, 24 auf einer gemeinsamen Welle 26 beabstandet voneinander angeordnet sind. Der Turbolader 12 weist ein Turboladergehäuse 28 auf, das mehrere Gehäuseteile, wie beispielsweise ein Turbinengehäuse 29, ein Lagergehäuse 30 und ein Verdichtergehäuse 27, umfasst, die selbst wieder aus mehreren Gehäuseteilen bestehen können. Im Lagergehäuse 30 ist zwischen dem Turbinenlaufrad 24 und dem Verdichterlaufrad 22 die Welle 26 gelagert. Mittels eines Befestigungsfusses 31 ist der Turbolader 12 auf einer Konsole 34 des Motors (nicht dargestellt) befestigt. Zur Verminderung der Geräuschemission ist am Verdichtereingang 14 an einem Gehäuseteil 32 des Verdichters 18 der Filterschalldämpfer 16 befestigt. FIG. 1 shows in section to its longitudinal axis 10 a turbocharger 12 and a portion of a compressor inlet 14 attached to the turbocharger 12 filter muffler 16. The turbocharger 12 has a typical structure, ie it comprises a compressor 18 and a turbine 20 whose wheels 22, 24 on a common Shaft 26 are spaced from each other. The turbocharger 12 has a turbocharger housing 28, which comprises a plurality of housing parts, such as a turbine housing 29, a bearing housing 30 and a compressor housing 27, which themselves may consist of several housing parts. In the bearing housing 30, the shaft 26 is mounted between the turbine runner 24 and the compressor wheel 22. By means of a mounting foot 31, the turbocharger 12 is mounted on a bracket 34 of the engine (not shown). To reduce the noise emission, the filter silencer 16 is fastened to the compressor inlet 14 on a housing part 32 of the compressor 18.

Filterschalldämpfer 16 und Gehäuseteil 32 des Verdichters 18 sind via eine Befestigungsvorrichtung 36 starr miteinander verbunden. Die Befestigungsvorrichtung 36 umfasst in diesem Beispiel auf einer Kreislinie um die Turboladerachse 10 angeordnete, erste Befestigungsöffnungen 38, die im Gehäuseteil 32 des Verdichters 18 vorgesehen sind. Die ersten Befestigungsöffnungen 38 sind mit einem Gewinde versehen. Des weiteren umfasst die Befestigungsvorrichtung 36 in einem Flansch 40 des Filterschalldämpfers 16 angeordnete zweite Befestigungsöffnungen 42, die mit den ersten Befestigungsöffnungen 38 koaxial in Deckung bringbar sind. Ebenfalls zur Befestigungsvorrichtung 36 gehören Befestigungselemente 44, welche in diesem Beispiel als Schrauben ausgebildet sind, und die durch die zweiten Befestigungsöffnungen 42 in die ersten Befestigungsöffnungen 38 eingeschraubt sind, und so den Filterschalldämpfer 16 starr mit dem Gehäuseteil 32 des Verdichters 18 verbinden.Filter silencer 16 and housing part 32 of the compressor 18 are connected via a fastening device 36 rigidly together. The fastening device 36 comprises in this example on a circular line around the turbocharger axis 10 arranged, first mounting holes 38 which are provided in the housing part 32 of the compressor 18. The first attachment openings 38 are threaded. Furthermore, the fastening device 36 comprises second fastening openings 42, which are arranged in a flange 40 of the filter silencer 16 and can be coaxially brought into coincidence with the first fastening openings 38. Also to the fastening device 36 include fasteners 44, which are formed in this example as screws, and are screwed through the second mounting holes 42 in the first mounting holes 38, and so connect the filter muffler 16 rigidly with the housing part 32 of the compressor 18.

Wie aus Figur 1 ersichtlich ist die Distanz zwischen Befestigungsfuss 31 und dem Filterschalldämpfer 16 recht gross. Schwingungen, die über die Konsole 34 und den Befestigungsfuss 31 vom Motor (nicht dargestellt) auf den Turbolader 12 übertragen werden und Eigenschwingungen des Turboladers 12 werden via die starre Befestigungsvorrichtung 36 auf den Filterschalldämpfer 16 übertragen. Auf Grund der grossen Distanz zwischen Befestigungsfuss 31 und Filterschalldämpfer 16 ist die Schwingungsamplitude am Filterschalldämpfer 16 am grössten. Was die bereits genannten Nachteile mit sich bringt.How out FIG. 1 it can be seen that the distance between the mounting foot 31 and the filter muffler 16 is quite large. Vibrations transmitted to the turbocharger 12 via the bracket 34 and the mounting leg 31 from the engine (not shown), and natural vibrations of the turbocharger 12 are transmitted to the filter muffler 16 via the rigid attachment device 36. Due to the large distance between the mounting foot 31 and filter muffler 16, the vibration amplitude at the filter muffler 16 is the largest. What brings the already mentioned disadvantages.

Die Figuren 2 bis 4 zeigen jeweils eine erfindungsgemässe Befestigungsvorrichtung 36. Jede dieser Befestigungsvorrichtungen 36 umfasst im Gehäuseteil 32 des Verdichters 18 angeordnete, erste Befestigungsöffnungen 38 mit Gewinde sowie Befestigungselemente 44 in Form von Schrauben, die in die ersten Befestigungsöffnungen 38 eingeschraubt sind. Die Befestigungsöffnungen 38 sind vorzugsweise in einer Ebene die Senkrecht auf der Turboladerachse 10 steht, auf einem Ring rund um die Turboladerachse 10 angeordnet. Die Richtung, in der die Turboladerachse (10) liegt ist jeweils mit einem Pfeil a gekennzeichnet. Der Ring ist idealerweise ein Kreisring und die Befestigungsöffnungen 38 sind gleichmässig auf dem Ring verteilt. Des weiteren umfasst die erfindungsgemässe Befestigungsvorrichtung 36 einen Schwingungsentkoppler 46, der zwischen dem Filterschalldämpfer 16 und dem Gehäuseteil 32 des Verdichters 18 angeordnet ist. Der Schwingungsentkoppler 46 ist aus einem Elastomer gefertigt, der eine geringe Steifigkeit in Achsrichtung und quer zur Achsrichtung des Turboladers 12 aufweist. Die Steifigkeit wird so ausgewählt, dass die Eigenfrequenzen des Filterschalldämpfers 16 bei etwa 40% zumindest der tiefsten der Eigenfrequenzen des Turboladers 12 liegt. Die Steifigkeit hängt unter anderem von der Geometrie der Bauteile und von deren Gewicht, sowie von der Ausgestaltung der Befestigungsvorrichtung 36 ab.The FIGS. 2 to 4 Each one of these fastening devices 36 comprises, in the housing part 32 of the compressor 18, arranged first mounting holes 38 with thread and fasteners 44 in the form of screws which are screwed into the first mounting holes 38. The attachment openings 38 are preferably arranged in a plane perpendicular to the turbocharger axis 10, arranged on a ring around the turbocharger axis 10. The direction in which the turbocharger axle (10) lies is in each case marked by an arrow a. The ring is ideally a circular ring and the mounting holes 38 are evenly distributed on the ring. Furthermore, the inventive fastening device 36 comprises a vibration decoupler 46, which is arranged between the filter silencer 16 and the housing part 32 of the compressor 18. The vibration isolator 46 is made of an elastomer having low rigidity in the axial direction and transverse to the axial direction of the turbocharger 12. The stiffness is selected so that the natural frequencies of the filter silencer 16 is about 40% of at least the lowest of the natural frequencies of the turbocharger 12. The rigidity depends inter alia on the geometry of the components and their weight, as well as on the design of the fastening device 36.

Die in Fig. 2 gezeigte Befestigungsvorrichtung 36 umfasst zusätzlich zu den oben genannten Elementen einen O-ringförmigen Schwingungsentkoppler 46, eine in einem Element 60 des Filterschalldämpfers 16 angeordnete, radial nach aussen offene Ringnut 62 zur Abstützung des Schwingungsentkopplers 46 sowie zwei Befestigungsringe 64, 66. Die zwei Befestigungsringe 64, 66 weisen mit den ersten Befestigungsöffnungen 38 im Gehäuseteil 32 des Verdichters 18 koaxial in Deckung bringbare Löcher 68 zur Aufnahme der Befestigungselemente 44 auf. Sie sind koaxial zueinander und in Achsrichtung hintereinander, anschliessend an das Gehäuseteil 32 des Verdichters 18 angeordnet. Via die schraubenförmigen Befestigungselemente 44 sind die Befestigungsringe 64, 66 am Gehäuseteil 32 des Verdichters 18 fixiert. Auf ihrer radial innenliegenden Seite weisen die Befestigungsringe 64, 66 Stützflächen 67 auf, welche den O-Ring 46 unter einem Winkel von etwa +30°bis +50° bzw. -30° bis -50° abstützen. Die Stützflächen 67 bilden zusammen ebenfalls wieder eine Art Ringnut, die radial gegen innen offen ist und beabstandet zur Ringnut 62 im Element 60 parallel zu dieser verläuft. Der Durchmesser auf der radial innenliegenden Seite der Befestigungsringe 64, 66 und der Durchmesser der Ringnut 62 im Element 60 des Filterschalldämpfers 16 sind so gewählt, dass der zwischen ihnen angeordnete O-ringförmige Schwingungsentkoppler 46 im befestigten Zustand unter Vorspannung steht.In the Fig. 2 fastening device 36 shown comprises in addition to the above-mentioned elements an O-ring vibration isolator 46, a radially outwardly open annular groove 62 disposed in an element 60 of the filter silencer 62 for supporting the vibration isolator 46 and two fastening rings 64, 66. The two fastening rings 64, 66 have holes 68 which can be brought into coincidence with the first fastening openings 38 in the housing part 32 of the compressor 18 for accommodating the fastening elements 44. They are coaxial with each other and one behind the other in the axial direction, then arranged on the housing part 32 of the compressor 18. Via the helical fastening elements 44, the fastening rings 64, 66 are fixed to the housing part 32 of the compressor 18. On its radially inner side, the mounting rings 64, 66 support surfaces 67, which support the O-ring 46 at an angle of about + 30 ° to + 50 ° or -30 ° to -50 °. The support surfaces 67 together again form a kind of annular groove which is radially open towards the inside and spaced from the annular groove 62 in the element 60 extends parallel to this. The diameter on the radially inner side of the mounting rings 64, 66 and the diameter of the annular groove 62 in the element 60 of the filter muffler 16 are selected so that the arranged between them O-ring vibration isolator 46 is in the mounted state under bias.

Bei einem wiederum etwa 380Kg schweren Filterschalldämpfer 16 und dieser Konstruktion wird eine Eigenfrequenz des Filterschalldämpfer 16 von etwa 40% des Turboladers 12 mit einer axialen Steifigkeit von 7000 N/mm bis14000 N/mm und einer radialen Steifigkeit von 15000 bis 40000 N/mm erreicht.With a filter exhaust damper 16 again of about 380Kg and this construction, a natural frequency of the filter muffler 16 is obtained from about 40% of the turbocharger 12 having an axial rigidity of 7000 N / mm to 14000 N / mm and a radial rigidity of 15000 to 40,000 N / mm.

In Fig. 3 ist eine weitere Ausführungsform dargestellt, die analog zu der in Fig.2 gezeigten aufgebaut ist. Allerdings gehört in diesem Beispiel noch ein Sicherungselement 68 zur Befestigungsvorrichtung 36. Das Sicherungselement 68 ist axial anschliessend an den dem Filterschalldämpfer 16 benachbarten Befestigungsring 66 angeordnet und mit Hilfe des Befestigungsmittels 44 zusammen mit den Befestigungsringen 64, 66 am Gehäuseteil 32 befestigt. Es ragt radial sowohl nach innen wie auch nach aussen über die Befestigungsringe 64, 66 hinaus. bei einem Versagen des O-ringes hintergreift es das die Ringnut 62 tragenden Element 60 des Filterschalldämpfers 16 und verhindert so eine Auflösung der Verbindung zwischen Filterschalldämpfer 16 und Gehäuseteil 32 des Verdichters 18. Das Sicherungselement kann, wie die Befestigungsring 64, 66, ringförmig ausgestaltet sein oder aber, wie im gezeigten Beispiel, aus Ringsegmentstücken bestehen.In Fig. 3 a further embodiment is shown, which is analogous to that in Fig.2 shown is constructed. However, in this example, a securing element 68 still belongs to the fastening device 36. The securing element 68 is then arranged axially adjacent to the fastening ring 66 adjacent to the filter muffler 16 and fastened to the housing part 32 together with the fastening rings 64, 66 with the aid of the fastening means 44. It protrudes radially both inwards as well as outward on the mounting rings 64, 66 addition. in case of failure of the O-ring, it engages behind the annular groove 62 supporting element 60 of the filter muffler 16 and thus prevents a dissolution of the connection between the filter muffler 16 and housing part 32 of the compressor 18. The securing element, like the mounting ring 64, 66, be configured annular or, as in the example shown, consist of Ringsegmentstücken.

In einer weiteren nicht dargestellten Ausführungsform, die im Prinzip gleich aufgebaut ist wie die in Fig.3 bzw. in Fig. 2 dargestellte, ist der dem Gehäuseteil 32 des Verdichters 18 benachbarte Befestigungsring 64 einstückig mit dem Gehäuseteil 32 ausgebildet.In another embodiment, not shown, which is constructed in principle the same as in Figure 3 or in Fig. 2 shown, the housing part 32 of the compressor 18 adjacent mounting ring 64 is integrally formed with the housing part 32.

Eine weitere Ausführungsform, die schematisch in Fig. 4 dargestellt ist, zeigt eine weitere Variante der aus Fig. 2 bekannten Ausführungsform. Anstelle von schraubenförmigen Befestigungselementen 44 umfasst die Befestigungsvorrichtung 36 Befestigungselemente 44 in Form von Spannelementen 72. Daher weist das Gehäuseteil 32 des Verdichters 18 statt ersten Befestigungsöffnungen 38 einen Befestigungsflansch 70 auf. Auch die Befestigungsringe 64, 66 weisen keine Befestigungsöffnung 38 auf. Die Fixierung der Befestigungsringe 64, 66 am Gehäuseteil 32 des Verdichters 18 erfolgt statt mit schraubenförmigen Befestigungselementen 44 mit den Spannklammern 72, die über den Umfang verteilt für eine feste Verbindung zwischen den Bauteilen sorgen.Another embodiment, schematically in FIG Fig. 4 is shown, shows a further variant of Fig. 2 known embodiment. Instead of helical fastening elements 44, the fastening device 36 comprises fastening elements 44 in the form of clamping elements 72. The housing part 32 of the compressor 18 therefore has a fastening flange 70 instead of first fastening openings 38. The fastening rings 64, 66 have no attachment opening 38. The fixation of the mounting rings 64, 66 on the housing part 32 of the compressor 18 takes place instead of helical fasteners 44 with the clamping brackets 72, distributed over the circumference provide a firm connection between the components.

Bei dieser Konstruktion der Befestigungsvorrichtung 36 mit dem O-ringförmigen Schwingungsentkoppler 46 werden für die Montage zunächst der O-ringförmige Schwingungsentkoppler 46 und die Befestigungsringe 64, 66 - welche z.B. mittels Spannklammem oder mittels in sie eingebrachte Hilfslöcher und Hilfsschrauben miteinander verbunden werden können - am Filterschalldämpfer 16 vormontiert. Dann wird der Filterschalldämpfer 16 über die Befestigungsringe 64, 66 mittels der Befestigungselemente 44 mit dem Gehäuseteil 32 des Verdichters 18 und somit mit dem Turbolader 12 befestigt.In this construction of the mounting device 36 with the O-ring vibration isolator 46, for assembly, first the O-ring vibration isolator 46 and the mounting rings 64, 66 - which are e.g. can be connected to each other by means of Spannklammem or by means of introduced into them auxiliary holes and auxiliary screws - pre-assembled on the filter muffler 16. Then the filter muffler 16 is fastened via the fastening rings 64, 66 by means of the fastening elements 44 to the housing part 32 of the compressor 18 and thus to the turbocharger 12.

Bei einem wiederum etwa 380Kg schweren Filterschalldämpfer 16 und dieser Konstruktion wird eine Eigenfrequenz des Filterschalldämpfer 16 von etwa 40% des Turboladers 12 mit einer axialen Steifigkeit von 7000 N/mm bis14000 N/mm des Schwingungsentkopplers 46 und einer radialen Steifigkeit von 15000 bis 40000 N/mm des Schwingungsentkopplers 46 erreicht.With a filter muffler 16 again of about 380Kg and this design, a natural frequency of the filter muffler 16 is from about 40% of the turbocharger 12 having an axial stiffness of 7000 N / mm to 14000 N / mm of the vibration isolator 46 and a radial stiffness of 15,000 to 40,000 N / mm of the vibration isolator 46 reached.

Verschiedene weitere Variationen und Kombinationen der genannten Befestigungsvorrichtung 36 sind denkbar. So können beispielsweise Spannklammem 72 und schraubenförmige Befestigungselemente 44 kombiniert eingesetzt sein. Die zweiten Befestigungsöffnungen 42 können statt in einem Flansch 40 des Filterschalldämpfers 16 in einem andern dem Verdichtereingang 14 benachbarten Element des Filterschalldämpfer 16 angeordnet sein. Statt der ersten Befestigungsöffnungen 38 im Gehäuseteil 32 des Verdichters 18 können die zweiten Befestigungsöffnungen 42 im Filterschalldämpfer 16 mit einem Gewinde versehen sein. Die ersten Befestigungsöffnungen 38 im Gehäuseteil 32 des Verdichters 18 können in einem Flansch des Gehäuseteils 32 angeordnet sein. Die schraubenförmigen Befestigungselemente 44 können dann von der Verdichterseite her statt von der Seite des Filterschalldämpfers 16 eingeschraubt sein.Various other variations and combinations of said attachment device 36 are conceivable. For example, clamping brackets 72 and helical fastening elements 44 may be used in combination. The second attachment openings 42 may instead be arranged in a flange 40 of the filter silencer 16 in another of the compressor inlet 14 adjacent element of the filter silencer 16. Instead of the first attachment openings 38 in the housing part 32 of the compressor 18, the second attachment openings 42 may be provided in the filter muffler 16 with a thread. The first attachment openings 38 in the housing part 32 of the compressor 18 may be arranged in a flange of the housing part 32. The helical fasteners 44 may then be threaded from the compressor side rather than from the side of the filter muffler 16.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

1010
Turboladerlängsachseturbocharger longitudinal axis
1212
Turboladerturbocharger
1414
Verdichtereingangcompressor inlet
1616
Filterschalldämpferfilter silencer
1818
Verdichtercompressor
2020
Turbineturbine
2222
Verdichterlaufradcompressor impeller
2424
Turbinenlaufradturbine impeller
2626
Wellewave
2727
Verdichtergehäusecompressor housing
2828
Turboladergehäuseturbocharger housing
2929
Turbinengehäuseturbine housing
3030
Lagergehäusebearing housing
3131
Befestigungsfussmounting foot
3232
Gehäuseteilhousing part
3434
Konsoleconsole
3636
Befestigungsvorrichtungfastening device
3838
erste Befestigungsöffnungfirst attachment opening
4040
Flanschflange
4242
zweite Befestigungsöffnungsecond attachment opening
4444
Befestigungselementfastener
4646
Schwingungsentkopplervibration isolators
4747
Entkopplungselementdecoupling element
4848
Hohlzylinderhollow cylinder
5050
Elementflanschelement flange
5252
Öffnungopening
5454
Distanzbüchsespacer bushing
5656
Hohlzylinderhollow cylinder
5858
BüchsenflanschBüchsenflansch
6060
Elementelement
6262
Ringnutring groove
6464
Befestigungsringfixing ring
6666
Befestigungsringfixing ring
6767
Stützflächesupport surface
6868
Sicherungselementfuse element
7070
Befestigungsflanschmounting flange
7272
Spannklammerclamp
7474
7676
7878
8080
8282
8484
8686
8888
9090

Claims (10)

  1. Device, comprising a filter sound absorber (16) and a casing part (32) of a compressor (18) belonging to a turbocharger (12) for internal combustion engines,
    the filter sound absorber (16) being fastened releasably to the casing part of the compressor with the aid of fastening elements (44, 64, 66), characterized in that
    the device comprises a vibration uncoupler (46)designed in the form of an 0-ring, which vibration uncoupler (46) is arranged in the region of the fastening elements (44, 64, 66) between the filter sound absorber (16) and the casing part (32) of the compressor (18), so that, when the turbocharger is excited, the filter sound absorber (16) vibrates at a different frequency from the compressor casing (27), in that
    there are provided an annular groove (62), which is arranged in an element (60), adjacent to the compressor inlet (14), of the filter sound absorber (16) and which is open radially outwards, and a supporting face (67) fixed to the casing part (32) of the compressor (18) and designed as an annular groove which is open radially inwards, and in that
    the vibration uncoupler (46) is supported by the annular groove (62) of the filter sound absorber (16) and, by the supporting face (67) designed as an annular groove which is open radially inwards being formed by two fastening rings (64, 66), the radially inner sides of which run parallel to and at a radial distance from the annular groove (62), the two fastening rings (64, 66) being arranged one behind the other coaxially in the axial direction and being connected to the casing part (32) of the compressor (18) by means of fastening elements (44).
  2. Device according to the preceding claim, characterized in that the vibration uncoupler (46) provided is a wear-resistant, thermally resistant and oil-resistant elastomeric element preferably consisting of an elastomer.
  3. Device according to either of the preceding claims, characterized in that the vibration uncoupler (46) has low rigidity both in the axial direction (10) and transversely to the axial direction (10) of the turbocharger (12).
  4. Device according to one of the preceding claims, characterized in that the vibration uncoupler (46) has a rigidity such that the frequency at least of the lowest characteristic frequency of the uncoupled filter sound absorber (16) corresponds approximately to 40% of the lowest characteristic frequency of the turbocharger (12).
  5. Device according to one of the preceding claims, characterized in that a fastening ring (64) adjacent to the casing part (32) of the compressor (18), which fastening ring serves to support the vibration uncoupler (46), is formed in one piece with the casing part (32) of the compressor (18).
  6. Device according to one of the preceding claims, characterized in that a securing element (68) is provided, which, in the event of a failure of the vibration uncoupler (46), counteracts a cancellation of the connection between the filter sound absorber (16) and the casing part (32) of the compressor (18).
  7. Device according to Claim 6, characterized in that the securing element (68) is fastened to at least one fastening ring (64, 66) arranged adjacent to the casing part (32) of the compressor (18) and/or to the casing part (32) of the compressor (18) and, in the event of a failure of the vibration uncoupler (46), engages, from the side of the filter sound absorber (16), behind that element (60) of the filter sound absorber (16) which carries the annular groove (62).
  8. Device according to one of the preceding claims, characterized in that the vibration uncoupler (46) is prestressed mechanically.
  9. Device according to Claim 8, characterized in that the prestress is applied to the vibration uncoupler (46) via fastening rings (64, 66) fixed to the casing part (32) of the compressor (18), and the fastening rings (64, 66) support the vibration uncoupler (46) in the form of an 0-ring preferably at an angle of about +30° to +50° and -30° to -50° respectively.
  10. Turbocharger for charging internal combustion engines, characterized by a device according to one of the preceding claims.
EP00810814A 2000-09-08 2000-09-08 Filter silencer mounting device for turbo charger inlet Expired - Lifetime EP1186781B2 (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
EP00810814A EP1186781B2 (en) 2000-09-08 2000-09-08 Filter silencer mounting device for turbo charger inlet
DE50013694T DE50013694D1 (en) 2000-09-08 2000-09-08 Fastening device for a filter silencer at the compressor inlet of a turbocharger
TW090101395A TW576899B (en) 2000-09-08 2001-01-20 Fastening device for a filter sound absorber at a compressor inlet of a turbocharger
CNB018185827A CN1242179C (en) 2000-09-08 2001-08-21 Mounting device for filter and sound damper unit on compressor input of turbocharger
PCT/CH2001/000511 WO2002020996A1 (en) 2000-09-08 2001-08-21 Mounting device for a filter and sound damper unit on the compressor input of a turbocharger
KR1020037003374A KR100812585B1 (en) 2000-09-08 2001-08-21 A turbocharger for internal combustion and a mounting device for a filter and sound damper unit on the compressor input of the turbocharger
AU2001281644A AU2001281644A1 (en) 2000-09-08 2001-08-21 Mounting device for a filter and sound damper unit on the compressor input of a turbocharger
JP2002525376A JP4681211B2 (en) 2000-09-08 2001-08-21 Apparatus having turbocharger compressor casing part and filter sound absorber

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP00810814A EP1186781B2 (en) 2000-09-08 2000-09-08 Filter silencer mounting device for turbo charger inlet

Publications (3)

Publication Number Publication Date
EP1186781A1 EP1186781A1 (en) 2002-03-13
EP1186781B1 EP1186781B1 (en) 2006-11-02
EP1186781B2 true EP1186781B2 (en) 2012-05-30

Family

ID=8174898

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00810814A Expired - Lifetime EP1186781B2 (en) 2000-09-08 2000-09-08 Filter silencer mounting device for turbo charger inlet

Country Status (8)

Country Link
EP (1) EP1186781B2 (en)
JP (1) JP4681211B2 (en)
KR (1) KR100812585B1 (en)
CN (1) CN1242179C (en)
AU (1) AU2001281644A1 (en)
DE (1) DE50013694D1 (en)
TW (1) TW576899B (en)
WO (1) WO2002020996A1 (en)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10360770A1 (en) * 2003-12-23 2005-07-28 Abb Turbo Systems Ag muffler mounting
EP1586745B1 (en) 2004-04-13 2015-07-29 ABB Turbo Systems AG Compressor casing
EP1602803A1 (en) * 2004-06-03 2005-12-07 ABB Turbo Systems AG Vibration reduction device for combustion engine and turbocharger system
KR100659517B1 (en) * 2005-12-06 2006-12-20 양해숙 Noise reducing apparatus of compressor
JP2010501770A (en) * 2006-08-24 2010-01-21 アーベーベー ターボ システムズ アクチエンゲゼルシャフト Filter muffler mounting equipment
US8096127B2 (en) * 2007-02-09 2012-01-17 Mitsubishi Heavy Industries, Ltd. Exhaust turbo-supercharger
DE102008008886A1 (en) * 2008-02-13 2009-08-20 Man Turbo Ag Inlet nozzle for an axial compressor
EP2090756A1 (en) * 2008-02-18 2009-08-19 ABB Turbo Systems AG Fastening device for an exhaust turbocharger
KR100975121B1 (en) * 2010-01-15 2010-08-11 김기찬 A lotus flower lamp of fold type
JP6097188B2 (en) * 2013-09-25 2017-03-15 三菱重工業株式会社 Turbocharger
DE112017004638B4 (en) * 2016-09-15 2022-02-17 Ihi Corporation Method of assembling a turbocharger
DE102018212260B4 (en) * 2018-07-24 2024-10-02 Vitesco Technologies GmbH exhaust turbocharger with optimized acoustic behavior
DE102020207638A1 (en) * 2020-06-19 2021-12-23 Mahle International Gmbh Exhaust gas turbocharger arrangement with an exhaust gas turbocharger and with an actuator
CN111946501A (en) * 2020-08-06 2020-11-17 江门市大长江集团有限公司 Air filter and motorcycle

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1807288U (en) † 1959-04-29 1960-03-03 Mann & Hummel Filter INTAKE AIR FILTER FOR COMBUSTION MACHINES, COMPRESSORS AND OTHER AIR SUCTION MACHINES.
DE9210095U1 (en) † 1992-07-28 1992-09-24 Filterwerk Mann & Hummel Gmbh, 7140 Ludwigsburg Air filter
EP0514646A1 (en) † 1991-05-22 1992-11-25 Dr.Ing.h.c. F. Porsche Aktiengesellschaft Intake device for a multicylinder internal combustion engine
DE19503918A1 (en) † 1995-02-07 1996-08-08 Daimler Benz Ag Vibration-damping fastening element for holding a component, in particular an air filter of an internal combustion engine
DE19526934A1 (en) † 1995-07-24 1997-01-30 Mann & Hummel Filter Fastener

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1052164B (en) * 1953-11-10 1959-03-05 Napier & Son Ltd Method and device for cleaning an air compressor assigned to an internal combustion engine
DE3036890C2 (en) * 1980-09-30 1982-07-01 Aktiengesellschaft Kühnle, Kopp & Kausch, 6710 Frankenthal Compressors, especially for exhaust gas turbochargers
DE3131190C2 (en) * 1981-08-06 1985-01-17 Aktiengesellschaft Kühnle, Kopp & Kausch, 6710 Frankenthal Compressors, especially for exhaust gas turbochargers
JPH01113153U (en) * 1988-01-26 1989-07-31
DE4137465C2 (en) * 1991-11-14 1993-12-02 Licentia Gmbh One-sided attachment of a stator of a brushless DC motor to a housing part
DE59207544D1 (en) * 1992-06-17 1997-01-02 Asea Brown Boveri Filter silencer
JPH1054252A (en) * 1996-08-09 1998-02-24 Ishikawajima Harima Heavy Ind Co Ltd Silencer for turbo compressor
JPH1061509A (en) * 1996-08-27 1998-03-03 Mitsubishi Motors Corp Coupling structure and coupling structure of resonator
JP3814677B2 (en) * 1997-10-09 2006-08-30 トヨタ紡織株式会社 Air cleaner with resonator
JP3638005B2 (en) * 1998-11-06 2005-04-13 本田技研工業株式会社 Intake device for multi-cylinder internal combustion engine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1807288U (en) † 1959-04-29 1960-03-03 Mann & Hummel Filter INTAKE AIR FILTER FOR COMBUSTION MACHINES, COMPRESSORS AND OTHER AIR SUCTION MACHINES.
EP0514646A1 (en) † 1991-05-22 1992-11-25 Dr.Ing.h.c. F. Porsche Aktiengesellschaft Intake device for a multicylinder internal combustion engine
DE9210095U1 (en) † 1992-07-28 1992-09-24 Filterwerk Mann & Hummel Gmbh, 7140 Ludwigsburg Air filter
DE19503918A1 (en) † 1995-02-07 1996-08-08 Daimler Benz Ag Vibration-damping fastening element for holding a component, in particular an air filter of an internal combustion engine
DE19526934A1 (en) † 1995-07-24 1997-01-30 Mann & Hummel Filter Fastener

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JP4681211B2 (en) 2011-05-11
TW576899B (en) 2004-02-21
DE50013694D1 (en) 2006-12-14
KR100812585B1 (en) 2008-03-13
CN1242179C (en) 2006-02-15
WO2002020996A1 (en) 2002-03-14
CN1473245A (en) 2004-02-04
EP1186781B1 (en) 2006-11-02
KR20030032013A (en) 2003-04-23
EP1186781A1 (en) 2002-03-13
JP2004507668A (en) 2004-03-11
AU2001281644A1 (en) 2002-03-22

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