EP1186781B1 - Dispositif de montage d'un filtre silencieux pour l'entrée d'une turbo-soufflante - Google Patents

Dispositif de montage d'un filtre silencieux pour l'entrée d'une turbo-soufflante Download PDF

Info

Publication number
EP1186781B1
EP1186781B1 EP00810814A EP00810814A EP1186781B1 EP 1186781 B1 EP1186781 B1 EP 1186781B1 EP 00810814 A EP00810814 A EP 00810814A EP 00810814 A EP00810814 A EP 00810814A EP 1186781 B1 EP1186781 B1 EP 1186781B1
Authority
EP
European Patent Office
Prior art keywords
fastening
vibration
compressor
uncoupler
sound absorber
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)
English (en)
Other versions
EP1186781B2 (fr
EP1186781A1 (fr
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.)
Filing date
Publication date
Family has litigation
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(B1) "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/fr
Priority to DE50013694T priority patent/DE50013694D1/de
Priority to TW090101395A priority patent/TW576899B/zh
Priority to CNB018185827A priority patent/CN1242179C/zh
Priority to AU2001281644A priority patent/AU2001281644A1/en
Priority to PCT/CH2001/000511 priority patent/WO2002020996A1/fr
Priority to JP2002525376A priority patent/JP4681211B2/ja
Priority to KR1020037003374A priority patent/KR100812585B1/ko
Publication of EP1186781A1 publication Critical patent/EP1186781A1/fr
Publication of EP1186781B1 publication Critical patent/EP1186781B1/fr
Application granted granted Critical
Publication of EP1186781B2 publication Critical patent/EP1186781B2/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F04D29/70—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
    • 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
    • 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 securing a filter silencer to a housing part of a compressor belonging to a turbocharger for internal combustion engines according to the preamble of claim 1.
  • a turbocharger is disclosed in EP 0 574 605 A1.
  • 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 a 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 become.
  • 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 part of a filter silencer 16 attached to the compressor inlet 14 of the turbocharger 12.
  • the turbocharger 12 has a typical construction, ie it comprises a compressor 18 and a turbine 20 whose wheels 22, 24 are arranged on a common shaft 26 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.
  • 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 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.
  • the fastening device 36 shown in FIG. 2 also comprises second fastening openings 42 which are arranged congruently with the first fastening openings 38 in a flange 40 of the filter silencer 16.
  • the inner diameter of such a second attachment opening 42 is greater than that of the first attachment opening 38.
  • the vibration isolator 46 has two decoupling elements 47 made of an elastomer whose basic shape is a hollow cylinder 48, at one end of which a radially outwardly projecting element flange 50 is provided.
  • the outer diameter of the hollow cylinder 48 is approximately equal to the inner diameter of the second mounting hole 42.
  • the hollow cylinder 48 of the decoupling 47 are inserted from opposite sides into the second mounting hole 42 so that their element flanges 50 laterally project beyond the edges of the mounting hole 42 and a portion of the flange Cover 40.
  • the length of the hollow cylinder 48 is preferably selected so that touch their flangeless end faces when the element flanges 50 with the edges of the second mounting hole 42 into abutment.
  • the decoupling elements 47 are preferably formed the same, which simplifies the production. However, they can be designed differently, in particular with regard to the configuration of the element flange 50, if the shape of the second fastening openings 42 and / or of the flange 40 so requires.
  • the hollow cylinder 48 together form an opening 52 in the vibration isolator 46 for receiving the fastener 44.
  • a spacer bushing 54 is received in the opening 52 whose basic shape is again a hollow cylinder, at one end radially outwardly projecting sleeve flange 58 is provided.
  • the hollow cylinder 56 of the spacer bushing 54, the fastening element 44 is arranged encompassing in the opening 52.
  • the bush flange 58 is in abutment with the silencer-side element flange 50.
  • the decoupling elements 47 are inserted into the second fastening openings 42 of the flange 40 of the filter silencer 16.
  • the spacer bush 54 is inserted into the opening 52 formed by the decoupling elements 47.
  • the second attachment openings 42 and the first attachment openings 38 are brought into coincidence with each other and screwed together by means of the helical fastening elements 44.
  • the length of the hollow cylinder 58 of the spacer bushing 54 is shorter than the depth of the opening 52; ie: If the spacer bushing 54 inserted into the opening 52 is in abutment with its bushing flange with the silencer-side element flange 50 of the decoupling element 47, a gap remains between the flange-free end face of the hollow cylinder 58 and the edge of the first fastening opening 38. By tightening the screw 44, the spacer sleeve 54 is brought to the edge of the first mounting hole 38 to the stop and the decoupling elements 47 compressed.
  • the decoupling elements 47 are under a defined bias. This leaves under load produced by the fastening device 36 connection between the filter silencer 16 and the housing part 32 of the compressor 18 the various components always in contact with the vibration isolator 46 and this is protected from unequal loads.
  • the fastening device 36 shown in FIG. 3 comprises, in addition to the above-mentioned elements, an O-ring vibration isolator 46, a radially outwardly open annular groove 62 arranged in an element 60 of the filter silencer 16 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 further embodiment is shown, which is constructed analogously to that shown in Figure 3.
  • 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 inwardly and outwardly beyond the attachment rings 64, 66. 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 Ringsegment Swissen.
  • the housing part 32 of the compressor 18 adjacent mounting ring 64 is integrally formed with the housing part 32.
  • 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 fastening device 36 with the O-ring vibration isolator 46 are initially for mounting the O-ring Vibration decoupler 46 and the mounting rings 64, 66 - which can be connected to each other for example 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.

Landscapes

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

Claims (14)

  1. Dispositif comprenant un silencieux de filtre (16) ainsi qu'une partie de boîtier (32) d'un compresseur (18) appartenant à une turbosoufflante (12) pour moteurs à combustion interne, dans lequel le silencieux de filtre (16) est fixé à l'aide d'éléments de fixation (44, 64, 66) de manière desserrable sur la partie de boîtier du compresseur, caractérisé en ce que le dispositif présente un découpleur de vibrations (46) et en ce que le découpleur de vibrations (46) est disposé dans la région des éléments de fixation (44, 64, 66) entre le silencieux de filtre (16) et la partie de boîtier (32) du compresseur (18), de sorte que dans le cas d'une excitation de la turbosoufflante, le silencieux de filtre (16) vibre avec une autre fréquence que le boîtier du compresseur (27).
  2. Dispositif selon la revendication 1, caractérisé en ce que l'on prévoit comme découpleur de vibrations (46) un élément en caoutchouc élastique de préférence constitué d'un élastomère, résistant à l'usure et résistant à la température et à l'huile.
  3. Dispositif selon la revendication 1 ou 2, caractérisé en ce que le découpleur de vibrations (46) présente une faible rigidité à la fois dans la direction axiale (10) et transversalement à la direction axiale (10) de la turbosoufflante (12).
  4. Dispositif selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le découpleur de vibrations (46) présente une rigidité telle que la fréquence d'au moins la fréquence propre la plus basse du silencieux de filtre découplé (16) corresponde environ à 40% de la fréquence propre la plus basse de la turbosoufflante (12).
  5. Dispositif selon l'une quelconque des revendications précédentes, caractérisé en ce que le découpleur de vibrations (46) est précontraint mécaniquement.
  6. Dispositif selon l'une quelconque des revendications précédentes, caractérisé en ce que l'on prévoit dans le silencieux de filtre (16) et dans la partie de boîtier (32) du compresseur (18) des ouvertures de fixation se correspondant mutuellement (38, 42) pour recevoir un élément de fixation (44), un découpleur de vibrations (46) respectif pouvant être inséré dans les ouvertures de fixation (42) du silencieux de filtre (16), lequel présente pour sa part une ouverture (52) pour recevoir l'élément de fixation (44).
  7. Dispositif selon la revendication 5 ou 6, caractérisé en ce que le découpleur de vibrations (46) comprend deux éléments de découplage (47) de préférence réalisés de manière identique, dont la forme de base est un cylindre creux (56) avec une bride d'élément (50) de préférence en forme de disque circulaire, saillant à une extrémité du cylindre creux (56) depuis celui-ci, les cylindres creux (56) pouvant être insérés depuis des directions opposées dans la deuxième ouverture de fixation (42) du silencieux de filtre (16) et formant conjointement l'ouverture (52) pour recevoir l'élément de fixation (44), et les brides d'élément (50) saillant latéralement au-delà des bords de l'ouverture de fixation (42) de sorte qu'elles forment un tampon entre le silencieux de filtre (16) et la tête de l'élément de fixation (44) ou entre le silencieux de filtre (16) et la partie de boîtier (32) du compresseur (18).
  8. Dispositif selon les revendications 5 et 6 ou les revendications 5, 6 et 7, caractérisé en ce que la précontrainte est appliquée de manière définie sur le découpleur de vibrations (46) au moyen d'une douille d'espacement (54) qui peut être insérée dans l'ouverture (52) du découpleur de vibrations (46).
  9. Dispositif selon l'une quelconque des revendications 1 à 5, caractérisé en ce qu'une rainure annulaire (62) ouverte radialement vers l'extérieur, disposée dans un élément (60) du silencieux de filtre (16) adjacent à l'entrée du compresseur (14), ainsi que deux bagues de fixation (64, 66) sont prévues, dont les côtés radialement internes s'étendent de manière espacée radialement depuis la rainure annulaire (62) parallèlement à celle-ci, et en ce que le découpleur de vibrations (46) est réalisé sous forme de joint torique qui est supporté d'une part par la rainure annulaire (62) du silencieux de filtre (16) et d'autre part par les deux bagues de fixation (64, 66), les deux bagues de fixation (64, 66) étant disposées l'une derrière l'autre coaxialement dans la direction axiale et étant connectées au moyen d'éléments de fixation (44) à la partie de boîtier (32) du compresseur (18).
  10. Dispositif selon les revendications 5 et 9, caractérisé en ce que la précontrainte est appliquée par le biais des bagues de fixation (64, 66) sur le découpleur de vibrations (46) et les bagues de fixation (64, 66) supportent le découpleur de vibrations en forme de joint torique (46) de préférence suivant un angle d'environ +30° à +50° ou de -30° à -50°.
  11. Dispositif selon la revendication 9 ou 10, caractérisé en ce que la bague de fixation (64) voisine de la partie de boîtier (32) du compresseur (18) est réalisé d'une seule pièce avec celui-ci.
  12. Dispositif selon l'une quelconque des revendications 9 à 11, caractérisé en ce qu'il est prévu un élément de fixation (68) qui, lors d'un défaillance du découpleur de vibrations (46) s'oppose à un desserrage de la connexion entre le silencieux de filtre (16) et la partie de boîtier (32) du compresseur (18).
  13. Dispositif selon la revendication 12, caractérisé en ce que l'élément de fixation (68) est fixé sur au moins l'une parmi les bagues de fixation (64, 66) et/ou la partie de boîtier (32) du compresseur (18) et en cas de défaillance du découpleur de vibrations (46) vient en prise depuis le côté du silencieux de filtre (16) avec l'élément (60) du silencieux de filtre (16) portant la rainure annulaire (62).
  14. Turbosoufflante pour suralimenter des moteurs à combustion interne, caractérisée par un dispositif selon l'une quelconque des revendications précédentes.
EP00810814A 2000-09-08 2000-09-08 Dispositif de montage d'un filtre silencieux pour l'entrée d'une turbo-soufflante Expired - Lifetime EP1186781B2 (fr)

Priority Applications (8)

Application Number Priority Date Filing Date Title
EP00810814A EP1186781B2 (fr) 2000-09-08 2000-09-08 Dispositif de montage d'un filtre silencieux pour l'entrée d'une turbo-soufflante
DE50013694T DE50013694D1 (de) 2000-09-08 2000-09-08 Befestigungsvorrichtung für einen Filterschalldämpfer am Verdichtereingang eines Turboladers
TW090101395A TW576899B (en) 2000-09-08 2001-01-20 Fastening device for a filter sound absorber at a compressor inlet of a turbocharger
JP2002525376A JP4681211B2 (ja) 2000-09-08 2001-08-21 ターボチャージャの圧縮機のケーシング部分並びにフィルタ吸音器を有する装置
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
PCT/CH2001/000511 WO2002020996A1 (fr) 2000-09-08 2001-08-21 Dispositif de fixation destine a un silencieux a filtre se trouvant a l'entree du compresseur d'un turbocompresseur
CNB018185827A CN1242179C (zh) 2000-09-08 2001-08-21 在涡轮增压器的压缩机入口上的过滤消声器的固定装置
KR1020037003374A KR100812585B1 (ko) 2000-09-08 2001-08-21 내연 기관용 터보차저 및 터보차저의 압축기 입구에서의 필터 흡음기용 고정 장치

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP00810814A EP1186781B2 (fr) 2000-09-08 2000-09-08 Dispositif de montage d'un filtre silencieux pour l'entrée d'une turbo-soufflante

Publications (3)

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

Family

ID=8174898

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00810814A Expired - Lifetime EP1186781B2 (fr) 2000-09-08 2000-09-08 Dispositif de montage d'un filtre silencieux pour l'entrée d'une turbo-soufflante

Country Status (8)

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

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10360770A1 (de) * 2003-12-23 2005-07-28 Abb Turbo Systems Ag Schalldämpferbefestigung
EP1586745B1 (fr) * 2004-04-13 2015-07-29 ABB Turbo Systems AG Carter de compresseur
EP1602803A1 (fr) * 2004-06-03 2005-12-07 ABB Turbo Systems AG Agencement de réduction de vibrations d'un système de moteur à combustion et turbocompresseur
KR100659517B1 (ko) * 2005-12-06 2006-12-20 양해숙 압축기의 소음저감장치
EP2054630B1 (fr) * 2006-08-24 2011-10-19 ABB Turbo Systems AG Fixation de silencieux-filtre
KR101052447B1 (ko) * 2007-02-09 2011-07-28 미츠비시 쥬고교 가부시키가이샤 배기 터빈 과급기
DE102008008886A1 (de) * 2008-02-13 2009-08-20 Man Turbo Ag Eintrittsstutzen für einen Axialverdichter
EP2090756A1 (fr) * 2008-02-18 2009-08-19 ABB Turbo Systems AG Dispositif de fixation pour une turbocompresseur de gaz d'échappement
KR100975121B1 (ko) * 2010-01-15 2010-08-11 김기찬 접이식 연등
JP6097188B2 (ja) * 2013-09-25 2017-03-15 三菱重工業株式会社 過給機
CN111878222A (zh) * 2016-09-15 2020-11-03 株式会社Ihi 增压器
DE102018212260A1 (de) * 2018-07-24 2020-01-30 Continental Automotive Gmbh Abgasturbolader mit optimiertem akustischen Verhalten
DE102020207638A1 (de) * 2020-06-19 2021-12-23 Mahle International Gmbh Abgasturbolader-Anordnung mit einem Abgasturbolader und mit einem Aktuator

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1052164B (de) * 1953-11-10 1959-03-05 Napier & Son Ltd Verfahren und Vorrichtung zum Reinigen eines einer Brennkraftmaschine zugeordneten Luftverdichters
DE1807288U (de) † 1959-04-29 1960-03-03 Mann & Hummel Filter Ansaugluftfilter fuer brennkraftmaschinen, kompressoren und sonstige luftansaugende maschinen.
DE3131190C2 (de) * 1981-08-06 1985-01-17 Aktiengesellschaft Kühnle, Kopp & Kausch, 6710 Frankenthal Verdichter, insbesondere für Abgasturbolader
DE3036890C2 (de) * 1980-09-30 1982-07-01 Aktiengesellschaft Kühnle, Kopp & Kausch, 6710 Frankenthal Verdichter, insbesondere für Abgasturbolader
JPH01113153U (fr) * 1988-01-26 1989-07-31
DE4116653A1 (de) † 1991-05-22 1992-11-26 Porsche Ag Ansauganlage fuer eine mehrzylindrige brennkraftmaschine
DE4137465C2 (de) * 1991-11-14 1993-12-02 Licentia Gmbh Einseitige Befestigung eines Stators eines bürstenlosen Gleichstrommotors an einem Gehäuseteil
DE59207544D1 (de) * 1992-06-17 1997-01-02 Asea Brown Boveri Filterschalldämpfer
DE9210095U1 (fr) † 1992-07-28 1992-09-24 Filterwerk Mann & Hummel Gmbh, 7140 Ludwigsburg, De
DE19503918C2 (de) † 1995-02-07 2001-10-11 Daimler Chrysler Ag Schwingungsdämpfendes Befestigungselement zur Halterung eines Bauteiles, insbesondere eines Luftfilters einer Brennkraftmaschine
DE19526934A1 (de) † 1995-07-24 1997-01-30 Mann & Hummel Filter Befestigungselement
JPH1054252A (ja) * 1996-08-09 1998-02-24 Ishikawajima Harima Heavy Ind Co Ltd ターボ圧縮機用消音器
JPH1061509A (ja) * 1996-08-27 1998-03-03 Mitsubishi Motors Corp 結合構造及びレゾネータの結合構造
JP3814677B2 (ja) * 1997-10-09 2006-08-30 トヨタ紡織株式会社 レゾネータ付きエアクリーナ
JP3638005B2 (ja) * 1998-11-06 2005-04-13 本田技研工業株式会社 多気筒内燃機関の吸気装置

Also Published As

Publication number Publication date
EP1186781B2 (fr) 2012-05-30
JP2004507668A (ja) 2004-03-11
AU2001281644A1 (en) 2002-03-22
EP1186781A1 (fr) 2002-03-13
CN1242179C (zh) 2006-02-15
WO2002020996A1 (fr) 2002-03-14
KR20030032013A (ko) 2003-04-23
KR100812585B1 (ko) 2008-03-13
TW576899B (en) 2004-02-21
CN1473245A (zh) 2004-02-04
JP4681211B2 (ja) 2011-05-11
DE50013694D1 (de) 2006-12-14

Similar Documents

Publication Publication Date Title
EP1186781B1 (fr) Dispositif de montage d'un filtre silencieux pour l'entrée d'une turbo-soufflante
DE3134310C2 (de) "Einrichtung zur Dämpfung von Schwingungen im Antriebsstrang eines Kraftfahrzeuges"
EP0286883B1 (fr) Ensemble de paliers pour suralimentateur
EP3017146A1 (fr) Rotor pour dispositif turbocompresseur, dispositif turbocompresseur équipé d'un rotor et arbre pour un tel rotor
DE102016118245A1 (de) Zahnradanordnung
EP3063428B1 (fr) Palier
DE102015222203A1 (de) Spielfreie Pendellagerung am Entkopplungsspanner
DE102012105549A1 (de) Planetengetriebe hohlradaufhängung
EP3199758A1 (fr) Rotor dans une turbine à gaz de type blisk (disque a aubes) ou bling (bague à aubes)
EP0716222A1 (fr) Agencement de soupape de gaz d'échappement
EP3456999A1 (fr) Dispositif formant engrenage planétaire pour une turbomachine
DE102010052892A1 (de) Lageranordnung für eine Welle eines Turbinenrades
DE102012002806A1 (de) Federbein und Gehäuse eines Federbeins
DE102015217911A1 (de) Kolben für eine Brennkraftmaschine
EP1598525A1 (fr) Structure de support d'un turbocompresseur
EP0681117A1 (fr) Dispositif de support
DE102018115429A1 (de) Unwuchtwelle
DE102013202690B4 (de) Drehschwingungsdämpfer
DE102022101762A1 (de) Rotor mit einem Wuchtflansch, Rotoranordnung mit zumindest einem Rotor und Strömungsmaschine mit zumindest einem Rotor oder mit einer Rotoranordnung
EP0926388B1 (fr) Amortisseur de vibrations torsionelles
DE102005005770B4 (de) Frequenzvariabler Tilger, insbesondere für eine Anwendung in Flugzeugen
DE102011079617A1 (de) Schraubverbindung
DE10042214A1 (de) Kolbenkompressor mit einem dynamischen Massenausgleich im Bereich der Kurbeltriebe, insbesondere für Schienenfahrzeuge (Ausgleichspleuel)
EP0985838B1 (fr) Palier et méthode pour sa fabrication
DE19649580A1 (de) Entkopplungselement

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): DE FR GB

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 20020819

AKX Designation fees paid

Free format text: DE FR GB

17Q First examination report despatched

Effective date: 20050513

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RTI1 Title (correction)

Free format text: FILTER SILENCER MOUNTING DEVICE FOR TURBO CHARGER INLET

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): DE FR GB

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 50013694

Country of ref document: DE

Date of ref document: 20061214

Kind code of ref document: P

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20070129

ET Fr: translation filed
PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

26 Opposition filed

Opponent name: MAN DIESEL SE

Effective date: 20070801

PLAX Notice of opposition and request to file observation + time limit sent

Free format text: ORIGINAL CODE: EPIDOSNOBS2

PLAF Information modified related to communication of a notice of opposition and request to file observations + time limit

Free format text: ORIGINAL CODE: EPIDOSCOBS2

PLBB Reply of patent proprietor to notice(s) of opposition received

Free format text: ORIGINAL CODE: EPIDOSNOBS3

PLAB Opposition data, opponent's data or that of the opponent's representative modified

Free format text: ORIGINAL CODE: 0009299OPPO

R26 Opposition filed (corrected)

Opponent name: MAN DIESEL & TURBO SE

Effective date: 20070801

PUAH Patent maintained in amended form

Free format text: ORIGINAL CODE: 0009272

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: PATENT MAINTAINED AS AMENDED

27A Patent maintained in amended form

Effective date: 20120530

AK Designated contracting states

Kind code of ref document: B2

Designated state(s): DE FR GB

REG Reference to a national code

Ref country code: DE

Ref legal event code: R102

Ref document number: 50013694

Country of ref document: DE

Effective date: 20120530

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 16

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 17

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 18

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20190918

Year of fee payment: 20

Ref country code: FR

Payment date: 20190925

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20190920

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 50013694

Country of ref document: DE

Owner name: ABB SCHWEIZ AG, CH

Free format text: FORMER OWNER: ABB TURBO SYSTEMS AG, BADEN, CH

Ref country code: DE

Ref legal event code: R082

Ref document number: 50013694

Country of ref document: DE

Representative=s name: ZIMMERMANN & PARTNER PATENTANWAELTE MBB, DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 50013694

Country of ref document: DE

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20200907

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

Free format text: REGISTERED BETWEEN 20200924 AND 20200930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20200907