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 fastening a filter muffler to a housing part of a compressor belonging to a turbocharger for internal combustion engines according to the preamble of patent claim 1.
• a filter silencer is usually arranged at the compressor inlet, which reduces these noise emissions. Since the filter silencer is rigidly connected to a housing part of the compressor and this is not uncoupled from the turbocharger in terms of vibration, the vibrations of the turbocharger are transmitted to the filter silencer. For its part, the turbocharger is usually fastened either directly or via a fastening foot to a console of an internal combustion engine. The axial distance between the mounting foot and the filter silencer is usually very large. If the turbocharger is excited by engine vibrations and / or is subjected to natural frequency vibrations, the vibration amplitude is greatest due to the geometry of the filter silencer. This is undesirable, among other things, because of the resulting large material load. In countries with corresponding regulations, this vibration problem can lead to rejection of the technical approval. Presentation of the invention
• the fastening device has a vibration isolator for connecting a filter muffler to a housing part of a compressor at the compressor inlet between the filter muffler and the housing part of the compressor.
• the filter silencer is largely separated from the compressor housing part and thus from the turbocharger.
• the vibration decoupler is optimally adapted to the operating conditions, which ensures a long service life of the vibration decoupler. It has been shown that from one. Elastomeric elements (such as those made of Viton ® by du Pont or made of silicone) are very suitable as vibration isolators.
• the vibration decoupler When viewed in the installed state, the vibration decoupler advantageously has low rigidity in the axial direction and transversely to the axial direction of the
• Turbocharger Depending on the six natural frequencies of the turbocharger, the stiffnesses in the axial direction and transverse to the axial direction can be selected differently become. The low rigidity ensures adequate vibration isolation between the filter silencer and the housing part of the compressor.
• the vibration isolator is chosen to be as soft as possible. At least the stiffness is selected such that, taking into account the weight of the components and their geometry and taking into account the geometry of the connection between the filter silencer and the housing part of the compressor, the filter silencer finally has a natural frequency of approximately 25% to 50%, preferably 40% at least has the lowest of the natural frequencies of the turbocharger.
• the filter silencer When the turbocharger is excited in the natural frequency range, for example by engine vibrations, the filter silencer then vibrates in the supercritical range.
• the vibration decoupler is pretensioned. In this way, it can be prevented that the contact between the vibration decoupler and a component is lost and abrasion and wear occur on the vibration decoupler.
• the formation of the vibration decoupler in the form of an O-ring is particularly advantageous, since in this embodiment the forces to be absorbed by the connection are distributed over the entire circumference of the O-ring.
• Fig. 1 in section along the turbocharger axis, a turbocharger with a
• FIG. 3 in an analogous representation as in Figure 2 part of a second
• FIG. 4 shows the fastening device from FIG. 3 with a securing element
• FIG. 5 in an analogous representation as in Figure 2 part of a third
• FIG. 1 shows, in section with its longitudinal axis 10, a turbocharger 12 and part of a filter muffler 16 attached to the compressor inlet 14 of the turbocharger 12.
• the turbocharger 12 has a typical structure, ie it comprises a compressor 18 and a turbine 20 whose impellers 22, 24 are spaced apart on a common shaft 26.
• 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 can themselves consist of a plurality of housing parts.
• the shaft 26 is supported in the bearing housing 30 between the turbine impeller 24 and the compressor impeller 22.
• the turbocharger 12 is fastened on a bracket 34 of the engine (not shown) by means of a fastening foot 31.
• the filter silencer 16 is attached 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 rigidly connected to one another via a fastening device 36.
• the fastening device 36 comprises first fastening openings 38 which are arranged on a circular line around the turbocharger axis 10 and which are in the housing part 32 of the compressor 18
• the first fastening openings 38 are provided with a thread. Furthermore, the fastening device 36 comprises second fastening openings 42 arranged in a flange 40 of the filter muffler 16, which can be coaxially aligned with the first fastening openings 38. Fastening elements 44, which are shown in FIG.
• FIG. 1 ' the distance between the fastening foot 31 and the filter silencer 16 is quite large. Vibrations which are transmitted from the engine (not shown) to the turbocharger 12 via the bracket 34 and the fastening foot 31 and natural vibrations of the turbocharger 12 are transmitted to the filter silencer 16 via the rigid fastening device 36. Due to the large distance between the mounting foot 31 and the filter silencer 16, the 30 vibration amplitude at the filter silencer 16 is greatest. Which brings the disadvantages already mentioned.
• FIGS. 2 to 4 each show a fastening device 36 according to the invention.
• Each of these fastening devices 36 comprises, in the housing part 32 of the compressor 18, first fastening openings 38 with a thread and fastening elements 44 in the form of screws which are screwed into the first fastening openings 38.
• the fastening opening 38 are preferably arranged in a plane that is perpendicular to the turbocharger axis 10, on a ring around the turbocharger axis 10. The direction in which the turbocharger axis (10) lies is identified by an arrow a.
• the ring is ideally a circular ring and the fastening openings 38 are evenly distributed on the ring.
• the fastening device 36 according to the invention comprises a vibration decoupler 46, which is arranged between the filter silencer 16 and the housing part 32 of the compressor 18.
• the vibration decoupler 46 is made of an elastomer which has low rigidity in the axial direction and transverse to the axial direction of the turbocharger 12.
• the stiffness is selected such that the natural frequencies of the filter silencer 16 are around 40% of at least the lowest of the natural frequencies of the turbocharger 12.
• the rigidity depends, among other things, on the geometry of the components and their weight, and on the design of the fastening device 36.
• the fastening device 36 shown in FIG. 2 also includes second fastening openings 42, which are arranged in a flange 40 of the filter muffler 16 in a congruent manner with the first fastening openings 38.
• the inner diameter of such a second fastening opening 42 is larger than that of the first fastening opening 38.
• the vibration decoupler 46 has two decoupling elements 47 made of an elastomer, the basic shape of which 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 fastening opening 42.
• the hollow cylinders 48 of the decoupling elements 47 are inserted into the second fastening opening 42 from opposite sides, so that their element flanges 50 protrude laterally beyond the edges of the fastening opening 42 and part of the flange Cover 40.
• the length of the hollow cylinder 48 is preferably selected so that its flangeless end faces touch when the element flanges 50 stop with the edges of the second fastening opening 42.
• the decoupling elements 47 are preferably of identical design, which simplifies production. However, they can be designed differently, especially with regard to the configuration of the element flange 50, if the shape of the second 5 fastening openings 42 and / or the flange 40 so require.
• the hollow cylinders 48 together form an opening 52 in the vibration decoupler 46 for receiving the fastening element 44.
• a spacer sleeve 54 is accommodated in the opening 52, the basic shape of which is in turn a hollow cylinder, with one of them At the end of a radially outwardly projecting sleeve flange 58 is provided.
• the hollow cylinder 56 of the spacer sleeve 54 is arranged around the fastening element 44 in the opening 52.
• the sleeve flange 58 is in abutment with the element flange 50 on the muffler side.
• the decoupling elements 47 are first inserted into the second fastening openings 42 of the flange 40 of the filter silencer 16.
• the spacer sleeve 54 is inserted into the opening 52 formed by the decoupling elements 47. Then the second fastening openings 42 and the first fastening openings 38 are brought into coincidence with one another and are screw-guided.
• the length of the hollow cylinder 58 of the spacer sleeve 54 is shorter than the depth of the opening 52-, ie: If the spacer sleeve 54 inserted into the opening 52 with its sleeve flange is in abutment with the silencer-side element flange 50 of the decoupling element 47, there remains between the flangeless end face of the hollow cylinder 58 and
• the spacer sleeve 54 is brought to a stop with the edge of the first fastening opening 38 and the decoupling elements 47 are pressed together.
• the decoupling elements 47 are under a defined prestress, so that the load produced by the fastening device 36 remains under load.
• the fastening device 36 shown in FIG. 3 includes, in addition to the above-mentioned elements, an O-ring-shaped vibration decoupler 46, an annular groove 62, which is arranged in an element 60 of the filter muffler 16 and is open radially outwards to support the vibration decoupler 46, and two fastening rings 64, 66.
• the two fastening rings 64, 66, with the first fastening openings 38 in the housing part 32 of the compressor 18, have holes 68 which can be brought into coaxial alignment to accommodate the fastening elements 44. They are arranged coaxially to one another and one behind the other in the axial direction, adjoining the housing part 32 of the compressor 18.
• the fastening rings 64, 66 are fixed on the housing part 32 of the compressor 18 via the helical fastening elements 44.
• the fastening rings 64, 66 On its radially inner side, the fastening rings 64, 66 have support surfaces 67 which support the O-ring 46 at an angle of approximately + 30 ° to + 50 ° or -30 ° to -50 °.
• the support surfaces 67 together again form a kind of annular groove, which is open radially towards the inside and runs at a distance from the annular groove 62 in the element 60 parallel to the latter.
• the diameter on the radially inner side of the fastening rings 64, 66 and the diameter of the annular groove 62 in the element 60 of the filter muffler 16 are selected such that the O-ring-shaped vibration isolator 46 arranged between them is pretensioned in the fastened state.
• a natural frequency of the filter silencer 16 of approximately 40% of the Turbocharger 12 achieved with an axial rigidity of 7000 N / mm to 14000 N / mm and a radial rigidity of 15000 to 40,000 N / mm.
• a securing element 68 also belongs to the fastening device 36.
• the securing element 68 is arranged axially adjoining the fastening ring 66 adjacent to the filter silencer 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 and outwards beyond the fastening rings 64, 66; if the O-ring fails, it engages behind the element 60 of the filter silencer 16 which supports the annular groove 62 and thus prevents the connection between the filter silencer 16 and 16 from being broken Housing part 32 of the compressor 18.
• the securing element like the fastening ring 64, 66, can be configured in a ring shape or, as in the example shown, can consist of ring segment pieces.
• the fastening ring 64 adjacent to the housing part 32 of the compressor 18 is formed in one piece with the housing part 32.
• FIG. 5 shows a further variant of the embodiment known from FIG. 3.
• the fastening device 36 comprises fastening elements 44 in the form of tensioning 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 also have no fastening opening 38.
• the fixing rings 64, 66 are fixed to the housing part 32 of the compressor 18 instead of using screw-shaped fastening elements 44 with the clamping clips 72, which ensure a firm connection between the components distributed over the circumference.
• the O-ring-shaped are first used for assembly Vibration decoupler 46 and the mounting rings 64, 66 - which can be connected to one another, for example, by means of tension clamps or by means of auxiliary holes and auxiliary screws introduced into them - are pre-assembled on the filter silencer 16. Then the filter silencer 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.
• clamps 72 and helical fasteners 44 can be used in combination.
• the second fastening openings 42 can be arranged in another element of the filter silencer 16 adjacent to the compressor inlet 14.
• the first fastening openings 38 in the housing part 32 of the compressor 18 can be provided with a thread.
• the first fastening openings 38 in the housing part 32 of the compressor 18 can be arranged in a flange of the housing part 32.
• the screw-shaped fastening elements 44 can then be screwed in from the compressor side instead of from the side of the filter silencer 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)

Priority Applications (3)

Applications Claiming Priority (2)

Publications (1)

Family

ID=8174898

Family Applications (1)

Country Status (8)

Cited By (2)

Families Citing this family (11)

Citations (5)

Family Cites Families (10)

• 2000
  • 2000-09-08 DE DE50013694T patent/DE50013694D1/de not_active Expired - Lifetime
  • 2000-09-08 EP EP00810814A patent/EP1186781B2/de not_active Expired - Lifetime
• 2001
  • 2001-01-20 TW TW090101395A patent/TW576899B/zh not_active IP Right Cessation
  • 2001-08-21 WO PCT/CH2001/000511 patent/WO2002020996A1/de active Application Filing
  • 2001-08-21 JP JP2002525376A patent/JP4681211B2/ja not_active Expired - Lifetime
  • 2001-08-21 CN CNB018185827A patent/CN1242179C/zh not_active Expired - Lifetime
  • 2001-08-21 AU AU2001281644A patent/AU2001281644A1/en not_active Abandoned
  • 2001-08-21 KR KR1020037003374A patent/KR100812585B1/ko active IP Right Grant

Patent Citations (5)

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