EP3412916B1 - Kreiselverdichter, turbolader und verfahren zur herstellung des kreiselverdichters - Google Patents

Kreiselverdichter, turbolader und verfahren zur herstellung des kreiselverdichters Download PDF

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Publication number
EP3412916B1
EP3412916B1 EP18185764.0A EP18185764A EP3412916B1 EP 3412916 B1 EP3412916 B1 EP 3412916B1 EP 18185764 A EP18185764 A EP 18185764A EP 3412916 B1 EP3412916 B1 EP 3412916B1
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EP
European Patent Office
Prior art keywords
axial line
flange section
casing
section
centrifugal compressor
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Application number
EP18185764.0A
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English (en)
French (fr)
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EP3412916A1 (de
Inventor
Hiroyuki Arakawa
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Publication of EP3412916A1 publication Critical patent/EP3412916A1/de
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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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • 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
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet
    • 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
    • F05D2260/00—Function
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/31—Retaining bolts or nuts

Definitions

  • the present invention relates to a centrifugal compressor and a supercharger.
  • centrifugal compressors are known (refer to Japanese Unexamined Patent Application, Publication No. 2011-117417 , for example).
  • the centrifugal compressor includes an impeller mounted on a rotor shaft, an inlet casing that houses the impeller, and a scroll section into which compressed air discharged from the inlet casing flows. While compressing air flowing in from an intake in the direction of an axial line, the centrifugal compressor guides the compressed air in the direction inclined from the direction of the axial line to discharge the compressed air from a discharge port.
  • Patent Literature 2 discloses a centrifugal compressor provided with an impact absorbing partition wall that protects a tank housing lubricant such that the lubricant does not leak due to a scattered impeller even in a case where one part of the impeller (compressor impeller) is scattered outward by centrifugal force.
  • the present invention has been made in view of the above circumstances, and an object of the present invention is to provide a centrifugal compressor capable of suppressing faults such as scattering of all or one part of an impeller to the outside in a case where all or one part of an inlet casing scatters with fracture or falling of the all or the one part of the impeller.
  • an object of the present invention is to provide a supercharger including the above centrifugal compressor.
  • a centrifugal compressor includes: an impeller that is mounted on a rotor shaft, and compresses fluid flowing in from an intake, and then discharges the compressed fluid from a discharge port; an inlet casing that houses the impeller; a scroll section that is disposed on an outer peripheral side with respect to the inlet casing, and has a scroll casing for forming a volute chamber into which the compressed fluid discharged from the discharge port flows; a bearing pedestal having a bearing section for supporting the rotor shaft, and a flange section for supporting the scroll section; a plurality of flange section fastening bolts that fasten the flange section to the scroll casing at a plurality of fastening positions around the axial line of the rotor shaft, and extend in the direction of the axial line; and a plurality of clamp members having recesses which surround an outer peripheral edge of the flange section and an outer peripheral edge of the scroll casing from an outer peripheral side, and through holes which are opened to the recesses, and
  • the centrifugal compressor according to the present invention even in a case where the plurality of flange section fastening bolts are fractured, and the flange section of the bearing pedestal and the scroll casing are separated from each other, the end face in the direction of the axial line of the other of either the flange section or the scroll casing comes into contact with the end faces in the direction of the axial line of the recesses. Impact caused by this contact is absorbed by the plurality of clamp members mounted in the peripheral direction around the axial line. Consequently, it is possible to suppress faults such as a gap generated by the scattering of all or one part of the impeller in a part of the centrifugal compressor, scattering the all or the one part of the damaged impeller to the outside from the gap.
  • the flange section may have the fastening holes, and is fastened to the clamp members by the clamp member fastening bolts, and predetermined gaps are provided between an end face in the direction of the axial line of the scroll casing, and end faces in the direction of the axial line of the recesses, and the flange section has a stepped section that connects a contact surface that is in contact with the scroll casing, and an end face of the flange section that forms a second flow passage for allowing the compressed fluid to circulate, and is disposed on a side closer to the second flow passage than the contact surface.
  • a width in the direction of the axial line of the stepped section is wider than a width of each of the predetermined gaps, so that opening can be more reliably suppressed.
  • a supercharger according to the present invention includes: a centrifugal compressor described any of the above; and a turbine that is rotated around the axial line by exhaust gas exhausted from an internal combustion engine, and is connected to the rotor shaft.
  • the supercharger according to the present invention it is possible to suppress faults such as a gap generated by the scattering of the inlet casing provided in the centrifugal compressor in a part of the centrifugal compressor, scattering one part of the impeller to the outside from the gap.
  • a method for manufacturing a centrifugal compressor includes the steps of: mounting an impeller on a rotor shaft, the impeller for compressing fluid flowing in from an intake and then discharging the compressed fluid from a discharge port; mounting an inlet casing so as to house the impeller, and forming a flow passage for leading the fluid flowing in from the intake to the discharge port; disposing a scroll section, into which the compressed fluid discharged from the discharge port flows, on an outer peripheral side in a radial direction orthogonal to the direction of the axial line with respect to the inlet casing; and providing a plurality of partition plates on an upstream side in a fluid circulation direction with respect to the intake, and radially disposing about the axial line so as to each have a predetermined length in the direction of the axial line, each of the plurality of partition plates having a plate thickness of 4 mm or more and 9 mm or less.
  • the centrifugal compressor manufactured by such manufacturing method in a case where all or one part of the impeller is fractured or falls, the all or the one part of the impeller scatters to collide with the inlet casing.
  • the inlet casing forms a flow passage for guiding the fluid flowing in from the intake in the direction of the axial line of the rotor shaft, in a direction inclined from the direction of the axial line, and then leading the fluid to the discharge port. Therefore, when the all or the one part of the impeller which scatters in the radial direction collides with the inlet casing, impact in the radial direction is applied to the inlet casing.
  • the plurality of partition plates are radially disposed about the axial line on the upstream side in the fluid circulation direction with respect to the intake. Therefore, the all or the one part of the impeller that scatters, or the all or the one part of the inlet casing that scatters in the direction away from the scroll section due to impact resulting from the scattering of the impeller collides with the plurality of partition plates housed in the silencer casing.
  • the plurality of partition plates each are the rolled steel material having a plate thickness of 4 mm or more and 9 mm or less, and therefore the plurality of partition plates are suitably plastically deformed by collision with the all or the one part of the inlet casing, and then absorb energy resulting from the collision.
  • centrifugal compressor capable of suppressing faults such as scattering of all or one part of an impeller to the outside in a case where all or one part of an inlet casing scatters with fracture or falling of the all or the one part of the impeller.
  • a supercharger 100 of this embodiment will be described with reference to the drawings.
  • the supercharger 100 of this embodiment is a device that increases air (gas) to be supplied to a marine diesel engine (internal combustion engine) used in a vessel to atmospheric pressure or more, and improves combustion efficiency of the marine diesel engine.
  • a marine diesel engine internal combustion engine
  • the supercharger 100 of this embodiment includes a centrifugal compressor 10, a turbine (not illustrated), and a bearing pedestal 20.
  • the centrifugal compressor 10 and the turbine are connected to a rotor shaft 30.
  • the rotor shaft 30 is supported by the bearing pedestal 20 while being rotatable around an axial line X.
  • the centrifugal compressor 10 is a device that compresses air flowing in from the outside of the supercharger 100, and then supplies, to an intake manifold (not illustrated) communicated with the inside of a cylinder liner (not illustrated) forming the marine diesel engine, air that has been compressed (hereinafter, referred to as compressed air (compressed fluid)).
  • the centrifugal compressor 10 includes an impeller 11, an air inlet casing 12 (inlet casing), a scroll section 13, partition plates 14, and a silencer 15.
  • the supercharger 100 of this embodiment leads exhaust gas exhausted from the marine diesel engine to the turbine to rotate a turbine disc mounted with a turbine blade around the axial line X.
  • the impeller 11 connected through the rotor shaft 30 rotates with the rotation of the turbine disc, air flowing in from an intake 11a is compressed, and the compressed air is discharged from a discharge port 11b.
  • the compressed air discharged from the discharge port 11b flows in the scroll section 13 to be led to the intake manifold of the marine diesel engine.
  • the air inlet casing 12 and the scroll section 13 are formed of a metal member manufactured by casting in order to form a complicated shape.
  • a metal member for example, cast iron that is a Fe-C based alloy containing iron as a main component and containing 2% or more of carbon is used.
  • various materials such as gray cast iron can be used.
  • ductile cast iron (FCD: Ferrum Casting Ductile) where black smoke is spheroidized in a basic structure is preferably used.
  • FCD Ferrum Casting Ductile
  • the impeller 11 is mounted on the rotor shaft 30 extending along the axial line X, and rotates about the axial line X with the rotation of the rotor shaft 30 around the axial line X.
  • the impeller 11 rotates around the axial line X, so that air flowing in from the intake 11a is compressed to be discharged from the discharge port 11b.
  • the impeller 11 includes a hub 11c mounted on the rotor shaft 30, blades 11d mounted on an outer peripheral surface of the hub 11c, and a flow passage 11e.
  • the impeller 11 is provided with a space defined by the outer peripheral surface of the hub 11c and an inner peripheral surface of the air inlet casing 12, and this space is partitioned into a plurality of spaced by a plurality of the blades 11d.
  • the impeller 11 applies radial centrifugal force to air flowing in from the intake 11a in the direction of the axial line X to discharge the air in the direction orthogonal to the direction of the axial line X (radial direction of the impeller 11), and allows compressed air discharged from the discharge port 11b to flow into a diffuser 13a.
  • the air inlet casing 12 is a member that houses the impeller 11 and discharges, from the discharge port 11b, air flowing in from the intake 11a in the direction of the axial line X of the rotor shaft 30.
  • the air inlet casing 12 forms the flow passage 11e for guiding air flowing in from the intake 11a along the axial line X in the radial direction orthogonal to the axial line X, and then leading the air to the discharge port 11b, together with the impeller 11.
  • the scroll section 13 is a device in which compressed air discharged from the discharge port 11b flows, and which converts kinetic energy (dynamic pressure) applied to the compressed air into pressure energy (static pressure).
  • the scroll section 13 is disposed on the outer peripheral side in the radial direction orthogonal to the direction of the axial line X with respect to the air inlet casing 12.
  • the scroll section 13 includes the diffuser 13a, a scroll casing 13b, and a volute chamber 13c.
  • the volute chamber 13c is a space formed by the scroll casing 13b.
  • the scroll casing 13b is connected to a flange section 20a of the bearing pedestal 20 by fastening bolts 41.
  • the diffuser 13a is an airfoil member disposed on the downstream side of the discharge port 11b of the impeller 11, and forms a flow passage for leading compressed air from the discharge port 11b to the volute chamber 13c.
  • the diffuser 13a is provided so as to surround the discharge port 11b for compressed air provided on the whole periphery of the impeller 11.
  • the diffuser 13a decelerates the flow velocity of the compressed air discharged from the discharge port 11b of the impeller 11, so that kinetic energy (dynamic pressure) applied to the compressed air is converted into the pressure energy (static pressure).
  • the compressed air whose flow velocity is decelerated when passing through the diffuser 13a flows in the volute chamber 13c communicated with the diffuser 13a.
  • the working fluid flowing in the volute chamber 13c is discharged to a discharge pipe (not illustrated).
  • the partition plates 14 are plate members provided on the upstream side in the air circulation direction with respect to the intake 11a, and have predetermined lengths in the direction of the axial line X. As illustrated in Fig. 2 , the partition plates 14 are formed by four partition plates 14a, 14b, 14c, 14d. The four partition plates 14a, 14b, 14c, 14d are radially disposed about the axial line X. The partition plates 14 are devised so as to function as an impact absorbing material for absorbing impact due to collision with all or one part of the air inlet casing 12. Additionally, the partition plates 14 support a silencer casing 15a of the silencer 15, and each function as a straightening vane for straightening air circulating inside the silencer 15.
  • the partition plate 14b is formed in a rectangle whose cross-section along the axial line X is long in the direction of the axial line X.
  • Fig. 3 illustrates only the partition plate 14b, but other partition plates 14a, 14c, 14d each have a similar sectional shape.
  • the partition plates 14 are each formed of a metal member manufactured by rolling.
  • a metal member for example, a rolled steel material that is a Fe-C based alloy containing iron as a main component and containing a slight amount (about 0.2%) of carbon is used.
  • the rolled steel material various materials can be used. However, a rolled steel material for general structural use (JIS G 3101; ASTM A283), called SS400, is preferably used.
  • the metal material by rolling is composed of a composition suitable for a rolling process, and has ductility resulting in breakage after large plastic deformation.
  • the metal material by casting is composed of a composition suitable for a casting process, and has elongation up to breakage which is smaller than the elongation up to breakage of the metal material by rolling.
  • the metal material by rolling has larger elongation up to breakage than the metal material by casting, that is, has high ductility. Accordingly, the metal material by rolling has higher breaking strength against impact than the metal material by casting.
  • the ductile cast iron material and the SS400 material each have the tensile strength of 400 N/mm 2 to 500 N/mm 2 at a normal temperature.
  • the ductile cast iron material has elongation of about 10% in breakage
  • the SS400 material has elongation of 20% or more in breakage. Accordingly, the SS400 material has higher ductility than the ductile cast iron material.
  • centrifugal compressor 10 of this embodiment all or one part of the blades 11d of the impeller 11 is fractured or falls to scatter in the radial direction, and collides with the air inlet casing 12.
  • the flow passage 11e of the centrifugal compressor 10 is a flow passage that gradually inclines from the intake 11a toward the discharge port 11b in the direction of the axial line X. Therefore, radial impact force, and impact force in the direction of the axial line X are applied to the air inlet casing 12.
  • the impact force in the direction of the axial line X is impact force of scattering the air inlet casing 12 in the direction away from the scroll section 13, and therefore there is a possibility that the air inlet casing 12 formed of the metal member manufactured by casting is damaged to fall from a mounting position.
  • the partition plates 14 each formed of the metal member by rolling have large plastic deformation ductility resulting in breakage, and therefore when impact load is generated, kinetic energy of impact is absorbed by plastic deformation. Consequently, it is possible to make the all or the one part of the air inlet casing 12 to stop scattering.
  • the partition plates 14 are intentionally deformably damaged to absorb impact, so that it is possible to suppress the scattering of the air inlet casing 12 to the outside of the supercharger 100, or suppress failure such as generation of a gap (opening) due to impact applied to other part.
  • each partition plate 14 of this embodiment is in the range of 4 mm to 9 mm. Additionally, the plate thickness of each partition plate 14 is more desirably in the range of 5 mm to 7 mm, and particularly, the plate thickness is preferably 6 mm. In a case where the rigidity of the partition plates 14 is too low, even when the partition plates 14 are largely deformed by the impact load of the all or the one part of the air inlet casing 12 which has been damaged to scatter, the partition plates 14 cannot sufficiently absorb the impact load, and the all or the one part of the air inlet casing 12 scatters outside the supercharger 100.
  • the inventors perform experiments while changing the plate thickness of each partition plate 14, and obtain knowledge that a plate thickness which does not cause the air inlet casing 12 to scatter to the outside, and does not cause the generation of the gap (opening) in other part is in the range of 4 mm to 9 mm, and therefore the plate thickness of each partition plate 14 is set in this range.
  • the silencer 15 illustrated in Fig. 1 is a device that lowers a level of noise generated in the centrifugal compressor 10.
  • the silencer 15 includes the silencer casing 15a.
  • the silencer casing 15a defines a flow passage 15b for leading, to the intake 11a of the air inlet casing 12, air flowing in from the direction illustrated by the arrow in Fig. 1 (direction orthogonal to the axial line X).
  • a noise reduction material 15e is disposed around the flow passage 15b so as to surround the flow passage 15b. This noise reduction material 15e absorbs a part of the noise generated in the centrifugal compressor 10, and the level of the noise is lowered.
  • the silencer casing 15a houses inside the partition plates 14. An end of each partition plate 14 is connected to the silencer casing 15a. Accordingly, each partition plate 14 functions as a support member for supporting the silencer casing 15a as well.
  • the partition plates 14 each formed of the rolled steel material absorb and stop kinetic energy of impact by plastically deforming when impact load is generated.
  • a structure in which the kinetic energy of the impact is absorbed by a part other than the partition plates 14 will be described.
  • a flange section 13d provided in an end, on a side close to the silencer 15, of the scroll casing 13b, and a flange section 15c provided in an end, on a side close to the scroll casing 13b, of the silencer casing 15a are fastened to each other at fastening positions (first fastening positions) illustrated in Fig. 4 by fastening bolts 40 (first fastening bolts).
  • a plurality of fastening positions are provided in the peripheral direction around the axial line X at constant intervals.
  • the flange section 13d is fastened to the flange section 15c by the fastening bolts 40.
  • chromium molybdenum steel containing a carbon amount of 0.33% to 0.38% is preferably used as the fastening bolts 40.
  • the SCM435 is excellent in high strength, and a large elongation amount up to fracture when tensile load is applied.
  • the flange section 15c is provided with fastening holes 15d extending along the axial line X. Additionally, the flange section 13d is provided with fastening holes 13e extending along the axial line X. Inner peripheral surfaces of these fastening holes 15d, 13e are formed with female screws. On the other hand, an outer peripheral surface of a shaft section 40b of each fastening bolt 40 extending along the axial line X is formed with a male screw on a whole surface from the vicinity of a boundary section between a head section 40a and the shaft section 40b to the vicinity of a tip of the shaft section 40b.
  • Deformations at the respective parts of the outer peripheral surfaces of the shaft sections 40b are made uniform, so that tensile load is generated in the fastening bolts 40. Even in a case where plastic deformation is performed until the elongation amount increases, stress is hardly locally concentrated on the bolts 40, and therefore fracture is not caused until large elongation, which is suitable.
  • the flange section 13d and the flange section 15c are fastened to each other in a state where cylindrical spacers 50 (first spacer members) each having an inner diameter d1 smaller than the diameter d2 of the head section 40a of each fastening bolt 40, and having a predetermined length are inserted into the shaft sections 40b of the fastening bolts 40.
  • the male screw formed on the shaft section 40b of each fastening bolt 40 meshes with the female screws formed on the inner peripheral surfaces of the fastening holes 15d, 13e.
  • the spacers 50 are each formed of a metal member manufactured by rolling.
  • a metal member for example, a rolled steel material that is a Fe-C based alloy containing iron as a main component and containing a slight amount (about 0.2%) of carbon is used.
  • the rolled steel material various materials can be used. However, a rolled steel material for general structural use (JIS G 3101; ASTM A283), called SS400, is preferably used.
  • the metal material by rolling has ductility resulting in breakage after large plastic deformation, and therefore has higher breaking strength against impact than the metal material by casting.
  • the air inlet casing 12 and the scroll casing 13b are fastened to each other by fastening bolts 42 inserted into through holes provided in a flange section 12a of the air inlet casing 12. Only one fastening position is illustrated in Fig. 4 , but a plurality of fastening positions are provided in the peripheral direction around the axial line X at constant intervals. At the plurality of fastening positions, the air inlet casing 12 is fastened to the scroll casing 13b by the fastening bolts 42.
  • the plastic deformations of the partition plates 14 absorb and stop kinetic energy of impact.
  • a structure in which the kinetic energy of the impact can be absorbed by the fastening bolts 40 and the spacers 50 other than the partition plates 14 will be described.
  • each spacer 50 is inserted into the shaft section 40b of the fastening bolt 40 .
  • the predetermined length of each spacer 50 is made longer than at least the diameter of the shaft section 40b of each fastening bolt 40, and is set to a length so as not to cause a trouble on fastening work.
  • the elongation amounts are increased, so that the fastening bolts 40 are prevented from being fractured, and kinetic energy of impact due to collision with the all or the one part of the air inlet casing 12 that falls from the mounting position to scatter can be absorbed by the elongation of the fastening bolts 40.
  • the reason why the spacers 50 are provided is that kinetic energy of impact is absorbed by the spacers 50 formed of the rolled steel materials having ductility.
  • the lengths in the direction of the axial line X of the spacers 50 disposed between the head sections 40a of the fastening bolts 40 and the flange section 15c are contracted by impact that acts on the fastening positions of the fastening bolts 40 and the flange section 15c.
  • the spacers 50 formed of the rolled steel materials have ductility resulting in breakage after large plastic deformation, and therefore the spacers 50 are contracted in the direction of the axial line X, so that it is possible to absorb the kinetic energy due to the above impact.
  • the bearing pedestal 20 of this embodiment includes flange section 20a for supporting the scroll section 13, and a bearing section 20b for supporting the rotor shaft 30.
  • a flange section 13f provided in an end, on a side close to the bearing pedestal 20, of the scroll casing 13b, and a flange section 20a provided in an end, on a side close to the scroll casing 13b, of the bearing pedestal 20 are fastened to each other at fastening positions (second fastening positions) illustrated in Fig. 5 by fastening bolts 41 (second fastening bolts).
  • chromium molybdenum steel containing a carbon amount of 0.33% to 0.38% is preferably used as the fastening bolts 41.
  • the SCM435 is excellent in high strength, and a large elongation amount.
  • the flange section 13f is provided with fastening holes 13g extending along the axial line X. Additionally, the flange section 20a is provided with fastening holes 20c extending along the axial line X. Inner peripheral surfaces of these fastening holes 13g, 20c are formed with female screws. On the other hand, an outer peripheral surface of a shaft section 41b of each fastening bolt 41 extending along the axial line X is formed with a male screw on a whole surface from a head section 41a and a tip.
  • the flange section 13f and the flange section 20a are fastened to each other in a state where cylindrical spacers 51 (second spacer members) each having an inner diameter d3 smaller than the diameter d4 of the head section 41a of each fastening bolt 41 are inserted into the shaft sections 41b of the fastening bolts 41.
  • the male screw formed on the shaft section 41b of each fastening bolt 41 meshes with the female screws formed on the inner peripheral surfaces of the fastening holes 13g, 20c.
  • the spacers 51 are each formed of a metal member manufactured by rolling.
  • a metal member for example, a rolled steel material that is a Fe-C based alloy containing iron as a main component and containing a slight amount (about 0.2%) of carbon is used.
  • the rolled steel material various materials can be used. However, a rolled steel material for general structural use (JIS G 3101; ASTM A283), called SS400, is preferably used.
  • the metal material by rolling has ductility resulting in breakage after large plastic deformation, and therefore has higher breaking strength against impact than the metal material by casting.
  • the reason why fastening is performed in a state where each spacer 51 is inserted into shaft section 41b of the fastening bolt 41 is that the length in the direction of the axial line X of each fastening bolt 41 is increased and a large elongation amount is ensured.
  • the elongation amounts are increased, so that the fastening bolts 41 are prevented from being fractured, and kinetic energy of impact due to collision with the all or the one part of the air inlet casing 12 that falls from the mounting position to scatter can be absorbed by the elongation of the fastening bolts 41.
  • the reason why the spacers 51 are provided is that kinetic energy of impact is absorbed by the spacers 51 formed of the rolled steel materials having ductility.
  • the lengths in the direction of the axial line X of the spacers 51 disposed between the head sections 41a of the fastening bolts 41 and the flange section 13f are contracted by impact that acts on the fastening positions of the fastening bolts 41 and the flange section 13f.
  • the spacers 51 formed of the rolled steel materials have ductility resulting in breakage after large plastic deformation, and therefore the spacers 51 are contracted in the direction of the axial line X, so that it is possible to absorb the kinetic energy due to the above impact.
  • FIG. 6 is a diagram of the outer peripheral edges of the flange section 13f of the scroll casing 13b and the flange section 20a as viewed from the P direction illustrated in Fig. 1 .
  • a plurality of the clamp members 60 are mounted between a plurality of the fastening positions (second fastening positions) by the fastening bolts 41, in the peripheral direction around the axial line X.
  • the clamp members 60 have respective recesses 60a that surround the outer peripheral edge of the flange section 20a and the outer peripheral edge of the flange section 13f of the scroll casing 13b from the outer peripheral side. Additionally, the clamp members 60 have respective through holes 60b which are opened to the recesses 60a, and extend in the direction of the axial line X.
  • the flange section 20a has fastening holes 20d extending in the direction of the axial line X. Only one fastening hole 20d is illustrated in Fig. 7 , but a plurality of fastening positions are provided in the peripheral direction around the axial line X at equal intervals.
  • female screws are formed on inner peripheral surfaces of the fastening holes 20d.
  • male screws are formed on outer peripheral surfaces of shaft sections of fastening bolts 43 (third fastening bolts) inserted into the through holes 60b and the fastening holes 20d.
  • the male screws of the fastening bolts 43 meshes with the female screws of the fastening holes 20d, so that the flange section 20a and the clamp members 60 are fastened to each other.
  • predetermined gaps 60c are provided between an end face 13i in the direction of the axial line X of the scroll casing 13b, and end faces 60e in the direction of the axial line X of the recesses 60a.
  • the width along the axial line X of each gap 60c is denoted by d5.
  • the flange section 20a includes a contact surface 20e that is in contact with the scroll casing 13b, an end face 20f that forms a flow passage 13h (second flow passage) for allowing compressed air to circulate, and a stepped section 20g that connects the contact surface 20e and the end face 20f. As illustrated in Fig. 7 , the end face 20f is disposed on a side closer to the flow passage 13h than the contact surface 20e.
  • the width d6 in the direction of the axial line X of the stepped section 20g is wider than the width d5 of each gap 60c.
  • the reason why the predetermined gaps 60c are provided is that in a case where impact in the direction of the axial line X due to scattering of all or one part of the impeller 11 cannot be sufficiently absorbed, and the fastening bolts 41 are fractured and the scroll casing 13b is separated from the bearing pedestal 20, the clamp members 60 absorb impact caused by the separated scroll casing 13b.
  • the width d6 in the direction of the axial line X of the stepped section 20g is wider than the width d5 of the gap 60d. Therefore, faults are prevented such as the gap 60d brought into communication with the flow passage 13h, causing a gap (opening) for allowing a damaged member to pass.
  • the gaps 60c are intentionally provided between the end face 13i in the direction of the axial line X of the scroll casing 13b and the end faces 60e in the direction of the axial line X of the recesses 60a, so that fracture at a position other than the fastening positions of the fastening bolts 41 is prevented. Then, in a case where the fastening bolts 41 are fractured, the impact caused by separation of the scroll casing 13b from the bearing pedestal 20 is absorbed by the clamp members 60.
  • the centrifugal compressor 10 is manufactured by the following steps.
  • the impeller 11 that compresses air flowing in from the intake 11a, and then discharges the compressed air from the discharge port 11b is mounted on the rotor shaft 30.
  • the flow passage for guiding the air flowing in from the intake 11a in the direction of the axial line X of the rotor shaft 30, in the direction inclined from the direction of the axial line X, and then leading the air to the discharge port 11b is formed by mounting the air inlet casing 12 so as to house the impeller 11.
  • the scroll section 13 in which the compressed air discharged from the discharge port 11b flows is disposed on the outer peripheral side in the radial direction orthogonal to the direction of the axial line X with respect to the air inlet casing 12.
  • a plurality of the partition plates 14 each having a plate thickness of 4 mm or more and 9 mm or less are provided on the upstream side in the air circulation direction with respect to the intake 11a, and are radially disposed about the axial line X so as to have predetermined lengths in the direction of the axial line X.
  • the centrifugal compressor 10 of this embodiment is manufactured.
  • centrifugal compressor 10 provided in the supercharger 100 of this embodiment, in a case where all or one part of the impeller 11 is fractured or falls, all or one part of the impeller 11 scatters in the radial direction to collide with the air inlet casing 12.
  • the air inlet casing 12 forms the flow passage 11e for guiding air flowing in from the intake 11a in the direction of the axial line X of the rotor shaft 30, in the direction inclined from the direction of the axial line X, and leading the air to the discharge port 11b.
  • the air inlet casing 12 forms the flow passage 11e for guiding air flowing in from the intake 11a in the direction of the axial line X of the rotor shaft 30, in the direction inclined from the direction of the axial line X, and leading the air to the discharge port 11b.
  • the impact in the direction of the axial line X is impact causing the all or the one part of the air inlet casing 12 to scatter in the direction away from the scroll section 13, and therefore there is a possibility that the all or the one part of the air inlet casing 12 falls from the mounting position.
  • the plurality of partition plates 14 each having a predetermined length in the direction of the axial line X are radially disposed about the axial line X on the upstream side in the air circulation direction with respect to the intake 11a. Therefore, the all or the one part of the impeller 11 that scatters, or the all or the one part of the air inlet casing 12 that scatters in the direction away from the scroll section 13 collides with the plurality of partition plates 14 due to impact resulting from the scattering of the impeller 11.
  • the plurality of partition plates 14 each are a rolled steel material having a plate thickness of 4 mm or more and 9 mm or less. Therefore, the plurality of partition plates 14 are suitably plastically deformed by collision with the all or the one part of the air inlet casing 12, and then absorbs energy resulting from the collision. Consequently, it is possible to suppress faults such as a gap generated by the scattering of the all or the one part of the air inlet casing 12 in a part of the centrifugal compressor 10, scattering the all or the one part of the impeller 11 to the outside from the gap.
  • the centrifugal compressor 10 of this embodiment when the all or the one part of the air inlet casing 12 that scatters in the direction away from the scroll section 13 collides with the silencer casing 15a that houses the partition plates 14, impact is applied in the direction in which the silencer casing 15a is separated from the scroll casing. This impact is absorbed by contraction of the spacers 50 disposed between the head sections 40a of the fastening bolts 40 and the silencer casing 15a. Thus, the impact in the direction of the axial line is absorbed by use of the spacers 50 fastened while being inserted into the fastening bolts 40, so that faults such as fracture of the fastening bolts 40 are suppressed.
  • the fastening bolts 40 include male screws formed on the outer peripheral surfaces of the shaft sections 40b from the head sections 40a to the tips. Consequently, deformations at the respective parts of the outer peripheral surfaces of the shaft sections 40b from the head sections 40a to the tips are made uniform, so that the above failure can be suppressed by use of the fastening bolts 40 having increased energy absorption of impact.
  • the centrifugal compressor 10 of this embodiment when the all or the one part of the air inlet casing 12 that scatters in the direction away from the scroll section 13 collides with the silencer casing 15a that houses the partition plates 14, impact in the direction in which the scroll casing 13b is separated from the flange section 20a of the bearing pedestal 20 is applied.
  • This impact is absorbed by contraction of the spacers 51 disposed between the head sections 41a of the fastening bolts 41 and the scroll casing 13b.
  • impact in the direction of the axial line X is absorbed by use of the spacers 51 fastened while being inserted into the fastening bolts 41, so that faults such as fracture of the fastening bolts 41 are suppressed.
  • the fastening bolts 41 include male screws formed on the outer peripheral surfaces of the shaft sections 41b from the head sections 41a to the tips. Consequently, deformations at the respective parts of the outer peripheral surfaces of the shaft sections 41b from the head sections 41a to the tips are made uniform, so that the above failure can be suppressed by use of the fastening bolts 41 having increased energy absorption of impact.
  • the centrifugal compressor 10 of this embodiment includes a plurality of the clamp members 60 having recesses 60a that surround the outer peripheral edge of the flange section 20a and the outer peripheral edge of the scroll casing 13b from the outer peripheral side, and the through holes 60b that are opened to the recesses 60a, and extend in the direction of the axial line X.
  • the flange section 20a has a plurality of the fastening holes 20d extending in the direction of the axial line X, in the peripheral direction around the axial line X. Then, the flange section 20a and the clamp members 60 are fastened to each other by the fastening bolts 43 inserted into the through holes 60b and the fastening holes 20d. Furthermore, the predetermined gaps 60c are provided between the end face 13i in the direction of the axial line X of the scroll casing 13b, and the end faces 60e in the direction of the axial line X of the recesses 60a.
  • the flange section 20a is fastened to the clamp members 60 by the fastening bolts 43, and the predetermined gaps 60c are provided between the end face 13i in the direction of the axial line X of the scroll casing 13b, and the end faces 60e in the direction of the axial line X of the recesses 60a. Additionally, the flange section 20a has the stepped section 20g that connects the contact surface 20e that is in contact with the scroll casing 13b, and the end face 20f of the flange section 20a that forms the flow passage 13h for allowing compressed air to circulate, and is disposed on the side closer to the flow passage 13h than the contact surface 20e.
  • the flange section 20a of the bearing pedestal 20 and the scroll casing 13b are separated from each other, and the end face 13i in the direction of the axial line X of the scroll casing 13b comes into contact with the end faces 60e in the direction of the axial line X of the recesses 60a, opening between the flange section 20a and the scroll casing 13b is suppressed by existence of the stepped section 20g.
  • the width d6 in the direction of the axial line X of the stepped section 20g is wider than the width d5 of the predetermined gap 60d, and therefore a communicated gap is not generated, and opening can be more reliably suppressed.
  • the rotor shaft 30 connected to the impeller 11 provided in the centrifugal compressor 10 rotates around the axial line X by a turbine (not illustrated) rotated by exhaust gas exhausted from the marine diesel engine.
  • a turbine not illustrated
  • the rotor shaft 30 may be rotated by other power source other than a motor connected to the rotor shaft 30, or the like.
  • the four partition plates 14 are disposed at intervals of 90 degrees about the axial line X.
  • Other aspect may be employed.
  • An arbitrary number of partition plates may be disposed.
  • six partition plates may be radially disposed at intervals of 60 degrees about the axial line X, or eight partition plates may be disposed at intervals of 45 degrees about the axial line X.
  • the clamp members 60 are fastened to the flange section 20a of the bearing pedestal 20.
  • the clamp members 60 may be fastened to the flange section 13f of the scroll casing 13b.
  • the flange section 13f of the scroll casing 13b has a plurality of fastening holes extending in the direction of the axial line X, in the peripheral direction around the axial line X.
  • the fastening bolts 43 are fastened to the plurality of fastening holes, so that the clamp members 60 are fastened to the flange section 13f of the scroll casing 13b.
  • the gaps 60c described above are provided between the end face in the direction of the axial line X of the flange section 20a of the bearing pedestal 20, and the end face in the direction of the axial line X of the recesses of the clamp members 60.

Landscapes

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

Claims (4)

  1. Zentrifugalkompressor (10), umfassend:
    ein Laufrad (11), das auf einer Rotorwelle (30) montiert ist und das von einem Einlass einströmendes Fluid komprimiert und dann das komprimierte Fluid aus einer Auslassöffnung austrägt;
    ein Einlassgehäuse (12), das das Laufrad (11) aufnimmt;
    einen Spiralabschnitt (13), der auf einer äußeren Umfangsseite bezüglich des Einlassgehäuses (12) angeordnet ist, und ein Spiralgehäuse (13b) aufweist, das eine Spiralkammer bildet, in die das aus der Auslassöffnung austretende komprimierte Fluid strömt;
    einen Lagerträger (20), der einen Lagerabschnitt zum Abstützen der Rotorwelle und einem Flanschabschnitt (20a) zum Abstützen des Spiralabschnitts (13) aufweist;
    eine Vielzahl von Flanschabschnitt-Befestigungsschrauben (41), die den Flanschabschnitt (20a) an das Spiralgehäuse (13b) an einer Vielzahl von Befestigungspositionen um die axiale Linie der Rotorwelle (30) herum befestigen und die sich in Richtung der axialen Linie erstrecken;
    dadurch gekennzeichnet, dass
    der Zentrifugalkompressor (10) weiter umfasst:
    eine Vielzahl von Klemmelementen (60), die Aussparungen, die eine äußere Umfangskante des Flanschabschnitts (20a) und eine äußere Umfangskante des Spiralgehäuses (13b) von einer äußeren Umfangsseite umgeben, und Durchgangslöcher aufweisen, die zu den Aussparungen geöffnet sind und sich in Richtung der axialen Linie erstrecken, wobei
    eines von entweder dem Flanschabschnitt (20a) oder dem Spiralgehäuse (13b) eine Vielzahl von Befestigungslöchern aufweist, die sich in Richtung der axialen Linie in einer Umfangsrichtung um die axiale Linie erstrecken,
    eines von entweder dem Flanschabschnitt (20a) oder dem Spiralgehäuse (13b), und die Klemmelemente (60) durch Klemmelement-Befestigungsschrauben (43) aneinander befestigt sind, die in die Durchgangslöcher und die Befestigungslöcher eingesetzt sind, und
    zwischen einer Stirnfläche in Richtung der axialen Linie des anderen von entweder dem Flanschabschnitt (20a) oder dem Spiralgehäuse (13b), und Stirnflächen in Richtung der axialen Linie der Aussparungen vorbestimmte Lücken vorgesehen sind.
  2. Zentrifugalkompressor (10) nach Anspruch 1, wobei
    der Flanschabschnitt (20a) die Befestigungslöcher aufweist und mit den Klemmelement-Befestigungsschrauben (43) an den Klemmelementen (60) befestigt ist,
    vorbestimmte Lücken zwischen einer Stirnfläche in Richtung der axialen Linie des Spiralgehäuses (13b) und Stirnflächen in Richtung der axialen Linie der Aussparungen vorgesehen sind, und
    der Flanschabschnitt (20a) einen gestuften Abschnitt (20g) aufweist, der eine Kontaktfläche (20e), die mit dem Spiralgehäuse (13b) in Kontakt steht, und eine Stirnfläche des Flanschabschnitts (20a), die einen zweiten Strömungskanal bildet, um die Zirkulation des komprimierten Fluids zu ermöglichen, verbindet, und auf einer Seite angeordnet ist, die näher an dem zweiten Strömungskanal liegt als die Kontaktfläche (20e).
  3. Zentrifugalkompressor (10) nach Anspruch 2, wobei
    eine Breite in Richtung der axialen Linie des gestuften Abschnitts (20g) breiter ist als eine Breite jeder der vorbestimmten Lücken.
  4. Turbolader (100), umfassend:
    einen Zentrifugalkompressor (10) nach einem der Ansprüche 1 bis 3; und
    eine Turbine, die durch Abgase eines Verbrennungsmotors um die axiale Linie gedreht wird und mit der Rotorwelle (30) verbunden ist.
EP18185764.0A 2014-03-31 2015-02-24 Kreiselverdichter, turbolader und verfahren zur herstellung des kreiselverdichters Active EP3412916B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2014074071A JP6391970B2 (ja) 2014-03-31 2014-03-31 遠心圧縮機、過給機、および遠心圧縮機の製造方法、並びにサイレンサ
EP15774147.1A EP3128184B1 (de) 2014-03-31 2015-02-24 Kreiselverdichter, turbolader und verfahren zur herstellung des kreiselverdichters
PCT/JP2015/055240 WO2015151653A1 (ja) 2014-03-31 2015-02-24 遠心圧縮機、過給機、および遠心圧縮機の製造方法

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EP15774147.1A Division EP3128184B1 (de) 2014-03-31 2015-02-24 Kreiselverdichter, turbolader und verfahren zur herstellung des kreiselverdichters
EP15774147.1A Division-Into EP3128184B1 (de) 2014-03-31 2015-02-24 Kreiselverdichter, turbolader und verfahren zur herstellung des kreiselverdichters

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JP6391970B2 (ja) 2018-09-19
EP3128184A4 (de) 2017-08-16
KR20160125467A (ko) 2016-10-31
EP3128184A1 (de) 2017-02-08
EP3412916A1 (de) 2018-12-12
WO2015151653A1 (ja) 2015-10-08
JP2015197053A (ja) 2015-11-09
CN106104006B (zh) 2019-06-18
EP3128184B1 (de) 2018-09-26
KR101918377B1 (ko) 2018-11-13
CN108799204B (zh) 2020-03-13
CN106104006A (zh) 2016-11-09
CN108799204A (zh) 2018-11-13

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