EP3128184A1 - Centrifugal compressor, supercharger, and method for manufacturing centrifugal compressor - Google Patents
Centrifugal compressor, supercharger, and method for manufacturing centrifugal compressor Download PDFInfo
- Publication number
- EP3128184A1 EP3128184A1 EP15774147.1A EP15774147A EP3128184A1 EP 3128184 A1 EP3128184 A1 EP 3128184A1 EP 15774147 A EP15774147 A EP 15774147A EP 3128184 A1 EP3128184 A1 EP 3128184A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- axial line
- casing
- section
- scroll
- centrifugal compressor
- 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.)
- Granted
Links
- 238000004519 manufacturing process Methods 0.000 title claims description 10
- 238000000034 method Methods 0.000 title claims description 8
- 238000005192 partition Methods 0.000 claims abstract description 71
- 230000002093 peripheral effect Effects 0.000 claims abstract description 60
- 230000003584 silencer Effects 0.000 claims abstract description 41
- 239000000463 material Substances 0.000 claims abstract description 33
- 229910000831 Steel Inorganic materials 0.000 claims abstract description 23
- 239000010959 steel Substances 0.000 claims abstract description 23
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 10
- 125000006850 spacer group Chemical group 0.000 claims description 37
- 239000012530 fluid Substances 0.000 claims description 36
- NJPPVKZQTLUDBO-UHFFFAOYSA-N novaluron Chemical compound C1=C(Cl)C(OC(F)(F)C(OC(F)(F)F)F)=CC=C1NC(=O)NC(=O)C1=C(F)C=CC=C1F NJPPVKZQTLUDBO-UHFFFAOYSA-N 0.000 claims description 27
- 238000002485 combustion reaction Methods 0.000 claims description 5
- 238000007599 discharging Methods 0.000 claims description 2
- 239000007769 metal material Substances 0.000 description 12
- 238000005266 casting Methods 0.000 description 11
- 238000005096 rolling process Methods 0.000 description 11
- 229910052751 metal Inorganic materials 0.000 description 10
- 239000002184 metal Substances 0.000 description 10
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 9
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 6
- 229910052799 carbon Inorganic materials 0.000 description 6
- 229910001141 Ductile iron Inorganic materials 0.000 description 4
- 229910017112 Fe—C Inorganic materials 0.000 description 4
- 238000010521 absorption reaction Methods 0.000 description 4
- 229910045601 alloy Inorganic materials 0.000 description 4
- 239000000956 alloy Substances 0.000 description 4
- 230000008602 contraction Effects 0.000 description 4
- 229910052742 iron Inorganic materials 0.000 description 4
- 239000000314 lubricant Substances 0.000 description 3
- 229910001018 Cast iron Inorganic materials 0.000 description 2
- VNTLIPZTSJSULJ-UHFFFAOYSA-N chromium molybdenum Chemical compound [Cr].[Mo] VNTLIPZTSJSULJ-UHFFFAOYSA-N 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 229910001060 Gray iron Inorganic materials 0.000 description 1
- 239000011358 absorbing material Substances 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000000644 propagated effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000000779 smoke Substances 0.000 description 1
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
- F04D29/40—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, a supercharger, and a method for manufacturing a centrifugal compressor.
- centrifugal compressors are known (refer to Patent Literature 1, 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, and a method for manufacturing the above centrifugal compressor.
- the present invention employs the following solutions.
- 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 which is disposed on an outer peripheral side with respect to the inlet casing, and into which the compressed fluid discharged from the discharge port flows; a plurality of partition plates provided on an upstream side in a fluid circulation direction with respect to the intake, and each having a predetermined length in a direction of an axial line of the rotor shaft; and a silencer for housing the plurality of partition plates, wherein the plurality of partition plates are radially disposed about the axial line, and each are a rolled steel material having a plate thickness of 4 mm or more and 9 mm or less.
- the centrifugal compressor 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 leading the fluid to the discharge port.
- the plurality of partition plates each having a predetermined length in the direction of the axial line 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, to absorb 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 inlet casing in a part of the centrifugal compressor, scattering the all or the one part of the impeller to the outside from the gap.
- the scroll section may have a scroll casing forming a volute chamber into which the compressed fluid discharged from the discharge port flows, the scroll casing and the silencer casing may be fastened to each other at a plurality of first fastening positions in a peripheral direction around the axial line by a plurality of first fastening bolts extending in the direction of the axial line, and the scroll casing and the silencer casing may be fastened to each other in a state where cylindrical first spacer members each having an inner diameter smaller than a diameter of a head section of each of the first fastening bolts are inserted into shaft sections of the first fastening bolts.
- centrifugal compressor having this configuration, when the all or the one part of the inlet casing that scatters in the direction away from the scroll section collides with the silencer casing that houses the partition plates, impact in the direction in which the silencer casing is separated from the scroll casing is applied. This impact is absorbed by contraction of the first spacer members disposed between the head sections of the first fastening bolts and the silencer casing.
- each first spacer member for example, a rolled steel material having ductility resulting in breakage after large plastic deformation is used, so that it is possible to absorb kinetic energy resulting from axial impact.
- the impact in the direction of the axial line is absorbed by use of the first spacer members fastened while being inserted into the first fastening bolts, so that faults such as fracture of the first fastening bolts are suppressed. Accordingly, it is possible to suppress faults such as a gap generated by the scattering of the all or the one part of the inlet casing in a part of the centrifugal compressor, scattering the all or the one part of the impeller to the outside from the gap.
- the first fastening bolts may each include a male screw formed on an outer peripheral surface of the shaft section from the head section to a tip.
- the centrifugal compressor having the above configuration may include a bearing pedestal having a bearing section for supporting the rotor shaft, and a flange section for supporting the scroll section, wherein the flange section and the scroll casing may be fastened to each other at a plurality of second fastening positions around the axial line by a plurality of second fastening bolts extending in the direction of the axial line, and the flange section and the scroll casing may be fastened to each other in a state where cylindrical second spacer members each having an inner diameter smaller than a diameter of a head section of each of the second fastening bolts are inserted into shaft sections of the second fastening bolts.
- the centrifugal compressor of this aspect when the all or the one part of the inlet casing that scatters in the direction away from the scroll section collides with the silencer casing that houses the partition plates, impact in the direction in which the scroll casing is separated from the flange section of the bearing pedestal is applied. This impact is absorbed by contraction of the second spacer members disposed between the head sections of the second fastening bolts and the scroll casing. Thus, impact in the direction of the axial line is absorbed by use of the second spacer members fastened while being inserted into the second fastening bolts, so that faults such as fracture of the second fastening bolts are suppressed.
- the second fastening bolts may each include a male screw formed on an outer peripheral surface of the shaft section from the head section to a tip.
- 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
- the centrifugal compressor according to the second aspect of 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 third 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 the manufacturing method according to the present invention 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. Consequently, it is possible to suppress faults such as a gap generated by the scattering of the all or the one part of the inlet casing in a part of the centrifugal compressor, scattering the all or the one part of the impeller to the outside from the gap.
- 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 S400 material has elongation of 20% or more in breakage.
- 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 14b.
- 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 40b from the head sections 41a to the tips. Consequently, deformations at the respective parts of the outer peripheral surfaces of the shaft sections 40b 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 13e of the scroll casing 13b.
- the flange section 13e 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 13e 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)
Abstract
Description
- The present invention relates to a centrifugal compressor, a supercharger, and a method for manufacturing a centrifugal compressor.
- Conventionally, as compressors for a supercharger that increases the pressure of air to be supplied to an internal combustion engine used in a vessel or the like above atmospheric pressure, centrifugal compressors are known (refer to Patent Literature 1, 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.
- In the centrifugal compressor, there is a possibility that faults occur such as fracture or falling off of one part of the impeller due to the influence of centrifugal force by high-speed rotation. 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.
-
- {PTL 1} Japanese Unexamined Patent Application, Publication No.
2011-117417 - {PTL 2} Japanese Unexamined Patent Application, Publication No.
2001-132465 - In the centrifugal compressor disclosed in Patent Literature 2, in a case where faults occur such as fracture or falling off of the one part of the impeller due to the influence of centrifugal force by high-speed rotation, the tank housing lubricant is protected.
- However, in a case where all or one part of the impeller is fractured or falls to collide with an inlet casing, there is a possibility that since the impact load is large, the inlet casing is broken, and all or one part of the inlet casing scatters to the outside together with the all or the one part of the impeller. Additionally, even in a case where the inlet casing is not broken, there is a possibility that all or one part of the inlet casing falls from a mounting position, and scatters in the direction away from a scroll section along the axial line of a rotor shaft. In this case, there is a possibility that a gap (opening) is generated in a part of the centrifugal compressor due to scattering of all or one part of the inlet casing, and a part of the broken impeller scatters to the outside from the gap.
- 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.
- Additionally, an object of the present invention is to provide a supercharger including the above centrifugal compressor, and a method for manufacturing the above centrifugal compressor.
- In order to achieve the above objects, the present invention employs the following solutions.
- A centrifugal compressor according to a first aspect of the present invention 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 which is disposed on an outer peripheral side with respect to the inlet casing, and into which the compressed fluid discharged from the discharge port flows; a plurality of partition plates provided on an upstream side in a fluid circulation direction with respect to the intake, and each having a predetermined length in a direction of an axial line of the rotor shaft; and a silencer for housing the plurality of partition plates, wherein the plurality of partition plates are radially disposed about the axial line, and each are a rolled steel material having a plate thickness of 4 mm or more and 9 mm or less.
- According to the centrifugal compressor according to the first aspect of the present invention, 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 leading the fluid to the discharge port. 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. Similarly, when the all or the one part of the impeller which scatters in the direction of the axial line collides with the inlet casing, impact in the direction of the axial line is applied to the inlet casing. The impact in the direction of the axial line is impact causing the all or the one part of the inlet casing to scatter in the direction away from the scroll section, and therefore there is a possibility that all or one part of the inlet casing falls from a mounting position.
- According to the centrifugal compressor according to the first aspect of the present invention, the plurality of partition plates each having a predetermined length in the direction of the axial line 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, to absorb 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 inlet casing in a part of the centrifugal compressor, scattering the all or the one part of the impeller to the outside from the gap.
- In the centrifugal compressor of the first aspect of the present invention, the scroll section may have a scroll casing forming a volute chamber into which the compressed fluid discharged from the discharge port flows, the scroll casing and the silencer casing may be fastened to each other at a plurality of first fastening positions in a peripheral direction around the axial line by a plurality of first fastening bolts extending in the direction of the axial line, and the scroll casing and the silencer casing may be fastened to each other in a state where cylindrical first spacer members each having an inner diameter smaller than a diameter of a head section of each of the first fastening bolts are inserted into shaft sections of the first fastening bolts.
- According to the centrifugal compressor having this configuration, when the all or the one part of the inlet casing that scatters in the direction away from the scroll section collides with the silencer casing that houses the partition plates, impact in the direction in which the silencer casing is separated from the scroll casing is applied. This impact is absorbed by contraction of the first spacer members disposed between the head sections of the first fastening bolts and the silencer casing. As each first spacer member, for example, a rolled steel material having ductility resulting in breakage after large plastic deformation is used, so that it is possible to absorb kinetic energy resulting from axial impact. Thus, the impact in the direction of the axial line is absorbed by use of the first spacer members fastened while being inserted into the first fastening bolts, so that faults such as fracture of the first fastening bolts are suppressed. Accordingly, it is possible to suppress faults such as a gap generated by the scattering of the all or the one part of the inlet casing in a part of the centrifugal compressor, scattering the all or the one part of the impeller to the outside from the gap.
- In the centrifugal compressor having the above configuration, the first fastening bolts may each include a male screw formed on an outer peripheral surface of the shaft section from the head section to a tip.
- Consequently, deformations at the respective parts of the outer peripheral surfaces of the shaft sections from the head sections to the tips are made uniform, so that the above failure can be suppressed by use of the first fastening bolts having increased energy absorption of impact.
- The centrifugal compressor having the above configuration may include a bearing pedestal having a bearing section for supporting the rotor shaft, and a flange section for supporting the scroll section, wherein the flange section and the scroll casing may be fastened to each other at a plurality of second fastening positions around the axial line by a plurality of second fastening bolts extending in the direction of the axial line, and the flange section and the scroll casing may be fastened to each other in a state where cylindrical second spacer members each having an inner diameter smaller than a diameter of a head section of each of the second fastening bolts are inserted into shaft sections of the second fastening bolts.
- According to the centrifugal compressor of this aspect, when the all or the one part of the inlet casing that scatters in the direction away from the scroll section collides with the silencer casing that houses the partition plates, impact in the direction in which the scroll casing is separated from the flange section of the bearing pedestal is applied. This impact is absorbed by contraction of the second spacer members disposed between the head sections of the second fastening bolts and the scroll casing. Thus, impact in the direction of the axial line is absorbed by use of the second spacer members fastened while being inserted into the second fastening bolts, so that faults such as fracture of the second fastening bolts are suppressed. Accordingly, it is possible to suppress faults such as a gap generated by the scattering of the all or the one part of the inlet casing in a part of the centrifugal compressor, scattering the all or the one part of the impeller to the outside from the gap.
- In the centrifugal compressor of the above aspect, the second fastening bolts may each include a male screw formed on an outer peripheral surface of the shaft section from the head section to a tip.
- Consequently, deformations at the respective parts of the outer peripheral surfaces of the shaft sections from the head sections to the tips are made uniform, so that the above failure can be suppressed by use of the second fastening bolts having increased energy absorption of impact.
- A centrifugal compressor according to a second aspect of the present invention 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 extend in the direction of the axial line, wherein one of either the flange section or the scroll casing has a plurality of fastening holes extending in the direction of the axial line, in a peripheral direction around the axial line, one of either the flange section or the scroll casing, and the clamp members are fastened to each other by clamp member fastening bolts inserted into the through holes and the fastening holes, and predetermined gaps are provided between an end face in the direction of the axial line of the other of either the flange section or the scroll casing, and end faces in the direction of the axial line of the recesses.
- According to the centrifugal compressor according to the second aspect of 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.
- In the above aspect, the flange section may have the fastening holes, and is fastened to the clamp members by the third 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.
- Consequently, in a case where the plurality of flange section fastening bolts are fractured, the flange section of the bearing pedestal and the scroll casing are separated from each other, and the end face in the direction of the axial line of the scroll casing comes into contact with the end faces in the direction of the axial line of the recesses, opening between the flange section and the scroll casing is suppressed by existence of the stepped section.
- Furthermore, 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 according to the present invention 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.
- According to the centrifugal compressor manufactured by the manufacturing method according to the present invention, 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. Similarly, when the all or the one part of the impeller which scatters in the direction of the axial line collides with the inlet casing, impact in the direction of the axial line is applied to the inlet casing. The impact in the direction of the axial line is impact causing the all or the one part of the inlet casing to scatter in the direction away from the scroll section, and therefore there is a possibility that all or one part of the inlet casing falls from a mounting position.
- According to the centrifugal compressor manufactured by the manufacturing method according to the present invention, 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. Consequently, it is possible to suppress faults such as a gap generated by the scattering of the all or the one part of the inlet casing in a part of the centrifugal compressor, scattering the all or the one part of the impeller to the outside from the gap.
- According to the present invention, it is possible 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.
- Additionally, according to the present invention, it is possible to provide a supercharger including the above centrifugal compressor, and a method for manufacturing the above centrifugal compressor.
-
- {
Fig. 1} Fig. 1 is a longitudinal sectional view illustrating an embodiment of a supercharger. - {
Fig. 2} Fig. 2 is a sectional view taken along the A-A arrow of a silencer illustrated inFig. 1 . - {
Fig. 3} Fig. 3 is a sectional view taken along the B-B arrow of the silencer illustrated inFig. 2 . - {
Fig. 4} Fig. 4 is a partial enlarged view illustrating the vicinity of a fastening position of the silencer casing and a scroll casing illustrated inFig. 1 . - {
Fig. 5} Fig. 5 is a partial enlarged view illustrating the vicinity of a fastening position of the scroll casing and a flange section illustrated inFig. 1 . - {
Fig. 6} Fig. 6 is a diagram of outer peripheral edges of the scroll casing and the flange section as viewed from the P direction illustrated inFig. 1 . - {
Fig. 7} Fig. 7 is a sectional view taken along the C-C arrow of the outer peripheral edges of the scroll casing and the flange section illustrated inFig. 6 , which illustrates a state where the scroll casing and the flange section are in contact with each other. - {
Fig. 8} Fig. 8 is a sectional view taken along the C-C arrow of the outer peripheral edges of the scroll casing and the flange section illustrated inFig. 6 , which illustrates a state where the scroll casing and the flange section are separated from each other. - 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. - As illustrated in
Fig. 1 , thesupercharger 100 of this embodiment includes acentrifugal compressor 10, a turbine (not illustrated), and a bearingpedestal 20. Thecentrifugal compressor 10 and the turbine are connected to arotor shaft 30. Therotor shaft 30 is supported by the bearingpedestal 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 thesupercharger 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)). Thecentrifugal compressor 10 includes animpeller 11, an air inlet casing 12 (inlet casing), ascroll section 13,partition plates 14, and asilencer 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. Theimpeller 11 connected through therotor shaft 30 rotates with the rotation of the turbine disc, air flowing in from anintake 11a is compressed, and the compressed air is discharged from adischarge port 11b. The compressed air discharged from thedischarge port 11b flows in thescroll section 13 to be led to the intake manifold of the marine diesel engine. - The
air inlet casing 12 and thescroll section 13 are formed of a metal member manufactured by casting in order to form a complicated shape. As this 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. As the cast iron, various materials such as gray cast iron can be used. However, ductile cast iron (FCD: Ferrum Casting Ductile) where black smoke is spheroidized in a basic structure is preferably used. The metal material by casting is easily formed in a complicated shape by casting, but has a brittle characteristic. - Now, respective components included in the
centrifugal compressor 10 will be described. - As illustrated in
Fig. 1 , theimpeller 11 is mounted on therotor shaft 30 extending along the axial line X, and rotates about the axial line X with the rotation of therotor shaft 30 around the axial line X. Theimpeller 11 rotates around the axial line X, so that air flowing in from theintake 11a is compressed to be discharged from thedischarge port 11b. - As illustrated in
Fig. 1 , theimpeller 11 includes ahub 11c mounted on therotor shaft 30,blades 11d mounted on an outer peripheral surface of thehub 11c, and aflow passage 11e. Theimpeller 11 is provided with a space defined by the outer peripheral surface of thehub 11c and an inner peripheral surface of theair inlet casing 12, and this space is partitioned into a plurality of spaced by a plurality of theblades 11d. Theimpeller 11 applies radial centrifugal force to air flowing in from theintake 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 thedischarge port 11b to flow into adiffuser 13a. - The
air inlet casing 12 is a member that houses theimpeller 11 and discharges, from thedischarge port 11b, air flowing in from theintake 11a in the direction of the axial line X of therotor shaft 30. The air inlet casing 12 forms theflow passage 11e for guiding air flowing in from theintake 11a along the axial line X in the radial direction orthogonal to the axial line X, and then leading the air to thedischarge port 11b, together with theimpeller 11. - The
scroll section 13 is a device in which compressed air discharged from thedischarge port 11b flows, and which converts kinetic energy (dynamic pressure) applied to the compressed air into pressure energy (static pressure). Thescroll 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 theair inlet casing 12. - The
scroll section 13 includes thediffuser 13a, ascroll casing 13b, and avolute chamber 13c. Thevolute chamber 13c is a space formed by thescroll casing 13b. As illustrated inFig. 2 , thescroll casing 13b is connected to aflange section 20a of the bearingpedestal 20 by fasteningbolts 41. - The
diffuser 13a is an airfoil member disposed on the downstream side of thedischarge port 11b of theimpeller 11, and forms a flow passage for leading compressed air from thedischarge port 11b to thevolute chamber 13c. Thediffuser 13a is provided so as to surround thedischarge port 11b for compressed air provided on the whole periphery of theimpeller 11. - The
diffuser 13a decelerates the flow velocity of the compressed air discharged from thedischarge port 11b of theimpeller 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 thediffuser 13a flows in thevolute chamber 13c communicated with thediffuser 13a. The working fluid flowing in thevolute 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 theintake 11a, and have predetermined lengths in the direction of the axial line X. As illustrated inFig. 2 , thepartition plates 14 are formed by fourpartition plates partition plates 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 theair inlet casing 12. Additionally, thepartition plates 14 support asilencer casing 15a of thesilencer 15, and each function as a straightening vane for straightening air circulating inside thesilencer 15. - As illustrated in
Fig. 3 , thepartition 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 thepartition plate 14b, butother partition plates - The
partition plates 14 are each formed of a metal member manufactured by rolling. As this 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. As 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. On the other hand, 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. Thus, 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.
- For example, the ductile cast iron material and the SS400 material each have the tensile strength of 400 N/mm2 to 500 N/mm2 at a normal temperature. On the other hand, the ductile cast iron material has elongation of about 10% in breakage, the S400 material has elongation of 20% or more in breakage. Accordingly, the SS400 material has higher ductility than the ductile cast iron material.
- In the
centrifugal compressor 10 of this embodiment, all or one part of theblades 11d of theimpeller 11 is fractured or falls to scatter in the radial direction, and collides with theair inlet casing 12. Theflow passage 11e of thecentrifugal compressor 10 is a flow passage that gradually inclines from theintake 11a toward thedischarge 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 theair inlet casing 12. The impact force in the direction of the axial line X is impact force of scattering theair inlet casing 12 in the direction away from thescroll section 13, and therefore there is a possibility that theair inlet casing 12 formed of the metal member manufactured by casting is damaged to fall from a mounting position. - In a case where the all or the one part of the
air inlet casing 12 falls from the mounting position, and scatters toward thesilencer 15, the all or the one part of theair inlet casing 12 collides with thepartition plates 14 disposed inside thesilencer 15. Accordingly, thepartition 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 theair inlet casing 12 to stop scattering. That is, thepartition plates 14 are intentionally deformably damaged to absorb impact, so that it is possible to suppress the scattering of theair inlet casing 12 to the outside of thesupercharger 100, or suppress failure such as generation of a gap (opening) due to impact applied to other part. - The plate thickness of each
partition plate 14 of this embodiment is in the range of 4 mm to 9 mm. Additionally, the plate thickness of eachpartition 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 thepartition plates 14 is too low, even when thepartition plates 14 are largely deformed by the impact load of the all or the one part of theair inlet casing 12 which has been damaged to scatter, thepartition plates 14 cannot sufficiently absorb the impact load, and the all or the one part of theair inlet casing 12 scatters outside thesupercharger 100. - On the other hand, when the rigidity of the
partition plates 14 is too high, deformations of thepartition plates 14 against the impact load of the all or the one part of theair inlet casing 12 which has scattered are reduced. Then, thepartition plates 14 cannot sufficiently absorb the impact load, and the impact load is propagated to other part, so that a gap (opening) is generated. - 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 theair 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 eachpartition plate 14 is set in this range. - The
silencer 15 illustrated inFig. 1 is a device that lowers a level of noise generated in thecentrifugal compressor 10. As illustrated inFig. 1 , thesilencer 15 includes thesilencer casing 15a. Thesilencer casing 15a defines aflow passage 15b for leading, to theintake 11a of theair inlet casing 12, air flowing in from the direction illustrated by the arrow inFig. 1 (direction orthogonal to the axial line X). Anoise reduction material 15e is disposed around theflow passage 15b so as to surround theflow passage 15b. Thisnoise reduction material 15e absorbs a part of the noise generated in thecentrifugal compressor 10, and the level of the noise is lowered. - As illustrated in
Fig. 1 , thesilencer casing 15a houses inside thepartition plates 14. An end of eachpartition plate 14 is connected to thesilencer casing 15a. Accordingly, eachpartition plate 14 functions as a support member for supporting thesilencer casing 15a as well. - Now, a structure of fastening positions at which the
silencer casing 15a is fastened to thescroll casing 13b will be described. - As described above, when all or one part of the
air inlet casing 12 falls from the mounting position to scatter, the all or the one part of theair inlet casing 12 collides with thepartition plates 14. In the above description, thepartition plates 14 each formed of the rolled steel material absorb and stop kinetic energy of impact by plastically deforming when impact load is generated. In the following description, a structure in which the kinetic energy of the impact is absorbed by a part other than thepartition plates 14 will be described. - As illustrated in
Fig. 4 , aflange section 13d provided in an end, on a side close to thesilencer 15, of thescroll casing 13b, and aflange section 15c provided in an end, on a side close to thescroll casing 13b, of thesilencer casing 15a are fastened to each other at fastening positions (first fastening positions) illustrated inFig. 4 by fastening bolts 40 (first fastening bolts). - 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, theflange section 13d is fastened to theflange section 15c by thefastening bolts 40. - As the
fastening bolts 40, chromium molybdenum steel containing a carbon amount of 0.33% to 0.38%, called SCM435, is preferably used. 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 withfastening holes 15d extending along the axial line X. Additionally, theflange section 13d is provided withfastening holes 13e extending along the axial line X. Inner peripheral surfaces of thesefastening holes shaft section 40b of eachfastening 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 ahead section 40a and theshaft section 40b to the vicinity of a tip of theshaft 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 thefastening bolts 40. Even in a case where plastic deformation is performed until the elongation amount increases, stress is hardly locally concentrated on thebolts 40, and therefore fracture is not caused until large elongation, which is suitable. - The
flange section 13d and theflange 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 thehead section 40a of eachfastening bolt 40, and having a predetermined length are inserted into theshaft sections 40b of thefastening bolts 40. In this state, the male screw formed on theshaft section 40b of eachfastening bolt 40 meshes with the female screws formed on the inner peripheral surfaces of thefastening holes - The
spacers 50 are each formed of a metal member manufactured by rolling. As this 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. As 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.
- As illustrated in
Fig. 4 , theair inlet casing 12 and thescroll casing 13b are fastened to each other by fasteningbolts 42 inserted into through holes provided in aflange section 12a of theair inlet casing 12. Only one fastening position is illustrated inFig. 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, theair inlet casing 12 is fastened to thescroll casing 13b by thefastening bolts 42. - In the above description, the plastic deformations of the
partition plates 14 absorb and stop kinetic energy of impact. Herein, a structure in which the kinetic energy of the impact can be absorbed by thefastening bolts 40 and thespacers 50 other than thepartition plates 14 will be described. - As described above, when all or one part of the
air inlet casing 12 falls from the mounting position to scatter, the all or the one part of theair inlet casing 12 collides with thepartition plates 14. By this collision, impact in the direction separated from thescroll casing 13b is applied to thesilencer casing 15a. This impact acts on the fastening positions of thefastening bolts 40, theflange section 15c, and theflange section 13d. - As illustrated in
Fig. 4 , the reason why fastening is performed in a state where eachspacer 50 is inserted into theshaft section 40b of thefastening bolt 40 is that the length in the direction of the axial line X of eachfastening bolt 40 is increased and a large elongation amount is ensured. The predetermined length of eachspacer 50 is made longer than at least the diameter of theshaft section 40b of eachfastening 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 thefastening bolts 40 are prevented from being fractured, and kinetic energy of impact due to collision with the all or the one part of theair inlet casing 12 that falls from the mounting position to scatter can be absorbed by the elongation of thefastening bolts 40. - As illustrated in
Fig. 4 , the reason why thespacers 50 are provided is that kinetic energy of impact is absorbed by thespacers 50 formed of the rolled steel materials having ductility. The lengths in the direction of the axial line X of thespacers 50 disposed between thehead sections 40a of thefastening bolts 40 and theflange section 15c are contracted by impact that acts on the fastening positions of thefastening bolts 40 and theflange section 15c. Thespacers 50 formed of the rolled steel materials have ductility resulting in breakage after large plastic deformation, and therefore thespacers 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. - Now, a structure of fastening positions at which the
scroll casing 13b is fastened to the bearingpedestal 20 will be described. - As illustrated in
Fig. 1 , the bearingpedestal 20 of this embodiment includesflange section 20a for supporting thescroll section 13, and abearing section 20b for supporting therotor shaft 30. - As illustrated in
Fig. 5 , aflange section 13f provided in an end, on a side close to the bearingpedestal 20, of thescroll casing 13b, and aflange section 20a provided in an end, on a side close to thescroll casing 13b, of the bearingpedestal 20 are fastened to each other at fastening positions (second fastening positions) illustrated inFig. 5 by fastening bolts 41 (second fastening bolts). - As the
fastening bolts 41, chromium molybdenum steel containing a carbon amount of 0.33% to 0.38%, called SCM435, is preferably used. The SCM435 is excellent in high strength, and a large elongation amount. - The
flange section 13f is provided withfastening holes 13g extending along the axial line X. Additionally, theflange section 20a is provided withfastening holes 20c extending along the axial line X. Inner peripheral surfaces of thesefastening holes shaft section 41b of eachfastening bolt 41 extending along the axial line X is formed with a male screw on a whole surface from ahead section 41a and a tip. - The
flange section 13f and theflange 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 thehead section 41a of eachfastening bolt 41 are inserted into theshaft sections 41b of thefastening bolts 41. In this state, the male screw formed on theshaft section 41b of eachfastening bolt 41 meshes with the female screws formed on the inner peripheral surfaces of thefastening holes - The
spacers 51 are each formed of a metal member manufactured by rolling. As this 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. As 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.
- As described above, when all or one part of the
air inlet casing 12 falls from the mounting position, the all or the one part of theair inlet casing 12 collides with thepartition plates 14. By this collision, impact in the direction in which thescroll casing 13b is separated from the bearingpedestal 20 is applied. This impact acts on the fastening positions of thefastening bolts 41, theflange section 13f, and theflange section 20a. - As illustrated in
Fig. 5 , the reason why fastening is performed in a state where eachspacer 51 is inserted intoshaft section 41b of thefastening bolt 41 is that the length in the direction of the axial line X of eachfastening bolt 41 is increased and a large elongation amount is ensured. The elongation amounts are increased, so that thefastening bolts 41 are prevented from being fractured, and kinetic energy of impact due to collision with the all or the one part of theair inlet casing 12 that falls from the mounting position to scatter can be absorbed by the elongation of thefastening bolts 41. - As illustrated in
Fig. 5 , the reason why thespacers 51 are provided is that kinetic energy of impact is absorbed by thespacers 51 formed of the rolled steel materials having ductility. The lengths in the direction of the axial line X of thespacers 51 disposed between thehead sections 41a of thefastening bolts 41 and theflange section 13f are contracted by impact that acts on the fastening positions of thefastening bolts 41 and theflange section 13f. Thespacers 51 formed of the rolled steel materials have ductility resulting in breakage after large plastic deformation, and therefore thespacers 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. - Now, scroll
clamp members 60 mounted on outer peripheral edges of thecasing 13b and the bearingpedestal 20 will be described. The vicinity of the fastening position of theflange section 13f of thescroll casing 13b, and theflange section 20a of the bearingpedestal 20 is illustrated inFig. 6. Fig. 6 is a diagram of the outer peripheral edges of theflange section 13f of thescroll casing 13b and theflange section 20a as viewed from the P direction illustrated inFig. 1 . - As illustrated in
Fig. 6 , a plurality of theclamp members 60 are mounted between a plurality of the fastening positions (second fastening positions) by thefastening bolts 41, in the peripheral direction around the axial line X. - As illustrated in
Fig. 7 , theclamp members 60 haverespective recesses 60a that surround the outer peripheral edge of theflange section 20a and the outer peripheral edge of theflange section 13f of thescroll casing 13b from the outer peripheral side. Additionally, theclamp members 60 have respective throughholes 60b which are opened to therecesses 60a, and extend in the direction of the axial line X. - As illustrated in
Fig. 7 , theflange section 20a hasfastening holes 20d extending in the direction of the axial line X. Only onefastening hole 20d is illustrated inFig. 7 , but a plurality of fastening positions are provided in the peripheral direction around the axial line X at equal intervals. On inner peripheral surfaces of thefastening holes 20d, female screws are formed. On the other hand, on outer peripheral surfaces of shaft sections of fastening bolts 43 (third fastening bolts) inserted into the throughholes 60b and thefastening holes 20d, male screws are formed. The male screws of thefastening bolts 43 meshes with the female screws of thefastening holes 20d, so that theflange section 20a and theclamp members 60 are fastened to each other. - In a state where the
clamp members 60 are fastened to theflange section 20a,predetermined gaps 60c are provided between an end face 13i in the direction of the axial line X of thescroll casing 13b, and end faces 60e in the direction of the axial line X of therecesses 60a. The width along the axial line X of eachgap 60c is denoted by d5. - The
flange section 20a includes acontact surface 20e that is in contact with thescroll casing 13b, anend face 20f that forms aflow passage 13h (second flow passage) for allowing compressed air to circulate, and a steppedsection 20g that connects thecontact surface 20e and theend face 20f. As illustrated inFig. 7 , theend face 20f is disposed on a side closer to theflow passage 13h than thecontact 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 eachgap 60c. - As described above, when the
air inlet casing 12 falls from the mounting position, theair inlet casing 12 collides with thepartition plates 14. By this collision, impact in the direction in which thescroll casing 13b is separated from the bearingpedestal 20 is applied. This impact force acts on the fastening positions of thefastening bolts 41, theflange section 13f, and theflange section 20a. - As illustrated in
Fig. 7 , the reason why thepredetermined 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 theimpeller 11 cannot be sufficiently absorbed, and thefastening bolts 41 are fractured and thescroll casing 13b is separated from the bearingpedestal 20, theclamp members 60 absorb impact caused by the separatedscroll casing 13b. - In a case where the
predetermined gaps 60c are provided, fastening force in the vicinities of theclamp members 60 increases, and thefastening bolts 41 are hardly fractured. In this case, while fracture of thefastening bolts 41 can be prevented, there is a possibility that load is applied to other part (for example, thescroll casing 13b), and the part to which the load is applied is fractured. - When the
fastening bolts 41 are fractured, and thescroll casing 13b is separated from the bearingpedestal 20, thescroll casing 13b is brought into the state illustrated inFig. 8 from the state illustrated inFig. 7 . - When the
scroll casing 13b is brought into the state illustrated inFig. 8 , the end face 13i in the direction of the axial line X of thescroll casing 13b comes into contact with the end faces 60e in the direction of the axial line X of therecesses 60a. In this state, on thecontact surface 20e, agap 60d having a width d5 in the direction of the axial line X is formed. When thisgap 60d is communicated with theflow passage 13h to cause the gap (opening), there is a possibility that a part of the damagedblades 11d scatters from theflow passage 13h to the outside. - In this embodiment, as illustrated in
Fig. 8 , the width d6 in the direction of the axial line X of the steppedsection 20g is wider than the width d5 of thegap 60d. Therefore, faults are prevented such as thegap 60d brought into communication with theflow passage 13h, causing a gap (opening) for allowing a damaged member to pass. - In this embodiment, the
gaps 60c are intentionally provided between the end face 13i in the direction of the axial line X of thescroll casing 13b and the end faces 60e in the direction of the axial line X of therecesses 60a, so that fracture at a position other than the fastening positions of thefastening bolts 41 is prevented. Then, in a case where thefastening bolts 41 are fractured, the impact caused by separation of thescroll casing 13b from the bearingpedestal 20 is absorbed by theclamp members 60. - Now, a method for manufacturing the centrifugal compressor of this embodiment will be described.
- In a method for manufacturing the
centrifugal compressor 10 of this embodiment, thecentrifugal compressor 10 is manufactured by the following steps. - In a first step, the
impeller 11 that compresses air flowing in from theintake 11a, and then discharges the compressed air from thedischarge port 11b is mounted on therotor shaft 30. - In a second step, the flow passage for guiding the air flowing in from the
intake 11a in the direction of the axial line X of therotor shaft 30, in the direction inclined from the direction of the axial line X, and then leading the air to thedischarge port 11b is formed by mounting theair inlet casing 12 so as to house theimpeller 11. - In a third step, the
scroll section 13 in which the compressed air discharged from thedischarge 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 theair inlet casing 12. - In a fourth step, 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 theintake 11a, and are radially disposed about the axial line X so as to have predetermined lengths in the direction of the axial line X. - By the above steps, the
centrifugal compressor 10 of this embodiment is manufactured. - Operation and effects exerted by the
centrifugal compressor 10 provided in thesupercharger 100 of this embodiment described above will be described. - According to the
centrifugal compressor 10 provided in thesupercharger 100 of this embodiment, in a case where all or one part of theimpeller 11 is fractured or falls, all or one part of theimpeller 11 scatters in the radial direction to collide with theair inlet casing 12. - The air inlet casing 12 forms the
flow passage 11e for guiding air flowing in from theintake 11a in the direction of the axial line X of therotor shaft 30, in the direction inclined from the direction of the axial line X, and leading the air to thedischarge port 11b. When all or one part of theimpeller 11 which scatters in the radial direction collides with theair inlet casing 12, impact in the radial direction is applied to theair inlet casing 12. Similarly, when all or one part of theimpeller 11 which scatters in the radial direction collides with theair inlet casing 12, impact in the direction of the axial line X is applied to theair inlet casing 12. The impact in the direction of the axial line X is impact causing the all or the one part of theair inlet casing 12 to scatter in the direction away from thescroll section 13, and therefore there is a possibility that the all or the one part of theair inlet casing 12 falls from the mounting position. - According to the
centrifugal compressor 10 of this embodiment, the plurality ofpartition 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 theintake 11a. Therefore, the all or the one part of theimpeller 11 that scatters, or the all or the one part of theair inlet casing 12 that scatters in the direction away from thescroll section 13 collides with the plurality ofpartition plates 14 due to impact resulting from the scattering of theimpeller 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 ofpartition plates 14 are suitably plastically deformed by collision with the all or the one part of theair 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 theair inlet casing 12 in a part of thecentrifugal compressor 10, scattering the all or the one part of theimpeller 11 to the outside from the gap. - According to the
centrifugal compressor 10 of this embodiment, when the all or the one part of theair inlet casing 12 that scatters in the direction away from thescroll section 13 collides with thesilencer casing 15a that houses thepartition plates 14, impact is applied in the direction in which thesilencer casing 15a is separated from the scroll casing. This impact is absorbed by contraction of thespacers 50 disposed between thehead sections 40a of thefastening bolts 40 and thesilencer casing 15a. Thus, the impact in the direction of the axial line is absorbed by use of thespacers 50 fastened while being inserted into thefastening bolts 40, so that faults such as fracture of thefastening bolts 40 are suppressed. Accordingly, it is possible to suppress faults such as a gap generated by the scattering of the all or the one part of theair inlet casing 12 in a part of thecentrifugal compressor 10, scattering the all or the one part of theimpeller 11 to the outside from the gap. - In the
centrifugal compressor 10 of this embodiment, thefastening bolts 40 include male screws formed on the outer peripheral surfaces of theshaft sections 40b from thehead sections 40a to the tips. Consequently, deformations at the respective parts of the outer peripheral surfaces of theshaft sections 40b from thehead sections 40a to the tips are made uniform, so that the above failure can be suppressed by use of thefastening bolts 40 having increased energy absorption of impact. - According to the
centrifugal compressor 10 of this embodiment, when the all or the one part of theair inlet casing 12 that scatters in the direction away from thescroll section 13 collides with thesilencer casing 15a that houses thepartition plates 14, impact in the direction in which thescroll casing 13b is separated from theflange section 20a of the bearingpedestal 20 is applied. This impact is absorbed by contraction of thespacers 51 disposed between thehead sections 41a of thefastening bolts 41 and thescroll casing 14b. Thus, impact in the direction of the axial line X is absorbed by use of thespacers 51 fastened while being inserted into thefastening bolts 41, so that faults such as fracture of thefastening bolts 41 are suppressed. Accordingly, it is possible to suppress faults such as a gap generated by the scattering of the all or the one part of theair inlet casing 12 in a part of thecentrifugal compressor 10, scattering the all or the one part of theimpeller 11 to the outside from the gap. - In the
centrifugal compressor 10 of this embodiment, thefastening bolts 41 include male screws formed on the outer peripheral surfaces of theshaft sections 40b from thehead sections 41a to the tips. Consequently, deformations at the respective parts of the outer peripheral surfaces of theshaft sections 40b from thehead sections 41a to the tips are made uniform, so that the above failure can be suppressed by use of thefastening bolts 41 having increased energy absorption of impact. - The
centrifugal compressor 10 of this embodiment includes a plurality of theclamp members 60 havingrecesses 60a that surround the outer peripheral edge of theflange section 20a and the outer peripheral edge of thescroll casing 13b from the outer peripheral side, and the throughholes 60b that are opened to therecesses 60a, and extend in the direction of the axial line X. Theflange section 20a has a plurality of thefastening holes 20d extending in the direction of the axial line X, in the peripheral direction around the axial line X. Then, theflange section 20a and theclamp members 60 are fastened to each other by thefastening bolts 43 inserted into the throughholes 60b and thefastening holes 20d. Furthermore, thepredetermined gaps 60c are provided between the end face 13i in the direction of the axial line X of thescroll casing 13b, and the end faces 60e in the direction of the axial line X of therecesses 60a. - Consequently, even in a case where the plurality of
fastening bolts 41 are fractured, and theflange section 20a of the bearingpedestal 20 and thescroll casing 13b are separated from each other, the end face 13i in the direction of the axial line X of thescroll casing 13b comes into contact with the end faces 60e in the direction of the axial line X of therecesses 60a. Impact caused by this contact is absorbed by the plurality ofclamp members 60 mounted in the peripheral direction around the axial line X. Consequently, it is possible to suppress faults such as a gap generated by the scattering of theair inlet casing 12 in a part of thecentrifugal compressor 10, scattering the all or the one part of the damagedimpeller 11 to the outside from the gap. - In this embodiment, the
flange section 20a is fastened to theclamp members 60 by thefastening bolts 43, and thepredetermined gaps 60c are provided between the end face 13i in the direction of the axial line X of thescroll casing 13b, and the end faces 60e in the direction of the axial line X of therecesses 60a. Additionally, theflange section 20a has the steppedsection 20g that connects thecontact surface 20e that is in contact with thescroll casing 13b, and theend face 20f of theflange section 20a that forms theflow passage 13h for allowing compressed air to circulate, and is disposed on the side closer to theflow passage 13h than thecontact surface 20e. - Consequently, in a case where the plurality of
fastening bolts 41 are fractured, theflange section 20a of the bearingpedestal 20 and thescroll casing 13b are separated from each other, and the end face 13i in the direction of the axial line X of thescroll casing 13b comes into contact with the end faces 60e in the direction of the axial line X of therecesses 60a, opening between theflange section 20a and thescroll casing 13b is suppressed by existence of the steppedsection 20g. Furthermore, the width d6 in the direction of the axial line X of the steppedsection 20g is wider than the width d5 of thepredetermined gap 60d, and therefore a communicated gap is not generated, and opening can be more reliably suppressed. - In the above description, the
rotor shaft 30 connected to theimpeller 11 provided in thecentrifugal compressor 10 rotates around the axial line X by a turbine (not illustrated) rotated by exhaust gas exhausted from the marine diesel engine. However, other aspect may be employed. For example, therotor shaft 30 may be rotated by other power source other than a motor connected to therotor shaft 30, or the like. - In the above description, the four
partition plates 14 are disposed at intervals of 90 degrees about the axial line X. However, other aspect may be employed. An arbitrary number of partition plates may be disposed. For example, 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. - In the above description, the
clamp members 60 are fastened to theflange section 20a of the bearingpedestal 20. However, other aspect may be employed. For example, theclamp members 60 may be fastened to theflange section 13e of thescroll casing 13b. In this case, theflange section 13e of thescroll 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. Additionally, thefastening bolts 43 are fastened to the plurality of fastening holes, so that theclamp members 60 are fastened to theflange section 13e of thescroll casing 13b. In this case, thegaps 60c described above are provided between the end face in the direction of the axial line X of theflange section 20a of the bearingpedestal 20, and the end face in the direction of the axial line X of the recesses of theclamp members 60. -
- 10 centrifugal compressor
- 11 impeller
- 11a intake
- 11b discharge port
- 11d blade
- 11e flow passage
- 12 air inlet casing (inlet casing)
- 13 scroll section
- 13b scroll casing
- 13d flange section
- 13f flange section
- 13h flow passage (second flow passage)
- 13i end face
- 14 partition plate
- 15 silencer
- 15a silencer casing
- 15b flow passage (first flow passage)
- 15c flange section
- 20 bearing pedestal
- 20a flange section
- 20e contact surface
- 20f end face
- 20g stepped section
- 30 rotor shaft
- 40 fastening bolt (first fastening bolt)
- 41 fastening bolt (second fastening bolt; flange section fastening bolt)
- 43 fastening bolt (third fastening bolts; clamp member fastening bolt)
- 50 spacer (first spacer member)
- 51 spacer (second spacer member)
- 60 clamp members
- 60a recess
- 60b through hole
- 60c gap
- 60d gap
- 60e end face
- 100 supercharger
Claims (10)
- A centrifugal compressor comprising: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 which is disposed on an outer peripheral side with respect to the inlet casing, and into which the compressed fluid discharged from the discharge port flows;a plurality of partition plates provided on an upstream side in a fluid circulation direction with respect to the intake, and each having a predetermined length in a direction of an axial line of the rotor shaft; anda silencer having a silencer casing for housing the plurality of partition plates, whereinthe plurality of partition plates are radially disposed about the axial line, and each are a rolled steel material having a plate thickness of 4 mm or more and 9 mm or less.
- The centrifugal compressor according to claim 1, wherein
the scroll section has a scroll casing forming a volute chamber into which the compressed fluid discharged from the discharge port flows,
the scroll casing and the silencer casing are fastened to each other at a plurality of first fastening positions in a peripheral direction around the axial line by a plurality of first fastening bolts extending in the direction of the axial line, and
the scroll casing and the silencer casing are fastened to each other in a state where cylindrical first spacer members each having an inner diameter smaller than a diameter of a head section of each of the first fastening bolts are inserted into shaft sections of the first fastening bolts. - The centrifugal compressor according to claim 2, wherein
the first fastening bolts each include a male screw formed on an outer peripheral surface of the shaft section from the head section to a tip. - The centrifugal compressor according to claim 2 or 3, comprising
a bearing pedestal having a bearing section for supporting the rotor shaft, and a flange section for supporting the scroll section, wherein
the flange section and the scroll casing are fastened to each other at a plurality of second fastening positions around the axial line by a plurality of second fastening bolts extending in the direction of the axial line, and
the flange section and the scroll casing are fastened to each other in a state where cylindrical second spacer members each having an inner diameter smaller than a diameter of a head section of each of the second fastening bolts are inserted into shaft sections of the second fastening bolts. - The centrifugal compressor according to claim 4, wherein
the second fastening bolts each include a male screw formed on an outer peripheral surface of the shaft section from the head section to a tip. - A centrifugal compressor comprising: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 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; anda 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 extend in the direction of the axial line, whereinone of either the flange section or the scroll casing has a plurality of fastening holes extending in the direction of the axial line, in a peripheral direction around the axial line,
one of either the flange section or the scroll casing, and the clamp members are fastened to each other by clamp member fastening bolts inserted into the through holes and the fastening holes, and
predetermined gaps are provided between an end face in the direction of the axial line of the other of either the flange section or the scroll casing, and end faces in the direction of the axial line of the recesses. - The centrifugal compressor according to claim 6, wherein
the flange section has the fastening holes, and is fastened to the clamp members by the clamp member fastening bolts,
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. - The centrifugal compressor according to claim 7, wherein a width in the direction of the axial line of the stepped section is wider than a width of each of the predetermined gaps.
- A supercharger comprising:a centrifugal compressor according to any one of claims 1 to 8; anda turbine that is rotated around the axial line by exhaust gas exhausted from an internal combustion engine, and is connected to the rotor shaft.
- A method for manufacturing a centrifugal compressor comprising 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; andproviding 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.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP18185764.0A EP3412916B1 (en) | 2014-03-31 | 2015-02-24 | Centrifugal compressor, supercharger, and method for manufacturing centrifugal compressor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014074071A JP6391970B2 (en) | 2014-03-31 | 2014-03-31 | Centrifugal compressor, supercharger, centrifugal compressor manufacturing method, and silencer |
PCT/JP2015/055240 WO2015151653A1 (en) | 2014-03-31 | 2015-02-24 | Centrifugal compressor, supercharger, and method for manufacturing centrifugal compressor |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18185764.0A Division-Into EP3412916B1 (en) | 2014-03-31 | 2015-02-24 | Centrifugal compressor, supercharger, and method for manufacturing centrifugal compressor |
EP18185764.0A Division EP3412916B1 (en) | 2014-03-31 | 2015-02-24 | Centrifugal compressor, supercharger, and method for manufacturing centrifugal compressor |
Publications (3)
Publication Number | Publication Date |
---|---|
EP3128184A1 true EP3128184A1 (en) | 2017-02-08 |
EP3128184A4 EP3128184A4 (en) | 2017-08-16 |
EP3128184B1 EP3128184B1 (en) | 2018-09-26 |
Family
ID=54239989
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15774147.1A Active EP3128184B1 (en) | 2014-03-31 | 2015-02-24 | Centrifugal compressor, supercharger, and method for manufacturing centrifugal compressor |
EP18185764.0A Active EP3412916B1 (en) | 2014-03-31 | 2015-02-24 | Centrifugal compressor, supercharger, and method for manufacturing centrifugal compressor |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18185764.0A Active EP3412916B1 (en) | 2014-03-31 | 2015-02-24 | Centrifugal compressor, supercharger, and method for manufacturing centrifugal compressor |
Country Status (5)
Country | Link |
---|---|
EP (2) | EP3128184B1 (en) |
JP (1) | JP6391970B2 (en) |
KR (1) | KR101918377B1 (en) |
CN (2) | CN106104006B (en) |
WO (1) | WO2015151653A1 (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2020179985A1 (en) * | 2019-03-06 | 2020-09-10 | (주)플로닉스 | Pump casing and magnet pump including same |
US20210156400A1 (en) * | 2019-11-27 | 2021-05-27 | James E. Petersen, Jr. | Noise abatement for air blowers |
US11177489B2 (en) | 2017-11-01 | 2021-11-16 | Ihi Corporation | Centrifugal compressor with diffuser |
US11248612B2 (en) | 2017-11-01 | 2022-02-15 | Ihi Corporation | Centrifugal compressor with gas and liquid cooling lines |
US11339800B2 (en) | 2017-11-01 | 2022-05-24 | Ihi Corporation | Centrifugal compressor with heat exchanger |
WO2023086775A1 (en) * | 2021-11-11 | 2023-05-19 | Progress Rail Locomotive Inc. | Compressor joint |
US11992612B2 (en) | 2018-03-30 | 2024-05-28 | Murata Manufacturing Co., Ltd. | Continuous positive airway pressure (CPAP) device |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015014550A1 (en) * | 2015-11-11 | 2017-05-11 | Man Diesel & Turbo Se | Intake system for an exhaust gas turbocharger and turbocharger |
JP6240251B2 (en) | 2016-03-30 | 2017-11-29 | 三菱重工業株式会社 | Compressor and supercharger |
DE102016111081A1 (en) * | 2016-06-17 | 2017-12-21 | Man Diesel & Turbo Se | flow machine |
JP6847683B2 (en) * | 2017-01-31 | 2021-03-24 | 三菱重工業株式会社 | Centrifugal compressor and turbocharger |
US11067098B2 (en) | 2018-02-02 | 2021-07-20 | Carrier Corporation | Silencer for a centrifugal compressor assembly |
JP2019203446A (en) * | 2018-05-23 | 2019-11-28 | 株式会社オティックス | Compressor housing for turbo charger and manufacturing method of the same |
JP7393095B2 (en) * | 2018-06-07 | 2023-12-06 | トヨタ自動車株式会社 | gas compression equipment |
JP7164346B2 (en) * | 2018-07-24 | 2022-11-01 | 三菱重工マリンマシナリ株式会社 | Rotating machines and turbochargers |
GB201910815D0 (en) * | 2019-07-29 | 2019-09-11 | Cummins Ltd | Bearing housing and method of manufacture |
KR20230002936A (en) * | 2020-06-04 | 2023-01-05 | 미쓰비시주코마린마시나리 가부시키가이샤 | Turbine housing and supercharger |
CN117823463A (en) * | 2023-12-08 | 2024-04-05 | 南京磁谷科技股份有限公司 | High-speed centrifugal compressor air inlet chamber structure, centrifugal compressor and air inlet method |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3635580A (en) * | 1970-02-26 | 1972-01-18 | Westinghouse Electric Corp | Centrifugal refrigerant gas compressor capacity control |
US4181466A (en) * | 1977-03-17 | 1980-01-01 | Wallace Murray Corp. | Centrifugal compressor and cover |
JPS6413299U (en) * | 1987-07-15 | 1989-01-24 | ||
JP4359798B2 (en) | 1999-11-05 | 2009-11-04 | 株式会社Ihi | Exhaust turbine turbocharger |
DE10002581C2 (en) * | 2000-01-21 | 2002-01-17 | Man B & W Diesel Ag | turbocharger |
DE10050931C5 (en) * | 2000-10-13 | 2007-03-29 | Man Diesel Se | Turbomachine with radial impeller |
DE10107807C1 (en) * | 2001-02-20 | 2002-07-25 | Man B & W Diesel Ag | Flow machine with radial compressor wheel, used as a turbosupercharger, has cavity between inner cylinder of spiral casing and casing insertion piece |
WO2005012800A1 (en) * | 2003-07-31 | 2005-02-10 | Matsushita Electric Industrial Co., Ltd. | Air conditioner |
EP1860284A1 (en) * | 2006-05-23 | 2007-11-28 | ABB Turbo Systems AG | Casings assembling |
KR101050987B1 (en) * | 2006-08-24 | 2011-07-21 | 에이비비 터보 시스템즈 아게 | Fixing filter muffler |
JP4648347B2 (en) * | 2007-02-23 | 2011-03-09 | 三菱重工業株式会社 | Hybrid exhaust turbine turbocharger |
JP5297457B2 (en) * | 2008-07-17 | 2013-09-25 | 名古屋油化株式会社 | Buffer sound absorbing material and sound absorbing structure |
JP2010127240A (en) * | 2008-11-28 | 2010-06-10 | Mitsubishi Heavy Ind Ltd | Fitting structure of impeller |
JP5230590B2 (en) * | 2009-12-07 | 2013-07-10 | 三菱重工業株式会社 | Exhaust inlet casing of exhaust turbine supercharger |
US20110305554A1 (en) * | 2010-06-14 | 2011-12-15 | Honeywell International Inc. | Light weight vaneless compressor containment design |
DE102010038631B4 (en) * | 2010-07-29 | 2017-07-06 | Man Diesel & Turbo Se | Turbo compressor for an internal combustion engine |
JP6008495B2 (en) * | 2011-12-16 | 2016-10-19 | 三菱重工業株式会社 | Exhaust turbine turbocharger |
CN202483956U (en) * | 2012-01-05 | 2012-10-10 | 黄晓东 | Centrifugal cooling water pump |
-
2014
- 2014-03-31 JP JP2014074071A patent/JP6391970B2/en active Active
-
2015
- 2015-02-24 EP EP15774147.1A patent/EP3128184B1/en active Active
- 2015-02-24 CN CN201580013773.6A patent/CN106104006B/en active Active
- 2015-02-24 CN CN201810697793.5A patent/CN108799204B/en active Active
- 2015-02-24 KR KR1020167026159A patent/KR101918377B1/en active IP Right Grant
- 2015-02-24 WO PCT/JP2015/055240 patent/WO2015151653A1/en active Application Filing
- 2015-02-24 EP EP18185764.0A patent/EP3412916B1/en active Active
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11177489B2 (en) | 2017-11-01 | 2021-11-16 | Ihi Corporation | Centrifugal compressor with diffuser |
US11248612B2 (en) | 2017-11-01 | 2022-02-15 | Ihi Corporation | Centrifugal compressor with gas and liquid cooling lines |
US11339800B2 (en) | 2017-11-01 | 2022-05-24 | Ihi Corporation | Centrifugal compressor with heat exchanger |
US11992612B2 (en) | 2018-03-30 | 2024-05-28 | Murata Manufacturing Co., Ltd. | Continuous positive airway pressure (CPAP) device |
WO2020179985A1 (en) * | 2019-03-06 | 2020-09-10 | (주)플로닉스 | Pump casing and magnet pump including same |
US20210156400A1 (en) * | 2019-11-27 | 2021-05-27 | James E. Petersen, Jr. | Noise abatement for air blowers |
US11859641B2 (en) * | 2019-11-27 | 2024-01-02 | James E. Petersen, Jr. | Noise abatement for air blowers |
WO2023086775A1 (en) * | 2021-11-11 | 2023-05-19 | Progress Rail Locomotive Inc. | Compressor joint |
Also Published As
Publication number | Publication date |
---|---|
KR20160125467A (en) | 2016-10-31 |
CN108799204B (en) | 2020-03-13 |
JP6391970B2 (en) | 2018-09-19 |
KR101918377B1 (en) | 2018-11-13 |
CN106104006A (en) | 2016-11-09 |
CN106104006B (en) | 2019-06-18 |
WO2015151653A1 (en) | 2015-10-08 |
EP3128184A4 (en) | 2017-08-16 |
EP3128184B1 (en) | 2018-09-26 |
EP3412916B1 (en) | 2019-06-26 |
EP3412916A1 (en) | 2018-12-12 |
CN108799204A (en) | 2018-11-13 |
JP2015197053A (en) | 2015-11-09 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP3412916B1 (en) | Centrifugal compressor, supercharger, and method for manufacturing centrifugal compressor | |
EP3324053B1 (en) | Compression device and supercharger | |
JP6272248B2 (en) | Centrifugal compressor and supercharger provided with the same | |
JP6404087B2 (en) | Centrifugal compressor and supercharger provided with the same | |
EP2395203A2 (en) | Light weight vaneless compressor containment design | |
EP3067569B1 (en) | Centrifugal compressor, supercharger, and method for manufacturing centrifugal compressor | |
EP2868910A1 (en) | Silencer for supercharger | |
JP6847683B2 (en) | Centrifugal compressor and turbocharger | |
EP3073091A1 (en) | Compressor | |
JP6517386B2 (en) | Centrifugal compressor and supercharger | |
JP6404082B2 (en) | Centrifugal compressor and supercharger provided with the same | |
EP3051144B1 (en) | Compressor and supercharger | |
EP3163090B1 (en) | Centrifugal compressor and supercharger with same | |
JP6456596B2 (en) | Centrifugal compressor, supercharger, and method of manufacturing centrifugal compressor | |
CN1178288A (en) | Rupture-protection arrangement for radial turbines of turbochargers | |
JP6541956B2 (en) | Centrifugal compressor and turbocharger equipped with the same | |
EP4047186A1 (en) | Gas expander |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE |
|
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 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE |
|
17P | Request for examination filed |
Effective date: 20160922 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F04D 29/44 20060101AFI20170306BHEP Ipc: F04D 29/66 20060101ALI20170306BHEP Ipc: F04D 29/42 20060101ALI20170306BHEP |
|
DAX | Request for extension of the european patent (deleted) | ||
A4 | Supplementary search report drawn up and despatched |
Effective date: 20170719 |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F04D 29/42 20060101ALI20170713BHEP Ipc: F04D 29/66 20060101ALI20170713BHEP Ipc: F04D 29/44 20060101AFI20170713BHEP |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
INTG | Intention to grant announced |
Effective date: 20180531 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: ARAKAWA, HIROYUKI |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 1046357 Country of ref document: AT Kind code of ref document: T Effective date: 20181015 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602015017155 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20180926 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181226 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181227 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181226 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 1046357 Country of ref document: AT Kind code of ref document: T Effective date: 20180926 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190126 Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190126 Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602015017155 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20190627 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20190224 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190224 Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20190228 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190224 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190224 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190228 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190228 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190224 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R082 Ref document number: 602015017155 Country of ref document: DE Representative=s name: HOFFMANN - EITLE PATENT- UND RECHTSANWAELTE PA, DE Ref country code: DE Ref legal event code: R081 Ref document number: 602015017155 Country of ref document: DE Owner name: MITSUBISHI HEAVY INDUSTRIES MARINE MACHINERY &, JP Free format text: FORMER OWNER: MITSUBISHI HEAVY INDUSTRIES, LTD., TOKYO, JP |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: NV Representative=s name: KELLER SCHNEIDER PATENT- UND MARKENANWAELTE AG, CH Ref country code: CH Ref legal event code: PUE Owner name: MITSUBISHI HEAVY INDUSTRIES MARINE MACHINERY A, JP Free format text: FORMER OWNER: MITSUBISHI HEAVY INDUSTRIES, LTD., JP |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20150224 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180926 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20231229 Year of fee payment: 10 Ref country code: CH Payment date: 20240301 Year of fee payment: 10 |