EP3067569B1 - Kreiselverdichter, turbolader und verfahren zur herstellung des kreiselverdichters - Google Patents

Kreiselverdichter, turbolader und verfahren zur herstellung des kreiselverdichters Download PDF

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Publication number
EP3067569B1
EP3067569B1 EP15774141.4A EP15774141A EP3067569B1 EP 3067569 B1 EP3067569 B1 EP 3067569B1 EP 15774141 A EP15774141 A EP 15774141A EP 3067569 B1 EP3067569 B1 EP 3067569B1
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EP
European Patent Office
Prior art keywords
axis line
guide cylinder
containment ring
radial direction
centrifugal compressor
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Application number
EP15774141.4A
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English (en)
French (fr)
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EP3067569A4 (de
EP3067569A1 (de
Inventor
Taiji Tezuka
Yasuharu Chuman
Hiroyuki Arakawa
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Priority claimed from JP2014074070A external-priority patent/JP6456596B2/ja
Priority claimed from JP2014212793A external-priority patent/JP6541956B2/ja
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP3067569A1 publication Critical patent/EP3067569A1/de
Publication of EP3067569A4 publication Critical patent/EP3067569A4/de
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    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • F01D21/04—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for responsive to undesired position of rotor relative to stator or to breaking-off of a part of the rotor, e.g. indicating such position
    • F01D21/045—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for responsive to undesired position of rotor relative to stator or to breaking-off of a part of the rotor, e.g. indicating such position special arrangements in stators or in rotors dealing with breaking-off of part of rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/04—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector
    • 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers

Definitions

  • the present invention relates to a centrifugal compressor, a turbocharger, and a method for manufacturing a centrifugal compressor.
  • a centrifugal compressor As a compressor of a turbocharger which increases the pressure of air which is supplied to an internal combustion engine which is used in a ship or the like, to atmospheric pressure or more, a centrifugal compressor is known (refer to, for example, Japanese Unexamined Patent Application Publication No. 2011-117417 ).
  • the centrifugal compressor is provided with a delivery fan which is mounted on a rotor shaft, a guide cylinder which accommodates the delivery fan, and a scroll part into which compressed air which is discharged from the guide cylinder flows.
  • the centrifugal compressor discharges compressed air from a discharge port by guiding the compressed air from a direction of an axis line to an inclined direction while compressing air which flows in in the direction of the axis line from an intake port.
  • Japanese Unexamined Patent Application Publication No. 2001-132465 discloses a centrifugal compressor which is provided with a shock-absorbing partition wall which protects a tank accommodating lubricating oil such that even in a case where the whole or a part of a delivery fan (a compressor impeller) is thrown to the outside by a centrifugal force, the lubricating oil does not leak out due to the thrown delivery fan.
  • US 2011/0041494 A1 discloses a compressor with an impeller wheel including a plurality of blades which is rotatably mounted within a housing between an inlet and outlet volute.
  • the housing has an inner wall defining a surface located in close proximity to radially outer edges of the impeller blades which sweep across the surface as the impeller wheel rotates.
  • the compressor housing incorporates at least one section comprised of a deformable, energy absorbing material arranged to deform and absorb energy generated as a result of impellor wheel failure.
  • JP 2013-170545 A also discloses the provision of an annular member inside a centrifugal compressor which surrounds the impeller and forms part of the flow path through which the compressed fluid is discharged.
  • EP 0 834 646 A1 discloses these structural features embodied in the turbine of a turbocharger instead of a compressor.
  • the whole or a part of the delivery fan breaks or falls off, thereby being thrown in a radial direction orthogonal to a direction of an axis line of a rotor shaft
  • the whole or a part of the delivery fan may break a guide cylinder which is located outside and be thrown to the outside.
  • the whole or a part of the delivery fan may collide with the guide cylinder, thereby causing a gap (a port opening) in a part of the centrifugal compressor, and the whole or a part of the delivery fan which has been broken may be thrown from the gap to the outside.
  • the present invention has been made in view of such circumstances and has an object to provide a centrifugal compressor in which in a case where the whole or a part of a delivery fan breaks or falls off, thereby being thrown in a radial direction orthogonal to a direction of an axis line of a rotor shaft, it is possible to prevent a problem in that the whole or a part of the delivery fan is thrown to the outside.
  • the present invention has an object to provide a turbocharger provided with the above-described centrifugal compressor, and a method for manufacturing the above-described centrifugal compressor.
  • centrifugal compressor with the features of claim 1, a turbocharger with the features of claim 6 and a method for manufacturing a centrifugal compressor with the features of claim 7.
  • Preferred embodiments follow from the other claims.
  • the present invention adopts the following means.
  • a centrifugal compressor including: an impeller (delivery fan) which is mounted on a rotor shaft and compresses a fluid flowing in from an intake port and discharges a compressed fluid from a discharge port; a guide cylinder which accommodates the delivery fan; a scroll part which is disposed further toward the outer periphery side than is the guide cylinder, and into which the compressed fluid discharged from the discharge port flows; and an annular member being a first containment ring which is mounted at a linking position between the discharge port side of the guide cylinder and the scroll part so as to surround the delivery fan around an axis line of the rotor shaft.
  • an impeller delivery fan
  • the outer diameter of a blade is made to be larger on the discharge port side than on the intake port side. Therefore, the center of gravity of the delivery fan is located on the discharge port side. Further, the linking position between the discharge port side of the guide cylinder and the scroll part is at a position corresponding to the center of gravity of the delivery fan (hereinafter referred to as a position of the center of gravity) in the axis line, or in the vicinity of the position of the center of gravity.
  • the broken or fallen-off portion When the whole or a part of the delivery fan breaks or falls off at the position of the center of gravity or in the vicinity of the position of the center of gravity, the broken or fallen-off portion has a large weight, and thus an impact force when being thrown in the radial direction orthogonal to the direction of the axis line is large.
  • the annular member is provided at the linking position and disposed such that the whole or a part of the delivery fan which has been broken or fallen off collides therewith even in a case of being thrown in the radial direction orthogonal to the direction of the axis line from the position of the center of gravity of the delivery fan. Even in a case where the guide cylinder is subjected to brittle fracture due to the collision of the whole or a part of the delivery fan which has been broken or fallen off, in the collision with the annular member, the annular member is restricted to undergoing plastic deformation without this leading to brittle fracture. Accordingly, it is possible to prevent a problem in that the whole or a part of the delivery fan which has been broken or fallen off is thrown to the outside.
  • the annular member is configured of a material having a higher ductility than that of the guide cylinder.
  • the annular member can more reliably be restricted to undergoing plastic deformation without this leading to brittle fracture.
  • ductility being high indicates having characteristics in which large plastic deformation involves breakage, and indicates that the brittleness which leads to breakage in a situation where plastic deformation is small is small. Specifically, by comparing tensile fracture strength leading to breakage with elongation (rate), it can be confirmed that ductility is high.
  • the centrifugal compressor further includes a tubular member which is disposed coaxially with the rotor shaft further toward the outer periphery side in the radial direction orthogonal to the axis line than is the guide cylinder and further toward the inner periphery side in the radial direction than is the scroll part.
  • the centrifugal compressor having this configuration, in a case where the whole or a part of the delivery fan breaks or falls off, the whole or a part of the delivery fan is thrown in the radial direction orthogonal to the direction of the axis line of the rotor shaft, thereby colliding with the guide cylinder.
  • a part of the delivery fan which has collided with the guide cylinder may cause brittle fracture of the guide cylinder and be further thrown to the outside in the radial direction, thereby reaching the tubular member. Even in a case where the guide cylinder is subjected to brittle fracture, the tubular member is plastically deformed, thereby a problem of a part of the delivery fan being thrown to the outside being prevented.
  • an end portion on the discharge port side of the tubular member and an end portion on the intake port side of the annular member may be disposed at positions overlapping in the radial direction and close to each other in the radial direction.
  • the tubular member may be configured of a material having a higher ductility than that of the guide cylinder, a diameter of the annular member and a diameter of the tubular member may coincide with each other with respect to the axis line, and an end face in a direction of the axis line of the annular member and an end face in the direction of the axis line of the tubular member may be spaced apart from each other with a predetermined distance therebetween in the direction of the axis line.
  • the diameter of the annular member and the diameter of the tubular member coincide with each other, and therefore, the annular member and the tubular member form one cylindrical surface surrounding the guide cylinder around the rotor shaft.
  • the whole or a part of the delivery fan which causes brittle fracture of the guide cylinder and is thrown to the outside in the radial direction collides with either of the annular member or the tubular member which form one cylindrical surface.
  • One cylindrical surface is formed, and therefore, a gap occurring in a case where the diameter of the outer peripheral surface of the annular member and the diameter of the outer peripheral surface of the tubular member are different from each other is not formed. For this reason, a problem in that the whole or a part of the delivery fan is thrown from a gap which is formed due to a difference between the diameters of the outer peripheral surfaces of the annular member and the tubular member to the outside is prevented.
  • the end face in the direction of the axis line of the annular member and the tubular member are spaced apart from each other with a predetermined distance therebetween in the direction of the axis line.
  • the annular member and the tubular member are configured as separate members and are spaced apart from each other with a predetermined distance therebetween in the direction of the axis line, whereby even if a difference in thermal elongation amount due to a difference in temperature occurs between the respective members, deformation or breakage does not occur in either of the annular member or the tubular member.
  • a configuration is also acceptable in which a position of the center of gravity in the direction of the axis line of the delivery fan exists in a position range in the direction of the axis line, in which the annular member is disposed.
  • the broken or fallen-off portion When the whole or a part of the delivery fan has been broken or fallen off at the position of the center of gravity of the delivery fan or in the vicinity of the position of the center of gravity, the broken or fallen-off portion has a large weight, and thus an impact force when being thrown in the radial direction orthogonal to the direction of the axis line is large.
  • a configuration is made such that the position of the center of gravity in the direction of the axis line of the delivery fan exists in the position range in the direction of the axis line, in which the annular member is disposed.
  • the broken or fallen-off portion is able to collide with the annular member, whereby it is possible to prevent a problem in that the whole or a part of the delivery fan is thrown to the outside.
  • the annular member forms, along with the guide cylinder, a flow path wall of a flow path through which the compressed fluid which is discharged from the discharge port flows, the annular member has an annular projection portion protruding inward in the radial direction, on the inner periphery side in the radial direction orthogonal to the axis line and the flow path side in the direction of the axis line, the guide cylinder at the linking position has an annular step portion on the outer periphery side in the radial direction and the flow path side in the direction of the axis line, and the guide cylinder and the annular member are connected in a state where the annular projection portion is disposed at the annular step portion.
  • a pressure that the annular member receives from the compressed fluid increases as the pressure of the compressed fluid which is discharged from the discharge port increases due to an increase in the rotational frequency of the rotor shaft.
  • the annular projection portion that the annular member has on the flow path side is disposed at the annular step portion that the guide cylinder has on the flow path side. For this reason, a contact force between the annular projection portion and the annular step portion increases as the pressure that the annular member receives from the compressed fluid increases. In this way, a problem in that the compressed fluid leaks out at the connecting location between the annular member and the guide cylinder is prevented.
  • a turbocharger including: the centrifugal compressor according to any one of the above aspects; and a turbine which is rotated around the axis line by exhaust gas discharged from an internal combustion engine and is connected to the rotor shaft.
  • turbocharger in a case where the whole or a part in the vicinity of the position of the center of gravity of the delivery fan breaks or falls off, thereby being thrown in the radial direction orthogonal to the direction of the axis line of the rotor shaft, it is possible to prevent a problem in that the whole or a part of the delivery fan is thrown to the outside.
  • the centrifugal compressor which is manufactured by the manufacturing method according to the present invention, in a case where the whole or a part in the vicinity of the position of the center of gravity of the delivery fan breaks or falls off, the whole or a part of the delivery fan is thrown in the radial direction orthogonal to the direction of the axis line of the rotor shaft, thereby reaching the linking position between the guide cylinder and the scroll part.
  • the annular member is mounted at the linking position so as to surround the delivery fan, and therefore, the whole or a part of the delivery fan which has been thrown collides with the annular member. Even in a case where the guide cylinder is subjected to brittle fracture, the annular member is plastically deformed, whereby a problem in which the whole or a part of the delivery fan is thrown to the outside is prevented.
  • the present invention it is possible to provide a centrifugal compressor in which in a case where the whole or a part in the vicinity of the position of the center of gravity of a delivery fan breaks or falls off, thereby being thrown in a radial direction orthogonal to a direction of an axis line of a rotor shaft, it is possible to prevent a problem in that the whole or a part of the delivery fan is thrown to the outside.
  • a turbocharger 100 of this embodiment is a device for increasing the pressure air (gas) which is supplied to a ship diesel engine (internal combustion engine) which is used in a ship, to atmospheric pressure or more, thereby enhancing the combustion efficiency of the ship diesel engine.
  • the turbocharger 100 of this embodiment is provided with a centrifugal compressor 10 and a turbine 20.
  • Each of the centrifugal compressor 10 and the turbine 20 is connected to a rotor shaft 30.
  • the centrifugal compressor 10 is a device for compressing air flowing in from the outside of the turbocharger 100 and supplying the compressed air (hereinafter referred to as compressed air (compressed fluid)) to an intake manifold (not shown) which communicates with the inside of a cylinder liner (not shown) configuring the ship diesel engine.
  • compressed air compressed fluid
  • the centrifugal compressor 10 is provided with a delivery fan 11, an air-guiding cylinder 12, a scroll part 13, a first containment ring 14 (an annular member), a second containment ring 15 (a tubular member), and a silencer 16.
  • Each of the air-guiding cylinder 12 and the scroll part 13 is made of a metal member manufactured by casting in order to form a complicated shape.
  • this metal member for example, cast iron which is a Fe-C-based alloy containing iron as its main component and containing 2% or more of carbon is used. If it is cast iron, it is possible to use various materials such as gray cast iron. However, it is preferable to use ductile cast iron (FCD: Ferrum Cast Ductile) in which black smoke in a base structure is spheroidized.
  • FCD Ferrum Cast Ductile
  • a metal material by casting easily forms a complicated shape by pouring formation but has a brittle characteristic.
  • Each of the first containment ring 14 and the second containment ring 15 is made of a metal member manufactured by rolling.
  • this metal member for example, an iron and steel material which is a Fe-C-based alloy containing iron as its main component and containing a trace (about 0.2%) of carbon is used. If it is an iron and steel material, it is possible to use various materials. However, it is preferable to use rolled steel for a general structure (JIS G 3101; ASTM A283) called SS400.
  • a metal material by rolling is composed of a composition suitable for a rolling process and has ductility which leads to breakage after large plastic deformation.
  • the metal material by casting is composed of a composition suitable for a casting process and has smaller elongation which leads to breakage than the metal material by rolling. In this manner, in the metal material by rolling, the elongation which leads to breakage is larger than in the metal material by casting, that is, ductility is high. Therefore, the metal material by rolling has a characteristic in which breaking strength against impact is higher than in the metal material by casting.
  • tensile strength at normal temperature is in a range of 400 N/mm 2 to 500 N/mm 2 in both the ductile cast iron material and the SS400 material.
  • elongation at break is about 10%
  • SS400 material elongation at break is greater than or equal to 20%. Therefore, the SS400 material has higher ductility than the ductile cast iron material.
  • the turbine 20 is provided with a turbine housing 21, turbine blades 22, a turbine disk 23, and turbine nozzles 24.
  • the turbine housing 21 is a hollow tubular member which is disposed around an axis line X, and accommodates the turbine blades 22, the turbine disk 23, and the turbine nozzles 24 inside thereof. Exhaust gas which is discharged from the ship diesel engine flows into the turbine housing 21 along an arrow shown on the right side of Fig. 1 .
  • the exhaust gas led to the turbine housing 21 performs static pressure expansion when passing through the turbine nozzle 24 and is led to the turbine blade 22.
  • the turbine blades 22 are mounted at regular intervals around the axis line on the outer peripheral surface of the approximately circular plate-shaped turbine disk 23 fixed to the rotor shaft 30.
  • the exhaust gas which has performed static pressure expansion passes through the turbine blades 22, whereby a rotating force around the axis line X is applied to the turbine disk 23.
  • the rotating force serves as power which rotates the rotor shaft 30, and rotates the delivery fan 11 connected to the rotor shaft 30 around the axis line X.
  • the exhaust gas which is discharged from the ship diesel engine is led to the turbine 20, thereby rotating the turbine disk 23 with the turbine blades 22 mounted thereon around the axis line X.
  • the delivery fan 11 connected to the turbine disk 23 through the rotor shaft 30 rotates according to the rotation of the turbine disk 23, whereby air flowing in from an intake port 11a is compressed and the compressed air is discharged from a discharge port 11b.
  • the compressed air discharged from the discharge port 11b flows into the scroll part 13 and is led to the intake manifold of the ship diesel engine.
  • the silencer 16 is a device for reducing a level of noise which is generated in the centrifugal compressor 10. As shown in Fig. 1 , the silencer 16 defines a flow path which leads air flowing in from a direction orthogonal to the axis line X to the intake port 11a of the air-guiding cylinder 12. A sound-deadening material 16a is disposed around the flow path. Some of the noise which is generated in the centrifugal compressor 10 is absorbed by the sound-deadening material 16a, and thus a level of the noise is reduced.
  • the delivery fan 11 is mounted on the rotor shaft 30 extending along the axis line X and rotates around the axis line X according to the rotation of the rotor shaft 30 around the axis line X.
  • the delivery fan 11 rotates around the axis line X, thereby compressing air flowing in from the intake port 11a, and then discharging the compressed air from the discharge port 11b.
  • the delivery fan 11 is provided with a hub 11c which is mounted on the rotor shaft 30, a blade 11d which is mounted on the outer peripheral surface of the hub 11c, and a flow path 11e.
  • a space which is formed by the outer peripheral surface of the hub 11c and the inner peripheral surface of the air-guiding cylinder 12 is provided in the delivery fan 11, and the space is partitioned into a plurality of spaces by a plurality of blades 11d.
  • the delivery fan 11 applies a centrifugal force in a radial direction to air flowing in from the intake port 11a along a direction of the axis line X, thereby discharging the air in a direction (an inclined direction; a radial direction of the delivery fan 11) orthogonal to the direction of the axis line X and making the compressed air discharged from the discharge port 11b flow into a diffuser 13a.
  • the air-guiding cylinder 12 is a member for accommodating the delivery fan 11 and discharging air flowing in from the intake port 11a along the direction of the axis line X of the rotor shaft 30, from the discharge port 11b.
  • the air-guiding cylinder 12 forms, along with the delivery fan 11, the flow path 11e which guides air flowing in from the intake port 11a along the axis line X, in the radial direction orthogonal to the axis line X, thereby leading the air to the discharge port 11b.
  • the scroll part 13 is a device into which the compressed air discharged from the discharge port 11b flows and which converts kinetic energy (dynamic pressure) applied to the compressed air to pressure energy (static pressure).
  • the scroll part 13 is disposed further toward the outer periphery side in the radial direction orthogonal to the direction of the axis line X than is the air-guiding cylinder 12.
  • the scroll part 13 is provided with the diffuser 13a, a diffuser disk 13b, an outer scroll casing 13c (refer to Fig. 1 ), an inner scroll casing 13d, and a vortex-shaped chamber 13e.
  • the vortex-shaped chamber 13e is a space which is defined by the outer scroll casing 13c and the inner scroll casing 13d.
  • the inner scroll casing 13d is connected to the air-guiding cylinder 12 by a fastening bolt 43.
  • the diffuser 13a is a blade-shaped member which is disposed on the downstream side of the discharge port 11b of the delivery fan 11, and forms a flow path which leads the compressed air from the discharge port 11b to the vortex-shaped chamber 13e.
  • the diffusers 13a are provided at a plurality of locations in a circumferential direction of the circular ring-shaped diffuser disk 13b which is disposed coaxially with the rotor shaft 30.
  • the diffusers 13a are provided so as to surround the discharge port 11b for the compressed air, which is provided on the entire circumference of the delivery fan 11.
  • the diffuser disk 13b is connected to the inner scroll casing 13d by a fastening bolt 44.
  • the diffuser 13a converts kinetic energy (dynamic pressure) applied to the compressed air to pressure energy (static pressure) by reducing the flow velocity of the compressed air discharged from the discharge port 11b of the delivery fan 11.
  • the compressed air with the flow velocity reduced when passing through the diffuser 13a flows into the vortex-shaped chamber 13e which communicates with the diffuser 13a.
  • a working fluid which has flowed into the vortex-shaped chamber 13e is discharged to a discharge pipe (not shown).
  • the first containment ring 14 is an annular member which is mounted at a linking position between the discharge port 11b side of the air-guiding cylinder 12 and the inner scroll casing 13d so as to surround the delivery fan 11 around the axis line X. As shown in Fig. 1 , the first containment ring 14 is disposed coaxially with the rotor shaft 30. As shown in Fig. 2 , the first containment ring 14 is connected to the air-guiding cylinder 12 by a fastening bolt 41.
  • the second containment ring 15 is a tubular member which is disposed further toward the outer periphery side in the radial direction than is the air-guiding cylinder 12 and further toward the inner periphery side in the radial direction than is the scroll part 13. As shown in Fig. 1 , the second containment ring 15 is disposed coaxially with the rotor shaft 30. As shown in Fig. 2 , the second containment ring 15 is connected to the air-guiding cylinder 12 by a fastening bolt 42.
  • Each of the first containment ring 14 and the second containment ring 15 is made of a metal member manufactured by rolling and has higher ductility than that of the air-guiding cylinder 12 made of a metal member manufactured by casing.
  • ductility being high indicates that large plastic deformation involves breakage and the brittleness which leads to breakage in a situation where plastic deformation is small is small. For this reason, when an impact load is generated, a material having high ductility is plastically deformed, thereby being able to absorb and restrain the kinetic energy of impact. For this reason, it becomes possible for the material to remain in plastic deformation without leading to breakage even with respect to an impact load.
  • tensile strength at normal temperature is in a range of 400 N/mm 2 to 500 N/mm 2 and elongation is about 10%.
  • tensile strength at normal temperature is likewise in a range of 400 N/mm 2 to 500 N/mm 2 and elongation is about 20% or more. Therefore, from a difference in elongation, it can be confirm that the SS400 material is a material having higher ductility than the ductile cast iron material.
  • the first containment ring 14 and the second containment ring 15 have higher ductility than that of the air-guiding cylinder 12. For this reason, even when the delivery fan 11 is broken down or falls off, the first containment ring 14 and the second containment ring 15 prevent the whole or a part of the delivery fan 11 from being thrown to the outside, in a case where the whole or a part of the delivery fan 11 is thrown in the radial direction, thereby colliding with the air-guiding cylinder 12.
  • the first containment ring 14 and the second containment ring 15 are plastically deformed, thereby preventing a problem in that the whole or a part of the delivery fan is thrown to the outside.
  • a radius D1 of the outer peripheral surface of the first containment ring 14 and a radius D2 of the outer peripheral surface of the second containment ring 15 coincide with each other.
  • Making the radius D1 and the radius D2 coincide with each other is for preventing a gap occurring in a case where the diameter of the outer peripheral surface of the first containment ring 14 and the diameter of the outer peripheral surface of the second containment ring 15 are different from each other, from being formed. If this gap is formed, there is a possibility that the whole or a part of the delivery fan 11 may be thrown to the outside.
  • the radius D1 of the outer peripheral surface of the first containment ring 14 and the radius D2 of the outer peripheral surface of the second containment ring 15 may not necessarily be made to coincide with the same diameter.
  • an end face 14a in the direction of the axis line X of the first containment ring 14 and an end face 15a in the direction of the axis line X of the second containment ring 15 are spaced apart from each other with a predetermined distance W therebetween in the direction of the axis line X.
  • the first containment ring 14 and the second containment ring 15 are connected or are formed as a single member, if a difference in thermal elongation amount due to a difference in temperature occurs in both end portions in the direction of the axis line X of the member, there is a concern that the member may be deformed or broken down.
  • the first containment ring 14 and the second containment ring 15 are spaced apart from each other with the predetermined distance W therebetween in the direction of the axis line X, whereby even if a difference in thermal elongation amount due to a difference in temperature occurs between the respective members, deformation or breakage does not occur in either of the first containment ring 14 or the second containment ring 15.
  • the position in the direction of the axis line X, at which the first containment ring 14 is disposed, is a position P1.
  • the position P1 coincides with the position of the center of gravity in the direction of the axis line of the delivery fan 11.
  • the outer diameter of a blade is made to be larger on the discharge port 11b side than on the intake port 11a side. Therefore, the position of the center of gravity of the delivery fan 11 is at the position P1 closer to the discharge port 11b side than the intake port 11a side.
  • the delivery fan 11 rotates at a high speed around the axis line X (for example, a case where the delivery fan 11 rotates at a 10,000 or more revolutions per minute), there is a case where the whole or a part of the delivery fan 11 breaks or falls off.
  • An impact force in the radial direction orthogonal to the direction of the axis line X at the time of falling-off of the delivery fan 11 becomes particularly large at the position of the center of gravity.
  • the position P1 in the direction of the axis line X, at which the first containment ring 14 is disposed coincides with the position of the center of gravity in the direction of the axis line of the delivery fan 11.
  • the delivery fan 11 which has been broken or fallen off at the position of the center of gravity is thrown in the radial direction, it collides with the first containment ring 14. Then, the first containment ring 14 having high ductility is plastically deformed, whereby it is possible to prevent a problem in that the whole or a part of the delivery fan 11 is thrown to the outside.
  • the first containment ring 14 forms, along with the air-guiding cylinder 12, a flow path wall on the outer periphery side of the flow path 11e through which the compressed air which is discharged from the discharge port 11b flows.
  • the first containment ring 14 has an annular projection portion 14b protruding inward in the radial direction, on the outer periphery side in the radial direction and the flow path 11e side in the direction of the axis line X.
  • the air-guiding cylinder 12 has an annular step portion 12a on the outer periphery side in the radial direction and the flow path 11e side in the direction of the axis line X.
  • the air-guiding cylinder 12 and the first containment ring 14 are connected in a state where the annular projection portion 14b is disposed at the annular step portion 12a.
  • a gap is provided between the annular step portion 12a and the annular projection portion 14b. Due to this gap, even if there is thermal expansion of the air-guiding cylinder 12, it is possible to prevent deformation from propagating to the first containment ring 14 by thermal expansion.
  • An inner periphery-side end face 13f of the inner scroll casing 13d and an outer periphery-side end face 14c in the radial direction of the first containment ring 14 are disposed so as to face each other, at a linking position at which the inner scroll casing 13d and the air-guiding cylinder 12 are connected.
  • An endless annular groove portion 13g extending in the circumferential direction around the axis line X is formed in the inner periphery-side end face 13f.
  • An O-ring 13h (an annular seal member) is fitted in the annular groove portion 13g.
  • an endless annular groove portion 14d extending in the circumferential direction around the axis line X is formed in the outer periphery-side end face 14c.
  • An O-ring 14e (an annular seal member) is fitted in the annular groove portion 14d.
  • the O-ring 13h comes into contact with the outer periphery-side end face 14c and the O-ring 14e comes into contact with the inner periphery-side end face 13f, whereby outflow of the compressed air from the flow path 11e is cut off at the position at which the inner periphery-side end face 13f and the outer periphery-side end face 14c face each other.
  • the centrifugal compressor 10 is manufactured by the following processes.
  • the delivery fan 11 which compresses air flowing in from the intake port 11a and then discharges the compressed air from the discharge port 11b is mounted on the rotor shaft 30.
  • the air-guiding cylinder 12 is mounted so as to accommodate the delivery fan 11, thereby forming a flow path which guides air flowing in from the intake port 11a along the direction of the axis line X of the rotor shaft 30, from the direction of the axis line X to the inclined direction, thereby leading the air to the discharge port 11b.
  • the scroll part 13 into which the compressed air discharged from the discharge port 11b flows is disposed further toward the outer periphery side in the radial direction orthogonal to the direction of the axis line X than is the air-guiding cylinder 12.
  • the first containment ring 14 which is mainly configured of an iron and steel material having higher ductility than cast iron configuring the air-guiding cylinder 12 or the scroll part 13 is mounted at the linking position between the air-guiding cylinder 12 and the scroll part 13 so as to surround the delivery fan 11 around the axis line X.
  • the second containment ring 15 which is mainly configured of an iron and steel material having higher ductility than cast iron configuring the air-guiding cylinder 12 or the scroll part 13 is mounted further toward the outer periphery side in the radial direction than is the air-guiding cylinder 12 and further toward the inner periphery side than is the scroll part 13.
  • the centrifugal compressor 10 of this embodiment is manufactured.
  • a compressor which the turbocharger 100 of this embodiment has is a centrifugal compressor.
  • the outer diameter of the blade is made to be larger on the discharge port 11b side than on the intake port 11a side. Therefore, the position of the center of gravity of the delivery fan 11 is at the position P1 on the discharge port 11b side.
  • the linking position between the discharge port 11b side of the air-guiding cylinder 12 and the scroll part 13 is at the position of the center of gravity of the delivery fan 11 in the axis line X.
  • the broken or fallen-off portion When the whole or a part of the delivery fan breaks or falls off at the position of the center of gravity, the broken or fallen-off portion has a large weight, and thus an impact force when being thrown in the radial direction orthogonal to the direction of the axis line is large.
  • the first containment ring 14 (the annular member) which is mainly configured of an iron and steel material having higher ductility than cast iron configuring the air-guiding cylinder 12 and the scroll part 13 as a main body is provided at the linking position and disposed such that the whole or a part of the delivery fan 11 which has been broken or fallen off collides therewith even in a case of being thrown in the radial direction orthogonal to the direction of the axis line X from the position of the center of gravity of the delivery fan 11.
  • the air-guiding cylinder 12 is subjected to brittle fracture due to the collision of the whole or a part of the delivery fan 11 which has been broken or fallen off, in the collision with the first containment ring 14 having high ductility, the first containment ring 14 is restricted to undergoing plastic deformation without this leading to brittle fracture. Accordingly, it is possible to prevent a problem in that the whole or a part of the delivery fan 11 which has been broken or fallen off is thrown to the outside of the turbocharger 100.
  • the diameter of the outer peripheral surface of the first containment ring 14 and the diameter of the outer peripheral surface of the second containment ring 15 coincide with each other. For this reason, the first containment ring 14 and the second containment ring 15 form one cylindrical surface surrounding the air-guiding cylinder 12 around the rotor shaft 30.
  • One cylindrical surface is formed, and therefore, a gap occurring in a case where the diameter of the outer peripheral surface of the first containment ring 14 and the diameter of the outer peripheral surface of the second containment ring 15 are different from each other is not formed.
  • the end face 14a in the direction of the axis line X of the first containment ring 14 and the end face 15a in the direction of the axis line X of the second containment ring 15 are spaced apart from each other with the predetermined distance W therebetween in the direction of the axis line X.
  • the first containment ring 14 and the second containment ring 15 are connected or are formed as a single member, if a difference in thermal elongation amount due to a difference in temperature occurs in both end portions in the direction of the axis line X of the member, there is a concern that the member may be deformed or broken down.
  • the first containment ring 14 and the second containment ring 15 are configured as separate members and are spaced apart from each other with the predetermined distance W therebetween in the direction of the axis line X. In this way, even if a difference in thermal elongation amount due to a difference in temperature occurs between the respective members, deformation or breakage does not occur in either of the first containment ring 14 or the second containment ring 15.
  • pressure that the first containment ring 14 receives from the compressed air increases as the pressure of the compressed air which is discharged from the discharge port 11b increases due to an increase in the rotational frequency of the rotor shaft 30.
  • the annular projection portion 14b that the first containment ring 14 has on the flow path 11e side is disposed at the annular step portion 12a that the air-guiding cylinder 12 has on the flow path 11e side. For this reason, a contact force between the annular projection portion 14b and the annular step portion 12a increases as the pressure that the first containment ring 14 receives from the compressed air increases. In this way, a problem in that the compressed air leaks out at the connecting location between the first containment ring 14 and the air-guiding cylinder 12 is prevented.
  • the O-ring 13h and the O-ring 14e are disposed between the inner periphery-side end face 13f in the radial direction of the scroll part 13 and the outer periphery-side end face 14c in the radial direction of the first containment ring 14 at the linking position.
  • the compressed air leaks out at the position at which the scroll part 13 and the first containment ring 14 face each other is prevented.
  • Each of the air-guiding cylinder 12 and the scroll part 13 of this embodiment is formed of a metal member manufactured by casting.
  • this metal member it is preferable to use gray cast iron or ductile cast iron in which a complicated shape is easily manufactured.
  • each of the first containment ring 14 and the second containment ring 15 is formed of a metal member manufactured by rolling.
  • this metal member it is preferable to use rolled steel for a general structure called SS400 which has higher ductility than a cast iron material and does not easily lead to breakage by being plastically deformed even with respect to an impact load.
  • a turbocharger 200 of the second embodiment is a modification of the turbocharger 100 of the first embodiment.
  • first containment ring 14 and the second containment ring 15 are spaced apart from each other with the predetermined distance W therebetween in the direction of the axis line X.
  • a first containment ring 14' and a second containment ring 15' are made so as to be disposed at positions overlapping in the radial direction and close to each other in the radial direction.
  • the centrifugal compressor 10 is provided with the first containment ring 14' (an annular member) and the second containment ring 15' (a tubular member).
  • the first containment ring 14' and the second containment ring 15' are made of the same metal members as those of the first containment ring 14 and the second containment ring 15 of the first embodiment.
  • the first containment ring 14' is an annular member which is mounted at the linking position between the discharge port 11b side of the air-guiding cylinder 12 and the inner scroll casing 13d so as to surround the delivery fan 11 around the axis line X. As shown in Fig. 5 , the first containment ring 14' is disposed coaxially with the rotor shaft 30. As shown in Fig. 5 , the first containment ring 14' is connected to the air-guiding cylinder 12 by the fastening bolt 41.
  • the second containment ring 15' is a tubular member which is disposed further toward the outer periphery side in the radial direction than is the air-guiding cylinder 12 and further toward the inner periphery side in the radial direction than is the scroll part 13. As shown in Fig. 4 , the second containment ring 15' is disposed coaxially with the rotor shaft 30. As shown in Fig. 5 , the second containment ring 15' is connected to the air-guiding cylinder 12 by the fastening bolt 42.
  • a radius D1 of the outer peripheral surface of the first containment ring 14' and a radius D2 of the outer peripheral surface of the second containment ring 15' coincide with each other.
  • Making the radius D1 and the radius D2 coincide with each other is for preventing a gap occurring in a case where the diameter of the outer peripheral surface of the first containment ring 14' and the diameter of the outer peripheral surface of the second containment ring 15' are different from each other, from being formed. If this gap is formed, there is a possibility that the whole or a part of the delivery fan 11 may be thrown to the outside.
  • an end portion 15a' on the discharge port 11b side of the second containment ring 15' and an end portion 14a' on the intake port 11a side of the first containment ring 14' are disposed at positions overlapping in the radial direction and close to each other in the radial direction.
  • a gap in the radial direction between the end portion 14a' which is disposed on the inner periphery side and the end portion 15a' which is disposed on the outer periphery side is set so as to maintain a distance to the extent that these members do not come into contact with each other due to thermal expansion.
  • the gap in the radial direction between the end portion 14a' which is disposed on the inner periphery side and the end portion 15a' which is disposed on the outer periphery side is set so as to become a distance to the extent that the end portion 14a' comes into contact with the end portion 15a' when the end portion 14a' is plastically deformed by impact caused by a broken member. In this way, the end portion 14a' comes into contact with the end portion 15a' when being plastically deformed by impact caused by the broken member, whereby the impact caused by the broken member can be absorbed by both the first containment ring 14' and the second containment ring 15' .
  • the position in the direction of the axis line X, at which the first containment ring 14' is disposed, is the position P1.
  • the position P1 coincides with the position of the center of gravity in the direction of the axis line of the delivery fan 11.
  • the position P1 is a position which coincides with the end face on the intake port 11a side of the annular projection portion 14b of the first containment ring 14' shown in Fig. 6 .
  • the outer diameter of the blade is made to be larger on the discharge port 11b side than on the intake port 11a side. Therefore, the position of the center of gravity of the delivery fan 11 is at the position P1 closer to the discharge port 11b side than the intake port 11a side.
  • the delivery fan 11 rotates at a high speed around the axis line X (for example, a case where the delivery fan 11 rotates at a 10,000 or more revolutions per minute), there is a case where the whole or a part of the delivery fan 11 breaks or falls off.
  • An impact force in the radial direction orthogonal to the direction of the axis line X at the time of falling-off of the delivery fan 11 becomes particularly large at the position of the center of gravity.
  • the position P1 in the direction of the axis line X, at which the first containment ring 14' is disposed coincides with the position of the center of gravity in the direction of the axis line of the delivery fan 11.
  • the delivery fan 11 which has been broken or fallen off at the position of the center of gravity is thrown in the radial direction, thereby breaking the air-guiding cylinder 12, and is further thrown in the radial direction, the delivery fan 11 collides with the first containment ring 14'. Then, the first containment ring 14' having high ductility is plastically deformed, whereby it is possible to prevent a problem in that the whole or a part of the delivery fan 11 is thrown to the outside.
  • the first containment ring 14' forms, along with the air-guiding cylinder 12, a flow path wall on the outer periphery side of the flow path 11e through which the compressed air which is discharged from the discharge port 11b flows.
  • the first containment ring 14' has the annular projection portion 14b protruding inward in the radial direction, on the inner periphery side in the radial direction and the flow path 11e side in the direction of the axis line X.
  • the air-guiding cylinder 12 has the annular step portion 12a on the outer periphery side in the radial direction and the flow path 11e side in the direction of the axis line X.
  • the air-guiding cylinder 12 and the first containment ring 14' are connected in a state where the annular projection portion 14b is disposed at the annular step portion 12a.
  • a gap is provided between the annular step portion 12a and the annular projection portion 14b. Due to this gap, even if there is thermal expansion of the air-guiding cylinder 12, it is possible to prevent deformation from propagating to the first containment ring 14' by thermal expansion.
  • the inner periphery-side end face 13f of the inner scroll casing 13d and the outer periphery-side end face 14c in the radial direction of the first containment ring 14' are disposed so as to face each other, at the linking position at which the inner scroll casing 13d and the air-guiding cylinder 12 are connected.
  • a compressor which the turbocharger 200 of this embodiment has is a centrifugal compressor.
  • the outer diameter of the delivery fan blade is made to be larger on the discharge port 11b side than on the intake port 11a side. Therefore, the position of the center of gravity of the delivery fan 11 is at the position P1 on the discharge port 11b side.
  • the linking position between the discharge port 11b side of the air-guiding cylinder 12 and the scroll part 13 is at the position of the center of gravity of the delivery fan 11 in the axis line X.
  • the broken or fallen-off portion When the whole or a part of the delivery fan breaks or falls off at the position of the center of gravity, the broken or fallen-off portion has a large weight, and thus an impact force when being thrown in the radial direction orthogonal to the direction of the axis line is large.
  • the first containment ring 14' (the annular member) which is mainly configured of an iron and steel material having higher ductility than cast iron configuring the air-guiding cylinder 12 and the scroll part 13 as a main body is provided at the linking position and disposed such that the whole or a part of the delivery fan 11 which has been broken or fallen off (the broken member) collides therewith even in a case of being thrown in the radial direction orthogonal to the direction of the axis line X from the position of the center of gravity of the delivery fan 11.
  • the second containment ring 15' which is configured of a material having higher ductility than that of the air-guiding cylinder 12 is disposed further toward the outer periphery side in the radial direction than is the air-guiding cylinder 12 and further toward the inner periphery side in the radial direction than is the scroll part 13.
  • the end portion 15a' on the discharge port 11b side of the second containment ring 15' and the end portion 14a' on the intake port 11a side of the first containment ring 14' are disposed at positions overlapping in the direction of the axis line X and close to each other in the radial direction.
  • Both the second containment ring 15' and the first containment ring 14' have higher ductility than that of the air-guiding cylinder 12, and therefore, the impact caused by the collision is absorbed by the plastic deformation of both the second containment ring 15' and the first containment ring 14'.
  • the position of the center of gravity P1 in the direction of the axis line X of the delivery fan 11 exists in a position range in the direction of the axis line X, in which the first containment ring 14' is disposed.
  • the broken or fallen-off portion When the whole or a part at the position of the center of gravity P1 of the delivery fan 11 or in the vicinity of the position of the center of gravity P1 has been broken or fallen off, the broken or fallen-off portion has a large weight, and thus an impact force when being thrown in the radial direction orthogonal to the direction of the axis line X is large.
  • a configuration is made such that the position of the center of gravity P1 in the direction of the axis line X of the delivery fan 11 exists in the position range in the direction of the axis line X, in which the first containment ring 14' is disposed.
  • the broken or fallen-off portion is made to collide with the first containment ring 14', whereby it is possible to prevent a problem in that the whole or a part of the delivery fan 11 is thrown to the outside.
  • pressure that the first containment ring 14' receives from the compressed air increases as the pressure of the compressed air which is discharged from the discharge port 11b increases due to an increase in the rotational frequency of the rotor shaft 30.
  • the annular projection portion 14b that the first containment ring 14' has on the flow path 11e side is disposed at the annular step portion 12a that the air-guiding cylinder 12 has on the flow path 11e side. For this reason, a contact force between the annular projection portion 14b and the annular step portion 12a increases as the pressure that the first containment ring 14' receives from the compressed air increases. In this way, a problem in that the compressed air leaks out at the connecting location between the first containment ring 14' and the air-guiding cylinder 12 is prevented.
  • the O-ring 13h and the O-ring 14e are disposed between the inner periphery-side end face 13f in the radial direction of the scroll part 13 and the outer periphery-side end face 14c in the radial direction of the first containment ring 14' at the linking position.
  • the compressed air leaks out at the position at which the scroll part 13 and the first containment ring 14' face each other is prevented.
  • Each of the air-guiding cylinder 12 and the scroll part 13 of this embodiment is formed of a metal member manufactured by casting.
  • this metal member it is preferable to use gray cast iron or ductile cast iron in which a complicated shape is easily manufactured.
  • each of the first containment ring 14' and the second containment ring 15' is formed of a metal member manufactured by rolling.
  • this metal member it is preferable to use rolled steel for a general structure called SS400 which has higher ductility than a cast iron material and does not easily lead to breakage by being plastically deformed even with respect to an impact load.
  • the rotor shaft 30 to which the delivery fan 11 that the centrifugal compressor 10 has is connected is rotated around the axis line X by the turbine 20 which is rotated by exhaust gas which is discharged from the ship diesel engine.
  • the rotor shaft 30 may be rotated by other power sources such as a motor connected to the rotor shaft 30.
  • the position P1 in the direction of the axis line X, at which the first containment ring 14 or 14' is disposed, is set to be a position coinciding with the position of the center of gravity of the delivery fan 11.
  • the expression "coinciding" in the above description does not mean that the position P1 and the position of the center of gravity strictly coincide with each other. Even in a case where the position P1 is disposed in the vicinity of the position of the center of gravity, it is assumed that the position P1 coincides with the position of the center of gravity of the delivery fan 11.
  • the position P1 is a position at which it is possible to receive the impact force in the radial direction by the delivery fan 11 which becomes particularly large at the position of the center of gravity, it is assumed that the position P1 coincides with the position of the center of gravity of the delivery fan 11.
  • the radius D1 of the outer peripheral surface of the first containment ring 14 or 14' and the radius D2 of the outer peripheral surface of the second containment ring 15 or 15' are set to coincide with each other.
  • the expression "coinciding" in the above description does not mean that the radius D1 and the radius D2 strictly coincide with each other. Even in a case where the radius D1 and the radius D2 are different from each other, in a case where a gap to the extent that the broken member does not pass therethrough is provided between the first containment ring 14 or 14' and the second containment ring 15 or 15', it is assumed that the radius D1 and the radius D2 coincide with each other.
  • the shape of the first containment ring 14' and the shape of the second containment ring 15' are as shown in Fig. 6 . However, other aspects are also acceptable.
  • a configuration may be made in which the end portion 14a' of the first containment ring 14' has a tapered shape in which the outer diameter thereof is gradually reduced toward the intake port 11a side and the end portion 15a' of the second containment ring 15' has a tapered shape in which the inner diameter thereof gradually increases toward the discharge port 11b side.
  • the end portion 14a' of the first containment ring 14' has a tapered shape in which the outer diameter thereof is gradually reduced toward the intake port 11a side
  • the end portion 15a' of the second containment ring 15' has a tapered shape in which the inner diameter thereof gradually increases toward the discharge port 11b side.
  • the shape of the end portion 15a' of the second containment ring 15' may be the same as the shape of a portion other than the end portion 15a'.
  • the second containment ring 15' has a approximately constant plate thickness in the radial direction orthogonal to the axis line X from the end portion on the intake port 11a side to the end portion on the discharge port 11b side.
  • the second containment ring 15' can exert constant shock absorption performance at any position in the direction of the axis line X.
  • a configuration may be made in which the end portion 14a' of the first containment ring 14' is disposed on the outer periphery side and the end portion 15a' of the second containment ring 15' is disposed on the inner periphery side.

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Claims (7)

  1. Kreiselverdichter, umfassend:
    ein Laufrad (11), das auf einer Rotorwelle (30) montiert und dazu ausgebildet ist, ein Fluid, das aus einer Einlassöffnung (11a) einströmt, zu verdichten und ein verdichtetes Fluid aus einer Ausstoßöffnung (11b) auszustoßen;
    einen Führungszylinder (12), der das Laufrad (11) beherbergt;
    ein Spiralteil (13), das weiter zur Außenumfangsseite hin angeordnet ist als es der Führungszylinder (12) ist, und in den das aus der Ausstoßöffnung (11b) ausgestoßene verdichtete Fluid strömt; und
    ein ringförmiges Element (14), welches ein erster Aufnahmering ist, der an einer Anbindungsposition zwischen der Ausstoßöffnungsseite des Führungszylinders (12) und dem Spiralteil (13) so montiert ist, dass er das Laufrad (11) um eine Achsenlinie (X) der Rotorwelle (30) herum umgibt,
    wobei das ringförmige Element (14) zusammen mit dem Führungszylinder (12) eine Strömungspfadwand eines Strömungspfades bildet, durch den das verdichtete Fluid, das aus der Ausstoßöffnung (11b) ausgestoßen wird, strömt;
    wobei das ringförmige Element (14) aus einem Material ausgebildet ist, das eine höhere Duktilität aufweist als dasjenige des Führungszylinders; und
    einen in der radialen Richtung nach innen vorstehenden ringförmigen Vorsprungsabschnitt (14b) an der Innenumfangsseite in der radialen Richtung orthogonal zur Achsenlinie (X) und der Strömungspfadseite in der Richtung der Achsenlinie (X) aufweist, wobei
    der Führungszylinder (12) an der Anbindungsposition einen ringförmigen Stufenabschnitt (12a) an der Außenumfangsseite in der radialen Richtung und der Strömungspfadseite in der Richtung der Achsenlinie (X) aufweist,
    der Führungszylinder (12) und das ringförmige Element (14) in einem Zustand verbunden sind, in dem der ringförmige Vorsprungsabschnitt (14b) am ringförmigen Stufenabschnitt (12a) angeordnet ist; und
    wobei der Führungszylinder (12), das Spiralteil (13) und das ringförmige Element (14) als getrennte Teile bereitgestellt sind.
  2. Kreiselverdichter nach Anspruch 1, weiter umfassend:
    ein rohrförmiges Element (15), welches ein zweiter Aufnahmering ist, der koaxial zur Rotorwelle (30) weiter zur Außenumfangsseite in einer radialen Richtung orthogonal zur Achsenlinie (X) hin angeordnet ist, als es der Führungszylinder (12) ist, und weiter zur Innenumfangsseite in der radialen Richtung hin, als es das Spiralteil (13) ist.
  3. Kreiselverdichter nach Anspruch 2, wobei ein Endabschnitt an der Ausstoßöffnungsseite des rohrförmigen Elements (15) und ein Endabschnitt an der Einlassöffnungsseite des ringförmigen Elements (14) an Positionen angeordnet sind, die sich in der radialen Richtung überlappen und in der radialen Richtung nahe zueinander liegen.
  4. Kreiselverdichter nach Anspruch 2, wobei das rohrförmige Element (15) aus einem Material ausgebildet ist, das eine höhere Duktilität aufweist als dasjenige des Führungszylinders,
    ein Durchmesser des ringförmigen Elements (14) und ein Durchmesser des rohrförmigen Elements (15) in Bezug auf die Achsenlinie (X) miteinander übereinstimmen, und
    eine Endfläche (14a) in einer Richtung der Achsenlinie des ringförmigen Elements (14) und eine Endfläche (15a) in der Richtung der Achsenlinie des rohrförmigen Elements (15) um einen vorbestimmten Abstand (W) zwischen denselben in der Richtung der Achsenlinie (X) voneinander beabstandet sind.
  5. Kreiselverdichter nach einem der Ansprüche 1 bis 4, wobei eine Position des Schwerpunkts in der Richtung der Achsenlinie (X) des Laufrads (11) in einem Positionsbereich in der Richtung der Achsenlinie existiert, in der das ringförmige Element (14) angeordnet ist.
  6. Turbolader, umfassend:
    den Kreiselverdichter (10) nach einem der Ansprüche 1 bis 5; und
    eine Turbine, die durch Abgas, das aus einem Innenverbrennungsmotor ausstoßbar ist, um die Achsenlinie herum gedreht wird und mit der Rotorwelle (30) verbunden ist.
  7. Verfahren zur Herstellung eines Kreiselverdichters, umfassend:
    einen Prozess des Montierens eines Laufrads (11), welches dazu ausgebildet ist, ein aus einer Einlassöffnung einströmendes Fluid zu verdichten und ein verdichtetes Fluid aus einer Ausstoßöffnung an einer Rotorwelle auszustoßen;
    einen Prozess des Montierens eines Führungszylinders so, dass er das Laufrad (11) beherbergt, wodurch ein Strömungspfad gebildet wird, der das aus der Einlassöffnung einströmende Fluid zur Ausstoßöffnung leitet;
    einen Prozess des Anordnens eines Spiralteils, in den das aus der Ausstoßöffnung ausgestoßene verdichtete Fluid strömt, weiter zur Außenumfangsseite in einer radialen Richtung orthogonal zu einer Richtung einer Achsenlinie des Rotorschaftes hin, als es der Führungszylinder ist; und
    einen Prozess des Montierens eines ringförmigen Elements, das aus einem Material gefertigt ist, welches eine höhere Duktilität aufweist als dasjenige des Führungszylinders, an einer Anbindungsposition zwischen der Ausstoßöffnungsseite des Führungszylinders und dem Spiralteil, sodass es das Laufrad um die Achsenlinie herum umgibt, wobei
    das ringförmige Element einen in der radialen Richtung nach innen vorstehenden ringförmigen Vorsprungsabschnitt (14b) an der Innenumfangsseite in der radialen Richtung orthogonal zur Achsenlinie (X) und der Strömungspfadseite in der Richtung der Achsenlinie (X) aufweist, wobei
    der Führungszylinder (12) an der Anbindungsposition einen ringförmigen Stufenabschnitt (12a) an der Außenumfangsseite in der radialen Richtung und der Strömungspfadseite in der Richtung der Achsenlinie (X) aufweist,
    wobei der Montageprozess darin besteht, das ringförmige Element an der Anbindungsposition so zu montieren, dass zusammen mit dem Führungszylinder eine Strömungspfadwand eines Strömungspfades gebildet wird, durch den das verdichtete Fluid, das aus der Ausstoßöffnung ausgestoßen wird, strömt; und der Führungszylinder (12) und das ringförmige Element (14) in einem Zustand verbunden sind, in dem der ringförmige Vorsprungsabschnitt (14b) am ringförmigen Stufenabschnitt (12a) angeordnet ist; und
    wobei der Führungszylinder, das Spiralteil und das ringförmige Element als getrennte Teile bereitgestellt sind.
EP15774141.4A 2014-03-31 2015-03-19 Kreiselverdichter, turbolader und verfahren zur herstellung des kreiselverdichters Active EP3067569B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2014074070A JP6456596B2 (ja) 2014-03-31 2014-03-31 遠心圧縮機、過給機、および遠心圧縮機の製造方法
JP2014212793A JP6541956B2 (ja) 2014-10-17 2014-10-17 遠心圧縮機およびそれを備えた過給機
PCT/JP2015/058355 WO2015151844A1 (ja) 2014-03-31 2015-03-19 遠心圧縮機、過給機、および遠心圧縮機の製造方法

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JP6240251B2 (ja) * 2016-03-30 2017-11-29 三菱重工業株式会社 圧縮装置及び過給機
WO2018137137A1 (zh) * 2017-01-24 2018-08-02 游涛 涡旋发动机
US11519423B1 (en) * 2021-11-11 2022-12-06 Progress Rail Locomotive Inc. Compressor joint

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JPS62243997A (ja) * 1986-04-15 1987-10-24 Ebara Corp 遠心羽根車翼端隙間制御装置
DE19640654A1 (de) * 1996-10-02 1998-04-09 Asea Brown Boveri Berstschutzvorrichtung für Radialturbinen von Turboladern
JP4359798B2 (ja) 1999-11-05 2009-11-04 株式会社Ｉｈｉ 排気タービン過給機
GB0912796D0 (en) * 2009-07-23 2009-08-26 Cummins Turbo Tech Ltd Compressor,turbine and turbocharger
JP5230590B2 (ja) 2009-12-07 2013-07-10 三菱重工業株式会社 排気タービン過給機の排気入口ケーシング
DE102010027762B4 (de) * 2010-04-15 2015-06-25 Man Diesel & Turbo Se Einsatzstück für eine Strömungsmaschine und damit ausgerüstete Strömungsmaschine
JP5905736B2 (ja) * 2012-02-22 2016-04-20 トヨタ自動車株式会社 排気タービン過給機の製造方法及び排気タービン過給機
JP5263562B2 (ja) * 2012-03-12 2013-08-14 株式会社Ｉｈｉ 遠心圧縮機ケーシング

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KR20160088922A (ko) 2016-07-26
EP3067569A4 (de) 2016-12-21
EP3067569A1 (de) 2016-09-14
WO2015151844A1 (ja) 2015-10-08
KR101884101B1 (ko) 2018-07-31
CN106164497A (zh) 2016-11-23
CN106164497B (zh) 2019-06-28

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