WO2015151844A1 - Compresseur centrifuge, compresseur de suralimentation et procédé de fabrication de compresseur centrifuge - Google Patents

Compresseur centrifuge, compresseur de suralimentation et procédé de fabrication de compresseur centrifuge Download PDF

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Publication number
WO2015151844A1
WO2015151844A1 PCT/JP2015/058355 JP2015058355W WO2015151844A1 WO 2015151844 A1 WO2015151844 A1 WO 2015151844A1 JP 2015058355 W JP2015058355 W JP 2015058355W WO 2015151844 A1 WO2015151844 A1 WO 2015151844A1
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WO
WIPO (PCT)
Prior art keywords
impeller
guide cylinder
centrifugal compressor
containment ring
radial direction
Prior art date
Application number
PCT/JP2015/058355
Other languages
English (en)
Japanese (ja)
Inventor
泰治 手塚
中馬　康晴
広之 荒川
Original Assignee
三菱重工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2014074070A external-priority patent/JP6456596B2/ja
Priority claimed from JP2014212793A external-priority patent/JP6541956B2/ja
Application filed by 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Priority to KR1020167016418A priority Critical patent/KR101884101B1/ko
Priority to CN201580003047.6A priority patent/CN106164497B/zh
Priority to EP15774141.4A priority patent/EP3067569B1/fr
Publication of WO2015151844A1 publication Critical patent/WO2015151844A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—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 of manufacturing the centrifugal compressor.
  • a centrifugal compressor is known as a compressor of a supercharger which raises air supplied to an internal combustion engine used for a ship etc. to atmospheric pressure or more (see, for example, Patent Document 1).
  • the centrifugal compressor includes an impeller attached to a rotor shaft, a guide cylinder accommodating the impeller, and a scroll portion into which compressed air discharged from the guide cylinder flows.
  • the centrifugal compressor compresses the air flowing in the axial direction from the intake port, guides it in the direction inclined from the axial direction, and discharges the compressed air from the discharge port.
  • the present invention has been made in view of such circumstances, and when all or part of the impeller is broken or dropped and scattered in the radial direction orthogonal to the axial direction of the rotor shaft, the entire impeller is
  • An object of the present invention is to provide a centrifugal compressor capable of suppressing a problem in which a part of the dust scatters to the outside.
  • Another object of the present invention is to provide a supercharger including the above-described centrifugal compressor, and a method of manufacturing the above-described centrifugal compressor.
  • the present invention adopts the following means.
  • a centrifugal compressor mounted on a rotor shaft and compressing a fluid flowing in from an intake port and discharging the fluid from a discharge port
  • a guide cylinder housing the impeller, the guide The discharge port side of the guide cylinder and the scroll portion disposed on the outer peripheral side of the cylinder and in which the compressed fluid discharged from the discharge port flows and the impeller is surrounded around the axis of the rotor shaft And an annular member attached at a connecting position with the scroll portion.
  • the outer diameter of the blade is larger on the discharge port side than on the intake port side. Therefore, the center of gravity of the impeller is located on the discharge port side.
  • the connection position between the discharge port side of the guide cylinder and the scroll portion is a position corresponding to the center of gravity of the impeller on the axis (hereinafter referred to as the center of gravity position) or a position near the center of gravity.
  • an annular member is provided at this connection position, and all or part of the broken or dropped impeller is broken even in the radial direction orthogonal to the axial direction from the center of gravity of the impeller. Arranged to collide. Even in the case where the guide cylinder is broken due to the collision of all or part of the broken or dropped impeller, the collision with the annular member does not lead to the brittle failure but only plastic deformation. Accordingly, it is possible to suppress the problem that all or part of the broken or dropped impeller is scattered to the outside.
  • the annular member may be made of a material higher in ductility than the guide cylinder. In this way, when all or part of the broken or dropped impeller collides with the highly ductile annular member, it is more reliably ensured that the annular member remains in plastic deformation without reaching brittle fracture. Can.
  • high ductility means having the property accompanied by large plastic deformation until failure, and indicates that the brittle property leading to the failure is small when the plastic deformation is small. Specifically, it is possible to confirm that the ductility is high by comparing the tensile fracture strength to failure and the elongation (percentage).
  • the centrifugal compressor In the centrifugal compressor according to one aspect of the present invention, it is arranged coaxially with the rotor shaft on the outer peripheral side in the radial direction orthogonal to the axis than the guide cylinder and on the inner peripheral side in the radial direction than the scroll portion.
  • the configuration may include a cylindrical member. According to the centrifugal compressor of this configuration, when all or part of the impeller is broken or dropped, all or part of the impeller is scattered in the radial direction orthogonal to the axial direction of the rotor shaft and collides with the guide cylinder Do. A part of the impeller that has collided with the guide cylinder causes the guide cylinder to be brittlely broken and is further scattered outward in the radial direction to reach the cylindrical member.
  • the cylindrical member can suppress a problem in which a part of the impeller scatters to the outside due to plastic deformation, even when the guide cylinder is broken due to brittleness.
  • the end on the discharge port side of the cylindrical member and the end on the intake port side of the annular member overlap in the radial direction and are close in the radial direction It may be arranged in In this way, when the breaking member scatters to the outside and collides with either the cylindrical member or the annular member disposed on the inner peripheral side in the radial direction, one member that receives an impact is in the radial direction It moves toward the outer peripheral side of and collides with any other member. Thus, the formation of a gap between the cylindrical member and the annular member is restricted.
  • the cylindrical member is made of a material having a ductility higher than that of the guide cylinder, and the diameter of the annular member matches the diameter of the cylindrical member with respect to the axis.
  • the axial end face of the annular member and the axial end face of the cylindrical member may be separated by a predetermined distance in the axial direction.
  • the annular member and the cylindrical member form the same cylindrical surface surrounding the guide cylinder around the rotor axis. All or a part of the impeller that brittlely fractures the guide cylinder and scatters radially outward collides with either the annular member or the cylindrical member forming the same cylindrical surface. Since the same cylindrical surface is formed, no gap is formed when the diameter of the outer peripheral surface of the annular member is different from the diameter of the outer peripheral surface of the cylindrical member. Therefore, the problem that all or part of the impeller scatters from the gap formed due to the difference in diameter of the annular member and the outer peripheral surface of the cylindrical member to the outside is suppressed.
  • the end face in the axial direction of the annular member and the cylindrical member are separated at a predetermined distance in the axial direction.
  • the axial center of gravity position of the impeller may be present in the axial position range in which the annular member is disposed.
  • the axial center of gravity position of the impeller is present in the axial position range in which the annular member is disposed.
  • the annular member together with the guide cylinder, forms a flow path wall of a flow path through which the compressed fluid discharged from the discharge port flows, and the annular member is An annular projection projecting inward in the radial direction on the outer peripheral side in the radial direction orthogonal to the axis and on the flow passage side in the axial direction; and the guide cylinder at the connection position has an outer periphery in the radial direction
  • An annular step may be provided on the side and the flow path side in the axial direction, and the guide cylinder and the annular member may be connected in a state where the annular protrusion is disposed on the annular step.
  • the centrifugal compressor of this configuration As the rotation speed of the rotor shaft increases and the pressure of the compressed fluid discharged from the discharge port increases, the pressure received by the annular member from the compressed fluid increases.
  • the annular protrusion which an annular member has on the flow-path side is arrange
  • a supercharger is a centrifugal compressor according to any of the above, a turbine rotated about the axis by exhaust gas discharged from an internal combustion engine, and connected to the rotor shaft. Equipped with According to the turbocharger according to one aspect of the present invention, when all or a part in the vicinity of the center of gravity of the impeller is broken or dropped and scattered in the radial direction orthogonal to the axial direction of the rotor shaft, It is possible to suppress the problem that all or a part scatters to the outside.
  • a method of manufacturing a centrifugal compressor includes the steps of: attaching an impeller for compressing a fluid flowing in from an inlet and discharging the compressed fluid from an outlet to a rotor shaft; Forming a flow path through which a cylinder is attached to guide the fluid flowing in from the intake port to the discharge port; and a scroll portion into which the compressed fluid discharged from the discharge port flows in the rotor shaft rather than the guide cylinder And disposing an annular member at a connecting position between the guide cylinder and the scroll portion so as to surround the impeller around the axis line. It is characterized by: attaching an impeller for compressing a fluid flowing in from an inlet and discharging the compressed fluid from an outlet to a rotor shaft; Forming a flow path through which a cylinder is attached to guide the fluid flowing in from the intake port to the discharge port; and a scroll portion into which the compressed fluid discharged from the discharge port flows in the rotor shaft rather than the guide cylinder And disposing an annular member at a connecting
  • the centrifugal compressor manufactured by the manufacturing method according to one aspect of the present invention when all or a part in the vicinity of the center of gravity of the impeller is broken or dropped, the whole or a part of the impeller is the axis of the rotor shaft It is scattered in the radial direction orthogonal to the direction to reach the connecting position of the guide cylinder and the scroll portion.
  • the annular member In the connection position, the annular member is attached to surround the impeller, so that all or part of the scattered impeller collides with the annular member.
  • the annular member can suppress a problem that all or a part of the impeller scatters to the outside due to plastic deformation, even when the guide cylinder is broken due to brittleness.
  • the whole or a part of the impeller scatters to the outside It is possible to provide a centrifugal compressor capable of suppressing the above problems. Further, according to the present invention, it is possible to provide a supercharger equipped with the above-described centrifugal compressor, and a method of manufacturing the above-described centrifugal compressor.
  • the turbocharger 100 of the present embodiment is a device that raises the air (gas) supplied to a marine diesel engine (internal combustion engine) used for a ship to a pressure higher than atmospheric pressure to enhance the combustion efficiency of the marine diesel engine.
  • the turbocharger 100 of the present embodiment includes a centrifugal compressor 10 and a turbine 20.
  • the centrifugal compressor 10 and the turbine 20 are respectively connected to the rotor shaft 30.
  • the centrifugal compressor 10 compresses air flowing from the outside of the turbocharger 100, and compressed into an intake manifold (not shown) communicating with the inside of a cylinder liner (not shown) constituting a marine diesel engine (hereinafter referred to as “the air”). It is a device that supplies compressed air (compressed fluid).
  • the centrifugal compressor 10 includes an impeller 11, an air guide cylinder 12, a scroll portion 13, a first containment ring 14 (annular member), a second containment ring 15 (cylindrical member), and a silencer 16. Is equipped.
  • the air guide cylinder 12 and the scroll portion 13 are made of metal members manufactured by casting to form a complicated shape.
  • this metal member for example, cast iron which is an Fe—C based alloy containing iron as a main component and 2% or more of carbon is used. It is possible to use various materials such as gray cast iron if it is cast iron, but it is preferable to use ductile cast iron (FCD: Ferrum Casting Ductile) in which black smoke in base tissue is spheroidized. The cast metal material tends to form a complicated shape by casting, but has brittleness.
  • FCD Ferrum Casting Ductile
  • the first containment ring 14 and the second containment ring 15 are made of metal members manufactured by rolling.
  • the metal member for example, a steel material which is an Fe—C based alloy which contains iron as a main component and a slight amount (about 0.2%) of carbon is used.
  • SS400 JIS G 3101; ASTM A283
  • the metal material by rolling has a composition suitable for a rolling process, and retains ductility leading to fracture after large plastic deformation.
  • the metal material by casting consists of a composition suitable for a casting process, and the elongation to failure is smaller than the metal material by rolling.
  • the metal material by rolling has a greater elongation to failure than the metal material by casting, that is, the ductility is high. Therefore, the rolled metal material has the property of higher fracture strength to impact than the cast metal material.
  • the tensile strength at normal temperature is about 400 to 500 N / mm 2 for both ductile cast iron and SS400.
  • the elongation at break is about 10% of ductile cast iron material
  • SS400 material holds 20% or more. Therefore, the SS400 material has higher ductility than the ductile cast iron material.
  • the turbine 20 includes a turbine housing 21, a turbine blade 22, a turbine disk 23 and a turbine nozzle 24.
  • the turbine housing 21 is a hollow cylindrical member disposed around the axis X, and accommodates therein the turbine blade 22, the turbine disk 23, and the turbine nozzle 24. Exhaust gas exhausted from the marine diesel engine flows into the turbine housing 21 along the arrow shown on the right side of FIG.
  • the exhaust gas introduced to the turbine housing 21 is expanded by static pressure as it passes through the turbine nozzle 24 and is introduced to the turbine blade 22.
  • the turbine blades 22 are attached to the outer peripheral surface of the substantially disk-shaped turbine disk 23 fixed to the rotor shaft 30 at fixed intervals around the axis.
  • the turbine disk 23 is given rotational force about the axis X by passing the static pressure expanded exhaust gas through the turbine blade 22. This rotational force is a power for rotating the rotor shaft 30, and rotates the impeller 11 connected to the rotor shaft 30 about the axis X.
  • the turbocharger 100 guides the exhaust gas discharged from the marine diesel engine to the turbine 20 to rotate the turbine disk 23 on which the turbine blade 22 is attached around the axis X.
  • the impeller 11 connected via the rotor shaft 30 rotates with the rotation of the turbine disk 23, and the air flowing in from the inlet 11a is compressed, and the compressed air is discharged from the outlet 11b.
  • the compressed air discharged from the discharge port 11 b flows into the scroll portion 13 and is guided to the intake manifold of the marine diesel engine.
  • the silencer 16 is a device that reduces the level of noise generated in the centrifugal compressor 10. As shown in FIG. 1, the silencer 16 defines a flow path for guiding the air flowing in from the direction orthogonal to the axis X to the inlet 11 a of the air guide cylinder 12. A silencer material 16 a is disposed around the flow path. A part of the noise generated in the centrifugal compressor 10 is absorbed by the sound deadening material 16a, and the noise level is reduced.
  • the impeller 11 is attached to a rotor shaft 30 extending along the axis X, and rotates around the axis X as the rotor shaft 30 rotates around the axis X.
  • the impeller 11 rotates around the axis X to compress the air flowing in from the inlet 11 a and discharge the air from the outlet 11 b.
  • the impeller 11 has a hub 11c attached to the rotor shaft 30, a blade 11d attached on the outer peripheral surface of the hub 11c, and a flow passage 11e.
  • the impeller 11 is provided with a space formed by the outer peripheral surface of the hub 11c and the inner peripheral surface of the air guiding cylinder 12, and this space is partitioned into a plurality of spaces by a plurality of blades 11d. Then, the impeller 11 applies centrifugal force in the radial direction to the air flowing in from the intake port 11a along the axis X direction, and in a direction (inclined direction; radial direction of the impeller 11) orthogonal to the axis X direction.
  • the compressed air discharged from the discharge port 11b is made to flow into the diffuser 13a.
  • the air guide cylinder 12 is a member that accommodates the impeller 11 and discharges, from the discharge port 11 b, air flowing in from the intake port 11 a along the axis X direction of the rotor shaft 30.
  • the scroll unit 13 is a device for receiving the compressed air discharged from the discharge port 11b and converting kinetic energy (dynamic pressure) applied to the compressed air into pressure energy (static pressure).
  • the scroll portion 13 is disposed on the outer peripheral side in the radial direction orthogonal to the axial line X direction with respect to the air guide cylinder 12.
  • the scroll portion 13 includes a diffuser 13a, a diffuser disk 13b, an outer scroll casing 13c (see FIG. 1), an inner scroll casing 13d, and a spiral chamber 13e.
  • the spiral chamber 13e is a space defined by the outer scroll casing 13c and the inner scroll casing 13d.
  • the inner scroll casing 13 d is connected to the air guiding cylinder 12 by a fastening bolt 43.
  • the diffuser 13a is an airfoil-shaped member disposed on the downstream side of the discharge port 11b of the impeller 11, and forms a flow path for guiding the compressed air from the discharge port 11b to the spiral chamber 13e.
  • the diffusers 13 a are provided at a plurality of circumferential positions of the annular diffuser disc 13 b coaxially arranged with the rotor shaft 30.
  • the diffuser 13 a is provided so as to surround the discharge port 11 b of the compressed air provided around the entire circumference of the impeller 11. As shown in FIG. 2, the diffuser disk 13 b is coupled to the inner scroll casing 13 d by a fastening bolt 44.
  • the diffuser 13 a converts kinetic energy (dynamic pressure) imparted to the compressed air into pressure energy (static pressure) by decelerating the flow velocity of the compressed air discharged from the discharge port 11 b of the impeller 11.
  • the compressed air whose velocity is reduced when passing through the diffuser 13a flows into the vortex chamber 13e in communication with the diffuser 13a.
  • the working fluid having flowed into the spiral chamber 13e is discharged to a discharge pipe (not shown).
  • the first containment ring 14 is an annular member attached at a connecting position between the discharge port 11 b side of the air guiding cylinder 12 and the inner scroll casing 13 d so as to surround the impeller 11 around the axis 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 cylindrical member disposed on the outer peripheral side in the radial direction than the air guide cylinder 12 and on the inner peripheral side in the radial direction than the scroll portion 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.
  • the first containment ring 14 and the second containment ring 15 are made of metal members manufactured by rolling and have higher ductility than the air guide cylinder 12 made of metal members manufactured by casting.
  • high ductility is accompanied by large plastic deformation until failure, and indicates that the brittle property leading to failure is small in a situation where plastic deformation is small.
  • a material with high ductility can be absorbed and restrained by plastic deformation of kinetic energy of impact. Therefore, it becomes possible to hold
  • the ductile cast iron material used as the metal material manufactured by casting has a tensile strength at normal temperature of about 400 to 500 N / mm 2 and an elongation of about 10%.
  • the SS400 material used as a metal member manufactured by rolling has a tensile strength at normal temperature of about 400 to 500 N / mm 2 and an elongation of 20% or more. Therefore, SS400 material can be confirmed as a material with higher ductility than ductile cast iron material from the difference in elongation.
  • the first containment ring 14 and the second containment ring 15 have higher ductility than the air guide cylinder 12. Therefore, even when the impeller 11 is damaged or dropped, the first containment ring 14 and the second containment ring 15 scatter all or part of the impeller 11 in the radial direction and collide with the air guide cylinder 12 In this case, scattering of all or part of the impeller 11 to the outside is suppressed. That is, even in the case where the air guide tube 12 is broken due to the collision of all or a part of the impeller 11, the impeller ring is caused by the plastic deformation of the first containment ring 14 and the second containment ring 15. It is possible to suppress the problem that all or a part of the material scatters 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 coincide with each other.
  • the reason why the radius D1 and the radius D2 are made to coincide is that a gap that is generated when 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 is not formed. It is for. If this gap is formed, all or part of the impeller 11 may be scattered to the outside.
  • the radius D1 of the outer circumferential surface of the first containment ring 14 and the radius D2 of the outer circumferential surface of the second containment ring 15 do not match, the end of the first containment ring 14 in the axial line X direction If the gap between the part and the end of the second containment ring 15 in the direction of the axis X is small, the possibility that all or part of the impeller 11 scattering in the radial direction scatters to the outside can be reduced. it can. Therefore, the radius D1 of the outer circumferential surface of the first containment ring 14 and the radius D2 of the outer circumferential surface of the second containment ring 15 do not have to be the same diameter.
  • an end face 14 a in the direction of the axis X of the first containment ring 14 and an end face 15 a in the direction of the axis X of the second containment ring 15 are separated by a predetermined distance W in the axis X direction. It is separated.
  • the first expansion ring 14 and the second expansion ring 15 are separated by a predetermined distance W in the direction of the axis X, so that the difference in thermal expansion due to the temperature difference is each member.
  • the first containment ring 14 and the second containment ring 15 do not cause any deformation or breakage.
  • the position in the direction of the axis X at which the first containment ring 14 is disposed is a position P1.
  • the position P1 coincides with the axial center of gravity of the impeller 11.
  • the outer diameter of the blade is larger on the discharge port 11b side than on the intake port 11a side. Therefore, the center-of-gravity position of the impeller 11 is a position P1 closer to the discharge port 11b side than the intake port 11a side.
  • the impeller 11 When the impeller 11 rotates at high speed around the axis X (for example, when it rotates at 10,000 revolutions per minute or more), all or part of the impeller 11 may break or drop off.
  • the impact force in the radial direction orthogonal to the axis X direction when the impeller 11 drops off is particularly large at the center of gravity.
  • the position P1 in the direction of the axis X at which the first containment ring 14 is disposed coincides with the position of the center of gravity of the impeller 11 in the axial direction.
  • the first containment ring 14 forms a flow passage wall on the outer peripheral side of the flow passage 11 e through which the compressed air discharged from the discharge port 11 b flows together with the air guide cylinder 12.
  • the first containment ring 14 has an annular protruding portion 14 b that protrudes radially inward on the outer peripheral side in the radial direction and on the flow path 11 e side in the axial direction X.
  • the air guiding cylinder 12 has an annular stepped portion 12 a on the outer peripheral side in the radial direction and on the flow path 11 e side in the axis X direction.
  • the air guiding cylinder 12 and the first containment ring 14 are connected in a state where the annular protrusion 14 b is disposed on the annular step 12 a.
  • a gap is provided between the annular step 12a and the annular projection 14b. Due to this gap, even if there is thermal expansion of the air guide cylinder 12, deformation can be prevented from propagating to the first containment ring 14 due to the thermal expansion.
  • An endless annular groove 13g extending in the circumferential direction about the axis X is formed in the inner peripheral end face 13f.
  • An O-ring 13 h (annular seal member) is fitted into the annular groove 13 g.
  • an endless annular groove portion 14d extending in the circumferential direction around the axis X is formed in the outer peripheral side end face 14c.
  • An O-ring 14e (annular seal member) is fitted into the annular groove 14d.
  • the manufacturing method of the centrifugal compressor 10 of this embodiment manufactures the centrifugal compressor 10 by the following processes.
  • the impeller 11 which compresses the air flowing in from the inlet 11 a and discharges it from the outlet 11 b is attached to the rotor shaft 30.
  • the air guide cylinder 12 is attached so as to accommodate the impeller 11, and the air flowing from the intake port 11a along the axis X direction of the rotor shaft 30 is guided in the direction inclined from the axis X direction.
  • a flow path leading to the discharge port 11 b is formed.
  • the scroll portion 13 into which the compressed air discharged from the discharge port 11 b flows is disposed on the outer peripheral side in the radial direction orthogonal to the axis X direction with respect to the air guide cylinder 12.
  • the steel material is mainly made of a steel material having a ductility higher than that of cast iron constituting the air guide cylinder 12 or the scroll portion 13 at the connecting position of the air guide cylinder 12 and the scroll portion 13 so as to surround the impeller 11 around the axis X Attach the first containment ring 14 configured.
  • a steel material having a ductility higher than that of cast iron constituting the air guide cylinder 12 or the scroll portion 13 on the outer peripheral side in the radial direction than the air guide cylinder 12 and on the inner peripheral side in the radial direction Attach the second main containment ring 15.
  • the centrifugal compressor 10 of the present embodiment is manufactured by the above steps.
  • the compressor provided in the turbocharger 100 of the present embodiment is a centrifugal compressor. Therefore, in the impeller 11, the outer diameter of the blade is larger on the discharge port 11b side than on the intake port 11a side. Therefore, the gravity center position of the impeller 11 is the position P1 on the discharge port 11b side.
  • the connection position between the discharge port 11 b side of the air guide cylinder 12 and the scroll portion 13 is the center of gravity of the impeller 11 at the axis X.
  • a first containment ring 14 (annular member) mainly made of a steel material having higher ductility than cast iron mainly composed of the air guide cylinder 12 and the scroll portion 13 is provided at this connection position. Even in the case of scattering in the radial direction orthogonal to the axis X direction from the position of the center of gravity of the impeller 11, all or part of the broken or dropped impeller 11 is disposed to collide. Even when the air guide cylinder 12 is broken due to the collision of all or part of the broken or dropped impeller 11, the collision with the high ductility first containment ring 14 does not lead to the brittle failure. Staying in plastic deformation. Therefore, it is possible to suppress the problem that all or part of the broken or dropped impeller 11 scatters to the outside of the turbocharger 100.
  • the diameter of the outer circumferential surface of the first containment ring 14 matches the diameter of the outer circumferential surface of the second containment ring 15. Therefore, the first containment ring 14 and the second containment ring 15 form the same cylindrical surface surrounding the air guiding cylinder 12 around the rotor shaft 30.
  • All or a part of the impeller 11 that brittlely breaks the air guide cylinder 12 and scatters outward in the radial direction is either the first containment ring 14 or the second containment ring 15 that forms the same cylindrical surface. collide. Since the same cylindrical surface is formed, no gap is formed when 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. Therefore, the problem that all or a part of the impeller 11 scatters to the outside of the turbocharger 100 from the gap formed by the difference in diameter of the outer circumferential surface of the first containment ring 14 and the second containment ring 15 is suppressed. Be done.
  • the end face 14 a in the axial X direction of the first containment ring 14 and the end face 15 a in the axial X direction of the second containment ring 15 are It is separated by a predetermined distance W in the axis X direction.
  • the first containment ring 14 and the second containment ring 15 are configured as separate members, and are separated by a predetermined distance W in the axis X direction. As a result, even if a difference in thermal expansion amount caused by a temperature difference occurs in each member, neither deformation nor breakage occurs in any of the first containment ring 14 and the second containment ring 15.
  • the first containment ring 14 is compressed as the rotational speed of the rotor shaft 30 increases and the pressure of the compressed air discharged from the discharge port 11 b increases. The pressure from the air increases.
  • the annular projection 14b that the first containment ring 14 has on the flow passage 11e side is disposed in the annular step 12a that the air guiding cylinder 12 has on the flow passage 11e side. Therefore, as the pressure that the first containment ring 14 receives from the compressed air increases, the contact force between the annular protrusion 14 b and the annular step 12 a increases. Thereby, the problem that compressed air leaks out at the connection position of the first containment ring 14 and the air guiding cylinder 12 is suppressed.
  • the radially inner end face 13 f of the scroll portion 13 at the connection position and the radially outer end face 14 c of the first containment ring 14 are disposed between the two. In this way, the problem of compressed air leaking at the position where the scroll portion 13 and the first containment ring 14 face each other is suppressed.
  • the air guide cylinder 12 and the scroll portion 13 of the present embodiment are formed of metal members manufactured by casting.
  • this metal member it is preferable to use gray cast iron or ductile cast iron which is easy to manufacture a complicated shape.
  • the first containment ring 14 and the second containment ring 15 are formed of metal members manufactured by rolling.
  • this metal member it is preferable to use a general structural rolled steel material called SS400, which is higher in ductility than cast iron material and less likely to be damaged by plastic deformation even under impact load. By doing this, the ducts of the first containment ring 14 and the second containment ring 15, which are metal members manufactured by rolling, are compared with the air guide cylinder 12 and the scroll portion 13 which are metal members manufactured by casting. Can be higher than the ductility of the
  • turbocharger 200 of the second embodiment is a modification of the turbocharger 100 of the first embodiment. It shall be the same as that of supercharger 100 of a 1st embodiment except for the case where it explains especially below, and it omits explanation about what attached the same numerals.
  • the turbocharger 100 according to the first embodiment separates the first containment ring 14 and the second containment ring 15 by a predetermined distance W in the axis X direction.
  • the first containment ring 14 'and the second containment ring 15' are arranged so as to overlap in the radial direction and be in close proximity to each other in the radial direction. is there.
  • the centrifugal compressor 10 includes a first containment ring 14 ′ (annular member) and a second containment ring 15 ′ (cylindrical member).
  • the first containment ring 14 ′ and the second containment ring 15 ′ are made of the same metal members as the first containment ring 14 and the second containment ring 15 of the first embodiment.
  • the first containment ring 14 ′ is an annular ring attached to the connection position between the outlet 11 b side of the air guide cylinder 12 and the inner scroll casing 13 d so as to surround the impeller 11 around the axis X It is a member. 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 a fastening bolt 41.
  • the second containment ring 15 ′ is a cylindrical member disposed on the outer peripheral side in the radial direction than the air guide cylinder 12 and on the inner peripheral side in the radial direction than the scroll portion 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 a fastening bolt 42.
  • the radius D1 of the outer circumferential surface of the first containment ring 14 'and the radius D2 of the outer circumferential surface of the second containment ring 15' coincide with each other.
  • the reason why the radius D1 and the radius D2 are matched is that a gap is not formed which occurs when the diameter of the outer peripheral surface of the first containment ring 14 'is different from the diameter of the outer peripheral surface of the second containment ring 15'. In order to If this gap is formed, all or part of the impeller 11 may be scattered to the outside.
  • an end 15a 'on the discharge opening 11b side of the second containment ring 15' and an end 14a 'on the intake opening 11a side of the first containment ring 14' are in the radial direction. And are arranged at positions close to each other in the radial direction.
  • the gap in the radial direction between the end portion 14a 'disposed on the inner circumferential side and the end portion 15a' disposed on the outer circumferential side is set so as to maintain such a distance that these members do not contact due to thermal expansion. It is done.
  • the end 14a 'of the first containment ring 14' and the end 15a 'of the second containment ring 15' disposed on the outer circumferential side are in contact due to thermal expansion, and each is deformed Alternatively, the failure to break can be prevented.
  • the radial gap between the end portion 14a 'disposed on the inner circumferential side and the end portion 15a' disposed on the outer circumferential side is formed when the end portion 14a 'is plastically deformed by the impact of the breaking member.
  • the distance is set such that the end 14 a ′ contacts the end 15 a ′.
  • the position in the direction of the axis X at which the first containment ring 14 'is disposed is the position P1.
  • the position P1 coincides with the axial center of gravity of the impeller 11.
  • the position P1 coincides with the end face of the annular projection 14b of the first containment ring 14 'shown in FIG. 6 on the intake port 11a side.
  • the outer diameter of the blade is larger on the discharge port 11b side than on the intake port 11a side. Therefore, the center-of-gravity position of the impeller 11 is a position P1 closer to the discharge port 11b side than the intake port 11a side.
  • the impeller 11 When the impeller 11 rotates at high speed around the axis X (for example, when it rotates at 10,000 revolutions per minute or more), all or part of the impeller 11 may break or drop off.
  • the impact force in the radial direction orthogonal to the axis X direction when the impeller 11 drops off is particularly large at the center of gravity.
  • the position P1 in the direction of the axis X at which the first containment ring 14 'is disposed coincides with the position of the center of gravity of the impeller 11 in the axial direction.
  • the impeller 11 when the impeller 11 broken or dropped at the center of gravity scatters in the radial direction to damage the air guide cylinder 12 and further scatters in the radial direction, the impeller 11 collides with the first containment ring 14 ' . And the defect which all or one part of the impeller 11 disperses outside can be suppressed by plastically deforming the 1st containment ring 14 'with high ductility.
  • the first containment ring 14 ′ together with the air guide cylinder 12, forms a flow passage wall on the outer peripheral side of the flow passage 11 e through which the compressed air discharged from the discharge port 11 b flows.
  • the first containment ring 14 ′ has an annular protruding portion 14 b protruding inward in the radial direction on the inner peripheral side in the radial direction and on the flow passage 11 e side in the axial direction X.
  • the air guiding cylinder 12 has an annular stepped portion 12 a on the outer peripheral side in the radial direction and on the flow path 11 e side in the axis X direction.
  • a gap is provided between the annular step 12a and the annular projection 14b. Due to this gap, even if there is thermal expansion of the air guide cylinder 12, deformation can be prevented from propagating to the first containment ring 14 'due to the thermal expansion.
  • the compressor provided in the turbocharger 200 of the present embodiment is a centrifugal compressor. Therefore, in the impeller 11, the outer diameter of the blade is larger on the discharge port 11b side than on the intake port 11a side. Therefore, the gravity center position of the impeller 11 is the position P1 on the discharge port 11b side.
  • the connection position between the discharge port 11 b side of the air guide cylinder 12 and the scroll portion 13 is the center of gravity of the impeller 11 at the axis X.
  • a first containment ring 14 '(annular member) mainly made of a steel material having higher ductility than cast iron mainly composed of the air guide cylinder 12 and the scroll portion 13 is provided at this connection position. Even in the case of scattering in the radial direction orthogonal to the axis X direction from the position of the center of gravity of the impeller 11, all or part (rupturing member) of the impeller 11 that has been broken or dropped is disposed to collide. Even when the air guide cylinder 12 is broken due to the collision of the fracture member, the collision with the high ductility first containment ring 14 'does not lead to the brittle failure and plastic deformation occurs. Accordingly, it is possible to suppress the problem that the breaking member scatters to the outside of the turbocharger 200.
  • a second containment made of a material having a ductility higher than that of the air guiding cylinder 12 on the outer peripheral side in the radial direction than the air guiding cylinder 12 and on the inner peripheral side in the radial direction than the scroll portion 13 I placed the ring 15 '.
  • the center-of-gravity position P1 in the direction of the axis X of the impeller 11 is present in the position range in the direction of the axis X in which the first containment ring 14 'is disposed.
  • the gravity center position P1 of the axial line X direction of the impeller 11 is made to exist in the position range of the axial line X direction in which 1st containment ring 14 'is arrange
  • the first containment ring 14 ' is used as the rotational speed of the rotor shaft 30 increases and the pressure of the compressed air discharged from the discharge port 11b increases.
  • the pressure received from the compressed air is increased.
  • the annular projection 14b that the first containment ring 14 'has on the flow passage 11e side is disposed in the annular step 12a that the air guiding cylinder 12 has on the flow passage 11e side. Therefore, as the pressure received from the compressed air by the first containment ring 14 'increases, the contact force between the annular protrusion 14b and the annular step 12a increases. Thereby, the problem that compressed air leaks out at the connection position of the first containment ring 14 ′ and the air guiding cylinder 12 is suppressed.
  • the radially inner end face 13 f of the scroll portion 13 at the connection position and the radially outer end face 14 c of the first containment ring 14 ′ are disposed between the two. In this way, the problem of compressed air leaking out at the position where the scroll portion 13 and the first containment ring 14 'face each other is suppressed.
  • the air guide cylinder 12 and the scroll portion 13 of the present embodiment are formed of metal members manufactured by casting.
  • this metal member it is preferable to use gray cast iron or ductile cast iron which is easy to manufacture a complicated shape.
  • 1st containment ring 14 'and 2nd containment ring 15' are formed with the metal member manufactured by rolling.
  • this metal member it is preferable to use a general structural rolled steel material called SS400, which is higher in ductility than cast iron material and less likely to be damaged by plastic deformation even under impact load.
  • the ducts of the first containment ring 14 'and the second containment ring 15' which are metal members manufactured by rolling, can be reduced by the air guide cylinder 12 and the scroll, which are metal members manufactured by casting.
  • the ductility of the part 13 can be made higher.
  • the rotor shaft 30 to which the impeller 11 provided in the centrifugal compressor 10 is connected is rotated about the axis X by the turbine 20 rotated by the exhaust gas discharged from the marine diesel engine. It may be another aspect.
  • the rotor shaft 30 may be rotated by another power source such as a motor connected to the rotor shaft 30.
  • the radius D1 of the outer circumferential surface of the first containment ring 14, 14 'and the radius D2 of the outer circumferential surface of the second containment ring 15, 15' coincide with each other.
  • "Match" in the above description does not mean that the radius D1 and the radius D2 exactly match. Even when the radius D1 and the radius D2 are different, a gap is provided between the first containment rings 14, 14 'and the second containment rings 15, 15' to such an extent that the breaking member does not pass through. In this case, 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, but may be other aspects.
  • the end portion 14a 'of the first containment ring 14' is tapered such that the outer diameter gradually decreases toward the intake port 11a, and the end portion of the second containment ring 15 '
  • the tapered shape may be such that the inner diameter gradually increases toward the discharge port 11b side.
  • the shape of the end 15a ′ of the second containment ring 15 ′ may be the same as the shape of the other portion than the end 15a ′.
  • the plate thickness in the radial direction orthogonal to the axis X is substantially constant from the end on the intake port 11a side to the end on the discharge port 11b side.
  • the end 14a 'of the first containment ring 14' is disposed on the outer circumferential side
  • the end 15a 'of the second containment ring 15' is disposed on the inner circumferential side. Good.

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

Abstract

La présente invention concerne un compresseur centrifuge, qui comprend : un impulseur (11) destiné à comprimer de l'air s'écoulant à partir d'un orifice d'admission (11a) et à évacuer l'air à partir d'un orifice d'évacuation (11b), l'impulseur (11) étant fixé à un arbre (30) de rotor ; un cylindre (12) de guidage d'air destiné à recevoir l'impulseur (11) ; une partie à spirales (13) dans laquelle s'écoule l'air comprimé évacué à partir de l'orifice d'évacuation (11b), la partie à spirales (13) étant agencée plus loin vers la périphérie que le cylindre (12) de guidage d'air ; et une première bague de confinement (14) fixée à une position de liaison entre le cylindre de guidage d'air (12) et la partie à spirales (13) de manière à entourer l'impulseur (11) autour d'une ligne d'axe (X) de l'arbre (30) de rotor.
PCT/JP2015/058355 2014-03-31 2015-03-19 Compresseur centrifuge, compresseur de suralimentation et procédé de fabrication de compresseur centrifuge WO2015151844A1 (fr)

Priority Applications (3)

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KR1020167016418A KR101884101B1 (ko) 2014-03-31 2015-03-19 원심 압축기, 과급기, 및 원심 압축기의 제조 방법
CN201580003047.6A CN106164497B (zh) 2014-03-31 2015-03-19 离心压缩机、增压器及离心压缩机的制造方法
EP15774141.4A EP3067569B1 (fr) 2014-03-31 2015-03-19 Compresseur centrifuge, compresseur de suralimentation et procédé de fabrication de compresseur centrifuge

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JP2014-074070 2014-03-31
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
JP2014-212793 2014-10-17
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

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US20180223871A1 (en) * 2016-03-30 2018-08-09 Mitsubishi Heavy Industries, Ltd. Compression device and supercharger
US11519423B1 (en) * 2021-11-11 2022-12-06 Progress Rail Locomotive Inc. Compressor joint

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WO2018137137A1 (fr) * 2017-01-24 2018-08-02 游涛 Moteur à vortex

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JPH10110622A (ja) * 1996-10-02 1998-04-28 Asea Brown Boveri Ag ターボチャージャの半径流タービン用の裂損防止装置
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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
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JPH10110622A (ja) * 1996-10-02 1998-04-28 Asea Brown Boveri Ag ターボチャージャの半径流タービン用の裂損防止装置
JP2012137091A (ja) * 2012-03-12 2012-07-19 Ihi Corp 遠心圧縮機ケーシング

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US20180223871A1 (en) * 2016-03-30 2018-08-09 Mitsubishi Heavy Industries, Ltd. Compression device and supercharger
US11359647B2 (en) * 2016-03-30 2022-06-14 Mitsubishi Heavy Industries Marine Machinery & Equipment Co., Ltd. Compression device and supercharger
US11519423B1 (en) * 2021-11-11 2022-12-06 Progress Rail Locomotive Inc. Compressor joint

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CN106164497A (zh) 2016-11-23
EP3067569A4 (fr) 2016-12-21
KR101884101B1 (ko) 2018-07-31
KR20160088922A (ko) 2016-07-26
EP3067569A1 (fr) 2016-09-14
EP3067569B1 (fr) 2018-07-18
CN106164497B (zh) 2019-06-28

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