WO2024038495A1 - Carter de turbine, turbine et compresseur de suralimentation - Google Patents

Carter de turbine, turbine et compresseur de suralimentation Download PDF

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Publication number
WO2024038495A1
WO2024038495A1 PCT/JP2022/030900 JP2022030900W WO2024038495A1 WO 2024038495 A1 WO2024038495 A1 WO 2024038495A1 JP 2022030900 W JP2022030900 W JP 2022030900W WO 2024038495 A1 WO2024038495 A1 WO 2024038495A1
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WIPO (PCT)
Prior art keywords
seat
scroll
valve body
channel
turbine housing
Prior art date
Application number
PCT/JP2022/030900
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English (en)
Japanese (ja)
Inventor
幹 惠比寿
Original Assignee
三菱重工エンジン＆ターボチャージャ株式会社
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.)
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Application filed by 三菱重工エンジン＆ターボチャージャ株式会社 filed Critical 三菱重工エンジン＆ターボチャージャ株式会社
Priority to PCT/JP2022/030900 priority Critical patent/WO2024038495A1/fr
Publication of WO2024038495A1 publication Critical patent/WO2024038495A1/fr

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    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere

Definitions

  • the present disclosure relates to a turbine housing, a turbine including the turbine housing, and a supercharger.
  • a first branch passage branching from the first scroll passage, a second branch passage branching from the second scroll passage, and a first branch passage and a second branch passage join together.
  • a merging flow path is formed that communicates with an exhaust flow path through which exhaust gas that has passed through a turbine wheel flows (see Patent Document 1).
  • a communication port provided between the merging flow path and the exhaust flow path can be closed, and the communication port provided between the merging flow path and the first branch flow path and the second branch flow path can be closed.
  • a valve having valve bodies that can be separated from each other is disclosed.
  • At least one embodiment of the present disclosure provides a turbine housing with a simple structure, a seal between two branch channels in a merging channel, and a seal between the merging channel and the exhaust channel. It is an object of the present invention to provide a turbine housing, a turbine, and a supercharger that can be sealed at the same time.
  • a turbine housing includes: A turbine housing in which two scroll passages are formed, a scroll flow path forming section that forms the two scroll flow paths; A first branch passage branching from one of the two scroll passages, a second branch passage branching from the other one of the two scroll passages, and the first branch passage.
  • a connecting channel that forms a connecting channel that includes a branch channel and the second branch channel that merge together, and a merging channel that communicates via a communication port with an exhaust channel through which exhaust gas that has passed through the turbine wheel flows.
  • a connecting channel forming section that is a forming section and has a branch wall that separates the first branch channel and the second branch channel
  • a turbine housing body including; a head capable of separating the two branching channels by abutting against the branching wall in the merging channel;
  • a valve having at least a seat portion that extends outward in a radial direction of the valve body from the head portion and is capable of closing the communication port by abutting against a seat wall surface of the turbine housing.
  • a scroll connection valve including a body; The seat portion has a deformation margin for causing the head portion to contact the branch wall after the seat portion contacts the seat wall surface during the closing operation of the scroll connection valve.
  • a turbine according to at least one embodiment of the present disclosure includes: the turbine housing; a turbine wheel rotatably housed in the turbine housing.
  • a supercharger according to at least one embodiment of the present disclosure, A turbine driven by exhaust gas discharged from an engine, the turbine; A compressor is coaxially connected to the turbine and supplies compressed air to the engine as it rotates.
  • the structure of the turbine housing is simple, and the sealing between two branch channels in the merging channel and the sealing between the merging channel and the exhaust channel are performed simultaneously.
  • a turbine housing, a turbine, and a supercharger are provided.
  • FIG. 1 is a schematic diagram of an engine system including a supercharger according to an embodiment.
  • FIG. 2 is a schematic cross-sectional view along the axis of a scroll connection valve of a turbine housing according to an embodiment.
  • FIG. 2 is a schematic cross-sectional view of the turbine housing according to the first embodiment taken along the axis of the scroll connection valve when the scroll connection valve is in a fully closed state.
  • FIG. 2 is a schematic cross-sectional view of the turbine housing according to the first embodiment taken along the axis of the scroll connection valve when the scroll connection valve is in a fully open state.
  • FIG. 1 is a schematic diagram of an engine system including a supercharger according to an embodiment.
  • FIG. 2 is a schematic cross-sectional view along the axis of a scroll connection valve of a turbine housing according to an embodiment.
  • FIG. 2 is a schematic cross-sectional view of the turbine housing according to the first embodiment taken along the axis of the scroll connection valve when the scroll connection valve is in
  • FIG. 7 is a schematic cross-sectional view of a turbine housing according to a modification of the first embodiment, taken along the axis of the scroll connection valve when the scroll connection valve is in a fully open state.
  • FIG. 7 is a schematic cross-sectional view of a turbine housing according to a second embodiment taken along the axis of the scroll connection valve when the scroll connection valve is in a fully closed state.
  • FIG. 7 is a schematic cross-sectional view of a turbine housing according to a third embodiment taken along the axis of the scroll connection valve when the scroll connection valve is in a fully closed state.
  • FIG. 1 is a schematic diagram of an engine system 11 including a supercharger 10 according to an embodiment.
  • the turbine 1 according to the present disclosure can be installed, for example, in a supercharger (turbocharger) 10 for automobiles, ships, or industries (for example, for land power generation).
  • a turbine 1 mounted on a supercharger (turbocharger) 10 will be described as an example, but the turbine 1 according to the present disclosure is not limited to one mounted on the supercharger 10. . Further, it is not necessary to limit the working fluid of the turbine 1 to exhaust gas.
  • the turbine 1 of the present disclosure only needs to be capable of converting working fluid energy into mechanical power (for example, rotational force), and even if it is configured by the turbine 1 alone, it may be configured with mechanisms or devices other than the compressor 13. It may be configured in combination. Further, there is no need to limit the usage of the turbine 1.
  • the supercharger 10 is configured to be driven by the energy of exhaust gas discharged from an engine (internal combustion engine) 12 and compress fluid (for example, air). has been done.
  • the supercharger 10 includes a turbine 1 driven by exhaust gas discharged from an engine 12, and a compressor 13 coaxially connected to the turbine 1 and configured to supply compressed air to the engine 12 as it rotates.
  • the turbine 1 includes a turbine wheel 3 and a turbine housing 2 configured to rotatably accommodate the turbine wheel 3.
  • the compressor 13 includes an impeller 131 and a compressor housing 132 configured to rotatably accommodate the impeller 131.
  • the supercharger 10 includes a rotating shaft 14 to which the turbine wheel 3 is connected at one end and an impeller 131 at the other end, and the rotating shaft 14 is rotatably supported between the turbine wheel 3 and the impeller 131.
  • the bearing 15 further includes a bearing 15 configured to.
  • the supercharger 10 may further include a bearing housing 16 arranged between the turbine housing 2 and the compressor housing 132 and configured to accommodate the bearing 15.
  • the turbine 1 is configured to rotate the turbine wheel 3 using the energy of exhaust gas discharged from the engine 12. Since the impeller 131 is coaxially connected to the turbine wheel 3 via the rotating shaft 14, it is driven to rotate around the axis LA of the supercharger 10 (rotating shaft 14) in conjunction with the rotation of the turbine wheel 3.
  • the compressor 13 sucks air (supply air, gas) into the compressor housing 132 by driving the impeller 131 to rotate around the axis LA, compresses the air, and sends the compressed air to the engine 12. It is composed of Compressed air sent from the compressor 13 to the engine 12 is provided for combustion in the engine 12. Exhaust gas generated by combustion in the engine 12 is sent from the engine 12 to the turbine 1 to rotate the turbine wheel 3.
  • the impeller 131 is configured to guide air introduced along the axial direction of the impeller 131 (i.e., the direction in which the axis LA extends) to the outside in the radial direction of the impeller 131.
  • the impeller 131 does not include an annular member surrounding the outer periphery of the blades of the impeller 131.
  • the turbine wheel 3 is configured to guide exhaust gas introduced from the outside in the radial direction of the turbine wheel 3 along the axial direction of the turbine wheel 3 (that is, the direction in which the axis LA extends).
  • the turbine wheel 3 does not include an annular member surrounding the outer periphery of the blades of the turbine wheel 3.
  • FIG. 2 is a schematic cross-sectional view of the scroll connection valve 5 of the turbine housing 2 according to one embodiment, taken along the axis LB.
  • the turbine housing 2 according to some embodiments includes a turbine housing body 20 and a scroll connection valve 5 attached to the turbine housing body 20.
  • the turbine housing main body 20 includes a scroll passage forming part 21 that forms two scroll passages (a first scroll passage 41 and a second scroll passage 42), and a first branch passage. 44, a connection flow path forming part 22 that forms a connection flow path 43 including a second branch flow path 45 and a merging flow path 46.
  • the turbine housing main body 20 may further include an exhaust flow path forming part 23 that forms an exhaust flow path 47 through which exhaust gas that has passed through the turbine wheel 3 flows.
  • a first scroll passage 41, a second scroll passage 42, a connecting passage 43, and an exhaust passage 47 are formed inside the turbine housing body 20 .
  • the turbine housing body 20 is made of a metal material.
  • Each of the first scroll passage 41 and the second scroll passage 42 is a passage for introducing exhaust gas into the turbine wheel 3.
  • Each of the first scroll passage 41 and the second scroll passage 42 is a spiral passage extending along the circumferential direction around the axis LA on the outer peripheral side of the turbine wheel 3.
  • the first branch flow path 44 is a flow path that branches from one of the two scroll flow paths 41 and 42 (first scroll flow path 41).
  • the second branch channel 45 is a channel that branches from the other scroll channel (second scroll channel 42) of the two scroll channels 41 and 42.
  • the merging flow path 46 communicates via a communication port 48 with an exhaust flow path 47 through which exhaust gas that has passed through the turbine 1 (specifically, the turbine wheel 3) flows.
  • first branch flow path 44 has one end connected to the first scroll flow path 41 and the other end connected to the second branch flow path 45 and the exhaust flow path 47 at the merging flow path 46 .
  • the second branch channel 45 has one end connected to the second scroll channel 42 and the other end connected to the first branch channel 44 and the exhaust channel 47 at a merging channel 46 .
  • the first branch flow path 44 and the second branch flow path 45 communicate exhaust gas between the first scroll flow path 41 and the second scroll flow path 42 so that the exhaust gas can flow therebetween. At least a portion of the exhaust gas flowing through the second scroll passage 42 is communicated with an exhaust passage 47 having a lower pressure than the first scroll passage 41 and the second scroll passage 42 so as to be dischargeable.
  • the scroll connection valve 5 is configured to connect between two branch channels (first branch channel 44 and second branch channel 45) in the merging channel 46 when the scroll connection valve 5 is in a fully closed state (during closing operation). This is for simultaneously performing sealing and sealing between the merging flow path 46 and the exhaust flow path 47. Further, when the scroll connection valve 5 is in a fully open state (during opening operation), the scroll connection valve 5 is connected between the two branch channels (the first branch channel 44 and the second branch channel 45) in the merging channel 46. This is to release the seal between the merging flow path 46 and the exhaust flow path 47, and to enable exhaust gas to flow between these flow paths.
  • the scroll connection valve 5 includes a valve body 6 and a valve rod 7 for driving the valve body 6.
  • the direction in which the axis LB of the valve body 6 extends is referred to as the axial direction of the valve body 6,
  • the direction perpendicular to the axis LB is referred to as the radial direction of the valve body 6, and the circumferential direction around the axis LB is referred to as the circumferential direction of the valve body 6.
  • the side where the head 61 is provided in the axial direction of the valve body 6 is defined as the distal end side, and the side opposite to the distal end side is defined as the proximal end side.
  • the scroll connection valve 5 is configured such that the opening degree of the valve body 6 can be adjusted.
  • the scroll connection valve 5 further includes a rotation drive device including an actuator (not shown) for rotating the valve stem 7 around the valve shaft RC.
  • the scroll connection valve 5 rotates the valve stem 7 and the valve body 6 connected to the valve stem 7 around the valve shaft RC, so that the opening degree of the valve body 6 corresponds to the angular position of the valve stem 7 in the circumferential direction.
  • the opening can be adjusted.
  • the scroll connection valve 5 is configured to be able to adjust the opening degree of the valve body 6 to fully open, fully closed, or at least one intermediate degree between fully open and fully closed.
  • the scroll connection valve 5 may include an axial drive device including an actuator (not shown) for moving the valve stem 7 along the axial direction of the valve body 6 instead of the rotation drive device described above.
  • the scroll connection valve 5 changes the opening degree of the valve body 6 by moving the valve stem 7 and the valve body 6 connected to the valve stem 7 along the axial direction of the valve body 6. The opening degree may be adjusted to correspond to the axial position of the opening.
  • valve body 6 (6A) In the valve body 6 (6A) according to the comparative example, as shown in FIG. 2, a valve body shaft portion 60, a head portion 61, a collar portion 63, and an inclined portion 65 are integrally formed.
  • the valve body 6 (6A) is made of a metal material.
  • the head 61 is provided on the distal end side of the valve body 6 in the axial direction, and is formed into a disk shape extending along a direction intersecting (orthogonal to in the illustrated example) the axis LB of the valve body 6.
  • the connection channel forming section 22 described above has a branch wall 221 that separates the first branch channel 44 and the second branch channel 45.
  • the head 61 extends along a direction that intersects (orthogonally in the illustrated example) the axis LB of the valve body 6 and has a head end surface 611 that faces the branch wall 221 .
  • the head end surface 611 is the end surface of the head 61 on the distal end side in the axial direction.
  • the head 61 can divide the two branch channels 44 and 45 by bringing the head end surface 611 into contact with the branch wall 221 in the merging channel 46 .
  • the flange portion 63 is formed into an annular plate shape that extends further outward (outer circumference side) in the radial direction of the valve body 6 than the head portion 61 .
  • the flange portion 63 is provided closer to the proximal end of the valve body 6 in the axial direction than the head portion 61 .
  • the exhaust flow path forming section 23 described above has a sheet wall surface 231.
  • a communication port 48 is formed in the sheet wall surface 231 .
  • the flange portion 63 has an annular seat surface 631 that extends along a direction that intersects (orthogonally in the illustrated example) the axis LB of the valve body 6 and faces the seat wall surface 231 .
  • the annular seat surface 631 is an end surface of the flange portion 63 on the distal end side in the axial direction.
  • the flange portion 63 can close the communication port 48 by bringing the annular seat surface 631 into contact with the seat wall surface 231 .
  • being able to close the communication port 48 means that communication between the merging flow path 46 and the exhaust flow path 47 via the communication port 48 can be released.
  • valve body 6 (6A) according to the comparative example has a shape that makes it difficult to simultaneously bring the head 61 into contact with the branch wall 221 and bring the flange 63 into contact with the seat wall surface 231. ing. As shown in FIG. 2, when the flange portion 63 is brought into contact with the sheet wall surface 231, a gap G is generated between the head end surface 611 of the head portion 61 and the branch wall 221. On the other hand, when the head 61 is brought into contact with the branch wall 221, a gap is created between the seat surface 631 of the collar portion 63 and the seat wall surface 231.
  • the turbine housing 2 includes the above-described turbine housing main body 20, a scroll connection valve 5 including the valve body 6 (6B to 6E), and the above-described valve rod 7. Equipped with As shown in FIG. 3, FIG. 4, FIG. 6, and FIG. and a seat portion 62 extending toward the outer circumferential side.
  • the head 61 can divide the two branch channels 44 and 45 by abutting against the branch wall 221 in the merging channel 46 .
  • the seat portion 62 can close the communication port 48 by coming into contact with the seat wall surface 231 described above.
  • the seat portion 62 contacts the seat wall surface 231 during the closing operation of the scroll connection valve 5, and then the head portion 61 contacts the branch wall 221. It has a deformation allowance DA for bringing it into contact.
  • the scroll connection valve 5 uses a driving force that drives the valve body 6 to apply a pressing force to the seat portion 62 in contact with the seat wall surface 231 toward the distal end side in the axial direction of the valve body 6 . Due to this pressing force, at least a portion of the seat portion 62 is elastically deformed within the range of the deformation allowance DA.
  • the seat portion 62 has the deformation allowance DA.
  • the turbine housing 2 can simultaneously seal between the two branch channels 44 and 45 in the merging channel 46 and sealing between the merging channel 46 and the exhaust channel 47.
  • the structure of the turbine housing 2 can be simplified by making the seat portion 62 have a deformation allowance DA.
  • FIG. 3 is a schematic sectional view of the turbine housing 2 according to the first embodiment taken along the axis LB of the scroll connection valve 5 when the scroll connection valve 5 is in a fully closed state (during a closing operation).
  • FIG. 4 is a schematic cross-sectional view of the turbine housing 2 according to the first embodiment taken along the axis LB of the scroll connection valve 5 when the scroll connection valve 5 is in a fully open state (during an opening operation).
  • the seat portion 62 of the valve body 6B includes the flange portion 63 and an annular elastic seal member 64.
  • the valve body 6B has a valve body shaft portion 60, a head portion 61, a collar portion 63, and an inclined portion 65 that are integrally formed.
  • the valve body shaft portion 60, the head portion 61, the collar portion 63, the elastic seal member 64, and the inclined portion 65 are made of a metal material.
  • the valve body shaft portion 60 extends along the direction in which the axis LB of the valve body 6 extends, and an end (one end) on the distal end side in the axial direction of the valve body 6 is connected to the head 61.
  • the valve body shaft portion 60 is connected to the valve rod 7 at its proximal end (other end) in the axial direction of the valve body 6 .
  • the inclined portion 65 is formed in a cylindrical shape that extends from the outer peripheral edge of the head 61 and is inclined such that the distance from the axis LB increases as the distance from the head 61 increases in the direction in which the axis LB of the valve body 6 extends. There is. In the embodiment shown in FIGS. 3 and 4, one end of the inclined portion 65 is connected to the outer circumferential edge of the head portion 61, and the other end of the inclined portion 65 is connected to the inner circumferential end of the collar portion 63.
  • the elastic seal member 64 is disposed between the seat surface 631 of the flange portion 63 and the seat wall surface 231, and has the above deformation amount DA. That is, the elastic seal member 64 is configured to be able to contract along the axial direction of the valve body 6 by the above-mentioned pressing force.
  • the elastic seal member 64 is attached to the flange portion 63 by fitting such as riveting, welding, adhesion, or the like.
  • the elastic seal member 64 contacts the seat wall surface 231 when the scroll connection valve 5 is in a fully closed state (during a closing operation), and is in contact with the seat wall surface 231 when the scroll connection valve 5 is in a fully open state (during an opening operation). They are becoming separated.
  • the elastic seal member 64 has the above deformation allowance DA.
  • the elastic seal member 64 By elastically deforming the elastic seal member 64 during the closing operation of the scroll connection valve 5, it is possible to simultaneously bring the seat portion 62 into contact with the seat wall surface 231 and bring the head 61 into contact with the branch wall 221. can. Thereby, the turbine housing 2 can simultaneously seal between the two branch channels 44 and 45 in the merging channel 46 and sealing between the merging channel 46 and the exhaust channel 47.
  • the elastic seal member 64 described above includes an annular first plate portion 641 extending along the radial direction of the valve body 6 and an annular first plate portion 641 extending along the radial direction of the valve body 6. It includes a second plate part 642 and an annular connecting part 643 that connects the outer peripheral end of the first plate part 641 and the outer peripheral end of the second plate part 642.
  • the elastic seal member 64 has a C-shaped cross section.
  • the first plate portion 641 is in contact with the annular seat surface 631.
  • the second plate portion 642 is provided so as to be able to come into contact with and separate from the seat wall surface 231, and comes into contact with the seat wall surface 231 when the valve body 6 is in the fully closed position.
  • FIG. 5 is a schematic cross-sectional view of the turbine housing 2 according to a modification of the first embodiment, taken along the axis LB of the scroll connection valve 5 when the scroll connection valve 5 is in a fully open state (during an opening operation).
  • the elastic seal member 64 was attached to the seat surface 631 of the collar portion 63, but it may be attached to the seat wall surface 231.
  • the turbine housing 2 includes the above-described turbine housing main body 20, the scroll connection valve 5 including the valve body 6C and the above-described valve rod 7, and an annular elastic seal member. 64A.
  • the valve body 6C has the above-mentioned valve body shaft portion 60, head portion 61, collar portion 63, and inclined portion 65, similarly to the valve body 6A according to the comparative example.
  • the elastic seal member 64A is disposed between the seat surface 631 of the flange portion 63 and the seat wall surface 231, and has the above deformation amount DA. That is, the elastic seal member 64A is configured to be able to contract along the axial direction of the valve body 6 by the above-mentioned pressing force.
  • the elastic seal member 64A is made of a metal material.
  • the elastic seal member 64A is attached to the sheet wall surface 231 by fitting such as riveting, welding, adhesion, or the like. The elastic seal member 64A can close the communication port 48 by coming into contact with the seat surface 631.
  • the elastic seal member 64A contacts the seat surface 631 when the scroll connection valve 5 is in a fully closed state (during a closing operation), and is in contact with the seat surface 631 when the scroll connection valve 5 is in a fully open state (during an opening operation). They are becoming separated.
  • the elastic seal member 64A has the deformation allowance DA.
  • the turbine housing 2 can simultaneously seal between the two branch channels 44 and 45 in the merging channel 46 and sealing between the merging channel 46 and the exhaust channel 47.
  • the structure of the turbine housing 2 can be simplified by making the elastic seal member 64A have a deformation allowance DA.
  • the above-described elastic seal member 64A includes an annular first plate portion 641A extending in the radial direction of the valve body 6 and a first plate portion 641A extending in the radial direction of the valve body 6, as shown in FIG. It includes an annular second plate portion 642A extending along the second plate portion 642A, and an annular connecting portion 643A connecting the outer circumferential end of the first plate portion 641A and the outer circumferential end of the second plate portion 642A.
  • the elastic seal member 64A has a C-shaped cross section.
  • the first plate portion 641A is provided so as to be able to come into contact with and separate from the annular seat surface 631, and comes into contact with the annular seat surface 631 when the valve body 6 is in the fully closed position.
  • the second plate portion 642A is in contact with the sheet wall surface 231.
  • attaching the elastic seal member 64 to the seat surface 631 of the flange portion 63 is easier than attaching the elastic seal member 64A to the seat wall surface 231. Furthermore, when the elastic seal member 64 is attached to the seat surface 631 of the flange portion 63, the area in contact with the turbine housing body 20 can be reduced compared to when the elastic seal member 64A is attached to the seat wall surface 231. Since the amount of heat input from the elastic seal member can be reduced, thermal damage to the elastic seal member can be suppressed.
  • FIG. 6 is a schematic cross-sectional view of the turbine housing 2 according to the second embodiment, taken along the axis LB of the scroll connection valve 5 when the scroll connection valve 5 is in a fully closed state.
  • the valve body 6 (6D) includes the above-mentioned head 61, the above-mentioned inclined part 65, and a seat part 62, as shown in FIG.
  • the seat portion 62 includes a flange portion 66 that extends outward in the radial direction of the valve body 6 from the head portion 61 and has an annular seat surface 661 that faces the seat wall surface 231 .
  • the inner peripheral end of the flange portion 66 is connected to the inclined portion 65, and has the above-mentioned deformation amount DA. That is, the flange portion 66 can be elastically bent so that the outer peripheral end thereof is closer to the proximal end in the axial direction of the valve body 6 than the inner peripheral end thereof by the above-mentioned pressing force.
  • the flange portion 66 may have a connecting portion P1 between the flange portion 66 and the inclined portion 65 as a base point of elastic deformation, or may have a connecting portion P2 between the inclined portion 65 and the head portion 61 as a base point of elastic deformation.
  • the thickness T1 of the flange 66 may be made thinner than the thickness T2 of the head. Further, the thickness T1 of the flange portion 66 may be made thinner than the thickness of the inclined portion 65.
  • the flange portion 66 has the above deformation allowance DA.
  • the turbine housing 2 can simultaneously seal between the two branch channels 44 and 45 in the merging channel 46 and sealing between the merging channel 46 and the exhaust channel 47.
  • the above-mentioned flange portion 66 has an annular convex portion 662 that protrudes toward the sheet wall surface 231.
  • the annular convex portion 662 protrudes from the annular seat surface 631 toward the distal end side in the axial direction of the valve body 6 .
  • the annular convex portion 662 of the flange portion 66 is arranged on the outside in the radial direction of the valve body 6, the bending moment acting on the portion where the annular convex portion 662 and the seat wall surface 231 come into contact is increased. can.
  • the sealing performance between the annular convex portion 662 and the sheet wall surface 231 can be improved.
  • the annular convex portion 662 is preferably provided at a position away from the axis LB in order to increase the bending moment.
  • the annular convex portion 662 is formed on the outer peripheral edge of the seat surface 631 of the collar portion 66 .
  • FIG. 7 is a schematic cross-sectional view of the turbine housing 2 according to the third embodiment, taken along the axis LB of the scroll connection valve 5 when the scroll connection valve 5 is in a fully closed state.
  • the valve body 6 (6E), as shown in FIG. ,including.
  • the seat portion 62 includes an annular plate member 67 that extends outward from the head 61 in the radial direction of the valve body 6 and has an annular seat surface 671 that faces the seat wall surface 231 .
  • the annular plate member 67 is configured separately from the valve body shaft portion 60, the head portion 61, and the inclined portion 65.
  • the annular plate member 67 has an inner peripheral end attached to the valve body shaft portion 60 .
  • the valve body shaft portion 60 includes a step surface 601 that makes the proximal end smaller in diameter than the distal end, and a stepped surface 601 formed on at least a portion of the outer peripheral surface on the proximal end side of the step surface 601.
  • a threaded portion 602 is formed.
  • the annular plate member 67 By sandwiching the inner circumferential end 673 of the annular plate member 67 between the step surface 601 and the nut member 68 having a threaded portion 681 that is screwed into the threaded portion 602, the annular plate member 67 is attached to the valve body shaft portion 60. is fixed.
  • the annular plate member 67 includes the annular inner peripheral end 673, an annular outer peripheral end 675 having a seat surface 671, and an annular connecting plate portion 674 connecting the outer peripheral end 675 and the inner peripheral end 673.
  • the connecting plate portion 674 is bent toward the proximal end with respect to the inner circumferential end 673, and is bent toward the distal end with respect to the outer circumferential end 675.
  • the annular plate member 67 has a deformation allowance DA. That is, the annular plate member 67 can be bent at least at the outer peripheral end 675 toward the proximal end by elastic deformation by the above pressing force.
  • the annular plate member 67 may have a connecting portion P3 between the outer peripheral end 675 and the connecting plate portion 674 as a base point for elastic deformation.
  • the annular plate member 67 has the above deformation allowance DA.
  • the turbine housing 2 can simultaneously seal between the two branch channels 44 and 45 in the merging channel 46 and sealing between the merging channel 46 and the exhaust channel 47.
  • the annular plate member 67 by making the annular plate member 67 separate from the head 61, the inclined part 65, and the valve body shaft part 60, the annular plate member 67 can be connected to the head 61, the inclined part 65, and the valve body shaft part 60. Compared to the case where the annular plate member 67 is integral with the valve body shaft portion 60, it becomes easier to form the deformation allowance DA in the annular plate member 67, and the deformation starting point P3 of the annular plate member 67 is set in the radial direction of the valve body 6. Can be placed inside.
  • the annular plate member 67 described above has an annular curved portion 672 that curves so as to protrude toward the sheet wall surface 231.
  • an annular curved portion 672 is formed at the outer circumferential edge of outer circumferential end 675 .
  • the curved portion 672 has a convex shape that projects toward the distal end side in the axial direction of the valve body 6.
  • the annular curved portion 672 of the annular plate member 67 by arranging the annular curved portion 672 of the annular plate member 67 on the outside in the radial direction of the valve body 6, the bending that acts on the portion where the annular curved portion 672 and the seat wall surface 231 come into contact is caused.
  • the moment can be increased.
  • the sealing performance between the annular curved portion 672 and the sheet wall surface 231 can be improved.
  • the turbine 1 includes the above-mentioned turbine housing 2 and the above-mentioned turbine wheel 3.
  • a supercharger 10 according to some embodiments includes the turbine 1 described above and the compressor 13 described above, as shown in FIG.
  • the turbine housing 2 can simultaneously seal between the two branch channels 44 and 45 in the merging channel 46 and sealing between the merging channel 46 and the exhaust channel 47. becomes. Thereby, leakage loss of exhaust gas in the turbine 1 can be suppressed, so that the efficiency of the turbine 1 and the supercharger 10 can be improved.
  • expressions expressing shapes such as a square shape or a cylindrical shape do not only mean shapes such as a square shape or a cylindrical shape in a strict geometric sense, but also within the range where the same effect can be obtained. , shall also represent shapes including uneven parts, chamfered parts, etc.
  • the expressions "comprising,””including,” or “having" one component are not exclusive expressions that exclude the presence of other components.
  • turbine housing 2 of the present disclosure is applicable to a double scroll turbine or a twin scroll turbine.
  • a turbine housing (2) includes: A turbine housing (2) in which two scroll passages (41, 42) are formed, a scroll passage forming part (21) forming the two scroll passages (41, 42); A first branch channel (44) branching from one scroll channel (41) of the two scroll channels (41, 42), and a first branch channel (44) branching from one of the two scroll channels (41, 42); A second branch passage (45) branches from the scroll passage (42), and the first branch passage (44) and the second branch passage (45) merge, and the turbine wheel (3) A connection flow path forming part (22) forming a connection flow path (43) including an exhaust flow path (47) through which the passed exhaust gas flows and a merging flow path (46) communicating through a communication port (48).
  • a connecting flow path forming part (22) having a branch wall (221) that divides the first branch flow path (44) and the second branch flow path (45); a turbine housing body (20) including; a head (61) capable of separating the two branch channels (44, 45) by coming into contact with the branch wall (221) in the merging channel (46); A seat portion (62) extending toward the outer circumferential side of the head portion (61) and capable of closing the communication port (48) by abutting against the seat wall surface (231) of the turbine housing (2).
  • a valve body (6) having at least a seat portion (62); a scroll connection valve (5) including;
  • the seat portion (62) is configured to contact the branch wall (221) with the head portion after the seat portion (62) comes into contact with the seat wall surface (231) during the closing operation of the scroll connection valve (5). It has a deformation allowance (DA) for bringing (61) into contact.
  • DA deformation allowance
  • the seat portion (62) has a deformation allowance (DA).
  • DA deformation amount
  • the turbine housing (2) seals between the two branch channels (44, 45) in the merging channel (46) and seals between the merging channel (46) and the exhaust channel (47). It becomes possible to perform both stops at the same time.
  • leakage loss of exhaust gas in the turbine (1) can be reduced. Since this can be suppressed, the efficiency of the turbine (1) can be improved.
  • the turbine housing (2) can have a simple structure because the seat portion (62) has a deformation allowance (DA).
  • the seat portion (62) is A flange (63) having an annular seat surface (631) extending radially outward of the valve body (6) from the head (61) and facing the seat wall surface (231) with a gap therebetween. )and, An elastic seal member (64) having the deformation allowance (DA) attached to the flange (63), wherein the sheet surface (631) of the flange (63) and the sheet wall surface (231) an annular elastic seal member (64) disposed therebetween.
  • the elastic seal member (64) has the above deformation allowance (DA).
  • DA deformation allowance
  • the elastic seal member (64) is a first plate portion (641) extending along the radial direction of the valve body (6) and abutting the annular seat surface (631);
  • a second plate portion (642) extending along the radial direction of the valve body (6) is provided so as to be able to come into contact with and separate from the seat wall surface (231), and is provided so that the position of the valve body (6) is completely a second plate portion (642) that abuts the seat wall surface (231) when in the closed position;
  • a connecting portion (643) connecting the outer peripheral end of the first plate portion (641) and the outer peripheral end of the second plate portion (642) is included.
  • the elastic seal member (64) has the inner peripheral end of the first plate part (641) and the second plate part (642). ) A pressing force acts in the direction in which the inner peripheral end of the sheet spreads (separates), and this pressing force causes the elastic sealing member (64) to effectively seal between the seat surface (631) and the seat wall surface (231). sealed.
  • the valve body (6) is An inclined portion (61) that extends from the outer peripheral edge of the head (61) and slopes so that the distance from the axis increases as the distance from the head (61) increases in the direction in which the axis of the valve body (6) extends. 65) further comprising: The seat portion (62) extends outward in the radial direction of the valve body (6) from the head (61), and has an annular seat surface ( 661), the inner peripheral end of which is connected to the inclined portion (65); The flange (66) has the deformation allowance (DA).
  • the flange portion (66) has the above deformation allowance (DA).
  • the seat part (62) is brought into contact with the seat wall surface (231) and the head part is attached to the branch wall (221). (61) can be brought into contact at the same time.
  • the turbine housing (2) seals between the two branch channels (44, 45) in the merging channel (46) and seals between the merging channel (46) and the exhaust channel (47). It becomes possible to perform both stops at the same time.
  • the flange portion (66) has an annular convex portion (662) that protrudes toward the sheet wall surface (231).
  • the valve body (6) further includes a valve body shaft (60) that extends along the axial direction of the valve body (6) and has one end connected to the head (61),
  • the seat portion (62) extends outward in the radial direction of the valve body (6) from the head (62), and has an annular seat surface ( 671), the annular plate member (67) having an inner peripheral end attached to the valve body shaft (60),
  • the annular plate member (67) has the deformation allowance (DA).
  • the annular plate member (67) has the above deformation allowance (DA).
  • the seat portion (62) is brought into contact with the seat wall surface (231) and the head is brought into contact with the branch wall (221).
  • the turbine housing (2) seals between the two branch channels (44, 45) in the merging channel (46) and seals between the merging channel (46) and the exhaust channel (47). It becomes possible to perform both stops at the same time.
  • the annular plate member (67) is made separate from the head (62), the inclined portion (65), and the valve shaft portion (60). Forming a deformation allowance (DA) in the annular plate member (67) compared to the case where the annular plate member (67) is integral with the head (62), the inclined part (65), and the valve shaft part (60).
  • the starting point of deformation of the annular plate member (67) can be placed inside the valve body (6) in the radial direction. By arranging the deformation starting point of the annular plate member (67) inside the valve body (6) in the radial direction, it is possible to increase the bending moment that acts on the portion where the seat portion (62) and the seat wall surface (231) contact. . By increasing the bending moment, the sealing performance between the seat portion (62) and the seat wall surface (231) can be improved.
  • the annular plate member (67) has an annular curved portion (672) that curves to protrude toward the sheet wall surface (231).
  • the turbine housing (2) includes: A turbine housing (2) in which two scroll passages (41, 42) are formed, a scroll passage forming part (21) forming the two scroll passages (41, 42); A first branch channel (44) branching from one scroll channel (41) of the two scroll channels (41, 42), and a first branch channel (44) branching from one of the two scroll channels (41, 42); A second branch passage (45) branches from the scroll passage (42), and the first branch passage (44) and the second branch passage (45) merge, and the turbine wheel (3) A connection flow path forming part (22) forming a connection flow path (43) including an exhaust flow path (47) through which the passed exhaust gas flows and a merging flow path (46) communicating through a communication port (48).
  • a connecting flow path forming part (22) having a branch wall (221) that divides the first branch flow path (44) and the second branch flow path (45); a turbine housing body (20) including; a head (61) capable of separating the two branch channels (44, 45) by coming into contact with the branch wall (221) in the merging channel (46); a flange (63) having an annular seat surface (631) extending toward the outer periphery of the head (61) and facing the seat wall surface (231) of the turbine housing (2) with a gap therebetween; A valve body (6) having at least a scroll connection valve (5) comprising; An annular elastic seal member (64A) disposed between the seat surface (631) and the seat wall surface (231) and attached to the seat wall surface (231), the elastic seal member (64A) being in contact with the seat surface (631).
  • an elastic sealing member (64A) that can close the communication port (48) by contacting the elastic sealing member (64A);
  • the elastic seal member (64A) contacts the branch wall (221) after the elastic seal member (64A) contacts the seat surface (631) during the closing operation of the scroll connection valve (5). It has a deformation allowance (DA) for bringing the head (61) into contact.
  • the elastic seal member (64A) has a deformation allowance (DA).
  • DA deformation amount
  • the head (61) can be brought into contact with the branch wall (221).
  • the turbine housing (2) seals between the two branch channels (44, 45) in the merging channel (46) and seals between the merging channel (46) and the exhaust channel (47). It becomes possible to perform both stops at the same time.
  • leakage loss of exhaust gas in the turbine (1) can be reduced. Since this can be suppressed, the efficiency of the turbine (1) can be improved.
  • the structure of the turbine housing (2) can be simplified because the elastic seal member (64A) has a deformation allowance (DA).
  • the turbine (1) includes: The turbine housing (2) according to any one of 1) to 8) above; a turbine wheel (3) rotatably housed in the turbine housing.
  • the turbine housing (2) seals between the two branch channels (44, 45) in the merging channel (46) and the merging channel (46) and the exhaust channel (47). ) can be sealed at the same time. Thereby, leakage loss of exhaust gas in the turbine (1) can be suppressed, so that the efficiency of the turbine (1) can be improved.
  • a supercharger (10) according to at least one embodiment of the present disclosure, A turbine (1) driven by exhaust gas discharged from an engine (12), the turbine (1) described in 9) above; A compressor (13) is coaxially connected to the turbine (1) and supplies compressed air to the engine (12) as it rotates.
  • the turbine housing (2) seals between the two branch channels (44, 45) in the merging channel (46) and the merging channel (46) and the exhaust channel (47). ) can be sealed at the same time. Thereby, leakage loss of exhaust gas in the turbine (1) can be suppressed, so that the efficiency of the supercharger (10) can be improved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)

Abstract

La présente invention concerne un carter de turbine comprenant au moins une soupape de raccordement à spirale comprenant un obturateur de soupape comprenant au moins une partie tête et une partie support, la partie tête permettant de diviser deux canaux de ramification, chacun se ramifiant respectivement à partir de deux canaux de spirale, en venant en butée contre une paroi de ramification divisant les deux canaux de ramification individuellement dans un canal commun dans lequel les deux canaux de ramification se rejoignent et qui communique, par le biais d'un orifice de communication, avec un canal d'échappement dans lequel un gaz d'échappement qui a traversé une roue de turbine circule, la partie support s'étendant de manière périphérique vers l'extérieur au-delà de la partie tête et pouvant fermer l'orifice de communication en venant en butée contre une surface de paroi de support du carter de turbine, la partie support présentant une tolérance de déformation pour permettre à la partie tête de venir en butée contre la paroi de ramification après que la partie support vient en butée contre la surface de paroi de support lors de l'opération de fermeture de la soupape de raccordement à spirale.
PCT/JP2022/030900 2022-08-15 2022-08-15 Carter de turbine, turbine et compresseur de suralimentation WO2024038495A1 (fr)

Priority Applications (1)

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PCT/JP2022/030900 WO2024038495A1 (fr) 2022-08-15 2022-08-15 Carter de turbine, turbine et compresseur de suralimentation

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2022/030900 WO2024038495A1 (fr) 2022-08-15 2022-08-15 Carter de turbine, turbine et compresseur de suralimentation

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107448279A (zh) * 2016-05-30 2017-12-08 霍尼韦尔国际公司 带有柔性金属片密封构件的涡轮增压器废气门提升阀
JP2018537615A (ja) * 2015-12-21 2018-12-20 アイ・エイチ・アイ チャージング システムズ インターナショナル ゲーエムベーハー 排気タービン式過給機の排気流通部及び排気タービン式過給機の作動方法

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018537615A (ja) * 2015-12-21 2018-12-20 アイ・エイチ・アイ チャージング システムズ インターナショナル ゲーエムベーハー 排気タービン式過給機の排気流通部及び排気タービン式過給機の作動方法
CN107448279A (zh) * 2016-05-30 2017-12-08 霍尼韦尔国际公司 带有柔性金属片密封构件的涡轮增压器废气门提升阀

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