WO2021152742A1 - Dispositif compresseur et turbocompresseur de suralimentation - Google Patents

Dispositif compresseur et turbocompresseur de suralimentation Download PDF

Info

Publication number
WO2021152742A1
WO2021152742A1 PCT/JP2020/003235 JP2020003235W WO2021152742A1 WO 2021152742 A1 WO2021152742 A1 WO 2021152742A1 JP 2020003235 W JP2020003235 W JP 2020003235W WO 2021152742 A1 WO2021152742 A1 WO 2021152742A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
hole
tip
compressor
compressor wheel
Prior art date
Application number
PCT/JP2020/003235
Other languages
English (en)
Japanese (ja)
Inventor
浩範 本田
水田　徹
敬信 吉澤
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.)
Filing date
Publication date
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/JP2020/003235 priority Critical patent/WO2021152742A1/fr
Publication of WO2021152742A1 publication Critical patent/WO2021152742A1/fr

Links

Images

Classifications

    • 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
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00

Definitions

  • the present disclosure relates to a compressor device and a turbocharger equipped with the compressor device.
  • the compressor device incorporated in the turbocharger has a so-called bore-through structure compressor device in which a through hole is formed in the central axis of the compressor wheel and a shaft is inserted into the through hole, and an opening is provided in the back surface of the compressor wheel.
  • a compressor device having a so-called boreless structure in which an insertion hole at the bottom is formed and a shaft is inserted into the insertion hole.
  • a so-called boreless structure may be adopted in a compressor incorporated in a relatively large turbocharger attached to a commercial vehicle or an industrial engine. It has been confirmed that the boreless structure has advantages such as reduction of stress concentration generated in the area around the insertion hole.
  • Patent Document 1 discloses a turbocharger that employs a bore-through structure and a boreless structure for a compressor.
  • the axis of the shaft tends to deviate from the axis of the insertion hole during assembly, and the axis of the shaft is more likely to be displaced with respect to the axis of the insertion hole.
  • the inclination (deviation angle) of the shaft axis tends to increase. If the deviation angle becomes large, an unbalanced force is generated during the rotation of the shaft, which may impair the stable operation of the device such as vibration.
  • measures such as strict control of tolerances can be considered, but this measure requires high-precision processing and assembly, which leads to an increase in cost. This will be described with reference to FIGS. 5 and 6.
  • FIG. 5 is a vertical cross-sectional view showing a compressor wheel (including a hub portion) having a conventional boreless structure
  • FIG. 6 is a vertical cross-sectional view showing a compressor wheel (including a hub portion) having a conventional bore-through structure. It is a figure.
  • a bottomed insertion hole 026 having an opening in the back surface 023 is formed along the axis 022a, and the tip of the shaft 012 is inserted into the insertion hole 026 to insert the insertion hole. It is fixed at 026.
  • FIG. 5 is a vertical cross-sectional view showing a compressor wheel (including a hub portion) having a conventional boreless structure
  • FIG. 6 is a vertical cross-sectional view showing a compressor wheel (including a hub portion) having a conventional bore-through structure. It is a figure.
  • a bottomed insertion hole 026 having an opening in the back surface 023 is formed along the axis 022a, and the tip of the shaft 012 is inserted into
  • the compressor wheel 022B having a bore-through structure is formed with a through hole 027 penetrating the compressor wheel 022B in the axial direction, that is, from the back surface 023 to the tip side, and the tip portion of the shaft 012 is formed in the through hole 027. Is inserted.
  • the length of the fitting portion between the bore-through structure compressor wheel 022B and the shaft 012 is longer than the length of the fitting portion between the boreless structure compressor wheel 022A and the shaft 012.
  • the longer the length of the fitting portion the smaller the inclination angle (deviation angle) of the axis 012a of the shaft 012 with respect to the axis 022a of the compressor wheel 022A or 022B. Therefore, since the deviation angle ⁇ 1 in the case of the boreless structure is larger than the deviation angle ⁇ 2 in the case of the bore-through structure, an unbalanced force is generated during the rotation of the shaft 012, resulting in lack of stability.
  • the present disclosure has been made in view of the above-mentioned problems, and suppresses the misalignment between the shaft and the compressor wheel in a compressor device having a boreless structure without requiring high-precision machining or assembly.
  • the purpose is.
  • the compressor device is a compressor device including a compressor wheel and a shaft inserted into a bottomed insertion hole having an opening on the back surface of the compressor wheel.
  • the hole is a first hole portion having a first diameter, and has a first hole portion extending from the back surface toward the tip end side of the compressor wheel and a second hole portion having a second diameter smaller than the first diameter.
  • a second hole portion including a second hole portion extending from the tip end of the first hole portion toward the tip end side of the compressor wheel, and the shaft is fitted into the first hole portion. Includes a first shaft portion having one fitting portion and a second shaft portion having a second fitting portion that fits into the second hole portion.
  • the turbocharger according to the present disclosure includes the above-mentioned compressor device provided on one end side of the shaft and a turbine device including a turbine wheel fixed to the other end side of the shaft and rotated by exhaust gas.
  • the compressor device and turbocharger in a compressor device having a boreless structure, it is possible to suppress an axial misalignment between the shaft and the compressor wheel without requiring high-precision machining or assembly. .. As a result, it is possible to avoid an unbalanced force generated on the rotating shaft and vibration or the like, and stable operation of the device becomes possible.
  • FIG. 1 shows a compressor apparatus. It is a partially enlarged vertical sectional view of the compressor wheel which concerns on one Embodiment. It is a partially enlarged vertical sectional view of the compressor wheel which concerns on one Embodiment. It is a partially enlarged vertical sectional view of the compressor wheel which concerns on one Embodiment. It is a partially enlarged vertical sectional view of the compressor wheel which concerns on one Embodiment. It is a partially enlarged vertical sectional view which shows the compressor wheel of the conventional boreless structure. It is a partially enlarged vertical sectional view which shows the compressor wheel of the conventional bore-through structure.
  • expressions such as “same”, “equal”, and “homogeneous” that indicate that things are in the same state not only represent exactly the same state, but also have tolerances or differences to the extent that the same function can be obtained. It shall also represent the existing state.
  • an expression representing a shape such as a quadrangular shape or a cylindrical shape not only represents a shape such as a quadrangular shape or a cylindrical shape in a geometrically strict sense, but also an uneven portion or chamfering within a range in which the same effect can be obtained.
  • the shape including the part and the like shall also be represented.
  • the expressions “equipped”, “equipped”, “equipped”, “included”, or “have” one component are not exclusive expressions that exclude the existence of other components.
  • FIG. 1 is a vertical cross-sectional view showing a turbocharger 10 including a compressor device 20 having a boreless structure according to an embodiment
  • FIG. 2 is a partially enlarged view of FIG. 1 showing the compressor device 20.
  • the turbocharger 10 includes a compressor device 20 at one end of the shaft 12, and a turbine device 30 at the other end of the shaft 12 opposite to the compressor device 20.
  • the compressor device 20 includes a compressor wheel 22 fixed to one end of a shaft 12 and a plurality of compressor blades 24 provided on the outer periphery of the compressor wheel 22 in the circumferential direction.
  • An opening is provided in the back surface 23 of the compressor wheel 22, and a bottomed insertion hole 26 is formed on the axis 12a of the compressor wheel 22 along the axis, and one end of the shaft 12 is inserted and fixed in the insertion hole 26. ..
  • the turbine device 30 includes a turbine wheel 32 attached to the other end of the shaft 12 by means such as welding, and a plurality of turbine blades 34 provided in the circumferential direction on the outer periphery of the turbine wheel 32.
  • the shaft 12 is supported by a journal bearing (not shown) at the center in the direction along the axis 12a.
  • the compressor device 20 is housed inside a compressor housing (not shown)
  • the axial central portion of the shaft 12 is housed inside a bearing housing (not shown)
  • the turbine device 30 is housed in a turbine housing (not shown). It is housed inside (not shown).
  • a thrust collar 16 is provided around the shaft 12 near the compressor device 20.
  • a thrust bearing (not shown) that supports the shaft 12 with respect to an axial thrust load applied to the shaft 12 is provided, and the thrust collar 16 supports the thrust bearing.
  • 3A, 3B and 4 are vertical cross-sectional views of the vicinity of the insertion hole 26 of the compressor wheel 22 (including the hub portion 50 described later) according to some embodiments.
  • the insertion hole 26 has two holes 26a and 26b having different diameters.
  • the hole portion 26a first hole portion 26a
  • the hole portion 26b second hole portion 26b
  • the diameter of the cross section of the second hole portion 26b is configured to be smaller than the diameter of the cross section of the first hole portion 26a.
  • the tip of the shaft 12 inserted into the insertion hole 26 has a first shaft portion 40 and a second shaft portion 42.
  • the first shaft portion 40 has a first fitting portion 44 (44a, 44b) that fits into the first hole portion 26a
  • the second shaft portion 42 has a second fitting that fits into the second hole portion 26b. It has a joint 46 (46a, 46b). That is, the diameter of the cross section of the first fitting portion 44 (first diameter) is larger than the diameter of the cross section of the second fitting portion 46 (second diameter).
  • the first shaft portion 40 is fitted into the first hole portion 26a by the first fitting portion 44, and the second shaft portion is formed. 42 is fitted into the second hole portion 26b by the second fitting portion 46.
  • the tip end portion of the shaft 12 inserted into the insertion hole 26 is supported at two places, the first fitting portion 44 and the second fitting portion 46.
  • the deviation angle ⁇ 1 of the shaft 12 generated by the axial deviation between the insertion hole 26 and the shaft 12 is fitted by one from the first fitting portion 44 to the second fitting portion 46. It can be kept as small as when the portion is formed. This eliminates the imbalance during rotation of the shaft 12 and enables stable operation.
  • the shaft 12 is inserted into the insertion hole 26 and the second fitting portion 46 of the second shaft portion 42 is the first hole.
  • the inner peripheral surface of the first hole portion 26a and the second fitting portion 46 do not come into contact with each other. Therefore, the process of fitting the second fitting portion 46 into the second hole portion 26b becomes easy.
  • the insertion hole 26 and the tip of the shaft 12 are fitted only by the first fitting portion 44 and the second fitting portion 46, and the assembly tolerance can be set loosely for the other parts, so that high-precision machining is performed. Or assembly is not required. Therefore, the manufacturing cost of the compressor wheel 22 and the shaft 12 can be suppressed.
  • the insertion hole 26 is formed linearly along the axis of the compressor wheel 22, and the first shaft portion 40 and the second shaft portion 42 extend linearly along the axial direction of the insertion hole 26.
  • the insertion hole 26, the first shaft portion 40, and the second shaft portion 42 have a circular cross section. Further, the cross sections of the first shaft portion 40 and the second shaft portion 42 are arranged concentrically with the same center of the cross section.
  • the difference in diameter between the first hole 26a and the second hole 26b should be greater than or equal to the tolerance and less. That is, the smaller the diameter of the second hole portion 26b, the more difficult the assembly and the lower the strength.
  • the contact area between the first fitting portion 44 (44a) and the first hole portion 26a, and the contact area between the second fitting portion 46 (46a) and the second hole portion 26b. Can minimize the deterioration of assembling property by making it as small as possible.
  • a hub portion 50 extending toward the center of the shaft 12 along the axial direction is formed at the center of the back surface 23 of the compressor wheel 22, and the central portion of the hub portion 50 is formed.
  • An insertion hole 26 is formed in the hole 26.
  • L 0 indicates the length of the fitting portion between the hub portion 50 and the tip end portion of the shaft 12 in the insertion hole 26.
  • the hub portion 50 is rotatably supported by a support member (not shown) in contact with the outer peripheral surface of the hub portion 50.
  • an inclined planar chamfer 56 is formed on the outer periphery of the tip of the first shaft portion 40, whereby the first hole portion 26a of the first shaft portion 40 is formed. Easy positioning when inserting into. Further, a chamfer 58 having a curved surface at the outer peripheral end of the tip end portion of the second shaft portion 42 is formed, which facilitates positioning of the second shaft portion 42 at the time of insertion into the second hole portion 26b.
  • the first hole portion 26a includes a female screw portion 62 extending from the back surface 23 of the compressor wheel 22 toward the tip end side of the compressor wheel 22 and a female screw portion 62. It has a non-threaded portion 64 extending from the tip of the threaded portion 62 toward the tip end side of the compressor wheel 22.
  • the first shaft portion 40 has a male screw portion 66 that can be screwed into the female screw portion 62, and the first fitting portion 44 is configured to fit at least a part of the non-threaded portion 64. ing.
  • the first shaft portion 40 and the second shaft portion 42 are supported by the first fitting portion 44 and the second fitting portion 46, and the axial misalignment between the insertion hole 26 and the shaft 12 is provided.
  • the female screw portion 62 and the male screw portion 66 are screwed together to be fixed to the compressor wheel 22.
  • the first fitting portion 44 (44a, 44b) of the tip and the second fitting portion 46 (46a, 46b) the length L 1 between the tips of the non-threaded portion 64 tip and non It is configured to be longer than the length L 2 between the threaded portion 64 and the rear end (L 2 ⁇ L 1 ).
  • the tip of the second fitting portion 46 is inserted into the second hole portion 26b and the second shaft portion with respect to the second hole portion 26b. Axial alignment of 42 is performed.
  • the axis alignment between the second hole portion 26b and the second shaft portion 42 is performed before the axis alignment between the first hole portion 26a and the first shaft portion 40, so that the insertion after assembly is performed. It is possible to suppress the axial deviation of the shaft tip with respect to the hole 26.
  • the first fitting portion 44 (44b) and the second fitting portion 46 (46b) are gathered at substantially one point in the axial direction of the compressor wheel 22. Therefore, the front end and the rear end are almost at the same position. Also in this embodiment, when the length L 1 and the length L 2 are set (L 2 ⁇ L 1 ), the same effects as those in the embodiments shown in FIGS. 3A and 3B can be obtained.
  • an inclined surface 60 inclined with respect to the axial direction is formed at the tip of the non-threaded portion 64.
  • the positioning of the second shaft portion 42 with respect to the second hole portion 26b and the insertion of the first shaft portion 40 into the first hole portion 26a become easy.
  • stress is generated in the vicinity of the axis of the compressor wheel 22 in the region C along the axis of the compressor wheel 22.
  • the maximum stress is generated at the position where the compressor wheel 22 has the maximum diameter in the axial direction. Therefore, it is desirable that the insertion hole 26 does not extend to the position where it has the maximum diameter in the axial direction.
  • the axial length b of the inclined surface 60 is prevented from being larger than the radial length a (b ⁇ a).
  • the insertion hole 26 is formed in the stress generation region C, so that it is possible to avoid a decrease in the strength of the compressor wheel 22 in the stress generation region C.
  • the inclination angle ⁇ 3 of the inclined surface 60 with respect to the cross section perpendicular to the axial direction of the shaft 12 is set to 0 ° ⁇ ⁇ 3 ⁇ 45 °.
  • b ⁇ a can be set, and the insertion hole 26 can be prevented from extending to the position where the maximum diameter is obtained in the axial direction of the compressor wheel 22.
  • the length between the portion 62 and the rear end in the axial direction is larger than the length L 4 (L 4 ⁇ L 3 ).
  • the first fitting portion 44 (44b) and the second fitting portion 46 (46b) are gathered at substantially one point in the axial direction of the compressor wheel 22. Therefore, the front end and the rear end are almost at the same position. Also in this embodiment, when the length L 3 and the length L 4 are set (L 4 ⁇ L 3 ), the same effects as those in the embodiments shown in FIGS. 3A and 3B can be obtained.
  • At least one of the first fitting portion 44 (44b) or the second fitting portion 46 (46b) is formed in a curved surface shape that is convex outward in the radial direction. ing. According to this embodiment, at least one of the contact area between the first fitting portion 44 (44b) and the first hole portion 26a or the contact area between the second fitting portion 46 (46b) and the second hole portion 26b. Since it can be made smaller, the friction between the first fitting portion 44 (44b) and the first hole portion 26a or the friction between the second fitting portion 46 (46a, 46b) and the second hole portion 26b can be reduced. .. Therefore, the shaft 12 can be easily inserted into the insertion hole 26.
  • the outer edge of the axial cross section of the first fitting portion 44 (44b) or the second fitting portion 46 (46b) is configured to form an arc or an ellipse.
  • the first fitting portion 44 (44b) or the second fitting portion 46 (46b) can be brought into contact with the first hole portion 26a or the second hole portion 26b in a state close to point contact, so that friction between the two can be caused. Can be reduced.
  • the outer edge of the axial cross section of the first fitting portion 44 (44b) having at least a large cross-sectional diameter is configured to form an arc or an ellipse.
  • the distance between the first fitting portion 44 (44b) and the second fitting portion 46 (46b) is increased as much as possible. As a result, the deviation angle ⁇ 1 of the axis 12a at the tip of the shaft 12 with respect to the axis of the insertion hole 26 can be suppressed.
  • the turbocharger 10 is provided with a compressor device 20 according to each of the above embodiments at one end of a shaft 12, and exhaust gas discharged from an internal combustion engine at the other end of the shaft 12.
  • the compressor wheel 22 is rotated, and the pressurized air supply is supplied to the internal combustion engine by the rotation of the compressor wheel 22. do.
  • the turbocharger 10 includes the compressor device 20 according to each of the above embodiments, when the shaft 12 and the compressor wheel 22 are assembled, the shaft 12 is first fitted into the insertion hole 26 formed in the compressor wheel 22. It is supported by the joint portion 44 (44a, 44b) and the second fitting portion 46 (46a, 46b).
  • the deviation angle ⁇ 1 of the shaft 12 caused by the axial deviation between the insertion hole 26 and the shaft 12 can be suppressed to a small value, and the imbalance during rotation of the shaft 12 can be eliminated to enable stable operation.
  • the first diameter of the first shaft portion 40 larger than the second diameter of the second shaft portion 42, it is easy to align the axes of the second shaft portion 42 and the second hole portion 26b to be inserted first.
  • the strength of the tip of the shaft inserted into the insertion hole 26 can be increased.
  • the assembly tolerance can be set loosely except for the first fitting portion 44 and the second fitting portion 46, assembling can be facilitated and the manufacturing cost can be suppressed.
  • the compressor device (20) includes a compressor wheel (22) and a shaft (26) inserted into a bottomed insertion hole (26) having an opening on the back surface (23) of the compressor wheel (22). 12), the insertion hole is a first hole portion having a first diameter, and the first hole portion extending from the back surface toward the tip end side of the compressor wheel (12). 26a) and a second hole portion (26b) having a second diameter smaller than the first diameter portion and extending from the tip end of the first hole portion toward the tip end side of the compressor wheel.
  • the shaft includes the first shaft portion (40) having the first fitting portion (44 (44a, 44b)) to be fitted into the first hole portion, and the shaft is fitted into the second hole portion. Includes a second shaft portion (42) having a matching second fitting portion (46 (46a, 46b)).
  • the shaft has a first shaft portion having a first fitting portion to be fitted into the first hole portion and a second fitting portion to be fitted into the second hole portion. Since it has a biaxial portion, it is supported by the first fitting portion and the second fitting portion with respect to the insertion hole. Therefore, the deviation angle ( ⁇ 1) of the shaft generated by the axial deviation between the insertion hole and the shaft is equivalent to the case where one fitting portion is formed from the first fitting portion to the second fitting portion. Can be kept small. This eliminates the imbalance during rotation of the shaft and enables stable operation. Further, since the diameter of the first hole is larger than the diameter of the second hole, when the shaft is inserted into the insertion hole and the second fitting portion of the second shaft portion passes through the first hole.
  • the inner peripheral surface of the first hole portion and the second fitting portion do not come into contact with each other. Therefore, the process of fitting the second fitting portion into the second hole portion becomes easy. Furthermore, the insertion hole and the tip of the shaft are fitted only at the first fitting part and the second fitting part, and the assembly tolerance can be set loosely for the other parts, so high-precision machining and assembly are required. Do not. Therefore, the manufacturing cost of the compressor wheel and the shaft can be suppressed.
  • the compressor device is the compressor device according to 1), and the first hole portion is a female extending from the back surface of the compressor wheel toward the tip end side of the compressor wheel.
  • the first shaft portion includes a threaded portion (62) and a non-threaded portion (64) extending from the tip of the female threaded portion toward the tip end side of the compressor wheel, and the first shaft portion is attached to the female threaded portion. It has a screwable male screw portion (66), and the first fitting portion is configured to be fitted with a part of the non-threaded portion.
  • the first shaft portion and the second shaft portion are supported by the first fitting portion and the second fitting portion, and the first hole is suppressed while suppressing the axial deviation between the insertion hole and the shaft.
  • the female screw portion and the male screw portion are screwed together to be fixed to the compressor wheel.
  • the compressor device according to still another aspect is the compressor device according to 2), and the length L 1 between the tip of the first fitting portion and the tip of the second fitting portion is It is configured to be longer than the length L 2 between the tip of the non-threaded portion and the rear end of the non-threaded portion.
  • the tip of the second fitting portion is inserted into the second hole portion before the first fitting portion is fitted into the first hole portion.
  • the axis of the second shaft portion is aligned with the second hole portion. In this way, the axis alignment between the second hole portion and the second shaft portion is performed before the axis alignment between the first hole portion and the first shaft portion, so that the tip of the shaft with respect to the insertion hole after assembly is performed. It is possible to suppress the misalignment of the axis of the part.
  • the compressor device according to still another aspect is the compressor device according to 2) or 3), wherein the length L 3 between the tip of the first fitting portion and the tip of the male screw portion is , and it is configured to be larger than the length L 4 between the rear end of the tip and the female screw portion of the female threaded portion.
  • the compressor device is the compressor device according to any one of 1) to 4), and at least one of the first fitting portion or the second fitting portion is radially outside. It is formed in a curved shape that is convex toward.
  • At least one of the contact area between the first fitting portion and the first hole portion or the contact area between the second fitting portion and the second hole portion can be reduced, so that the insertion hole and the tip of the shaft can be reduced. Friction between the parts can be reduced. As a result, the shaft can be easily inserted into the insertion hole.
  • the turbocharger (10) according to one embodiment is fixed to the compressor device according to any one of 1) to 5) provided on one end side of the shaft and the other end side of the shaft, and is driven by exhaust gas. It comprises a turbine apparatus (30) including a rotating turbine wheel.
  • the shaft and the compressor wheel when the shaft and the compressor wheel are assembled, the shaft is supported by the first fitting portion and the second fitting portion with respect to the insertion hole formed in the compressor wheel.
  • the deviation angle of the shaft caused by the misalignment between the insertion hole and the shaft can be suppressed to the same level as when one fitting portion is formed from the first fitting portion to the second fitting portion. can.
  • the diameter of the first hole portion is larger than the diameter of the second hole portion, when the shaft is inserted into the insertion hole and the second fitting portion of the second shaft portion passes through the first hole portion. Since the inner peripheral surface of the first hole portion and the second fitting portion do not come into contact with each other, the process of fitting the second fitting portion into the second hole portion becomes easy.
  • the insertion hole and the tip of the shaft are fitted only at the first fitting part and the second fitting part, and the assembly tolerance can be set loosely for the other parts, so high-precision machining and assembly are required. Do not.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

La présente invention concerne un dispositif compresseur qui, selon un mode de réalisation, est un dispositif compresseur pourvu d'une roue de compresseur et d'un arbre qui est inséré dans un trou d'insertion d'extrémité fermée qui présente une ouverture dans une surface arrière de la roue de compresseur, le trou d'insertion comprenant une première section trou, ayant un premier diamètre, qui s'étend à partir de la surface arrière de la roue de compresseur vers l'extrémité distale de la roue de compresseur et une seconde section trou, ayant un second diamètre qui est inférieur au premier diamètre, qui s'étend de l'extrémité distale de la première section trou vers l'extrémité distale de la roue de compresseur ; et l'arbre comprenant une première section arbre, comprenant une première section d'ajustement qui s'ajuste dans la première section trou, et une seconde section arbre, comprenant une seconde section d'ajustement qui s'ajuste dans la seconde section trou.
PCT/JP2020/003235 2020-01-29 2020-01-29 Dispositif compresseur et turbocompresseur de suralimentation WO2021152742A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2020/003235 WO2021152742A1 (fr) 2020-01-29 2020-01-29 Dispositif compresseur et turbocompresseur de suralimentation

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2020/003235 WO2021152742A1 (fr) 2020-01-29 2020-01-29 Dispositif compresseur et turbocompresseur de suralimentation

Publications (1)

Publication Number Publication Date
WO2021152742A1 true WO2021152742A1 (fr) 2021-08-05

Family

ID=77078182

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2020/003235 WO2021152742A1 (fr) 2020-01-29 2020-01-29 Dispositif compresseur et turbocompresseur de suralimentation

Country Status (1)

Country Link
WO (1) WO2021152742A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03210024A (ja) * 1990-01-12 1991-09-13 Nissan Motor Co Ltd ターボチャージャのコンプレッサ
JP2002235547A (ja) * 2001-02-09 2002-08-23 Shozo Shimizu ターボチャージャ用タービン軸の接合方法
US20050056013A1 (en) * 2003-08-28 2005-03-17 General Electric Company Turbocharger compressor wheel having a counterbore treated for enhanced endurance to stress-induced fatigue and configurable to provide a compact axial length
US20050111998A1 (en) * 2003-11-25 2005-05-26 Louthan Gary R. Compressor wheel joint
JP2011208620A (ja) * 2010-03-30 2011-10-20 Toyota Motor Corp タービンローターの製造方法
WO2018167892A1 (fr) * 2017-03-15 2018-09-20 三菱重工エンジン＆ターボチャージャ株式会社 Turbocompresseur

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03210024A (ja) * 1990-01-12 1991-09-13 Nissan Motor Co Ltd ターボチャージャのコンプレッサ
JP2002235547A (ja) * 2001-02-09 2002-08-23 Shozo Shimizu ターボチャージャ用タービン軸の接合方法
US20050056013A1 (en) * 2003-08-28 2005-03-17 General Electric Company Turbocharger compressor wheel having a counterbore treated for enhanced endurance to stress-induced fatigue and configurable to provide a compact axial length
US20050111998A1 (en) * 2003-11-25 2005-05-26 Louthan Gary R. Compressor wheel joint
JP2011208620A (ja) * 2010-03-30 2011-10-20 Toyota Motor Corp タービンローターの製造方法
WO2018167892A1 (fr) * 2017-03-15 2018-09-20 三菱重工エンジン＆ターボチャージャ株式会社 Turbocompresseur

Similar Documents

Publication Publication Date Title
US6896479B2 (en) Turbocharger rotor
US10036405B2 (en) Impeller rotator and method of assembling said impeller rotator
EP1805398B1 (fr) Turbochargeur a caracteristiques d'equilibrage
EP1193370B1 (fr) Accouplement permettant l'alignement des arbres d'une turbo soufflante
US10197065B2 (en) Centrifugal compressor, turbocharger provided with the centrifugal compressor, and method for producing the centrifugal compressor
US20060013693A1 (en) Outer diameter nut piloting for improved rotor balance
US10309300B2 (en) Electric rotor fit onto a turbomachine shaft
WO2016129039A1 (fr) Compresseur de suralimentation
WO2021152742A1 (fr) Dispositif compresseur et turbocompresseur de suralimentation
US10975878B2 (en) Rotary machine
WO2015002141A1 (fr) Arbre de turbine et compresseur
WO2010079767A1 (fr) Structure d'amortissement et machine rotative
WO2017203917A1 (fr) Corps rotatif et compresseur de suralimentation
WO2020194651A1 (fr) Dispositif buse et turbocompresseur d'échappement
US20220389874A1 (en) Assembly for a turbine engine
WO2022264313A1 (fr) Structure de montage de roue de compresseur et compresseur de suralimentation
JP2021134737A (ja) コンプレッサ装置及びターボチャージャ
JP2021134698A (ja) コンプレッサ装置及びターボチャージャ
US20240011545A1 (en) Welded torque converter component
JP2007224800A (ja) タービンロータ及びそれを備えたタービン
JP2010101269A (ja) ロータ

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 20916794

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

NENP Non-entry into the national phase

Ref country code: JP

122 Ep: pct application non-entry in european phase

Ref document number: 20916794

Country of ref document: EP

Kind code of ref document: A1