WO2021152742A1 - Compressor device and turbocharger - Google Patents

Compressor device and turbocharger Download PDF

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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
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WO
WIPO (PCT)
Prior art keywords
shaft
hole
tip
compressor
compressor wheel
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Application number
PCT/JP2020/003235
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French (fr)
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
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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/JP2020/003235 priority Critical patent/WO2021152742A1/en
Publication of WO2021152742A1 publication Critical patent/WO2021152742A1/en

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    • 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.

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  • 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

The compressor device according to one embodiment is a compressor device, provided with a compressor wheel and a shaft that is inserted into an closed-end insertion hole that has an opening in a back surface of the compressor wheel, wherein: the insertion hole includes a first hole section, having a first diameter, that extends from the back surface of the compressor wheel toward the distal end of the compressor wheel and a second hole section, having a second diameter that is less than the first diameter, that extends from the distal end of the first hole section toward the distal end of the compressor wheel; and the shaft includes a first shaft section, comprising a first fitting section that fits into the first hole section, and a second shaft section, comprising a second fitting section that fits into the second hole section.

Description

コンプレッサ装置及びターボチャージャCompressor device and turbocharger
　本開示は、コンプレッサ装置及び該コンプレッサ装置を備えたターボチャージャに関する。 The present disclosure relates to a compressor device and a turbocharger equipped with the compressor device.
　ターボチャージャに組み込まれたコンプレッサ装置には、コンプレッサホイールの中心軸に貫通孔が形成され、該貫通孔にシャフトが挿入される、所謂ボアスルー構造のコンプレッサ装置と、コンプレッサホイールの背面に開口を有する有底の挿入孔が形成され、該挿入孔にシャフトが挿入される、所謂ボアレス構造のコンプレッサ装置とがある。商用車や産業用エンジンに取り付けられる比較的大型のターボチャージャに組み込まれるコンプレッサでは、所謂ボアレス構造が採用される場合がある。ボアレス構造は挿入孔周辺の部位に発生する応力集中が低減されるなどの長所が確認されている。特許文献１には、コンプレッサにボアスルー構造及びボアレス構造を採用したターボチャージャが開示されている。 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. There is 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.
国際公開第２０１８／１６７８９２号International Publication No. 2018/167892
　ボアレス構造のコンプレッサ装置は、ボアスルー構造のコンプレッサ装置よりシャフトとコンプレッサホイールとの嵌合部の長さが短いため、組立時に挿入孔の軸線に対するシャフトの軸心ズレが起りやすく、挿入孔の軸線に対するシャフトの軸線の傾き（偏差角）が大きくなりやすい。偏差角が大きくなると、シャフトの回転中不均衡な力が発生し、振動の発生など装置の安定運転を損なうおそれがある。このような軸心ズレをなくすため、公差の管理を厳しくするなどの対策が考えられるが、この対策は高精度な加工や組立が求められるため、コスト増に繋がる。このことを図５及び図６を用いて説明する。 Since the length of the fitting portion between the shaft and the compressor wheel is shorter in the boreless structure compressor device than in the bore-through structure compressor device, 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. In order to eliminate such misalignment, 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.
　図５は、従来のボアレス構造を有するコンプレッサホイール（ハブ部を含む。）を示す縦断面図であり、図６は、従来のボアスルー構造を有するコンプレッサホイール（ハブ部を含む。）を示す縦断面図である。図５において、ボアレス構造を有するコンプレッサホイール０２２Ａには、背面０２３に開口を有する有底の挿入孔０２６が軸線０２２ａに沿って形成され、挿入孔０２６にシャフト０１２の先端部が挿入され、挿入孔０２６に固定される。図６において、ボアスルー構造を有するコンプレッサホイール０２２Ｂには、軸方向に、即ち、背面０２３から先端側へ向けてコンプレッサホイール０２２Ｂを貫通する貫通孔０２７が形成され、貫通孔０２７にシャフト０１２の先端部が挿入される。挿入孔０２６又は貫通孔０２７とシャフト０１２の先端部との組立公差が小さいほど、コンプレッサホイール０２２Ａ又は０２２Ｂの軸線０２２ａとシャフト０１２の軸線０１２ａとのズレは小さくなるが、両者の組立が難しくなるため、組立コストは増加する。　 FIG. 5 is a vertical cross-sectional view showing a compressor wheel (including a hub portion) having a conventional boreless structure, and 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. In FIG. 5, in the compressor wheel 022A having a boreless structure, 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. In FIG. 6, 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 smaller the assembly tolerance between the insertion hole 026 or the through hole 027 and the tip of the shaft 012, the smaller the deviation between the axis 022a of the compressor wheel 022A or 022B and the axis 012a of the shaft 012, but it becomes difficult to assemble both. , Assembly cost will increase.
　図５及び図６に示すように、ボアスルー構造のコンプレッサホイール０２２Ｂとシャフト０１２との嵌合部の長さは、ボアレス構造のコンプレッサホイール０２２Ａとシャフト０１２との嵌合部の長さより長くなる。そして、嵌合部の長さが長くなるほど、コンプレッサホイール０２２Ａ又は０２２Ｂの軸線０２２ａに対するシャフト０１２の軸線０１２ａの傾斜角（偏差角）は小さくなる。従って、ボアレス構造の場合の偏差角θ１はボアスルー構造の場合の偏差角θ２より大きくなるため、シャフト０１２の回転中アンバランスな力が発生し、安定性に欠ける。 As shown in FIGS. 5 and 6, 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 θ1 in the case of the boreless structure is larger than the deviation angle θ2 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.
　本開示は、上述する問題点に鑑みてなされたもので、ボアレス構造のコンプレッサ装置において、高精度な加工や組立を必要とすることなく、シャフトとコンプレッサホイールとの間の軸心ズレを抑制することを目的とする。 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.
　上記目的を達成するため、本開示に係るコンプレッサ装置は、コンプレッサホイールと、前記コンプレッサホイールの背面に開口を有する有底の挿入孔に挿入されるシャフトと、を備えるコンプレッサ装置であって、前記挿入孔は、第１直径を有する第１孔部であって、前記背面から前記コンプレッサホイールの先端側へ向かって延在する第１孔部と、前記第１直径より小さい第２直径を有する第２孔部であって、前記第１孔部の先端から前記コンプレッサホイールの前記先端側へ向かって延在する第２孔部と、を含み、前記シャフトは、前記第１孔部に嵌合する第１嵌合部を有する第１軸部と、前記第２孔部に嵌合する第２嵌合部を有する第２軸部と、を含む。 In order to achieve the above object, the compressor device according to the present disclosure 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.
　本開示に係るターボチャージャは、前記シャフトの一端側に設けられた上述のコンプレッサ装置と、前記シャフトの他端側に固定され、排ガスによって回転するタービンホイールを含むタービン装置と、を備える。 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.
　本開示に係るコンプレッサ装置及びターボチャージャによれば、ボアレス構造のコンプレッサ装置において、高精度な加工や組立を必要とすることなく、シャフトとコンプレッサホイールとの間の軸心ズレを抑制することができる。これによって、回転中のシャフトに不均衡な力が発生して振動などが発生するのを回避でき、装置の安定運転が可能になる。 According to the compressor device and turbocharger according to the present disclosure, 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.
一実施形態に係るターボチャージャの回転部位を示す一部断裁正面図である。It is a partially cut front view which shows the rotating part of the turbocharger which concerns on one Embodiment. コンプレッサ装置を示す図１の一部拡大縦断面図である。It is a partially enlarged vertical sectional view of FIG. 1 which shows a compressor apparatus. 一実施形態に係るコンプレッサホイールの一部拡大縦断面図である。It is a partially enlarged vertical sectional view of the compressor wheel which concerns on one Embodiment. 一実施形態に係るコンプレッサホイールの一部拡大縦断面図である。It is a partially enlarged vertical sectional view of the compressor wheel which concerns on one Embodiment. 一実施形態に係るコンプレッサホイールの一部拡大縦断面図である。It is a partially enlarged vertical sectional view of the compressor wheel which concerns on one Embodiment. 従来のボアレス構造のコンプレッサホイールを示す一部拡大縦断面図である。It is a partially enlarged vertical sectional view which shows the compressor wheel of the conventional boreless structure. 従来のボアスルー構造のコンプレッサホイールを示す一部拡大縦断面図である。It is a partially enlarged vertical sectional view which shows the compressor wheel of the conventional bore-through structure.
　以下、添付図面を参照して本発明の幾つかの実施形態について説明する。ただし、実施形態として記載され又は図面に示されている構成部品の寸法、材質、形状、その相対的配置等は、本発明の範囲をこれに限定する趣旨ではなく、単なる説明例にすぎない。
　例えば、「ある方向に」、「ある方向に沿って」、「平行」、「直交」、「中心」、「同心」或いは「同軸」等の相対的或いは絶対的な配置を表す表現は、厳密にそのような配置を表すのみならず、公差、若しくは、同じ機能が得られる程度の角度や距離をもって相対的に変位している状態も表すものとする。
　例えば、「同一」、「等しい」及び「均質」等の物事が等しい状態であることを表す表現は、厳密に等しい状態を表すのみならず、公差、若しくは、同じ機能が得られる程度の差が存在している状態も表すものとする。
　例えば、四角形状や円筒形状等の形状を表す表現は、幾何学的に厳密な意味での四角形状や円筒形状等の形状を表すのみならず、同じ効果が得られる範囲で、凹凸部や面取り部等を含む形状も表すものとする。
　一方、一つの構成要素を「備える」、「具える」、「具備する」、「含む」、又は「有する」という表現は、他の構成要素の存在を除外する排他的な表現ではない。 Hereinafter, some embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the components described as embodiments or shown in the drawings are not intended to limit the scope of the present invention to this, and are merely explanatory examples.
For example, expressions that represent relative or absolute arrangements such as "in a certain direction", "along a certain direction", "parallel", "orthogonal", "center", "concentric" or "coaxial" are exact. Not only does it represent such an arrangement, but it also represents a state of relative displacement with tolerances or angles and distances to the extent that the same function can be obtained.
For example, 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.
For example, 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.
On the other hand, the expressions "equipped", "equipped", "equipped", "included", or "have" one component are not exclusive expressions that exclude the existence of other components.
　図１は、一実施形態に係るボアレス構造のコンプレッサ装置２０を含むターボチャージャ１０を示す縦断面図であり、図２はコンプレッサ装置２０を示す図１の一部拡大図である。ターボチャージャ１０は、シャフト１２の一端部にコンプレッサ装置２０を備え、コンプレッサ装置２０と反対側のシャフト１２の他端部にタービン装置３０を備えている。コンプレッサ装置２０は、シャフト１２の一端部に固定されたコンプレッサホイール２２と、コンプレッサホイール２２の外周に周方向に設けられた複数のコンプレッサブレード２４とを備えている。コンプレッサホイール２２の背面２３に開口を有し、コンプレッサホイール２２の軸線１２ａ上に該軸線に沿って有底の挿入孔２６が形成され、挿入孔２６にシャフト１２の一端部が挿入固定されている。 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, and 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. ..
　タービン装置３０は、シャフト１２の他端部に例えば溶接などの手段で取り付けられたタービンホイール３２と、タービンホイール３２の外周に周方向に設けられた複数のタービンブレード３４とを備えている。シャフト１２は軸線１２ａに沿う方向の中央部においてジャーナル軸受（不図示）で支持される。図２に示すように、コンプレッサ装置２０はコンプレッサハウジング（不図示）の内部に収容され、シャフト１２の軸線方向中央部は軸受ハウジング（不図示）の内部に収容され、タービン装置３０はタービンハウジング（不図示）の内部に収容されている。 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. As shown in FIG. 2, 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), and the turbine device 30 is housed in a turbine housing (not shown). It is housed inside (not shown).
　図１に示す実施形態では、コンプレッサ装置２０寄りのシャフト１２の周囲にスラストカラー１６が設けられている。シャフト１２に加わる軸方向のスラスト荷重に対してシャフト１２を支持するスラスト軸受（不図示）が設けられ、スラストカラー１６は該スラスト軸受を支持している。 In the embodiment shown in FIG. 1, 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.
　図３Ａ、図３Ｂ及び図４は、幾つかの実施形態に係るコンプレッサホイール２２（後述するハブ部５０を含む。）の挿入孔２６付近の縦断面図である。これらの図に示すように、挿入孔２６は、直径が異なる２つの孔部２６ａ及び２６ｂを有している。孔部２６ａ（第１孔部２６ａ）は、コンプレッサホイール２２の背面２３からコンプレッサホイール２２の先端側へ向かって延在する。孔部２６ｂ（第２孔部２６ｂ）は、第１孔部２６ａの先端からコンプレッサホイール２２の先端側へ向かって延在する。第２孔部２６ｂの横断面の直径は第１孔部２６ａの横断面の直径より小さくなるように構成されている。 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. As shown in these figures, the insertion hole 26 has two holes 26a and 26b having different diameters. The hole portion 26a (first hole portion 26a) extends from the back surface 23 of the compressor wheel 22 toward the tip end side of the compressor wheel 22. The hole portion 26b (second hole portion 26b) extends from the tip end of the first hole portion 26a toward the tip end side of the compressor wheel 22. 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.
　一方、挿入孔２６に挿入されるシャフト１２の先端部は第１軸部４０及び第２軸部４２を有する。第１軸部４０は、第１孔部２６ａに嵌合する第１嵌合部４４（４４ａ、４４ｂ）を有し、第２軸部４２は、第２孔部２６ｂに嵌合する第２嵌合部４６（４６ａ、４６ｂ）を有する。即ち、第１嵌合部４４の横断面の直径（第１直径）は第２嵌合部４６の横断面の直径（第２直径）より大きい。 On the other hand, 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, and 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).
　このような構成によれば、挿入孔２６に挿入されたシャフト１２の先端部は、第１軸部４０が第１嵌合部４４で第１孔部２６ａに嵌合すると共に、第２軸部４２が第２嵌合部４６で第２孔部２６ｂに嵌合する。こうして、挿入孔２６に挿入されるシャフト１２の先端部は、第１嵌合部４４及び第２嵌合部４６の２か所で支持される。この２点支持によって、挿入孔２６とシャフト１２との間の軸心ズレによって発生するシャフト１２の偏差角θ１を、第１嵌合部４４から第２嵌合部４６に至るまで一つの嵌合部が形成されている場合と同等まで小さく抑えることができる。これによって、シャフト１２の回転中のアンバランスをなくし、安定運転が可能になる。 According to such a configuration, in the tip portion of the shaft 12 inserted into the insertion hole 26, 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. In this way, 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. By this two-point support, the deviation angle θ1 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.
　また、第２孔部２６ｂの直径よりも第１孔部２６ａの直径の方が大きいため、シャフト１２を挿入孔２６に挿入して第２軸部４２の第２嵌合部４６が第１孔部２６ａを通過する際に、第１孔部２６ａの内周面と第２嵌合部４６とが当接することがない。このため、第２嵌合部４６を第２孔部２６ｂに嵌合するまでの工程が容易になる。さらに、挿入孔２６とシャフト１２の先端部とは、第１嵌合部４４及び第２嵌合部４６のみで嵌合し、その他の部位は組立公差を緩めに設定できるので、高精度な加工や組立を必要としない。そのため、コンプレッサホイール２２やシャフト１２の製造コストを抑制できる。 Further, since the diameter of the first hole portion 26a is larger than the diameter of the second hole portion 26b, 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. When passing through the portion 26a, 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. Further, 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.
　一実施形態では、挿入孔２６はコンプレッサホイール２２の軸線上に沿って直線状に形成され、第１軸部４０及び第２軸部４２は、挿入孔２６の軸線方向に沿って直線状に延在し、挿入孔２６及び第１軸部４０、第２軸部４２は横断面が円形を有している。また、第１軸部４０及び第２軸部４２の横断面は互いに断面の中心を同じくする同心状に配置されている。第１孔部２６ａと第２孔部２６ｂとの直径の差は公差以上であってかつ少ないほうがよい。即ち、第２孔部２６ｂの直径が小さいほど、組立が難しくなりかつ強度が低下するためである。 In one embodiment, 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.
　図３Ａ及び３Ｂに示す実施形態において、第１嵌合部４４（４４ａ）と第１孔部２６ａとの接触面積、及び第２嵌合部４６（４６ａ）と第２孔部２６ｂとの接触面積は、できるだけ小さくすることで組立性の悪化を最小限に抑えることができる。 In the embodiment shown in FIGS. 3A and 3B, 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.
　一実施形態では、図２に示すように、コンプレッサホイール２２の背面２３の中心には、軸方向に沿ってシャフト１２の中央側へ延在するハブ部５０が形成され、ハブ部５０の中心部に挿入孔２６が形成されている。同図において、Ｌ０は、挿入孔２６におけるハブ部５０とシャフト１２の先端部との嵌合部の長さを示す。ハブ部５０は、ハブ部５０の外周面に接する支持部材（不図示）によって回転自在に支持されている。 In one embodiment, as shown in FIG. 2, 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. In the figure, 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.
　一実施形態では、図３Ａ、３Ｂ及び図４に示すように、第１軸部４０の先端外周に傾斜平面状の面取り５６が形成され、これによって、第１軸部４０の第１孔部２６ａへの挿入時の位置決めが容易になる。また、第２軸部４２の先端部の外周端を曲面とした面取り５８が形成され、これによって、第２軸部４２の第２孔部２６ｂへの挿入時の位置決めが容易になる。 In one embodiment, as shown in FIGS. 3A, 3B and 4, 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.
　一実施形態では、図３Ａ、３Ｂ及び図４に示すように、第１孔部２６ａは、コンプレッサホイール２２の背面２３からコンプレッサホイール２２の先端側へ向かって延在する雌ネジ部６２と、雌ネジ部６２の先端からコンプレッサホイール２２の先端側へ向かって延在する非ネジ部６４と、を有する。一方、第１軸部４０は、雌ネジ部６２に螺合可能な雄ネジ部６６を有し、第１嵌合部４４は、非ネジ部６４の少なくとも一部と嵌合するように構成されている。この実施形態によれば、第１軸部４０及び第２軸部４２は第１嵌合部４４及び第２嵌合部４６によって支持されて、挿入孔２６とシャフト１２との間の軸心ズレを抑えながら第１孔部２６ａ及び第２孔部２６ｂに挿入された後、雌ネジ部６２と雄ネジ部６６とが螺合することで、コンプレッサホイール２２に固定される。 In one embodiment, as shown in FIGS. 3A, 3B and 4, 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. On the other hand, 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. According to this embodiment, 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. After being inserted into the first hole portion 26a and the second hole portion 26b while suppressing the above, the female screw portion 62 and the male screw portion 66 are screwed together to be fixed to the compressor wheel 22.
　一実施形態では、第１嵌合部４４（４４ａ、４４ｂ）の先端と第２嵌合部４６（４６ａ、４６ｂ）の先端との間の長さＬ１は、非ネジ部６４の先端と非ネジ部６４の後端との間の長さＬ２より大きくなるように構成されている（Ｌ２＜Ｌ１）。これによって、第１嵌合部４４が第１孔部２６ａに嵌合する前に、第２嵌合部４６の先端が第２孔部２６ｂに挿入されて第２孔部２６ｂに対する第２軸部４２の軸心合わせが行われる。このように、第２孔部２６ｂと第２軸部４２との軸心合わせが、第１孔部２６ａと第１軸部４０との軸心合わせより先に行われるので、組付け後の挿入孔２６に対するシャフト先端部の軸心ズレを抑制できる。 In one embodiment, 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 ). As a result, before the first fitting portion 44 is fitted into the first hole portion 26a, 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. In this way, 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.
　なお、図４に示す実施形態では、後述するように、第１嵌合部４４（４４ｂ）及び第２嵌合部４６（４６ｂ）は、コンプレッサホイール２２の軸方向でほぼ１点に集約されるので、先端及び後端はほぼ同一位置となる。この実施形態においても、長さＬ１及び長さＬ２が設定されたとき（Ｌ２＜Ｌ１）、図３Ａ及び図３Ｂ示す実施形態と同様の作用効果を得ることができる。 In the embodiment shown in FIG. 4, as will be described later, 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.
　一実施形態では、図３Ａ、３Ｂ及び図４に示すように、非ネジ部６４の先端部に軸方向に対して傾斜した傾斜面６０が形成されている。傾斜面６０を形成することで、第２軸部４２の第２孔部２６ｂに対する位置決め及び第１軸部４０の第１孔部２６ａへの挿入が容易になる。一方、図１に示すように、ボアレス構造のコンプレッサホイール２２では、コンプレッサホイール２２の軸心付近に、コンプレッサホイール２２の軸線に沿う領域Ｃで応力が発生する。特に、軸方向でコンプレッサホイール２２が最大径となる位置に最大応力が発生する。そのため、挿入孔２６が軸方向で最大径となる位置まで延在しないことが望ましい。 In one embodiment, as shown in FIGS. 3A, 3B and 4, an inclined surface 60 inclined with respect to the axial direction is formed at the tip of the non-threaded portion 64. By forming the inclined surface 60, 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. On the other hand, as shown in FIG. 1, in the compressor wheel 22 having a boreless structure, 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. In particular, 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.
　そのために、一実施形態では、傾斜面６０の軸方向長さｂが径方向長さａより大きくならないようにする（ｂ≦ａ）。これによって、応力発生領域Ｃに挿入孔２６が形成されることで、応力発生領域Ｃでコンプレッサホイール２２の強度が低下するのを回避できる。別な実施形態では、シャフト１２の軸方向に直角な横断面に対する傾斜面６０の傾斜角θ３を０°≦θ３≦４５°とする。これによって、ｂ≦ａとすることができ、挿入孔２６がコンプレッサホイール２２の軸方向で最大径となる位置まで延在しないようにすることができる。 Therefore, in one embodiment, the axial length b of the inclined surface 60 is prevented from being larger than the radial length a (b ≦ a). As a result, 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. In another embodiment, the inclination angle θ3 of the inclined surface 60 with respect to the cross section perpendicular to the axial direction of the shaft 12 is set to 0 ° ≦ θ3 ≦ 45 °. As a result, 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.
　一実施形態では、第１嵌合部４４（４４ａ、４４ｂ）の軸方向先端と雄ネジ部６６の軸方向先端との間の長さＬ３は、雌ネジ部６２の軸方向先端と雌ネジ部６２の軸方向後端との間の長さＬ４より大きくなるように構成されている（Ｌ４＜Ｌ３）。この実施形態によれば、雌ネジ部６２と雄ネジ部６６とが螺合する前に、第１嵌合部４４の先端が第１孔部２６ａに挿入され、第１孔部２６ａに対する第１軸部４０の軸心合わせが行われる。このように、挿入孔２６とシャフト１２間の軸心合わせを終えた後で、挿入孔２６にシャフト１２を固定できる。 In one embodiment, the length L 3 between the axial tip of the axial tip and the male screw portion 66 of the first fitting portion 44 (44a, 44b), the axial tip and the female screw of the female screw portion 62 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 ). According to this embodiment, before the female screw portion 62 and the male screw portion 66 are screwed together, the tip of the first fitting portion 44 is inserted into the first hole portion 26a, and the first with respect to the first hole portion 26a. Axial alignment of the shaft portion 40 is performed. In this way, the shaft 12 can be fixed to the insertion hole 26 after the axial alignment between the insertion hole 26 and the shaft 12 is completed.
　なお、図４に示す実施形態では、後述するように、第１嵌合部４４（４４ｂ）及び第２嵌合部４６（４６ｂ）は、コンプレッサホイール２２の軸方向でほぼ１点に集約されるので、先端及び後端はほぼ同一位置となる。この実施形態においても、長さＬ３及び長さＬ４が設定されたとき（Ｌ４＜Ｌ３）、図３Ａ及び図３Ｂ示す実施形態と同様の作用効果を得ることができる。 In the embodiment shown in FIG. 4, as will be described later, 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.
　一実施形態では、図４に示すように、第１嵌合部４４（４４ｂ）又は第２嵌合部４６（４６ｂ）の少なくとも一方は、径方向外側に向かって凸となる曲面状に形成されている。この実施形態によれば、第１嵌合部４４（４４ｂ）と第１孔部２６ａとの接触面積又は第２嵌合部４６（４６ｂ）と第２孔部２６ｂとの接触面積の少なくとも一方を小さくできるため、第１嵌合部４４（４４ｂ）と第１孔部２６ａとの間の摩擦又は第２嵌合部４６（４６ａ、４６ｂ）と第２孔部２６ｂとの間の摩擦を低減できる。従って、挿入孔２６へのシャフト１２の挿入が容易になる。 In one embodiment, as shown in FIG. 4, 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.
　一実施形態では、第１嵌合部４４（４４ｂ）又は第２嵌合部４６（４６ｂ）の軸方向断面の外縁が円弧又は楕円形を形成するように構成する。これによって、第１嵌合部４４（４４ｂ）又は第２嵌合部４６（４６ｂ）を第１孔部２６ａ又は第２孔部２６ｂに点接触に近い状態で接触できるので、両者間の摩擦を軽減できる。
　一実施形態では、少なくとも横断面の直径が大きい第１嵌合部４４（４４ｂ）の軸方向断面の外縁が円弧又は楕円形を形成するように構成する。直径が大きい第１嵌合部４４（４４ｂ）をこのような形状の加工対象とすることで、加工が容易になる。
　一実施形態では、第１嵌合部４４（４４ｂ）と第２嵌合部４６（４６ｂ）との間隔をなるべく広げるようにする。これによって、挿入孔２６の軸線に対するシャフト１２の先端部の軸線１２ａの偏差角θ１を抑えることができる。 In one embodiment, 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. As a result, 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.
In one embodiment, 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. By targeting the first fitting portion 44 (44b) having a large diameter as a processing target having such a shape, processing becomes easy.
In one embodiment, 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 θ1 of the axis 12a at the tip of the shaft 12 with respect to the axis of the insertion hole 26 can be suppressed.
　一実施形態に係るターボチャージャ１０は、図１に示すように、シャフト１２の一端部に上記各実施形態に係るコンプレッサ装置２０が設けられ、シャフト１２の他端部に内燃機関から排出される排ガスによって回転するタービンホイール３２を含むタービン装置３０が設けられているタービンホイール３２及びシャフト１２が回転することで、コンプレッサホイール２２が回転し、コンプレッサホイール２２の回転によって加圧給気を内燃機関に供給する。ターボチャージャ１０は、上記各実施形態に係るコンプレッサ装置２０を備えているため、シャフト１２とコンプレッサホイール２２との組立時に、シャフト１２はコンプレッサホイール２２に形成された挿入孔２６に対して第１嵌合部４４（４４ａ、４４ｂ）及び第２嵌合部４６（４６ａ、４６ｂ）とで支持される。 As shown in FIG. 1, the turbocharger 10 according to one embodiment 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. When the turbine wheel 32 and the shaft 12 provided with the turbine device 30 including the turbine wheel 32 rotated by the turbine wheel 32 are rotated, 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. Since 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).
　これによって、挿入孔２６とシャフト１２間の軸心ズレによって発生するシャフト１２の偏差角θ１を小さく抑えることができると共に、シャフト１２の回転中のアンバランスをなくし、安定運転が可能になる。また、第１軸部４０の第１直径を第２軸部４２の第２直径より大きくすることで、先に挿入される第２軸部４２と第２孔部２６ｂとの軸心合わせが容易になると共に、挿入孔２６に挿入されるシャフト先端部の強度を増加できる。さらに、第１嵌合部４４及び第２嵌合部４６以外は組立公差を緩めに設定できるので、組付けが容易になると共に、製造コストを抑制できる。 As a result, the deviation angle θ1 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. Further, by making 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. At the same time, the strength of the tip of the shaft inserted into the insertion hole 26 can be increased. Further, since 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.
　上記各実施形態に記載の内容は、例えば以下のように把握される。 The contents described in each of the above embodiments are grasped as follows, for example.
　１）一つの態様に係るコンプレッサ装置（２０）は、コンプレッサホイール（２２）と、前記コンプレッサホイール（２２）の背面（２３）に開口を有する有底の挿入孔（２６）に挿入されるシャフト（１２）と、を備えるコンプレッサ装置であって、前記挿入孔は、第１直径を有する第１孔部であって、前記背面から前記コンプレッサホイールの先端側へ向かって延在する第１孔部（２６ａ）と、前記第１直径より小さい第２直径を有する第２孔部であって、前記第１孔部の先端から前記コンプレッサホイールの前記先端側へ向かって延在する第２孔部（２６ｂ）と、を含み、前記シャフトは、前記第１孔部に嵌合する第１嵌合部（４４（４４ａ、４４ｂ））を有する第１軸部（４０）と、前記第２孔部に嵌合する第２嵌合部（４６（４６ａ、４６ｂ））を有する第２軸部（４２）と、を含む。 1) The compressor device (20) according to one embodiment 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)).
　このような構成によれば、上記シャフトは、第１孔部に嵌合する第１嵌合部を有する第１軸部と、前記第２孔部に嵌合する第２嵌合部を有する第２軸部とを有するため、挿入孔に対して第１嵌合部と第２嵌合部とで支持される。従って、挿入孔とシャフト間の軸心ズレによって発生するシャフトの偏差角（θ１）を、第１嵌合部から第２嵌合部に至るまで一つの嵌合部が形成されている場合と同等まで小さく抑えることができる。これによって、シャフトの回転中のアンバランスをなくし、安定運転が可能になる。また、第２孔部の直径よりも第１孔部の直径の方が大きいため、シャフトを挿入孔に挿入して第２軸部の第２嵌合部が第１孔部を通過する際に、第１孔部の内周面と第２嵌合部とが当接することがない。このため、第２嵌合部を第２孔部に嵌合するまでの工程が容易になる。さらに、挿入孔とシャフトの先端部とは、第１嵌合部及び第２嵌合部のみで嵌合し、その他の部位は組立公差を緩めに設定できるので、高精度な加工や組立を必要としない。そのため、コンプレッサホイールやシャフトの製造コストを抑制できる。 According to such a configuration, 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 (θ1) 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.
　２）別な態様に係るコンプレッサ装置は、１）に記載のコンプレッサ装置であって、前記第１孔部は、前記コンプレッサホイールの前記背面から前記コンプレッサホイールの前記先端側へ向かって延在する雌ネジ部（６２）と、前記雌ネジ部の先端から前記コンプレッサホイールの前記先端側へ向かって延在する非ネジ部（６４）と、を含み、前記第１軸部は、前記雌ネジ部に螺合可能な雄ネジ部（６６）を有し、前記第１嵌合部は、前記非ネジ部の一部と嵌合するように構成される。 2) The compressor device according to another aspect 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.
　このような構成によれば、第１軸部及び第２軸部は、第１嵌合部及び第２嵌合部によって支持されて挿入孔とシャフトとの軸心ズレを抑えながら、第１孔部及び第２孔部に挿入された後、上記雌ネジ部と上記雄ネジ部とが螺合することで、コンプレッサホイールに固定される。 According to such a configuration, 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. After being inserted into the portion and the second hole portion, the female screw portion and the male screw portion are screwed together to be fixed to the compressor wheel.
　３）さらに別な態様に係るコンプレッサ装置は、２）に記載のコンプレッサ装置であって、前記第１嵌合部の先端と前記第２嵌合部の先端との間の長さＬ１は、前記非ネジ部の先端と前記非ネジ部の後端との間の長さＬ２より大きくなるように構成されている。 3) 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.
　このような構成によれば、Ｌ２＜Ｌ１であるため、第１嵌合部が第１孔部に嵌合する前に、第２嵌合部の先端が第２孔部に挿入されて第２孔部に対する第２軸部の軸心合わせが行われる。このように、第２孔部と第２軸部との軸心合わせが、第１孔部と第１軸部との軸心合わせより先に行われるので、組付け後の挿入孔に対するシャフト先端部の軸心ズレを抑制できる。 According to such a configuration, since L 2 <L 1 , 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.
　４）さらに別な態様に係るコンプレッサ装置は、２）又は３）に記載のコンプレッサ装置であって、前記第１嵌合部の先端と前記雄ネジ部の先端との間の長さＬ３は、前記雌ネジ部の先端と前記雌ネジ部の後端との間の長さＬ４より大きくなるように構成されている。 4) 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.
　このような構成によれば、Ｌ４＜Ｌ３であるため、上記雌ネジ部と上記雄ネジ部とが螺合する前に、第１嵌合部の先端が第１孔部に挿入され、第１孔部に対する第１軸部の軸心合わせが行われる。このように、挿入孔とシャフト間の軸心合わせを終えた後で、挿入孔にシャフトを固定できる。 According to such a configuration, since L 4 <L 3 , the tip of the first fitting portion is inserted into the first hole portion before the female screw portion and the male screw portion are screwed together. The axis alignment of the first shaft portion with respect to the first hole portion is performed. In this way, the shaft can be fixed to the insertion hole after the axial alignment between the insertion hole and the shaft is completed.
　５）さらに別な態様に係るコンプレッサ装置は、１）乃至４）の何れかに記載のコンプレッサ装置であって、前記第１嵌合部又は前記第２嵌合部の少なくとも一方は、径方向外側に向かって凸となる曲面状に形成されている。 5) The compressor device according to still another aspect 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.
　このような構成によれば、第１嵌合部と第１孔部との接触面積又は第２嵌合部と第２孔部との接触面積の少なくとも一方を小さくできるため、挿入孔とシャフト先端部との間の摩擦を低減できる。これによって、挿入孔へシャフトを容易に挿入できる。 According to such a configuration, 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.
　６）一つの態様に係るターボチャージャ（１０）は、前記シャフトの一端側に設けられた１）乃至５）の何れかに記載のコンプレッサ装置と、前記シャフトの他端側に固定され、排ガスによって回転するタービンホイールを含むタービン装置（３０）と、を備える。 6) 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.
　このような構成によれば、上記シャフトとコンプレッサホイールとの組立時に、上記シャフトはコンプレッサホイールに形成された挿入孔に対して第１嵌合部及び第２嵌合部とで支持されるため、挿入孔とシャフト間の軸心ズレによって発生するシャフトの偏差角を、第１嵌合部から第２嵌合部に至るまで一つの嵌合部が形成されている場合と同等まで小さく抑えることができる。また、第２孔部の直径よりも第１孔部の直径の方が大きいため、シャフトが挿入孔に挿入されて第２軸部の第２嵌合部が第１孔部を通過する際に、第１孔部の内周面と第２嵌合部とが当接することがないため、第２嵌合部を第２孔部に嵌合するまでの工程が容易になる。さらに、挿入孔とシャフトの先端部とは、第１嵌合部及び第２嵌合部のみで嵌合し、その他の部位は組立公差を緩めに設定できるので、高精度な加工や組立を必要としない。 According to such a configuration, 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. Further, since 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. 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.
　１０　　ターボチャージャ
　１２、０１２　　シャフト
　　１２ａ、０１２ａ　　軸線
　１４　　軸受ハウジング
　１６　　スラストカラー
　１８　　スラスト軸受
　２０　　コンプレッサ装置
　２２、０２２（０２２Ａ、０２２Ｂ）　　コンプレッサホイール
　　０２２ａ　　軸線
　２３、０２３　　背面
　２４　　コンプレッサブレード
　２６、０２６　　挿入孔
　　２６ａ　　第１孔部
　　２６ｂ　　第２孔部
　０２７　　貫通孔
　３０　　タービン装置
　３２　　タービンホイール
　３４　　タービンブレード
　４０　　第１軸部
　４２　　第２軸部
　４４（４４ａ、４４ｂ）　　第１嵌合部
　４６（４６ａ、４６ｂ）　　第２嵌合部
　５０　　ハブ部
　５６、５８　　面取り
　６０　　傾斜面
　６２　　雌ネジ部
　６４　　非ネジ部
　６６　　雄ネジ部
　Ｃ　　　応力発生領域
　θ１、θ２　　偏差角
　θ３　　傾斜角 10 Turbine Charger 12,012 Shaft 12a, 012a Axis 14 Bearing Housing 16 Thrust Color 18 Thrust Bearing 20 Compressor Device 22,022 (022A, 022B) Compressor Wheel 022a Axis 23,023 Rear 24 Compressor Blade 26, 022 Insertion Hole 26a 1st Hole 26b 2nd hole 027 Through hole 30 Turbine device 32 Turbine wheel 34 Turbine blade 40 1st shaft 42 2nd shaft 44 (44a, 44b) 1st fitting 46 (46a, 46b) 2nd fitting Part 50 Hub part 56, 58 Chamfering 60 Inclined surface 62 Female threaded part 64 Non-threaded part 66 Male threaded part C Stress generation area θ1, θ2 Deviation angle θ3 Tilt angle

Claims (6)

  1. 　コンプレッサホイールと、
    　前記コンプレッサホイールの背面に開口を有する有底の挿入孔に挿入されるシャフトと、
    を備えるコンプレッサ装置であって、
    　前記挿入孔は、
    　　第１直径を有する第１孔部であって、前記背面から前記コンプレッサホイールの先端側へ向かって延在する第１孔部と、
    　　前記第１直径より小さい第２直径を有する第２孔部であって、前記第１孔部の先端から前記コンプレッサホイールの前記先端側へ向かって延在する第２孔部と、
    　を含み、
    　前記シャフトは、
    　　前記第１孔部に嵌合する第１嵌合部を有する第１軸部と、
    　　前記第２孔部に嵌合する第２嵌合部を有する第２軸部と、
    　を含む
    コンプレッサ装置。     With the compressor wheel
    A shaft inserted into a bottomed insertion hole having an opening on the back surface of the compressor wheel,
    It is a compressor device equipped with
    The insertion hole is
    A first hole having a first diameter, which extends from the back surface toward the tip of the compressor wheel.
    A second hole having a second diameter smaller than the first diameter, and a second hole extending from the tip of the first hole toward the tip side of the compressor wheel.
    Including
    The shaft
    A first shaft portion having a first fitting portion that fits into the first hole portion, and a first shaft portion.
    A second shaft portion having a second fitting portion that fits into the second hole portion, and a second shaft portion.
    Compressor equipment including.
  2. 　前記第１孔部は、
    　　前記コンプレッサホイールの前記背面から前記コンプレッサホイールの前記先端側へ向かって延在する雌ネジ部と、
    　　前記雌ネジ部の先端から前記コンプレッサホイールの前記先端側へ向かって延在する非ネジ部と、を含み、
    　前記第１軸部は、前記雌ネジ部に螺合可能な雄ネジ部を有し、
    　前記第１嵌合部は、前記非ネジ部の一部と嵌合するように構成される
    請求項１に記載のコンプレッサ装置。     The first hole is
    A female screw portion extending from the back surface of the compressor wheel toward the tip end side of the compressor wheel.
    Includes a non-threaded portion extending from the tip of the female threaded portion toward the tip end side of the compressor wheel.
    The first shaft portion has a male screw portion that can be screwed into the female screw portion.
    The compressor device according to claim 1, wherein the first fitting portion is configured to fit a part of the non-threaded portion.
  3. 　前記第１嵌合部の先端と前記第２嵌合部の先端との間の長さＬ１は、前記非ネジ部の先端と前記非ネジ部の後端との間の長さＬ２より大きくなるように構成されている
    請求項２に記載のコンプレッサ装置。     The length L 1 between the tip of the first fitting portion and the tip of the second fitting portion is from the length L 2 between the tip of the non-threaded portion and the rear end of the non-threaded portion. The compressor device according to claim 2, which is configured to be large.
  4. 　前記第１嵌合部の先端と前記雄ネジ部の先端との間の名長さＬ３は、前記雌ネジ部の先端と前記雌ネジ部の後端との間の長さＬ４より大きくなるように構成されている
    請求項２又は３に記載のコンプレッサ装置。     Name length L 3 between the tip of the a tip of the first fitting portion externally threaded portion is greater than the length L 4 between the rear end of the tip and the female screw portion of the female screw portion The compressor device according to claim 2 or 3, which is configured to be.
  5. 　前記第１嵌合部又は前記第２嵌合部の少なくとも一方は、径方向外側に向かって凸となる曲面状に形成されている
    請求項１乃至４の何れか一項に記載のコンプレッサ装置。     The compressor device according to any one of claims 1 to 4, wherein at least one of the first fitting portion and the second fitting portion is formed in a curved surface shape that is convex outward in the radial direction.
  6. 　前記シャフトの一端側に設けられた請求項１乃至５の何れか一項に記載のコンプレッサ装置と、
    　前記シャフトの他端側に固定され、排ガスによって回転するタービンホイールを含むタービン装置と、
    を備えた
    ターボチャージャ。     The compressor device according to any one of claims 1 to 5, which is provided on one end side of the shaft.
    A turbine device including a turbine wheel fixed to the other end of the shaft and rotated by exhaust gas,
    Turbocharger with.
PCT/JP2020/003235 2020-01-29 2020-01-29 Compressor device and turbocharger WO2021152742A1 (en)

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03210024A (en) * 1990-01-12 1991-09-13 Nissan Motor Co Ltd Compressor for turbo-charger
JP2002235547A (en) * 2001-02-09 2002-08-23 Shozo Shimizu Join method for turbine shaft for turbocharger
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 (en) * 2010-03-30 2011-10-20 Toyota Motor Corp Method for manufacturing turbine rotor
WO2018167892A1 (en) * 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 Supercharger

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03210024A (en) * 1990-01-12 1991-09-13 Nissan Motor Co Ltd Compressor for turbo-charger
JP2002235547A (en) * 2001-02-09 2002-08-23 Shozo Shimizu Join method for turbine shaft for turbocharger
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 (en) * 2010-03-30 2011-10-20 Toyota Motor Corp Method for manufacturing turbine rotor
WO2018167892A1 (en) * 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 Supercharger

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