Variable geometry turbocharger

Abstract

A variable geometry turbocharger (100) includes a bearing housing (10) including a bearing-housing side support portion (40) configured to support a radially outer portion (38) of a nozzle mount (16) from a side opposite to a scroll flow passage (4) in an axial direction of a turbine rotor (2), and wherein at least one of the following condition (a) or (b) is satisfied: (a) the bearing-housing side support portion (40) includes at least one bearing-housing side recess portion (46) formed so as to be recessed in the axial direction so as not to be in contact with the radially outer portion (38); (b) the radially outer portion (38) of the nozzle mount (16) includes at least one nozzle-mount side recess portion (62) formed so as to be recessed in the axial direction so as not to be in contact with the bearing-housing side support portion (40).

Claims

1. A variable geometry turbocharger, comprising: a turbine rotor; a turbine housing which accommodates the turbine rotor and which forms at least a part of a scroll flow passage through which exhaust gas to be supplied to the turbine rotor flows; a bearing housing accommodating a bearing which rotatably supports the turbine rotor, the bearing housing being coupled to the turbine housing; and a variable nozzle mechanism for adjusting a flow of exhaust gas to the turbine rotor from the scroll flow passage formed on a radially outer side of the turbine rotor, wherein the variable nozzle mechanism includes: a nozzle vane disposed in an exhaust gas flow passage for guiding the exhaust gas from the scroll flow passage to the turbine rotor; a nozzle mount having an annular shape and supporting the nozzle vane rotatably, the nozzle mount forming a flow passage wall on a bearing-housing side of the exhaust gas flow passage; and a nozzle plate having an annular shape and being disposed so as to face the nozzle mount, the nozzle plate forming a flow passage wall of the exhaust gas flow passage, wherein the bearing housing includes a bearing-housing side support portion configured to support a radially outer portion of the nozzle mount from a side opposite to the scroll flow passage in an axial direction of the turbine rotor, wherein the turbine housing includes a turbine-housing side support portion configured to support the radially outer portion of the nozzle mount from a side opposite to the bearing-housing side support portion in the axial direction, wherein the nozzle mount is nipped by the turbine-housing side support portion and the bearing-housing side support portion, wherein the turbine-housing side support portion is disposed so as to protrude toward an inner side of the bearing-housing side support portion in a radial direction of the turbine rotor, along a surface of the nozzle mount, wherein a radially inner end of the turbine-housing side support portion is positioned on an inner side of a radially inner end of the bearing-housing side support portion with respect to the radial direction, and wherein the turbine-housing side support portion includes a contact portion being in contact with the radially outer portion of the nozzle mount and a non-contact portion formed adjacent to an inner side of the contact portion with respect to the radial direction and facing the nozzle mount via a gap.

2. The variable geometry turbocharger according to claim 1, wherein the non-contact portion includes a step formed from the contact portion so as to provide the gap between the non-contact portion and the nozzle mount.

3. The variable geometry turbocharger according to claim 1, wherein an expression 0≤(r1−r3)/(r2−r3)≤0.75 is satisfied, where r1 is a distance between a radially inner end of the non-contact portion and a rotational axis of the turbine rotor, r2 is a distance between a radially outer end of the nozzle mount and the rotational axis, and r3 is a distance between the radially outer end of the nozzle mount and the rotational axis.

4. The variable geometry turbocharger according to claim 3, wherein an expression 0≤(r1−r3)/(r2−r3)≤0.30 is satisfied.

Description

BRIEF DESCRIPTION OF DRAWINGS

(1) FIG. 1 is a schematic cross-sectional view of a variable geometry turbocharger 100 according to an embodiment of the present invention, taken along the rotational axis O of the turbocharger 100.

(2) FIG. 2 is a schematic enlarged cross-sectional view of a variable geometry turbocharger 100 (100A) according to an embodiment.

(3) FIG. 3 is a perspective view of a bearing housing 10 of the variable geometry turbocharger 100 (100A) depicted in FIG. 2.

(4) FIG. 4 is a schematic diagram showing positions of a bearing-housing side recess portion 46 and a bolt 44 with respect to the circumferential direction.

(5) FIG. 5 is a schematic enlarged cross-sectional view of a variable geometry turbocharger 100 (100B) according to an embodiment.

(6) FIG. 6 is a diagram showing a relationship between a temporal change of the temperature of exhaust gas flowing through the scroll flow passage 4 (004) and a temporal change of the heat release amount (passage heat amount) from the radially outer portion 38 (038) of the nozzle mount (016) to the bearing-housing side support portion 40 (040), for each of the variable geometry turbocharger 200 according to a comparative embodiment shown in FIG. 13, the variable geometry turbocharger 100 (100A) shown in FIG. 2, and the variable geometry turbocharger 100 (100B) shown in FIG. 5.

(7) FIG. 7 is a schematic enlarged cross-sectional view of a variable geometry turbocharger 100 (100C) according to an embodiment.

(8) FIG. 8 is a schematic perspective view showing a configuration example of a heat shield member 60.

(9) FIG. 9 is a schematic enlarged cross-sectional view of a variable geometry turbocharger 100 (100D) according to an embodiment.

(10) FIG. 10 is a schematic enlarged cross-sectional view of a variable geometry turbocharger 100 (100E) according to an embodiment.

(11) FIG. 11 is a schematic enlarged cross-sectional view of a variable geometry turbocharger 100 (100F) according to an embodiment.

(12) FIG. 12 is a schematic enlarged cross-sectional view of a variable geometry turbocharger 100 (100G) according to an embodiment.

(13) FIG. 13 is a schematic enlarged cross-sectional view of a variable geometry turbocharger 200 according to a comparative embodiment.

DETAILED DESCRIPTION

(14) Embodiments of the present invention will now be described in detail with reference to the accompanying drawings. It is intended, however, that unless particularly identified, dimensions, materials, shapes, relative positions and the like of components described in the embodiments shall be interpreted as illustrative only and not intended to limit the scope of the present invention.

(15) For instance, an expression of relative or absolute arrangement such as “in a direction”, “along a direction”, “parallel”, “orthogonal”, “centered”, “concentric” and “coaxial” shall not be construed as indicating only the arrangement in a strict literal sense, but also includes a state where the arrangement is relatively displaced by a tolerance, or by an angle or a distance whereby it is possible to achieve the same function.

(16) For instance, an expression of an equal state such as “same” “equal” and “uniform” shall not be construed as indicating only the state in which the feature is strictly equal, but also includes a state in which there is a tolerance or a difference that can still achieve the same function.

(17) Further, for instance, an expression of a shape such as a rectangular shape or a cylindrical shape shall not be construed as only the geometrically strict shape, but also includes a shape with unevenness or chamfered corners within the range in which the same effect can be achieved.

(18) On the other hand, an expression such as “comprise”, “include”, “have”, “contain” and “constitute” are not intended to be exclusive of other components.

(19) FIG. 1 is a schematic cross-sectional view of a variable geometry turbocharger 100 according to an embodiment of the present invention, taken along the rotational axis O of the turbocharger 100.

(20) The variable geometry turbocharger 100 includes a turbine rotor 2 disposed coaxially with a non-depicted compressor, a turbine housing 6 that houses the turbine rotor 2 and forms a scroll flow passage 4 on the radially outer side of the turbine rotor 2, a bearing housing 10 housing a bearing 8 supporting the turbine rotor 2 rotatably and being coupled to the turbine housing 6, and a variable nozzle mechanism 12 disposed between the turbine housing 6 and the bearing housing 10, for adjusting the flow of exhaust gas from the scroll flow passage 4 to the turbine rotor 2.

(21) Hereinafter, unless otherwise stated, the axial direction of the turbine rotor 2 is referred to as merely “axial direction”, and the radial direction of the turbine rotor 2 is referred to as merely “radial direction”, and the circumferential direction of the turbine rotor 2 is referred to as merely “circumferential direction”.

(22) The variable nozzle mechanism 12 includes a plurality of nozzle vanes 14, a nozzle mount 16, a nozzle plate 18, a plurality of lever plates 20, a drive ring 22, and a plurality of nozzle supports 24.

(23) The plurality of nozzle vanes 14 are disposed at intervals in the circumferential direction, in an exhaust gas flow passage 26 having an annular shape for introducing exhaust gas from the scroll flow passage 4 to the turbine rotor 2.

(24) The nozzle mount 16 is an annular plate disposed on the radially outer side of the turbine rotor 2, and forms a flow passage wall 28 on the side of the bearing housing 10, of the exhaust gas flow passage 26. The nozzle mount 16 is provided with a plurality of support holes 30 (through holes) for rotatably supporting the respective shaft portions 15 of the plurality of nozzle vanes 14.

(25) The nozzle plate 18 is an annular plate disposed on the radially outer side of the turbine rotor 2 so as to face the nozzle mount 16, and forms a flow passage wall 32 on the opposite side to the bearing housing 10, of the exhaust gas flow passage 26. Further, the nozzle plate 18 forms, on the downstream side of the flow passage wall 32, a shroud wall 34 facing the tip-side ends of the blades of the turbine rotor 2 via a gap. The nozzle mount 16 and the nozzle plate 18 are coupled by a plurality of nozzle supports 24.

(26) A back plate 23 is disposed between the back face of the turbine rotor 2 and the bearing housing 10, so that exhaust gas flowing from the exhaust gas flow passage 26 to the turbine rotor 2 does not leak toward the back side of the nozzle mount 16 (opposite to the exhaust gas flow passage 26) through the radially inner side of the nozzle mount 16. The back plate 23 is in contact with the nozzle mount 16 at one end side in the axial direction, and is in contact with the bearing housing 10 at the other end side in the axial direction.

(27) In the variable nozzle mechanism 12 described above, the drive ring 22 is rotary driven by a driving force transmitted from a non-depicted actuator. When the drive ring 22 rotates, the lever plates 20 being in engagement with the drive ring 22 rotate the shaft portions 15 of the nozzle vanes 14, and as a result, the nozzle vanes 14 rotate to change the vane angle of the nozzle vanes 14, thereby adjusting the flow of exhaust gas from the scroll flow passage 4 to the turbine rotor 2.

(28) In the depicted embodiment, an annular space 36 housing the lever plate 20 and the drive ring 22 is formed between the bearing housing 10 and the nozzle mount 16.

(29) The bearing housing 10 includes a bearing-housing side support portion 40 having an annular shape and supporting the radially outer portion 38 of the nozzle mount 16 from the opposite side to the scroll flow passage 4 in the axial direction of the turbine rotor 2. The bearing-housing side support portion 40 is formed on the radially outer side of the annular space 36. On the radially outer side of the bearing-housing side support portion 40, a seal ring 41 is disposed between the turbine housing 6 and the bearing housing, and the seal ring 41 prevents leakage of exhaust gas from between the bearing housing 10 and the turbine housing 6.

(30) The turbine housing 6 includes a turbine-housing side support portion 42 having an annular shape and supporting the radially outer portion 38 of the nozzle mount 16 from the opposite side to the bearing-housing side support portion 40 in the axial direction.

(31) The nozzle mount 16 is held between the bearing-housing side support portion 40 and the turbine-housing side support portion 42. In the depicted embodiment, the turbine housing 6 and the bearing housing 10 are fastened in the axial direction by a plurality of bolts 44 disposed at intervals in the circumferential direction, and the nozzle mount 16 is held between the bearing-housing side support portion 40 and the turbine-housing side support portion 42 by the axial force of the bolts 44.

(32) FIG. 2 is a schematic enlarged cross-sectional view of a configuration example 100 (100A) of a variable geometry turbocharger 100 (100A). FIG. 3 is a perspective view of a bearing housing 10 of the variable geometry turbocharger 100 (100A) depicted in FIG. 2.

(33) In an embodiment, as shown in FIGS. 2 and 3, the bearing-housing side support portion 40 includes at least one bearing-housing side recess portion 46 formed so as to be recessed opposite to the nozzle mount 16 in the axial direction. In the depicted embodiment, the bearing-housing side support portion 40 includes a plurality of bearing-housing side recess portions 46 disposed at intervals in the circumferential direction.

(34) According to the above configuration, with the bearing-housing side recess portions 46, it is possible to reduce the contact area between the bearing-housing side support portion 40 and the radially outer portion 38 of the nozzle mount 16, and to reduce the heat release amount from the radially outer portion 38 of the nozzle mount 16 to the bearing housing 10, through the heat insulating effect of an air layer 39 between the bearing-housing side recess portion 46 and the radially outer portion 38 of the nozzle mount 16. Accordingly, it is possible to reduce heat loss due to heat release from the radially outer portion 38 of the nozzle mount 16 to the bearing housing 10, and improve the turbine efficiency and the performance of the turbocharger 100.

(35) Further, it is possible to suppress a decrease in the exhaust gas temperature of the turbine outlet side. Thus, in a case where a catalyst for purifying exhaust gas is disposed on the downstream side of the turbine, it is possible to suppress performance deterioration of the catalyst due to the temperature decrease of the catalyst, and reduce content of impurity substances (e.g. NOx and SOx) in the exhaust gas.

(36) FIG. 4 is a schematic diagram showing positions of a bearing-housing side recess portion 46 and a bolt 44 with respect to the circumferential direction.

(37) In an embodiment, as shown in FIG. 4, with respect to the circumferential direction, each of the bearing-housing side recess portions 46 is formed in an angular range Ar that does not overlap with the center position Pv of a bolt 44 adjacent to the bearing-housing side recess portion 46, of the plurality of bolts 44.

(38) Accordingly, for the center position Pv and the angular range Ar do not overlap with each other, it is possible to reduce heat loss due to heat release from the radially outer portion 38 of the nozzle mount 16 to the bearing housing 10 while ensuring a fastening force between the bearing housing 10 and the turbine housing 6 achieved by the bolts 44.

(39) In an embodiment, as shown in FIG. 4, each of the bearing-housing side recess portions 46 is five degrees or more apart from the center position of the bolt 44 adjacent to the bearing-housing side recess portion 46, of the plurality of bolts 44. That is, the angle α shown in FIG. 4 is not smaller than five degrees.

(40) Accordingly, it is possible to reduce heat loss due to heat release from the radially outer portion 38 of the nozzle mount 16 to the bearing housing 10 while ensuring a strong fastening force between the bearing housing 10 and the turbine housing 6 achieved by the bolts 44.

(41) FIG. 5 is a schematic enlarged cross-sectional view of a configuration example 100 (100B) of a variable geometry turbocharger 100.

(42) In an embodiment, as shown in FIG. 5, the turbine-housing side support portion 42 is disposed so as to protrude inward in the radial direction from the bearing-housing side support portion 40 along the surface 48 of the radially outer portion 38 of the nozzle mount 16 (surface on the side of the scroll flow passage 4). That is, the radially inner end 54 of the turbine-housing side support portion 42 is positioned on the inner side of the radially inner end 59 of the bearing-housing side support portion 40 with respect to the radial direction.

(43) Typically, as shown in FIG. 13, to nip the nozzle mount 016 with a simple structure, the radially inner end 054 of the turbine-housing side support portion 42 is positioned on the same position as the radially inner end 059 of the bearing-housing side support portion 040 with respect to the radial direction.

(44) In contrast, in the configuration shown in FIG. 5, the turbine-housing side support portion 42 is disposed so as to protrude inward in the radial direction from the bearing-housing side support portion 40 along the surface 48 of the nozzle mount 16, and thus it is possible to increase the area of the nozzle mount 16 covered with the turbine-housing side support portion 42 compared to that in a typical structure shown in FIG. 13. Thus, it is possible to reduce the area of a portion of the nozzle mount 16 exposed to a high-temperature exhaust gas flow from the scroll flow passage 4 to the exhaust gas flow passage 26 (heat transfer area). Accordingly, the heat absorption amount of the nozzle mount 16 reduces, and thus an increase in the metal temperature of the nozzle mount 16 is suppressed. Accordingly, the temperature difference between the nozzle mount 16 and the bearing housing 10 becomes small, and thus it is possible to reduce heat loss due to heat release from the radially outer portion 38 of the nozzle mount 16 to the bearing housing 10, and improve the turbine efficiency and the performance of the turbocharger 100.

(45) Further, it is possible to suppress a decrease in the exhaust gas temperature of the turbine outlet side. Thus, in a case where a catalyst for purifying exhaust gas is disposed on the downstream side of the turbine, it is possible to suppress performance deterioration of the catalyst due to the temperature decrease of the catalyst, and reduce content of impurity substances (e.g. NOx and SOx) in the exhaust gas.

(46) In an embodiment, as shown in FIG. 5, the turbine-housing side support portion 42 includes a contact portion 50 being in contact with the radially outer portion 38 of the nozzle mount 16 and a non-contact portion 52 formed on the inner side of the contact portion 50 with respect to the radial direction and facing the nozzle mount 16 via a gap g. In the depicted embodiment, the non-contact portion 52 includes a step formed from the contact portion 50 so as to provide the gap g between the non-contact portion 52 and the nozzle mount 16.

(47) With the above configuration, the turbine-housing side support portion 42 has the non-contact portion 52 on the inner side of the contact portion 50 with respect to the radial direction, and thus it is possible to cover the radially outer portion 38 of the nozzle mount 16 with the turbine-housing side support portion 42 while suppressing an increase in the contact area between the bearing-housing side support portion 40 and the radially outer portion 38 of the nozzle mount 16. Accordingly, it is possible to reduce the area of a portion of the nozzle mount 16 exposed to a high-temperature exhaust gas flow from the scroll flow passage 4 to the exhaust gas flow passage 26 (heat transfer area), and suppress an increase in the heat input amount to the radially outer portion 38 of the nozzle mount 16 from the turbine-housing side support portion 42. Accordingly, it is possible to suppress an increase in the metal temperature of the nozzle mount 16 effectively, and reduce heat loss due to heat release from the radially outer portion 38 of the nozzle mount 16 to the bearing housing 10 effectively.

(48) In an embodiment, as shown in FIG. 5, an expression 0≤(r1−r3)/(r2−r3)≤0.75 is satisfied, where r1 is the distance between the radially inner end 54 of the turbine-housing side support portion 42 and the rotational axis O of the turbine rotor 2, r2 is the distance between the radially outer end 64 of the nozzle mount 16 and the rotational axis O, and r3 is the distance between the radially outer end of the nozzle mount and the rotational axis. In the depicted embodiment, an expression 0≤(r1−r3)/(r2−r3)≤0.30 is satisfied.

(49) With the above configuration, it is possible to suppress an increase in the metal temperature of the nozzle mount 16 effectively, and reduce heat loss due to heat release from the radially outer portion 38 of the nozzle mount 16 to the bearing housing 10 effectively, without interfering a smooth flow in the exhaust gas flow passage 26 between the nozzle mount 16 and the nozzle plate 18.

(50) Further, the bearing housing 10 in the embodiment depicted in FIG. 5 has the same configuration as the bearing housing 10 in the embodiment depicted in FIGS. 2 and 3, and thus the same reference numerals are used to avoid repeating the same description.

(51) FIG. 6 is a diagram showing a relationship between a temporal change of the temperature of exhaust gas flowing through the scroll flow passage 4 (004) and a temporal change of the heat release amount (passage heat amount) from the radially outer portion 38 (038) of the nozzle mount (016) to the bearing-housing side support portion 40 (040), for each of the variable geometry turbocharger 200 according to a comparative embodiment shown in FIG. 13, the variable geometry turbocharger 100 (100A) shown in FIG. 2, and the variable geometry turbocharger 100 (100B) shown in FIG. 5. In FIG. 6, the solid line indicates the temporal change of the exhaust gas temperature that is common in the respective embodiments, while the dotted line indicates the temporal change of the heat release amount in the variable geometry turbocharger 200 according to a comparative embodiment. Further, the single-dotted chain line indicates the temporal change of the heat release amount in the variable geometry turbocharger 100 (100A), while the double-dotted chain line indicates the temporal change of the heat release amount in the variable geometry turbocharger 100 (100B).

(52) As shown in FIG. 6, with the variable geometry turbocharger 100 (100A) depicted in FIG. 2, it is possible to reduce the heat release amount (heat passage amount) from the radially outer portion 38 (038) of the nozzle mount (016) to the bearing-housing side support portion 40 (040), compared to the variable geometry turbocharger 200 according to the comparative embodiment. According to estimation of the present inventors, with the variable geometry turbocharger 100 (100A), it is possible to reduce heat loss by approximately 47% compared to the variable geometry turbocharger 200.

(53) Furthermore, as shown in FIG. 6, with the variable geometry turbocharger 100 (100B) depicted in FIG. 5, it is possible to reduce the heat release amount (heat passage amount) from the radially outer portion 38 (038) of the nozzle mount (016) to the bearing-housing side support portion 40 (040), compared to the variable geometry turbocharger 200 according to the comparative embodiment. According to estimation of the present inventors, with the variable geometry turbocharger 100 (100B), it is possible to reduce heat loss by approximately 57% compared to the variable geometry turbocharger 200.

(54) FIG. 7 is a schematic enlarged cross-sectional view of a configuration example 100 (100C) of the variable geometry turbocharger 100.

(55) In an embodiment, as shown in FIG. 7, a heat shield member 60 is disposed between the bearing-housing side support portion 40 and the nozzle mount 16.

(56) With the above configuration, through the heat shield effect of the heat shield member 60, it is possible to reduce the heat release amount from the radially outer portion 38 of the nozzle mount 16 to the bearing housing 10. Accordingly, it is possible to reduce heat loss due to heat release from the radially outer portion 38 of the nozzle mount 16 to the bearing housing 10, and improve the turbine efficiency and the performance of the turbocharger 100. Further, it is possible to suppress a decrease in the exhaust gas temperature of the turbine outlet side. Thus, in a case where a catalyst for purifying exhaust gas is disposed on the downstream side of the turbine, it is possible to suppress performance deterioration of the catalyst due to the temperature decrease of the catalyst, and reduce content of impurity substances (e.g. NOx and SOx) in the exhaust gas.

(57) In an embodiment, in the variable geometry turbocharger 100 (100C) depicted in FIG. 7, the thermal conductivity of the heat shield member 60 is smaller than each of the thermal conductivity of the bearing housing 10 and the thermal conductivity of the nozzle mount 16.

(58) With the above configuration, it is possible to reduce the heat release amount from the radially outer portion 38 of the nozzle mount 16 to the bearing housing 10 effectively.

(59) In an embodiment, in the variable geometry turbocharger 100 (100C) depicted in FIG. 7, the heat shield member 60 is formed of austenitic stainless steel or nickel-based alloy. It is preferable to use an austenitic stainless steel other than SUS 304, for example, Cr-10Ni-6Mn-1Mo for boiler tubes. As a nickel-based alloy, the following can be used suitably: Incoloy 800 (Ni-45Fe-21Cr-0.4Ti), Inconel 600 (Ni-16Cr-6Fe), Inconel X-750 (Ni-15Cr-7Fe-2.5Ti-0.6Al-0.8Nb), Hastelloy C (Ni-16Mo-15Cr-4W-5Fe), or Nimonic 90 (Ni-20Cr-17Co-2.4Ti-1.4Al). Further, the heat shield member 60 may be formed of 25Cr-20Ni anti-heat cast steel (equivalent to SUS 310) and 35Ni-15Cr anti-heat cast steel (equivalent to SUS 330). It should be noted that Incoloy, Inconel, Hastelloy, and Nimonic are trademarks.

(60) With the above configuration, it is possible to reduce the heat release amount from the radially outer portion 38 of the nozzle mount 16 to the bearing housing 10 effectively, while ensuring the heat resistance performance of the heat shield member 60 itself.

(61) In an embodiment, in the variable geometry turbocharger 100 (100C) depicted in FIG. 7, the heat shield member 60 may be a ring-shaped heat shield plate (see FIG. 8) disposed so that the bearing-housing side support portion 40 and the nozzle mount 16 do not make contact with each other over the entire angular range in the circumferential direction.

(62) With the above configuration, it is possible to reduce the heat release amount from the radially outer portion 38 of the nozzle mount 16 to the bearing housing 10 through a simple configuration.

(63) In an embodiment, in the variable geometry turbocharger 100 (100C) depicted in FIG. 7, the heat shield member 60 may be a coating applied to the radially outer portion 38 of the nozzle mount 16 or the bearing housing 10 so that the bearing-housing side support portion 40 and the nozzle mount 16 do not make contact with each other over the entire angular range in the circumferential direction.

(64) With the above configuration, it is possible to reduce the heat release amount from the radially outer portion 38 of the nozzle mount 16 to the bearing housing 10 through a simple configuration.

(65) Embodiments of the present invention were described in detail above, but the present invention is not limited thereto, and various amendments and modifications may be implemented.

(66) For instance, in the variable geometry turbocharger 100 (100A) described with reference to FIGS. 2 to 4, the bearing-housing side support portion 40 includes a bearing-housing side recess portion 46 formed so as to be recessed opposite to the nozzle mount 16. Nevertheless, the present invention is not limited to the above embodiment, and as depicted in FIG. 9 for instance, the radially outer portion 38 of the nozzle mount 16 may include at least one nozzle-mount side recess portion 62 formed so as to be recessed opposite to the bearing housing 10 in the axial direction.

(67) Also with the above configuration, with the nozzle-mount side recess portions 62, it is possible to reduce the contact area between the bearing-housing side support portion 40 and the radially outer portion 38 of the nozzle mount 16, and to reduce the heat release amount from the radially outer portion 38 of the nozzle mount 16 to the bearing housing 10, through the heat insulating effect of the air layer 39 between the nozzle-mount side recess portion 62 and the bearing-housing side support portion 40. Accordingly, it is possible to reduce heat loss due to heat release from the radially outer portion 38 of the nozzle mount 16 to the bearing housing 10, and improve the turbine efficiency and the performance of the turbocharger 100. Furthermore, the preferable arrangement of the nozzle-mount side recess portion 62 in the circumferential direction is similar to the preferable arrangement of the bearing-housing side recess portion 46 in the circumferential direction described above with reference to FIGS. 3 and 4.

(68) Further, in the embodiment shown in FIGS. 2 and 3, the bearing-housing side recess portion 46 is formed from the radially inner side to the radially outer side of the bearing-housing side support portion 40. Nevertheless, the formation range of the bearing-housing side recess portion 46 in the radial direction is not limited this. For instance, the bearing-housing side recess portion 46 may be formed only on the radially inner side of the bearing-housing side support portion 40 as depicted in FIG. 10, only on the radially outer side of the bearing-housing side support portion 40 as depicted in FIG. 11, or only in the center of the bearing-housing side support portion 40 with respect to the radial direction. Furthermore, also in the embodiment shown in FIGS. 10 to 12, the preferable arrangement of the bearing-housing side recess portion 46 in the circumferential direction is similar to the preferable arrangement of the bearing-housing side recess portion 46 described above with reference to FIGS. 3 and 4. Further, the respective embodiments depicted in FIGS. 9 to 12 can be applied to the respective embodiments described with reference to FIGS. 1 to 8.

DESCRIPTION OF REFERENCE NUMERALS

(69) 2 Turbine rotor 4 Scroll flow passage 6 Turbine housing 8 Bearing 10 Bearing housing 12 Variable nozzle mechanism 14 Nozzle vane 15 Shaft portion 16 Nozzle mount 18 Nozzle plate 20 Lever plate 22 Drive ring 23 Back plate 24 Nozzle support 26 Exhaust gas flow passage 28 Flow passage wall 30 Support hole 32 Flow passage wall 34 Shroud wall 36 Annular space 38 Radially outer portion 39 Air layer 40 Bearing-housing side support portion 41 Seal ring 42 Turbine-housing side support portion 44 Bolt 46 Bearing-housing side recess portion 48 Surface 50 Contact portion 52 Non-contact portion 54 Radially inner end 59 Radially inner end 60 Heat shield member 62 Nozzle-mount side recess portion 64 Radially outer end 100 (100A to 199G) Variable geometry turbocharger 200 Variable geometry turbocharger Ar Angular range H Arrow O Rotational axis Pv Center position g Gap