Supercharger

Abstract

A supercharger is provided with: a turbine wheel; a turbine housing including a flow path through which the gas received from the inlet flows; a variable capacity mechanism that is disposed in the turbine housing, receives gas from the flow path, and guides the gas to the turbine wheel; and a coil spring that applies, to the variable capacity mechanism, a biasing force that presses the variable capacity mechanism against the turbine housing. The turbine housing has a turbine housing flange back surface in contact with the variable capacity mechanism in the direction of the rotational axis of the turbine wheel. The variable capacity mechanism has a nozzle ring outer flange main surface that is in contact with the turbine housing flange back surface in the direction of the rotational axis. At least one of the back surface of the turbine housing flange and the main surface of the nozzle ring outer flange is processed so as to increase the coefficient of friction.

Description

Technical Field

[0001] The present disclosure relates to superchargers. Background Art

[0002] Patent Document 1 discloses a variable capacity supercharger. The variable capacity supercharger includes a variable capacity mechanism. The variable capacity mechanism changes the flow path area of ​​the gas through a plurality of nozzle vanes. As a result, the flow rate of the gas supplied to the turbine impeller is controlled.

[0003] Patent Document 1: International Publication No. 2017 / 150450

[0004] Among the multiple components constituting the supercharger, the components that are not intended to be driven are fixed so as not to move relative to each other. However, when the supercharger is in operation, the degree of fixation may become loose due to the influence of thermal deformation of the components, etc. If the degree of fixation becomes loose, the components may slightly move relative to each other due to external forces. Summary of the invention

[0005] The present disclosure describes a supercharger capable of suppressing the occurrence of relative micro-motions between components.

[0006] A supercharger of one embodiment of the present disclosure comprises: a turbine impeller; a first housing including a flow path for the flow of gas received from an inlet; a variable capacity mechanism disposed on the first housing and receiving gas from the flow path and guiding it to the turbine impeller; and a force applying member that applies a force to the variable capacity mechanism to press the variable capacity mechanism against the first housing. The first housing comprises: a first housing abutment surface that contacts the variable capacity mechanism along the direction of the rotation axis of the turbine impeller. The variable capacity mechanism comprises: a first variable capacity mechanism abutment surface that contacts the first housing abutment surface along the direction of the rotation axis. Processing to increase the friction coefficient is performed on at least one of the first housing abutment surface and the first variable capacity mechanism abutment surface.

[0007] The supercharger of the present disclosure can suppress the occurrence of micro-movements of components relative to each other. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] Figure 1 It is a cross-sectional view showing a supercharger according to the embodiment.

[0009] Figure 2 Yes means Figure 1 A three-dimensional view of the variable capacity mechanism shown.

[0010] Figure 3 It is a magnified representation Figure 1 FIG. 2 is a diagram showing a portion where the turbine housing abuts against the variable displacement mechanism.

[0011] Figure 4 It is a magnified representation Figure 1A diagram showing the main parts of the heat shield, variable capacity mechanism, and bearing housing. DETAILED DESCRIPTION

[0012] A supercharger of one embodiment of the present disclosure comprises: a turbine impeller; a first housing including a flow path for the flow of gas received from an inlet; a variable capacity mechanism disposed on the first housing and receiving gas from the flow path and guiding it to the turbine impeller; and a force applying member that applies a force to the variable capacity mechanism to press the variable capacity mechanism against the first housing. The first housing comprises: a first housing abutment surface that contacts the variable capacity mechanism along the direction of the rotation axis of the turbine impeller. The variable capacity mechanism comprises: a first variable capacity mechanism abutment surface that contacts the first housing abutment surface along the direction of the rotation axis. Processing to increase the friction coefficient is performed on at least one of the first housing abutment surface and the first variable capacity mechanism abutment surface.

[0013] In the portion where the first housing and the variable capacity mechanism abut, a friction force corresponding to the force generated by the force-applying component and the friction coefficient is generated. Processing to increase the friction coefficient is performed on at least one of the abutting surface of the first housing and the abutting surface of the first variable capacity mechanism. Therefore, the friction force determined by the product of the friction coefficient and the force can be increased. The friction force can suppress the generation of relative micro-motion generated between the first housing and the variable capacity mechanism. Therefore, the generation of relative micro-motion between the components can be suppressed.

[0014] The supercharger further comprises: a second housing that rotatably supports the rotating shaft to which the turbine impeller is fixed; and an annular intermediate component that is arranged between the first housing and the variable capacity mechanism. The variable capacity mechanism comprises: a first arrangement hole for inserting the turbine impeller or the rotating shaft, and a second variable capacity mechanism abutment surface surrounding the first arrangement hole. The intermediate component comprises: a first intermediate component abutment surface that contacts the second variable capacity mechanism abutment surface. Processing to increase the friction coefficient may also be performed on at least one of the second variable capacity mechanism abutment surface and the first intermediate component abutment surface. According to this structure, the generation of relative micro-motion between the variable capacity mechanism and the intermediate component can be suppressed.

[0015] The supercharger further comprises: a second housing, which supports the rotating shaft to which the turbine impeller is fixed so as to be rotatable; and an annular intermediate component, which is arranged between the first housing and the variable capacity mechanism. The intermediate component comprises: a second intermediate component abutment surface which is opposite to the second housing and in contact with the force-applying component. The force-applying component comprises: a first force-applying component abutment surface in contact with the second intermediate component abutment surface. Processing to increase the friction coefficient may also be performed on at least one of the second intermediate component abutment surface and the first force-applying component abutment surface. According to this structure, the generation of relative micro-motion between the force-applying component and the intermediate component can be suppressed.

[0016] The supercharger further includes a second housing that rotatably supports the rotating shaft to which the turbine impeller is fixed. The second housing includes a second housing abutment surface that the force member contacts along the direction of the rotation axis. The force member includes a second force member abutment surface that contacts the second housing abutment surface. Processing to increase the friction coefficient may also be performed on at least one of the second housing abutment surface and the second force member abutment surface. According to this structure, the generation of relative micro-motion between the force member and the second housing can be suppressed.

[0017] The supercharger further includes a second housing that rotatably supports a rotating shaft to which a turbine impeller is fixed. The variable capacity mechanism includes: a first configuration hole for inserting the turbine impeller or the rotating shaft. The first configuration hole includes: an inner peripheral surface portion of the first configuration hole for configuring a second housing shoulder portion of the second housing. The second housing shoulder portion includes: a second housing shoulder surface that contacts the inner peripheral surface portion of the first configuration hole. Processing to increase the friction coefficient may also be performed on at least one of the inner peripheral surface portion of the first configuration hole and the second housing shoulder surface. According to this structure, the generation of relative micro-motion between the variable capacity mechanism and the second housing can be suppressed.

[0018] A supercharger of another embodiment of the present disclosure includes: a turbine impeller; a first housing including a flow path for the flow of gas received from the inlet; a variable capacity mechanism disposed in the first housing and receiving gas from the flow path and guiding the gas to the turbine impeller, the variable capacity mechanism including: a disk-shaped nozzle ring having a main surface facing the turbine impeller, and a plurality of nozzle blades disposed on the main surface side of the nozzle ring and forming a plurality of nozzle flow paths for guiding the gas; and a force member that applies a force to the variable capacity mechanism to press the variable capacity mechanism against the first housing. The first housing includes: a first housing abutment surface that contacts the variable capacity mechanism along the direction of the rotation axis of the turbine impeller. The variable capacity mechanism includes: a first variable capacity mechanism abutment surface that contacts the first housing abutment surface along the direction of the rotation axis. The nozzle ring includes: a separation surface that is separated from a first component different from the nozzle ring, and a sliding surface that slides on a second component different from the nozzle ring. The surface roughness of at least one of the first housing abutment surface and the first variable capacity mechanism abutment surface is greater than the surface roughness of the separation surface.

[0019] In the portion where the first housing abuts against the variable capacity mechanism, a friction force corresponding to the force and friction coefficient generated by the force-applying member is generated. The surface roughness of at least one of the abutting surface of the first housing and the abutting surface of the first variable capacity mechanism is greater than the surface roughness of the separation surface. Therefore, the friction force determined by the product of the friction coefficient corresponding to the surface roughness and the force can be increased. The friction force can suppress the generation of relative micromotion generated between the first housing and the variable capacity mechanism. Therefore, the generation of relative micromotion between the components can be suppressed.

[0020] In the supercharger, the surface roughness of at least one of the first housing contact surface and the first variable displacement mechanism contact surface may be greater than the surface roughness of the sliding surface. This configuration can also suppress the occurrence of micro-motion between components.

[0021] In the supercharger, the first component is the first housing. The separation surface may be an outer peripheral surface of the nozzle ring that faces the inner peripheral surface of the first housing and is separated from the inner peripheral surface of the first housing. This structure can also suppress the occurrence of relative micro-movement of the components.

[0022] In the above-mentioned supercharger, the second component is a nozzle vane. The sliding surface may also be a main surface of a nozzle ring on which a plurality of nozzle vanes slide. With this structure, it is also possible to suppress the occurrence of micro-movements between components relative to each other.

[0023] Hereinafter, the embodiment of the supercharger for implementing the present disclosure will be described in detail with reference to the drawings. In the description of the drawings, the same elements are denoted by the same reference numerals, and duplicate descriptions are omitted.

[0024] Figure 1 The supercharger 1 shown is a variable capacity supercharger. The supercharger 1 is applied to an internal combustion engine of a ship or a vehicle, for example. The supercharger 1 has a turbine 10 and a compressor 20. The turbine 10 has a turbine housing 11 (first housing), a turbine impeller 12, and a variable capacity mechanism 30. The turbine housing 11 has a vortex flow path 13 (flow path). The vortex flow path 13 extends circumferentially around the turbine impeller 12. The compressor 20 has a compressor housing 21 and a compressor impeller 22. The compressor impeller 22 is housed in the compressor housing 21. The compressor housing 21 has a vortex flow path 23. The vortex flow path 23 extends circumferentially around the compressor impeller 22.

[0025] The turbine impeller 12 is provided at the first end of the rotating shaft 2. The compressor impeller 22 is provided at the second end of the rotating shaft 2. A bearing housing 3 (second housing) is provided between the turbine housing 11 and the compressor housing 21. The rotating shaft 2 is rotatably supported by the bearing housing 3 via the bearing 4. The rotating shaft 2, the turbine impeller 12, and the compressor impeller 22 constitute an integrated rotating body 5. The rotating body 5 rotates around the rotation axis AX.

[0026] The turbine housing 11 has an inlet 14s and an outlet 14r. Exhaust gas discharged from the internal combustion engine flows into the turbine housing 11 through the inlet 14s. The inflowing exhaust gas flows into the turbine impeller 12 through the swirl flow path 13. The exhaust gas rotates the turbine impeller 12. Thereafter, the exhaust gas flows out to the outside of the turbine housing 11 through the outlet 14r.

[0027] The compressor housing 21 has an inlet 24 and an outlet. When the turbine impeller 12 rotates, the compressor impeller 22 rotates via the rotating shaft 2. The rotating compressor impeller 22 sucks in external air through the inlet 24. The sucked air passes through the compressor impeller 22 and the vortex flow path 23 and is compressed. The air is discharged from the outlet as compressed air. The compressed air is supplied to the internal combustion engine.

[0028] The turbine 10 has a connecting flow path S. The connecting flow path S guides the exhaust gas from the vortex flow path 13 to the turbine impeller 12. A plurality of nozzle blades 34 are arranged in the connecting flow path S. The plurality of nozzle blades 34 are arranged at equal intervals on a reference circle centered on the rotation axis AX. The mutually adjacent nozzle blades 34 constitute a nozzle. The nozzle blades 34 rotate synchronously around an axis parallel to the rotation axis AX. The cross-sectional area of ​​the connecting flow path S is adjusted by rotating the plurality of nozzle blades 34. As a mechanism for adjusting the cross-sectional area of ​​the connecting flow path S, the turbine 10 has a variable capacity mechanism 30. The variable capacity mechanism 30 is mounted on the turbine housing 11.

[0029] <Variable capacity mechanism>

[0030] like Figure 1 and Figure 2 As shown, the variable capacity mechanism 30 has a CC plate 31 (Clearance Control Plate), a nozzle ring 32, and a plurality of CC pins 33 (Clearance Control Pins). The nozzle ring 32 faces the CC plate 31. The CC pins 33 connect the CC plate 31 and the nozzle ring 32. A connecting flow path S is formed between the CC plate 31 and the nozzle ring 32. The variable capacity mechanism 30 has a plurality of nozzle blades 34, a drive ring 35, a plurality of nozzle link plates 36, and a drive link plate 37. The nozzle link plate 36 and the drive link plate 37 are arranged on the side opposite to the CC plate 31 relative to the nozzle ring 32. The drive ring 35 and the drive link plate 37 cooperate to rotate the nozzle link plate 36. If the nozzle link plate 36 rotates, the nozzle blades 34 rotate.

[0031] The shape of the CC plate 31 is annular with the rotation axis AX as the center. The CC plate 31 has an axial hole. The CC plate 31 circumferentially surrounds the turbine impeller 12 arranged in the axial hole 31h. The circumferential direction of the turbine impeller 12 refers to the direction centered on the rotation axis AX. The CC plate 31 is arranged between the vortex flow path 13 and the outflow port 14r. The CC plate 31 is separated from the nozzle ring 32 along the rotation axis AX. A connecting flow path S is formed between the CC plate 31 and the nozzle ring 32. The connecting flow path S connects the vortex flow path 13 and the outflow port 14r. The CC plate 31 is arranged on the opposite side of the bearing housing 3 relative to the nozzle ring 32. The CC plate 31 has a plurality of pin holes 31p. The circumferential intervals of the plurality of pin holes 31p are equal to each other.

[0032] The shape of the nozzle ring 32 is also annular with the rotation axis AX as the center. The nozzle ring 32 has a nozzle ring axial hole 32h. The nozzle ring 32 also surrounds the turbine impeller 12 arranged in the nozzle ring axial hole 32h in the circumferential direction. The nozzle ring 32 is also arranged between the vortex flow path 13 and the outflow port 14r. The CC plate 31 is parallel to the nozzle ring 32. The nozzle ring 32 has a plurality of pin holes 32p. The circumferential spacing of the plurality of pin holes 32p is equal to each other. The central axis of the pin hole 32p overlaps the central axis of the pin hole 31p. In other words, the pin hole 32p is coaxial with the pin hole 31p.

[0033] The nozzle ring 32 includes a nozzle ring body 32a and a drive ring support portion 32b. The nozzle ring body 32a is cylindrical in shape. The nozzle ring body 32a includes a nozzle ring shaft hole 32h. The nozzle ring body 32a includes a plurality of blade shaft holes 32c. The plurality of blade shaft holes 32c are spaced equally in the circumferential direction. The drive ring support portion 32b protrudes radially from the outer peripheral surface of the nozzle ring body 32a. The outer diameter of the nozzle ring 32 is determined by the outer diameter of the drive ring support portion 32b. The drive ring support portion 32b includes a plurality of pin holes 32p. The position of the pin hole 32p is located radially outside the nozzle ring 32 than the position of the blade shaft hole 32c.

[0034] The nozzle ring 32 is separated from the CC plate 31. A gap is formed between the nozzle ring 32 and the CC plate 31. The gap is a connecting flow path S through which the exhaust gas passes. The gap between the nozzle ring 32 and the CC plate 31 is maintained by the CC pin 33. The first end of the CC pin 33 is inserted into the pin hole 31p of the CC plate 31. The second end of the CC pin 33 is inserted into the pin hole 32p of the nozzle ring 32.

[0035] A plurality of nozzle blades 34 are arranged on a reference circle centered on the rotation axis AX. The nozzle blade 34 has a blade body 34a and a blade shaft 34b. The blade body 34a is arranged between the CC plate 31 and the nozzle ring 32. The blade body 34a is arranged in the connecting flow path S. The first end of the blade shaft 34b is fixed to the blade body 34a. The second end of the blade shaft 34b is inserted into the blade shaft hole 32c of the nozzle ring 32. The front end of the second end of the blade shaft 34b protrudes from the nozzle ring body 32a. The blade shaft 34b is rotatable relative to the nozzle ring 32. The blade body 34a rotates with the rotation of the blade shaft 34b. In the variable capacity mechanism 30, the cross-sectional area of ​​the connecting flow path S is adjusted by rotating the blade body 34a. As a result of adjusting the cross-sectional area, the flow rate of the exhaust gas supplied from the vortex flow path 13 to the turbine impeller 12 is controlled. Therefore, the rotation speed of the turbine impeller 12 can be controlled to a desired value.

[0036] The drive ring 35 is arranged on the drive ring support portion 32b. The shape of the drive ring 35 is annular with the rotation axis AX as the center. The drive ring 35 has an axial hole 35h. The nozzle ring body 32a is inserted into the axial hole 35h. The drive ring 35 is coaxial with the nozzle ring 32. The drive ring 35 can rotate relative to the nozzle ring 32 with the rotation axis AX as the center. The drive ring 35 has a drive ring body 35a and a plurality of link plate configuration portions 35b. The link plate configuration portions 35b are circumferentially spaced at equal intervals. The link plate configuration portion 35b has two rising parts separated from each other in the circumferential direction.

[0037] The nozzle link plate 36 is rod-shaped. The first end of the nozzle link plate 36 is fixed to the end of the blade shaft 34b. The second end of the nozzle link plate 36 is arranged at the link plate arrangement portion 35b of the drive ring 35. The second end of the nozzle link plate 36 is arranged between two rising parts of the link plate arrangement portion 35b. If the drive ring 35 receives a driving force from the drive link plate 37, the drive ring 35 rotates around the rotation axis AX. Through this rotation, the second end of the nozzle link plate 36 moves in the circumferential direction along with the rotation of the drive ring 35. As a result, the nozzle link plate 36 rotates around the blade shaft 34b. If the nozzle link plate 36 rotates, the blade shaft 34b mounted on the first end of the nozzle link plate 36 rotates. As the blade shaft 34b rotates, the blade body 34a mounted on the first end of the blade shaft 34b rotates. As a result, the intervals between the blade bodies 34a change. That is, the cross-sectional area of ​​the connecting flow path S changes.

[0038] A heat shield 61 (intermediate component) is provided between the variable capacity mechanism 30 and the bearing housing 3. The heat shield 61 is arranged on the inner side of the nozzle ring shaft hole 32h of the nozzle ring 32. The shape of the heat shield 61 is annular with the rotation axis AX as the center. The heat shield 61 prevents heat from moving from the turbine housing 11 to the bearing housing 3. As a result, the temperature rise of the components arranged on the side of the bearing housing 3 is suppressed. The disc spring 62 (force applying component) is compressed and deformed in the axial direction by being sandwiched between the heat shield 61 and the bearing housing 3. The disc spring 62 exerts an elastic force that counteracts the compression deformation. The disc spring 62 presses the heat shield 61 against the nozzle ring 32.

[0039] Figure 3 yes Figure 1 An enlarged view of area S1. Figure 3 The portion where the variable displacement mechanism 30 contacts the turbine housing 11 is shown in an enlarged manner. The nozzle ring 32 of the variable displacement mechanism 30 includes a nozzle ring outer flange 32f1 in addition to a nozzle ring main body 32a and a drive ring support portion 32b.

[0040] The nozzle ring outer flange 32f1 protrudes radially from the drive ring support portion outer peripheral surface 325 of the drive ring support portion 32b. The nozzle ring outer flange 32f1 has a nozzle ring outer flange outer peripheral surface 321, a nozzle ring outer flange main surface 322 (first variable capacity mechanism contact surface), and a nozzle ring outer flange back surface 323.

[0041] The nozzle ring outer flange outer peripheral surface 321 faces the turbine housing inner peripheral surface 111. The nozzle ring outer flange outer peripheral surface 321 does not contact the turbine housing inner peripheral surface 111. There is a gap between the nozzle ring outer flange outer peripheral surface 321 and the turbine housing inner peripheral surface 111.

[0042] The nozzle ring outer flange main surface 322 faces the turbine housing flange back surface 112 (first housing abutment surface). The nozzle ring outer flange main surface 322 contacts the turbine housing flange back surface 112 of the turbine housing flange 11f. The position of the variable capacity mechanism 30 along the rotation axis AX is determined by this contact. More specifically, the nozzle ring outer flange main surface 322 is pressed by the turbine housing flange back surface 112.

[0043] More specifically, the nozzle ring outer flange main surface 322 includes an area in contact with the turbine housing flange back surface 112 and an area not in contact with the turbine housing flange back surface 112. The area in contact with the turbine housing flange back surface 112 is referred to as a flange main surface contact area 322a. The area not in contact with the turbine housing flange back surface 112 is referred to as a flange main surface non-contact area 322b.

[0044] The back surface 323 of the outer flange of the nozzle ring is the same surface as the back surface 324 of the drive ring support portion. The back surface 323 of the outer flange of the nozzle ring and the back surface 324 of the drive ring support portion cooperate to form a drive ring support surface 32d. The drive ring support surface 32d faces the drive ring main surface 351. The drive ring support surface 32d contacts the drive ring main surface 351. The drive ring support surface 32d slides relative to the drive ring main surface 351 around the rotation axis AX.

[0045] The drive ring support portion outer peripheral surface 325 is a cylindrical surface located between the nozzle ring outer flange main surface 322 and the nozzle ring main surface 32e. The drive ring support portion outer peripheral surface 325 faces the turbine housing flange inner peripheral surface 113. The drive ring support portion outer peripheral surface 325 does not contact the turbine housing flange inner peripheral surface 113. There is a gap between the drive ring support portion outer peripheral surface 325 and the turbine housing flange inner peripheral surface 113. The gap corresponds to the above-mentioned flange main surface non-contact area 322b.

[0046] The nozzle ring outer flange main surface 322 is pressed against the turbine housing flange back surface 112. The force pressing the nozzle ring outer flange main surface 322 against the turbine housing flange back surface 112 is provided by the disc spring 62 (see Figure 1The force generated by the disc spring 62 generates a friction force between the nozzle ring outer flange main surface 322 and the turbine housing flange back surface 112. This friction force suppresses the relative micro-movement of the variable capacity mechanism 30 with respect to the turbine housing 11.

[0047] The friction force is determined by the product of the friction coefficient and the pressing force. The nozzle ring outer flange main surface 322 is subjected to surface processing to increase the friction coefficient. The surface processing to increase the friction coefficient can be exemplified by knurling or sandblasting.

[0048] In the case of processing such as knurling to provide minute concavo-convex shapes on the surface, the concavo-convex shapes may be formed so as to hinder the movement of the nozzle ring 32 rotating about the rotation axis AX. For example, in the case of forming minute grooves, radial shapes extending in the radial direction may be provided on the nozzle ring outer flange main surface 322. By knurling, the nozzle ring outer flange main surface 322 may be provided with concavo-convex shapes in a mesh pattern.

[0049] The surface processing may be formed at least in the flange main surface contact area 322a of the flange main surface 322 outside the nozzle ring. The flange main surface non-contact area 322b may or may not be subjected to surface processing for increasing the friction coefficient. The flange main surface contact area 322a may include an area subjected to surface processing for increasing the friction coefficient. The entire surface of the flange main surface contact area 322a may be subjected to surface processing for increasing the friction coefficient. The surface processing for increasing the friction coefficient may also be applied to a portion of the flange main surface contact area 322a.

[0050] The high friction coefficient of the nozzle ring outer flange main surface 322 means that the surface roughness of the nozzle ring outer flange main surface 322 is large. For example, the drive ring support surface 32d slides relative to the drive ring main surface 351. Generally, the surface roughness of the sliding surface is small. Therefore, the surface roughness of the nozzle ring outer flange main surface 322 is greater than the surface roughness of the drive ring support surface 32d. Similarly, the surface roughness of the nozzle ring outer flange main surface 322 is greater than the surface roughness of the sliding surface relative to the nozzle vane 34, that is, the nozzle ring main surface 32e.

[0051] There are also separation surfaces that do not contact other parts, such as the drive ring support portion outer peripheral surface 325 and the nozzle ring outer flange outer peripheral surface 321. The surface roughness of the separation surface that does not contact other parts is greater than that of the sliding surface such as the drive ring support surface 32d. The surface roughness of the nozzle ring outer flange main surface 322 is the same as the surface roughness of the drive ring support portion outer peripheral surface 325, or greater than the surface roughness of the drive ring support portion outer peripheral surface 325. The surface roughness of the nozzle ring outer flange main surface 322 is the same as the surface roughness of the nozzle ring outer flange outer peripheral surface 321, or greater than the surface roughness of the nozzle ring outer flange outer peripheral surface 321.

[0052] Regarding the relationship of surface roughness, it can also be processed in the same way as the surface processing for improving the friction coefficient. The area with the surface roughness that improves the friction coefficient can be formed at least in the flange main surface abutting area 322a of the flange main surface 322 outside the nozzle ring. The surface roughness of the flange main surface non-abutting area 322b can be the surface roughness that improves the friction coefficient, or it can be other surface roughness. The surface roughness of the flange main surface non-abutting area 322b can also be the surface roughness that improves the friction coefficient of the entire surface of the flange main surface abutting area 322a. The surface roughness of the flange main surface non-abutting area 322b can also be the surface roughness that improves the friction coefficient of a part of the flange main surface abutting area 322a.

[0053] The purpose of increasing the friction coefficient of the nozzle ring outer flange main surface 322 is to suppress micro-movement of the nozzle ring outer flange main surface 322 relative to the turbine housing flange back surface 112. Therefore, the surface processing and surface roughness processing for increasing the friction coefficient may also be performed on the turbine housing flange back surface 112 that contacts the nozzle ring outer flange main surface 322.

[0054] The surface processing and the prescribed surface roughness processing for improving the friction coefficient may be performed only on the nozzle ring outer flange main surface 322, and not on the turbine housing flange back surface 112. The surface processing and the prescribed surface roughness processing for improving the friction coefficient may not be performed on the nozzle ring outer flange main surface 322, and only on the turbine housing flange back surface 112. The surface processing and the prescribed surface roughness processing for improving the friction coefficient may be performed on both the nozzle ring outer flange main surface 322 and the turbine housing flange back surface 112.

[0055] By increasing the friction between the nozzle ring outer flange main surface 322 and the turbine housing flange back surface 112, micro-movement of the variable displacement mechanism 30 relative to the turbine housing 11 can be suppressed. This effect is further exerted when the supercharger 1 is in operation.

[0056] When the supercharger 1 is in operation, high-temperature gas flows in the variable capacity mechanism 30. As a result, the components constituting the variable capacity mechanism 30 are thermally deformed. Thermal deformation causes a slight deviation in the positional relationship between the components. For example, the distance from the heat shield 61 to the bearing housing 3 may also increase. If the distance from the heat shield 61 to the bearing housing 3 increases, the disc spring load generated by the disc spring 62 will decrease. Because the disc spring load is the force that presses the variable capacity mechanism 30 against the turbine housing 11, the reduction in the disc spring load generated by the disc spring 62 brings about a reduction in the force that presses the variable capacity mechanism 30 against the turbine housing 11. As described above, the force that presses the variable capacity mechanism 30 against the turbine housing 11 brings about a friction force for suppressing the micro-movement of the variable capacity mechanism 30 relative to the turbine housing 11. Therefore, the reduction in the force that presses the variable capacity mechanism 30 against the turbine housing 11 brings about a reduction in friction. As a result, the force restraining the variable displacement mechanism 30 with respect to the turbine housing 11 becomes weaker, and therefore the variable displacement mechanism 30 is more likely to slightly move with respect to the turbine housing 11 due to an external force.

[0057] As another important factor, the Young's modulus of the spiral spring 62 decreases due to the temperature rise of the spiral spring 62. The decrease in Young's modulus leads to a decrease in spring load. Therefore, due to this important factor, the friction force is also reduced, so that the variable capacity mechanism 30 is easy to slightly move relative to the turbine housing 11.

[0058] When the supercharger 1 is in operation, the force pressing the variable capacity mechanism 30 against the turbine housing 11 tends to weaken. The friction force is the product of the pressing force and the friction coefficient. Therefore, if the friction coefficient is large enough, when the pressing force is reduced, even if a force causing relative micro-motion acts between the variable capacity mechanism 30 and the turbine housing 11 due to external force, the friction force that can resist the force can be ensured.

[0059] From the point of view of suppressing micro-movement of the variable capacity mechanism 30 relative to the turbine housing 11 , the effect can be further enhanced by applying processing to increase the friction coefficient to other parts.

[0060] Figure 4 yes Figure 1 An enlarged view of area S2. Figure 4 The heat shield 61 and the coil spring 62 are shown in an enlarged manner. Figure 4 In the embodiment, the processing for increasing the friction coefficient is described by way of example in three places. First, the processing for increasing the friction coefficient may be performed on the portion where the heat shield plate 61 contacts the nozzle ring 32. Second, the processing for increasing the friction coefficient may be performed on the portion where the heat shield plate 61 contacts the disc spring 62. Third, the processing for increasing the friction coefficient may be performed on the portion where the disc spring 62 contacts the bearing housing 3.

[0061] The heat shield 61 is described. The heat shield 61 includes a heat shield body 61a and a heat shield flange 61f. The heat shield body 61a is annular and includes a heat shield body inner peripheral surface 611 and a heat shield body outer peripheral surface 612. The heat shield body inner peripheral surface 611 faces the bearing housing receiving surface 114. The heat shield body inner peripheral surface 611 contacts the bearing housing receiving surface 114. The heat shield body outer peripheral surface 612 faces the end of the nozzle ring 32. The end of the nozzle ring 32 refers to the nozzle ring inner flange 32f2 protruding from the inner peripheral surface surrounding the nozzle ring shaft hole 32h. More specifically, the heat shield body outer peripheral surface 612 contacts the inner peripheral surface 326 of the nozzle ring inner flange.

[0062] The heat shield body 61a has a heat shield body main surface 613. The heat shield body main surface 613 faces the turbine impeller back surface 121 of the turbine impeller 12. The heat shield body main surface 613 does not contact the turbine impeller back surface 121. There is a gap between the heat shield body main surface 613 and the turbine impeller back surface 121.

[0063] The heat shield body 61a has a heat shield body back surface 614. The heat shield body back surface 614 faces the bearing housing 3. Specifically, the heat shield body back surface 614 faces the bearing housing bottom surface 115. The heat shield body back surface 614 and the bearing housing bottom surface 115 are not in contact. There is a gap between the heat shield body back surface 614 and the bearing housing bottom surface 115. The disc spring 62 is arranged in the gap. Figure 1 As shown, the bearing housing 3 abuts against the turbine housing 11 at the abutment portion 3p. The distance from the heat shield body back surface 614 to the bearing housing bottom surface 115 is determined by this abutment.

[0064] The heat shield flange 61f has a heat shield flange outer peripheral surface 615. The heat shield flange outer peripheral surface 615 faces the nozzle ring shaft hole inner peripheral surface 32h1. The heat shield flange outer peripheral surface 615 and the nozzle ring shaft hole inner peripheral surface 32h1 do not contact. There is a gap between the heat shield flange outer peripheral surface 615 and the nozzle ring shaft hole inner peripheral surface 32h1.

[0065] The heat shield flange 61f has a heat shield flange main surface 616 (first intermediate member contact surface). The heat shield flange main surface 616 faces the nozzle ring inner flange back surface 327 (second variable capacity contact surface) of the nozzle ring inner flange 32f2. The entire surface of the heat shield flange main surface 616 contacts a part of the nozzle ring inner flange back surface 327. The heat shield flange main surface 616 is pressed by the nozzle ring inner flange back surface 327. The portion of the heat shield flange main surface 616 pressed by the nozzle ring inner flange back surface 327 is the above-mentioned first portion.

[0066] Therefore, at least one of the heat shield plate flange main surface 616 and the nozzle ring inner flange back surface 327 may be subjected to surface processing for increasing the friction coefficient or processing for obtaining a surface roughness that increases the friction coefficient.

[0067] The heat shield flange 61f has a heat shield flange back 617. The heat shield flange back 617 and the heat shield body back 614 constitute the heat shield back 61c. The heat shield back 61c faces the bearing housing bottom 115. The heat shield back 61c does not contact the bearing housing bottom 115. There is a gap between the heat shield back 61c and the bearing housing bottom 115. The gap is managed by the bearing housing 3 and the turbine housing 11 abutting against each other as described above. The disc spring 62 is arranged in the gap.

[0068] The coil spring 62 is described. The coil spring 62 is an annular member. The coil spring 62 has a coil spring inner peripheral surface 621 and a coil spring outer peripheral surface 622. The coil spring inner peripheral surface 621 deviates in the direction of the rotation axis AX relative to the coil spring outer peripheral surface 622. In order to eliminate this deviation, the coil spring 62 is compressed and deformed in the direction of the rotation axis AX to generate elastic force.

[0069] The coil spring 62 has a coil spring main surface 623 (first force application member contact surface). The coil spring main surface 623 faces the insulation board back surface 61c. The coil spring main surface 623 contacts the insulation board back surface 61c. The coil spring main surface 623 is pressed by the insulation board back surface 61c (second intermediate member contact surface). The coil spring main surface 623 is pressed by the insulation board flange back surface 617. The coil spring main surface outer peripheral portion 623a of the coil spring main surface 623 is pressed by the insulation board flange back surface 617. A portion of the coil spring main surface 623 contacts the insulation board flange back surface 617. The coil spring main surface inner peripheral portion 623b does not contact the insulation board flange back surface 617. The area of ​​the coil spring main surface 623 that contacts the insulation board flange back surface 617 changes depending on the degree to which the coil spring 62 is flattened. The portion of the coil spring main surface 623 that is pressed by the insulation board flange back surface 617 is the above-mentioned second portion.

[0070] Therefore, at least one of the spiral spring main surface 623 and the heat shield flange back surface 617 may be subjected to surface processing for increasing the friction coefficient or processing for obtaining a surface roughness that increases the friction coefficient.

[0071] The disc spring 62 has a disc spring back side 624 (second force application member abutment surface). The disc spring back side 624 faces the bearing housing bottom surface 115 (second housing abutment surface). The disc spring back side 624 faces the bearing housing bottom surface 115. The disc spring back side 624 is pressed by the bearing housing bottom surface 115. The disc spring back side inner peripheral portion 624a of the disc spring back side 624 is pressed by the bearing housing bottom surface 115. A portion of the disc spring back side 624 is in contact with the bearing housing bottom surface 115. The disc spring back side outer peripheral portion 624b is not in contact with the bearing housing bottom surface 115. The area in contact with the bearing housing bottom surface 115 as a portion of the disc spring main surface 623 varies depending on the degree to which the disc spring 62 is flattened. The portion that is pressed by the bearing housing bottom surface 115 as a portion of the disc spring back side 624 is the above-mentioned third position.

[0072] Therefore, at least one of the disc spring back surface 624 and the bearing housing bottom surface 115 may be subjected to surface processing to increase the friction coefficient. In addition, at least one of the disc spring back surface 624 and the bearing housing bottom surface 115 may be subjected to surface roughness processing to increase the friction coefficient.

[0073] <Effects>

[0074] In summary, the supercharger 1 of the present embodiment includes: a turbine wheel 12; a turbine housing 11 including a flow path through which the gas received from the inlet 14s flows; a variable capacity mechanism 30 disposed in the turbine housing 11 and receiving the gas from the flow path and guiding it to the turbine wheel 12; and a disc spring 62 for applying a force to the variable capacity mechanism 30 to press the variable capacity mechanism 30 against the turbine housing 11. The turbine housing 11 includes a turbine housing flange back surface 112 in contact with the variable capacity mechanism 30 along the direction of the rotation axis AX of the turbine wheel 12. The variable capacity mechanism 30 includes a nozzle ring outer flange main surface 322 in contact with the turbine housing flange back surface 112 along the direction of the rotation axis AX. Processing to increase the friction coefficient is performed on at least one of the turbine housing flange back surface 112 and the nozzle ring outer flange main surface 322.

[0075] In the portion where the turbine housing 11 contacts the variable capacity mechanism 30, a friction force corresponding to the force generated by the disc spring 62 and the friction coefficient is generated. Processing to increase the friction coefficient is performed on at least one of the turbine housing flange back surface 112 and the nozzle ring outer flange main surface 322. Therefore, the friction force determined by the product of the friction coefficient and the force can be increased. The friction force can suppress the generation of relative micromotion between the turbine housing 11 and the variable capacity mechanism 30. Therefore, the generation of relative micromotion between the components can be suppressed.

[0076] The supercharger 1 further includes a bearing housing 3 that rotatably supports the rotating shaft 2 to which the turbine impeller 12 is fixed, and an annular heat shielding plate 61 disposed between the turbine housing 11 and the variable capacity mechanism 30. The variable capacity mechanism 30 includes a nozzle ring shaft hole 32h through which the turbine impeller 12 or the rotating shaft 2 is inserted, and a nozzle ring inner flange back surface 327 that surrounds the nozzle ring shaft hole 32h. The heat shielding plate 61 includes a heat shielding plate flange main surface 616 that contacts the nozzle ring inner flange back surface 327. Processing to increase the friction coefficient is performed on at least one of the nozzle ring inner flange back surface 327 and the heat shielding plate flange main surface 616. According to this structure, the generation of relative micromotion between the variable capacity mechanism 30 and the heat shielding plate 61 can be suppressed.

[0077] The supercharger 1 further includes a bearing housing 3 that rotatably supports the rotating shaft 2 to which the turbine impeller 12 is fixed, and an annular heat shield 61 disposed between the turbine housing 11 and the variable capacity mechanism 30. The heat shield 61 has a heat shield flange back surface 617 that faces the bearing housing 3 and contacts the disc spring 62. The disc spring 62 has a disc spring main surface 623 that contacts the heat shield flange back surface 617. Processing to increase the friction coefficient is performed on at least one of the heat shield flange back surface 617 and the disc spring main surface 623. According to this structure, the generation of relative micromotion between the disc spring 62 and the heat shield 61 can be suppressed.

[0078] The supercharger 1 further includes a bearing housing 3 that rotatably supports the rotating shaft 2 to which the turbine impeller 12 is fixed. The bearing housing 3 has a bearing housing bottom surface 115 that the disc spring 62 contacts along the direction of the rotation axis AX. The disc spring 62 has a disc spring back surface 624 that contacts the bearing housing bottom surface 115. Processing to increase the friction coefficient is performed on at least one of the bearing housing bottom surface 115 and the disc spring back surface 624. According to this structure, the generation of relative micromotion between the disc spring 62 and the bearing housing 3 can be suppressed.

[0079] The supercharger 1 includes: a turbine wheel 12; a turbine housing 11 including a flow path through which the gas received from the inlet 14s flows; a variable displacement mechanism 30 disposed in the turbine housing 11 and receiving the gas from the flow path and guiding it to the turbine wheel 12, and including a nozzle ring 32 having a disk shape and a main surface facing the turbine wheel 12, and a plurality of nozzle blades 34 disposed on the main surface side of the nozzle ring 32 and forming a plurality of nozzle flow paths for guiding the gas; and a disc spring 62 for applying a force to the variable displacement mechanism 30 to press the variable displacement mechanism 30 against the turbine housing 11. The turbine housing 11 includes a turbine housing flange back surface 112 in contact with the variable displacement mechanism 30 along the direction of the rotation axis AX of the turbine wheel 12. The variable displacement mechanism 30 includes a nozzle ring outer flange main surface 322 in contact with the turbine housing flange back surface 112 along the direction of the rotation axis AX. The nozzle ring 32 has a separation surface separated from a first component different from the nozzle ring 32 and a sliding surface on which a second component different from the nozzle ring 32 slides relative to the nozzle ring 32. The surface roughness of at least one of the turbine housing flange back surface 112 and the nozzle ring outer flange main surface 322 is greater than the surface roughness of the separation surface.

[0080] In the portion where the turbine housing 11 and the variable capacity mechanism 30 abut, a friction force corresponding to the force and the friction coefficient generated by the disc spring 62 is generated. The surface roughness of at least one of the turbine housing flange back surface 112 and the nozzle ring outer flange main surface 322 is greater than the surface roughness of the separation surface. Therefore, the friction force determined by the product of the friction coefficient corresponding to the surface roughness and the force can be increased. This friction force can suppress the generation of relative micromotion generated between the turbine housing 11 and the variable capacity mechanism 30. Therefore, the generation of relative micromotion between the components can be suppressed.

[0081] The surface roughness of at least one of the turbine housing flange back surface 112 and the nozzle ring outer flange main surface 322 is greater than the surface roughness of the sliding surface. This structure can also suppress the occurrence of relative micro-motion between the components.

[0082] [Variation]

[0083] The supercharger of the present disclosure is not limited to the above-described embodiment, and various modifications can be made without departing from the gist of the present disclosure.

[0084] The variable capacity mechanism 30 is positioned relative to the bearing housing 3. The protrusion 3a (second housing shoulder surface) of the bearing housing 3 is embedded in the nozzle ring shaft hole 32h (first configuration hole). The protrusion outer peripheral surface 3a1 of the protrusion 3a contacts the nozzle ring shaft hole inner peripheral surface 32h1 (first configuration hole inner peripheral portion). Therefore, the variable capacity mechanism 30 and the bearing housing 3 cooperate to form a socket structure 39. The rib 32r and the protrusion 3a of the bearing housing 3 form the socket structure 39. The position of the variable capacity mechanism 30 relative to the bearing housing 3 is determined by the socket structure 39.

[0085] It is also possible to perform surface processing to increase the friction coefficient or surface roughness processing to increase the friction coefficient on at least one of the protrusion outer peripheral surface 3a1 of the protrusion 3a of the bearing housing 3 and the nozzle ring shaft hole inner peripheral surface 32h1. This part is not related to the micro-movement of the variable capacity mechanism 30 caused by the reduction of the pressing force of the disc spring 62 described in the present disclosure. On the other hand, if the friction coefficient of the protrusion outer peripheral surface 3a1 of the protrusion 3a and the nozzle ring shaft hole inner peripheral surface 32h1 is increased, the micro-movement of the variable capacity mechanism 30 relative to the turbine housing 11 around the rotation axis AX can be suppressed. With this structure, the micro-movement of the variable capacity mechanism 30 relative to the turbine housing 11 can also be suppressed.

[0086] In summary, the supercharger 1 further includes a bearing housing 3 that rotatably supports the rotating shaft 2 to which the turbine impeller 12 is fixed. The variable capacity mechanism 30 includes a nozzle ring shaft hole 32h through which the turbine impeller 12 or the rotating shaft 2 is inserted. The nozzle ring shaft hole 32h includes a nozzle ring shaft hole inner peripheral surface 32h1 on which the protrusion 3a of the bearing housing 3 is arranged. The protrusion 3a includes a protrusion outer peripheral surface 3a1 that contacts the nozzle ring shaft hole inner peripheral surface 32h1. Processing to increase the friction coefficient is performed on at least one of the nozzle ring shaft hole inner peripheral surface 32h1 and the protrusion outer peripheral surface 3a1 of the protrusion 3a of the bearing housing 3. According to this structure, the generation of relative micromotion between the variable capacity mechanism 30 and the bearing housing 3 can be suppressed.

[0087] [Note]

[0088] The present disclosure includes the following structures.

[0089] The supercharger disclosed in the present invention is [1] a supercharger, which comprises: a turbine impeller; a first housing, which includes a flow path for the flow of gas received from an inlet; a variable capacity mechanism, which is arranged in the first housing and receives the gas from the flow path and guides it to the turbine impeller; and a force applying member, which applies a force to the variable capacity mechanism to press the variable capacity mechanism against the first housing, wherein the first housing has: a first housing abutment surface that contacts the variable capacity mechanism along the direction of the rotation axis of the turbine impeller, and the variable capacity mechanism has: a first variable capacity mechanism abutment surface that contacts the first housing abutment surface along the direction of the rotation axis, and at least one of the first housing abutment surface and the first variable capacity mechanism abutment surface is processed to increase the friction coefficient.

[0090] The supercharger [2] disclosed in the present invention is the supercharger described in [1] above, and further comprises: a second housing that rotatably supports the rotating shaft to which the turbine impeller is fixed; and an annular intermediate component that is arranged between the first housing and the variable capacity mechanism, the variable capacity mechanism having: a first arrangement hole for inserting the turbine impeller or the rotating shaft, and a second variable capacity mechanism abutment surface surrounding the first arrangement hole, the intermediate component having: a first intermediate component abutment surface that contacts the second variable capacity mechanism abutment surface, and at least one of the second variable capacity mechanism abutment surface and the first intermediate component abutment surface is processed to increase the friction coefficient.

[0091] The supercharger [3] disclosed in the present invention is the supercharger described in [1] or [2] above, and further comprises: a second housing that rotatably supports the rotating shaft to which the turbine impeller is fixed; and an annular intermediate component that is arranged between the first housing and the variable capacity mechanism, the intermediate component having: a second intermediate component abutment surface that is opposite to the second housing and in contact with the force applying component, the force applying component having: a first force applying component abutment surface that is in contact with the second intermediate component abutment surface, and at least one of the second intermediate component abutment surface and the first force applying component abutment surface is processed to increase the friction coefficient.

[0092] The supercharger [4] disclosed in the present invention is a supercharger according to any one of the above [1] to [3], wherein it further comprises: a second housing that rotatably supports the rotating shaft to which the turbine impeller is fixed, the second housing having: a second housing abutment surface that the force-applying member contacts along the direction of the rotating axis, the force-applying member having: a second force-applying member abutment surface that contacts the second housing abutment surface, and at least one of the second housing abutment surface and the second force-applying member abutment surface is processed to increase the friction coefficient.

[0093] The supercharger [5] disclosed in the present invention is a supercharger according to any one of the above [1] to [4], wherein it also includes a second housing that supports the rotating shaft to which the turbine impeller is fixed so that it can rotate, and the variable capacity mechanism has: a first configuration hole for the turbine impeller or the rotating shaft to be inserted, the first configuration hole includes: a first configuration hole inner peripheral surface portion for configuring a second housing shoulder portion of the second housing, the second housing shoulder portion includes: a second housing shoulder surface that contacts the first configuration hole inner peripheral surface portion, and at least one of the first configuration hole inner peripheral surface portion and the second housing shoulder surface is processed to increase the friction coefficient.

[0094] Other superchargers disclosed herein [6] A supercharger, comprising: a turbine impeller; a first housing including a flow path through which gas received from an inlet flows; a variable displacement mechanism disposed in the first housing and receiving the gas from the flow path and guiding the gas toward the turbine impeller, the variable displacement mechanism comprising: a disk-shaped nozzle ring having a main surface facing the turbine impeller, and a plurality of nozzle blades disposed on the main surface side of the nozzle ring and forming a plurality of nozzle flow paths for guiding the gas; and a biasing member that applies a force to the variable displacement mechanism to press the variable displacement mechanism against the first housing, the first housing comprising: a first housing abutting surface in contact with the variable displacement mechanism along the direction of the rotation axis of the turbine impeller, the variable displacement mechanism comprising: a first variable displacement mechanism abutting surface in contact with the first housing abutting surface in contact with the first housing abutting surface along the direction of the rotation axis, the nozzle ring comprising: a separation surface separated from a first component different from the nozzle ring, and a sliding surface sliding on a second component different from the nozzle ring, the surface roughness of at least one of the first housing abutting surface and the first variable displacement mechanism abutting surface being greater than the surface roughness of the separation surface.

[0095] Another supercharger [7] disclosed in the present disclosure is the supercharger described in [6] above, wherein the surface roughness of at least one of the first housing abutment surface and the first variable displacement mechanism abutment surface is greater than the surface roughness of the sliding surface.

[0096] Another supercharger [8] disclosed herein is the supercharger described in [6] or [7] above, wherein the first component is the first housing, and the separation surface is an outer circumferential surface of a nozzle ring that is opposite to the inner circumferential surface of the first housing and is separated from the inner circumferential surface of the first housing.

[0097] Another supercharger [9] disclosed in the present invention is a supercharger according to any one of [6] to [8] above, wherein the second component is the nozzle vane, and the sliding surface is a main surface of the nozzle ring on which the plurality of nozzle vanes slide.

[0098] Description of reference numerals:

[0099] 1…supercharger; 2…rotating shaft; 3…bearing housing (second housing); 3a…protrusion (second housing shoulder); 3a1…outer peripheral surface of protrusion (second housing shoulder); 11…turbine housing (first housing); 112…back surface of turbine housing flange (first housing abutment surface); 115…bottom surface of bearing housing (second housing abutment surface); 12…turbine impeller; 13…vortex flow path (flow path); 14s…inflow port; 30…variable capacity mechanism; 32…nozzle ring; 322…main surface of nozzle ring outer flange (first variable capacity mechanism abutment surface); 327…inner side of nozzle ring Back side of flange (second variable capacity abutment surface); 32h…nozzle ring shaft hole (first configuration hole); 32h1…inner circumferential surface of nozzle ring shaft hole (inner circumferential surface of first configuration hole); 34…nozzle blade; 61…heat insulation board (middle component); 616…main surface of heat insulation board flange (first middle component abutment surface); 61c…back side of heat insulation board (second middle component abutment surface); 62…disc spring (force applying component); 623…main surface of disc spring (first force applying component abutment surface); 624…back side of disc spring (second force applying component abutment surface); 325…outer circumferential surface of drive ring support portion; AX…axis of rotation.

Claims

1. A supercharger, characterized in that: have: Turbine impeller; A first housing including a flow path through which the gas received from the inlet flows; a variable capacity mechanism disposed in the first housing and receiving the gas from the flow path and guiding the gas to the turbine impeller; and a force applying member that applies a force to the variable capacity mechanism to press the variable capacity mechanism against the first housing, The first housing has a first housing contact surface that contacts the variable displacement mechanism along the direction of the rotation axis of the turbine impeller. The variable displacement mechanism includes: a first variable displacement mechanism abutment surface that contacts the first housing abutment surface along the direction of the rotation axis; Processing for increasing the friction coefficient is performed on at least one of the first housing abutting surface and the first variable capacity mechanism abutting surface.

2. The supercharger according to claim 1, characterized in that: Also available: a second housing that rotatably supports a rotating shaft to which the turbine impeller is fixed; and an annular intermediate member disposed between the first housing and the variable capacity mechanism, The variable displacement mechanism includes a first arrangement hole through which the turbine impeller or the rotating shaft is inserted, and a second variable displacement mechanism contact surface surrounding the first arrangement hole. The intermediate member includes a first intermediate member abutting surface that contacts the second variable capacity mechanism abutting surface. Processing for increasing the friction coefficient is performed on at least one of the second variable capacity mechanism contact surface and the first intermediate member contact surface.

3. The supercharger according to claim 1, characterized in that: Also available: a second housing that rotatably supports a rotating shaft to which the turbine impeller is fixed; and an annular intermediate member disposed between the first housing and the variable capacity mechanism, The intermediate member includes a second intermediate member contact surface which faces the second housing and contacts the biasing member. The urging member includes a first urging member contact surface that contacts the second intermediate member contact surface. At least one of the second intermediate member contact surface and the first urging member contact surface is subjected to processing to increase the friction coefficient.

4. The supercharger according to claim 1, characterized in that: A second housing is further provided for rotatably supporting a rotating shaft to which the turbine impeller is fixed. The second housing has a second housing abutment surface with which the urging member contacts in the direction of the rotation axis. The urging member comprises: a second urging member abutting surface in contact with the second housing abutting surface; At least one of the second housing abutting surface and the second urging member abutting surface is subjected to processing to increase the friction coefficient.

5. The supercharger according to claim 1, characterized in that: A second housing is further provided for rotatably supporting a rotating shaft to which the turbine impeller is fixed. The variable displacement mechanism includes a first arrangement hole through which the turbine impeller or the rotating shaft is inserted. The first configuration hole comprises: a first configuration hole inner peripheral surface portion for configuring the second shell shoulder portion of the second shell, The second shell shoulder portion comprises: a second shell shoulder surface in contact with the inner peripheral surface portion of the first configuration hole, Processing for increasing the friction coefficient is performed on at least one of the first arrangement hole inner peripheral surface portion and the second housing shoulder surface.

6. A supercharger, characterized in that: have: Turbine impeller; A first housing including a flow path through which the gas received from the inlet flows; a variable capacity mechanism disposed in the first housing and receiving the gas from the flow path and guiding the gas toward the turbine impeller, the variable capacity mechanism comprising: a nozzle ring having a disk shape and a main surface facing the turbine impeller, and a plurality of nozzle blades disposed on the main surface side of the nozzle ring and forming a plurality of nozzle flow paths for guiding the gas; and a force applying member that applies a force to the variable capacity mechanism to press the variable capacity mechanism against the first housing, The first housing has a first housing contact surface that contacts the variable displacement mechanism along the direction of the rotation axis of the turbine impeller. The variable displacement mechanism includes: a first variable displacement mechanism abutment surface that contacts the first housing abutment surface along the direction of the rotation axis; The nozzle ring has a separation surface separated from a first member different from the nozzle ring and a sliding surface sliding on a second member different from the nozzle ring. The surface roughness of at least one of the first housing abutting surface and the first variable capacity mechanism abutting surface is greater than the surface roughness of the separation surface.

7. The supercharger according to claim 6, characterized in that: The surface roughness of at least one of the first housing abutting surface and the first variable capacity mechanism abutting surface is greater than the surface roughness of the sliding surface.

8. The supercharger according to claim 6 or 7, characterized in that: The first component is the first housing, The separation surface is an outer peripheral surface of the nozzle ring that faces the inner peripheral surface of the first housing and is separated from the inner peripheral surface of the first housing.

9. The supercharger according to claim 6, characterized in that: The second component is the nozzle vane, The sliding surface is a main surface of the nozzle ring on which the plurality of nozzle vanes slide.

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