supercharger

Abstract

The supercharger comprises a bearing housing, a variable capacity mechanism, and a limiting component. The variable capacity mechanism comprises a nozzle ring and a drive ring. The limiting component comprises a flange, a drive ring guide pin, and a phasing pin. The flange spans a first surface of the nozzle ring facing the bearing housing and a second surface of the drive ring facing the bearing housing, and is fixed in position relative to the nozzle ring. The drive ring guide pin is integrally formed with the flange and positioned in a first hole formed in the first surface. The phasing pin is integrally formed with the flange and positioned in a second hole formed in a third surface of the bearing housing facing the variable capacity mechanism.

Description

Technical Field

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

[0002] Patent Documents 1 to 3 describe superchargers equipped with variable displacement mechanisms. For example, the variable displacement mechanism described in Patent Document 1 includes a nozzle ring, a drive ring, a roller pin, and a roller. The roller pin and roller maintain the axial positional relationship between the nozzle ring and the drive ring.

[0003] Patent Document 1: Japanese Patent Application No. 2006-514191

[0004] Patent Document 2: Japanese Patent Application Laid-Open No. 2000-199433

[0005] Patent Document 3: Japanese Patent Application Laid-Open No. 2004-156592

[0006] In superchargers like the one described above, a restricting member is sometimes installed between the bearing housing and the variable displacement mechanism to maintain their circumferential positional relationship. In such cases, space must be secured for the restricting member in addition to the roller pin and roller, potentially reducing the design flexibility of the variable displacement mechanism. Summary of the Invention

[0007] Therefore, an object of the present invention is to provide a supercharger capable of increasing the degree of freedom in designing a variable displacement mechanism.

[0008] A supercharger according to one embodiment of the present invention includes: a bearing housing that rotatably supports a rotating shaft to which a turbine impeller is fixed; a variable capacity mechanism that surrounds the turbine impeller and guides a fluid toward the turbine impeller; and a plurality of limiting members disposed between the bearing housing and the variable capacity mechanism, the variable capacity mechanism including: a nozzle ring that surrounds the turbine impeller in a circumferential direction centered on a rotation axis of the rotating shaft; and a drive ring that surrounds the nozzle ring in a circumferential direction, the nozzle ring including a first surface opposing the bearing housing, the drive ring including a second surface opposing the bearing housing, and the bearing housing including a third surface opposing the variable capacity mechanism, at least one of the plurality of limiting members including: a flange portion that spans the first surface and the second surface and is fixed in position relative to the nozzle ring; a first pin that is integrally formed with the flange portion and is disposed in a first hole formed in the first surface; and a second pin that is integrally formed with the flange portion and is disposed in a second hole formed in the third surface.

[0009] According to the present invention, it is possible to provide a supercharger having an increased degree of freedom in designing a variable displacement mechanism. BRIEF DESCRIPTION OF THE DRAWINGS

[0010] Figure 1 It is a cross-sectional view showing the supercharger according to the first embodiment.

[0011] Figure 2 Yes Figure 1 A three-dimensional view of the variable capacity mechanism shown.

[0012] Figure 3 Yes Figure 1 A top view of the variable capacity mechanism is shown.

[0013] Figure 4 Yes Figure 1 A top view of the bearing housing is shown.

[0014] Figure 5 yes Figure 1 Magnified view of the V portion.

[0015] Figure 6 It is a cross-sectional view showing a supercharger according to a second embodiment.

[0016] Figure 7 yes Figure 6 Magnified view of part VII.

[0017] Figure 8 It is a cross-sectional view showing a turbocharger of a comparative example.

[0018] Figure 9 yes Figure 8 Magnified view of section IX.

[0019] Figure 10 It is a plan view showing a variable displacement mechanism included in a turbocharger of a comparative example. DETAILED DESCRIPTION

[0020] A supercharger according to one embodiment of the present invention includes: a bearing housing that rotatably supports a rotating shaft to which a turbine impeller is fixed; a variable capacity mechanism that surrounds the turbine impeller and guides a fluid toward the turbine impeller; and a plurality of limiting members disposed between the bearing housing and the variable capacity mechanism, the variable capacity mechanism including: a nozzle ring that surrounds the turbine impeller in a circumferential direction centered on a rotation axis of the rotating shaft; and a drive ring that surrounds the nozzle ring in a circumferential direction, the nozzle ring including a first surface opposing the bearing housing, the drive ring including a second surface opposing the bearing housing, and the bearing housing including a third surface opposing the variable capacity mechanism, at least one of the plurality of limiting members including: a flange portion that spans the first surface and the second surface and is fixed in position relative to the nozzle ring; a first pin that is integrally formed with the flange portion and is disposed in a first hole formed in the first surface; and a second pin that is integrally formed with the flange portion and is disposed in a second hole formed in the third surface.

[0021] According to this supercharger, the flange portion enables the positional relationship between the nozzle ring and the drive ring to be maintained in the axial direction along the axis of rotation. Furthermore, the first pin and the first hole, as well as the second pin and the second hole, enable the positional relationship between the bearing box and the variable capacity mechanism to be maintained in the circumferential direction. That is, in this supercharger, the positional relationship between the nozzle ring and the drive ring is maintained by a restricting component, and the positional relationship between the bearing box and the variable capacity mechanism is also maintained. As a result, for example, compared to a case where the positional relationship between the nozzle ring and the drive ring, and the positional relationship between the bearing box and the variable capacity mechanism, is maintained by separate components, the available space on the first surface of the nozzle ring and the second surface of the drive ring is increased. Consequently, the degree of freedom in the design of the variable capacity mechanism is increased.

[0022] In one embodiment, the first pin may be fixed to the nozzle ring. According to this configuration, by fixing the first pin to the nozzle ring, the position of the flange portion relative to the nozzle ring can be fixed.

[0023] In one embodiment, the second hole may be a long hole extending in a radial direction intersecting the axis of rotation, and the diameter of the second pin may be smaller than the width of the second hole. When the supercharger is in operation, high-temperature gas is supplied to the supercharger. As a result, the temperature of components such as the variable capacity mechanism of the supercharger rises. If the temperature of the components rises, thermal deformation of the components occurs. The degree of thermal deformation of the components constituting the supercharger with respect to temperature varies. According to the above structure, thermal deformation of the bearing box and the variable capacity mechanism in the radial direction can be allowed.

[0024] In one embodiment, the diameter of the second pin may be larger than that of the first pin. According to this configuration, the relatively large diameter of the second pin can relatively increase the surface area of the second pin, thereby suppressing wear of the second pin.

[0025] In one embodiment, the second pin may be fixed to the bearing box. According to this configuration, the position of the flange portion relative to the nozzle ring can be fixed by fixing the second pin to the bearing box.

[0026] In one embodiment, the first hole may be an elongated hole extending in a radial direction intersecting the rotation axis, and the diameter of the first pin may be smaller than the width of the first hole. This configuration allows for radial thermal deformation of the bearing housing and the variable capacity mechanism as described above.

[0027] In one embodiment, the diameter of the first pin may be larger than the diameter of the second pin. According to this configuration, the diameter of the first pin is relatively increased, thereby relatively increasing the surface area of the first pin. This can suppress wear of the first pin.

[0028] In one embodiment, all of the plurality of restricting members may include flanges, first pins, and second pins. This configuration can more reliably maintain the positional relationship between the nozzle ring and the drive ring in the axial direction, thereby ensuring structural stability of the supercharger including the variable displacement mechanism.

[0029] In one embodiment, the supercharger may include multiple restricting components, each having a first surface formed with multiple first holes for receiving the first pins of each of the multiple restricting components, and a third surface formed with multiple second holes for receiving the second pins of each of the multiple restricting components. This configuration, through the multiple restricting components, allows the axial positional relationship between the nozzle ring and the drive ring to be more reliably maintained. As a result, changes in the positional relationship between the nozzle ring and the drive ring caused by thermal deformation can be suppressed. This prevents undesirable movement of the variable capacity mechanism that could occur due to changes in the positional relationship between the nozzle ring and the drive ring, thereby ensuring reliable supercharger performance.

[0030] Hereinafter, the embodiment of the present disclosure will be described in detail with reference to the accompanying drawings. In the description of the drawings, the same elements are denoted by the same reference numerals and repeated descriptions are omitted.

[0031] <First embodiment>

[0032] <Supercharger>

[0033] Figure 1 as well as Figure 2 The supercharger 1 shown is a variable capacity supercharger. The supercharger 1 is suitable for use in, for example, an internal combustion engine of a ship or a vehicle. The supercharger 1 includes a turbine 10 and a compressor 20. The turbine 10 includes a turbine housing 11, a turbine impeller 12, and a variable capacity mechanism 30. The turbine housing 11 includes a vortex flow path 13. The vortex flow path 13 extends around the turbine impeller 12 in a circumferential direction (hereinafter referred to as "circumferential direction") centered around a rotation axis AX described later. The compressor 20 includes a compressor housing 21 and a compressor impeller 22. The compressor impeller 22 is housed in the compressor housing 21. The compressor housing 21 includes a vortex flow path 23. The vortex flow path 23 extends circumferentially around the compressor impeller 22.

[0034] 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 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 bearings 4. The rotating shaft 2, the turbine impeller 12, and the compressor impeller 22 form an integral rotating body 5. The rotating body 5 rotates about the rotation axis AX of the rotating shaft 2.

[0035] The turbine housing 11 has an inlet and an outlet 14 (not shown). Exhaust gas from an internal combustion engine (not shown) flows into the turbine housing 11 through the inlet. The inflowing exhaust gas passes through the vortex flow path 13 and flows into the turbine impeller 12. The exhaust gas then rotates the turbine impeller 12. Thereafter, the exhaust gas flows out of the turbine housing 11 through the outlet 14.

[0036] The compressor housing 21 has an intake port 24 and an exhaust port (not shown). When the turbine impeller 12 rotates, the compressor impeller 22 rotates via the rotating shaft 2. The rotating compressor impeller 22 draws in external air through the intake port 24. The drawn-in air passes through the compressor impeller 22 and the vortex flow path 23, where it is compressed. The air is discharged from the exhaust port as compressed air. The compressed air is then supplied to the internal combustion engine.

[0037] 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 vanes 34 are arranged in the connecting flow path S. The plurality of nozzle vanes 34 are arranged at equal intervals on a reference circle centered on the rotation axis AX. The mutually adjacent nozzle vanes 34 constitute a nozzle. The nozzle vanes 34 rotate synchronously around an axis parallel to the rotation axis AX. The plurality of nozzle vanes 34 rotate, thereby adjusting the cross-sectional area of the connecting flow path S. 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. The variable capacity mechanism 30 surrounds the turbine impeller 12 and guides the exhaust gas (fluid) to the turbine impeller 12.

[0038] <Variable capacity mechanism>

[0039] like Figures 1 to 3 As shown, the variable capacity mechanism 30 includes a CC plate (Clearance Control Plate) 31, a nozzle ring 32, and a plurality of CC pins (Clearance Control Pins) 33. 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 further includes a plurality of nozzle vanes 34, a drive ring 35, a plurality of nozzle link plates 36, and a drive link plate (not shown). The nozzle link plate 36 and the drive link plate are arranged on the side of the nozzle ring 32 opposite to the CC plate 31. The drive ring 35 and the drive link plate cooperate to rotate the nozzle link plate 36. When the nozzle link plate 36 rotates, the nozzle vanes 34 rotate.

[0040] The CC plate 31 is annular in shape with the rotation axis AX as the center. The CC plate 31 has an axial hole 31h (see Figure 1 ). The CC plate 31 circumferentially surrounds the turbine impeller 12 arranged in the axial hole 31h. The CC plate 31 is arranged between the vortex flow path 13 and the outflow port 14. The CC plate 31 is separated from the nozzle ring 32 in the axial direction along the rotation axis AX (hereinafter referred to as "axial direction"). 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 14. The CC plate 31 is arranged on the opposite side of the bearing box 3 relative to the nozzle ring 32. The CC plate 31 has a plurality of pin holes not shown in the figure. The circumferential intervals of the plurality of pin holes of the CC plate 31 are equal to each other.

[0041] The nozzle ring 32 also has an annular shape centered on the rotation axis AX. It has an axial hole 32h (through hole). The nozzle ring 32 also circumferentially surrounds the turbine wheel 12, which is located within the axial hole 32h. The nozzle ring 32 is also located between the vortex flow path 13 and the outflow port 14. The CC plate 31 is parallel to the nozzle ring 32. The nozzle ring 32 has multiple pinholes 32p. The circumferential spacing between the multiple pinholes 32p is equal. The central axis of the pinholes 32p overlaps with the central axis of the pinholes in the CC plate 31. In other words, the pinholes 32p are coaxial with the pinholes in the CC plate 31.

[0042] The nozzle ring 32 includes a nozzle ring body 32a and a nozzle ring flange 32b. The nozzle ring body 32a is cylindrical and has an axial hole 32h. The nozzle ring body 32a has multiple blade axial holes 32c. The multiple blade axial holes 32c are spaced evenly apart in the circumferential direction. The nozzle ring body 32a includes a first surface 32d that faces the bearing housing 3. Multiple (e.g., three) first holes 32e are formed in the first surface 32d. The cross-section of the first holes 32e is circular. The first holes 32e do not penetrate the nozzle ring body 32a. In other words, the first holes 32e have a bottom surface.

[0043] The nozzle ring flange 32b protrudes radially from the outer circumference of the nozzle ring body 32a. The outer diameter of the nozzle ring 32 is determined by the outer diameter of the nozzle ring flange 32b. The nozzle ring flange 32b has multiple pinholes 32p. The pinholes 32p are located radially outward of the blade shaft holes 32c in the nozzle ring 32.

[0044] The nozzle ring 32 is spaced apart from the CC plate 31. Specifically, a gap is formed between the nozzle ring 32 and the CC plate 31. This gap serves as a connecting flow path S through which exhaust gas passes. The gap between the nozzle ring 32 and the CC plate 31 is maintained by a CC pin 33. The first end of the CC pin 33 is inserted into a pin hole in the CC plate 31. The second end of the CC pin 33 is inserted into a pin hole 32p in the nozzle ring 32.

[0045] Multiple nozzle vanes 34 are arranged on a reference circle centered on the rotation axis AX. Each nozzle vane 34 includes a vane body 34a and a vane shaft 34b. The vane body 34a is positioned between the CC plate 31 and the nozzle ring 32. In other words, the vane body 34a is positioned in the connecting flow path S. The first end of the vane shaft 34b is fixed to the vane body 34a. The second end of the vane shaft 34b is inserted into the vane shaft hole 32c of the nozzle ring 32. The tip of the second end of the vane shaft 34b protrudes from the nozzle ring body 32a. The vane shaft 34b is rotatable relative to the nozzle ring 32. The vane body 34a rotates with the rotation of the vane shaft 34b. In the variable displacement mechanism 30, the cross-sectional area of the connecting flow path S is adjusted by rotating the vane body 34a. Adjusting the cross-sectional area allows the flow rate of the exhaust gas supplied from the vortex flow path 13 to the turbine impeller 12 to be controlled. Consequently, the rotational speed of the turbine impeller 12 can be controlled to a desired value.

[0046] The drive ring 35 is arranged on the nozzle ring flange 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. That is, the drive ring 35 surrounds the nozzle ring body 32a in the circumferential direction and is coaxial with the nozzle ring 32. The drive ring 35 is rotatable 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 parts 35b. The drive ring body 35a includes a second surface 35c opposite to the bearing box 3. The circumferential intervals of the link plate configuration parts 35b are equal to each other. The link plate configuration part 35b has two upright parts separated from each other in the circumferential direction.

[0047] The nozzle link plate 36 is rod-shaped. Its first end is fixed to the end of the blade shaft 34b. Its second end is located in the link plate mounting portion 35b of the drive ring 35. More specifically, the second end of the nozzle link plate 36 is located between the two upright components of the link plate mounting portion 35b. When the drive ring 35 receives driving force from the drive link plate, it rotates about the rotation axis AX. This rotation causes the second end of the nozzle link plate 36 to move circumferentially as the drive ring 35 rotates. Consequently, the nozzle link plate 36 rotates about the blade shaft 34b. Rotation of the nozzle link plate 36 rotates the blade shaft 34b attached to the first end of the nozzle link plate 36. This rotation also causes the blade bodies 34a attached to the first end of the blade shaft 34b to rotate. As a result, the spacing between the blade bodies 34a changes. In other words, the cross-sectional area of the connecting flow path S changes.

[0048] The variable capacity mechanism 30 is positioned relative to the bearing housing 3. More specifically, the protrusion 3a of the bearing housing 3 is embedded in the inner circumferential surface 32g of the nozzle ring 32 of the variable capacity mechanism 30. Specifically, the outer circumferential surface of the protrusion 3a (the embedded portion) contacts the inner circumferential surface 32g. Thus, the variable capacity mechanism 30 and the bearing housing 3 cooperate to form a centering location structure (spigot-type structure) 39. More specifically, the inner circumferential surface 32g of the nozzle ring body 32a and the protrusion 3a of the bearing housing 3 form the spigot structure 39. This spigot structure 39 determines the position of the variable capacity mechanism 30 relative to the bearing housing 3.

[0049] <Restricted parts>

[0050] The supercharger 1 further includes a plurality of (for example, three) restriction members 40 provided between the bearing housing 3 and the variable displacement mechanism 30. The restriction members 40 will be described in detail below.

[0051] like Figure 1 as well as Figure 4 As shown, an annular recess 3b is formed in the bearing housing 3. The recess 3b includes a third surface 3c that faces the variable capacity mechanism 30. The third surface 3c is the bottom surface of the recess 3b. A plurality (e.g., three) of second holes 3d are formed in the third surface 3c. The second holes 3d are elongated holes extending in a radial direction (hereinafter referred to as "radial direction") intersecting the rotation axis AX.

[0052] When viewed axially, the length of the second hole 3d in the radial direction is greater than the width of the second hole 3d in the circumferential direction. When viewed axially, the second hole 3d includes a radially extending middle portion and end portions connected to both ends of the radially extending middle portion. Each end portion may be, for example, semicircular in shape. The diameter of the semicircle is the same as the width of the circumferential middle portion. The second hole 3d does not penetrate the bearing housing 3. In other words, the second hole 3d has a bottom surface.

[0053] like Figure 5 As shown, the first surface 32d and the second surface 35c of the variable capacity mechanism 30 are separated from the third surface 3c of the bearing housing 3. The limiting member 40 is provided between the variable capacity mechanism 30 and the bearing housing 3 to maintain the positional relationship between the nozzle ring 32 and the drive ring 35 in the axial direction, and to maintain the positional relationship between the variable capacity mechanism 30 and the bearing housing 3 in the circumferential direction.

[0054] Specifically, the limiting component 40 is fixed to the variable capacity mechanism 30. The limiting component 40 has a flange portion 41, a drive ring guide pin portion 42 (first pin) and a phase-fixing pin portion 43 (second pin). The flange portion 41 is in the shape of a circular plate. The flange portion 41 spans the first surface 32d and the second surface 35c. The flange portion 41 overlaps with a portion of the first surface 32d and a portion of the second surface 35c when viewed from the axial direction. The diameter of the flange portion 41 is larger than the diameter of the first hole 32e. The outer edge 41c of the flange portion 41 has a portion that is located on the side opposite to the rotation axis AX than the outer edge 32r of the nozzle ring body 32a (refer to Figure 3 The outer edge 41c of the flange portion 41 has a portion located on the opposite side of the rotation axis AX from the inner edge 35d of the drive ring 35 (see Figure 3 ).

[0055] The thickness of the flange portion 41 is smaller than the distance between the first surface 32d and the third surface 3c. The limiting surface 41a of the flange portion 41 abuts against the first surface 32d. The surface 41b of the flange portion 41 on the side opposite to the limiting surface 41a is separated from the third surface 3c. The flange portion 41 maintains the positional relationship between the nozzle ring 32 and the drive ring 35 in the axial direction. The flange portion 41 prevents the drive ring 35 from falling off the nozzle ring 32. Specifically, when the drive ring 35 moves axially relative to the nozzle ring 32 toward the bearing box 3, the drive ring 35 abuts against the limiting surface 41a of the flange portion 41. In other words, the axial movement of the drive ring 35 is limited by the flange portion 41.

[0056] Furthermore, the thickness of the drive ring 35 is smaller than the distance between the first surface 32d and the guide surface 32f of the nozzle ring flange 32b (the surface facing the drive ring 35). In other words, the thickness of the drive ring 35 is smaller than the distance between the restriction surface 41a and the guide surface 32f. Consequently, the drive ring 35 is rotatable between the guide surface 32f and the restriction surface 41a.

[0057] The drive ring guide pin portion 42 is provided on the limiting surface 41a of the flange portion 41. The drive ring guide pin portion 42 is formed integrally with the flange portion 41. The drive ring guide pin portion 42 is cylindrical in shape. The diameter of the drive ring guide pin portion 42 is smaller than the diameter of the flange portion 41. The length of the drive ring guide pin portion 42 is smaller than the depth of the first hole 32e. The drive ring guide pin portion 42 is arranged in the first hole 32e. The drive ring guide pin portion 42 is fixed to the nozzle ring 32. The drive ring guide pin portion 42 is pressed into the first hole 32e. As a result, the position of the flange portion 41 relative to the nozzle ring 32 is fixed. The drive ring guide pin portion 42 is separated from the bottom surface of the first hole 32e.

[0058] The phasing pin portion 43 is provided on the surface 41b of the flange portion 41. The phasing pin portion 43 is formed integrally with the flange portion 41. The shape of the phasing pin portion 43 is cylindrical. The diameter of the phasing pin portion 43 is smaller than the diameter of the flange portion 41. The diameter of the phasing pin portion 43 is larger than the diameter of the drive ring guide pin portion 42. The length of the phasing pin portion 43 is larger than the distance between the surface 41b of the flange portion 41 and the third surface 3c. The length of the phasing pin portion 43 is larger than the depth of the second hole 3d. The front end portion of the phasing pin portion 43 is arranged in the second hole 3d. The phasing pin portion 43 is separated from the bottom surface of the second hole 3d.

[0059] The diameter of the phasing pin portion 43 is the same as or slightly smaller than the circumferential width of the second hole 3d. The phasing pin portion 43 is inserted into the second hole 3d. The side surfaces of the phasing pin portion 43 are in contact with the side surfaces of the middle portion of the second hole 3d (side surfaces that are opposite to each other in the circumferential direction). The phasing pin portion 43 is movable in the radial direction relative to the second hole 3d. In other words, when the phasing pin portion 43 is arranged in the second hole 3d, radial movement of the phasing pin portion 43 is allowed, and movement of the phasing pin portion 43 in other directions is prohibited.

[0060] Effects

[0061] As described above, according to the supercharger 1, the flange portion 41 maintains the axial positional relationship between the nozzle ring 32 and the drive ring 35. Furthermore, the drive ring guide pin portion 42 and the first hole 32e, and the phasing pin portion 43 and the second hole 3d, maintain the circumferential positional relationship between the bearing housing 3 and the variable displacement mechanism 30. Specifically, in the supercharger 1, the restricting member 40 maintains the positional relationship between the nozzle ring 32 and the drive ring 35, and also the positional relationship between the bearing housing 3 and the variable displacement mechanism 30. Consequently, for example, compared to a case where the positional relationship between the nozzle ring 32 and the drive ring 35, and the positional relationship between the bearing housing 3 and the variable displacement mechanism 30, is maintained by separate components, increasing the available space on the first surface 32d of the nozzle ring 32 and the second surface 35c of the drive ring 35. Consequently, the degree of freedom in the design of the variable displacement mechanism 30 is increased. Furthermore, since additional restricting members 40 can be provided in the increased available space on the first surface 32d of the nozzle ring 32 and the second surface 35c of the drive ring 35, by increasing the number of restricting members 40, it is possible to suppress wear of the phasing pins 43, for example. Furthermore, according to the supercharger 1, for example, the number of components can be reduced compared to a case where the positional relationship between the nozzle ring 32 and the drive ring 35, and the positional relationship between the bearing housing 3 and the variable displacement mechanism 30, are maintained by separate components, thereby simplifying assembly and reducing costs.

[0062] Figures 8 to 10 1B is a diagram showing a turbocharger 1B of a comparative example. Figure 8 as well as Figure 9 As shown, the supercharger 1B includes a restricting member 40B. The restricting member 40B differs from the restricting member 40 in that it does not include a phasing pin portion 43. The restricting member 40B maintains only the positional relationship between the nozzle ring 32 and the drive ring 35 in the axial direction and does not maintain the positional relationship between the variable displacement mechanism 30 and the bearing housing 3 in the circumferential direction.

[0063] like Figure 10 As shown, in the supercharger 1B, the circumferential positional relationship between the variable displacement mechanism 30B and the bearing housing 3B is maintained by the pin 3e of the bearing housing 3B and the hole 32m of the variable displacement mechanism 30B. Specifically, in the variable displacement mechanism 30B, a plurality of holes 32m are formed on the first surface 32d of the nozzle ring 32. Furthermore, the pin 3e of the bearing housing 3B is inserted into each of these holes 32m. Thus, in the supercharger 1B of the comparative example, the first surface 32d of the nozzle ring 32 requires not only a location for the restriction member 40B but also a location for the plurality of holes 32m.

[0064] In contrast, in the supercharger 1 of the embodiment, as described above, the restricting member 40 maintains the positional relationship between the nozzle ring 32 and the drive ring 35, and also maintains the positional relationship between the bearing housing 3 and the variable displacement mechanism 30. Therefore, unlike the supercharger 1B of the comparative example, it is not necessary to provide the hole 32m or the like on the first surface 32d of the nozzle ring 32 in order to maintain the circumferential positional relationship between the bearing housing 3 and the variable displacement mechanism 30. As described above, this increases the available space on the first surface 32d of the nozzle ring 32 and the second surface 35c of the drive ring 35.

[0065] The number of parts in the variable capacity mechanism is large, so there are cases where the configuration of each part is strictly restricted. In such a variable capacity mechanism, it is particularly important for one part to have multiple functions, such as the limiting part 40. Specifically, for example, Figure 10 As shown, in the variable displacement mechanism 30B of the comparative example, a plurality of nozzle linking plates 36 and a plurality of restricting members 40B are arranged on the first surface 32d of the nozzle ring 32 and the second surface 35c of the drive ring 35. Furthermore, a plurality of pin holes 32p and a plurality of holes 32m are formed on the first surface 32d.

[0066] When designing such a variable displacement mechanism, for example, first, space is secured on the first surface 32d and the second surface 35c for arranging the plurality of nozzle linking plates 36. Next, space is secured on the first surface 32d and the second surface 35c for arranging the plurality of pin holes 32p, excluding the space for arranging the plurality of nozzle linking plates 36. Next, space is secured on the first surface 32d and the second surface 35c for arranging the plurality of restricting members 40B, excluding the space for arranging the plurality of nozzle linking plates 36 and the plurality of pin holes 32p. Next, space is secured on the first surface 32d and the second surface 35c for arranging the plurality of holes 32m, excluding the space for arranging the plurality of nozzle linking plates 36, the plurality of pin holes 32p, and the plurality of restricting members 40B.

[0067] Thus, in the design of the variable capacity mechanism 30, space is sequentially secured for arranging various components and the like on the circumference centered on the rotation axis AX. That is, components such as the nozzle link plate 36 and the pin hole 32p are arranged in a limited area on the circumference centered on the rotation axis AX. Therefore, for components and the like that are arranged relatively late in the order of securing space (hereinafter referred to as "these components and the like"), there is a concern that the degree of freedom in the design of the components and the like will be reduced because there is relatively little remaining space. Specifically, for example, it is considered that the components and the like are arranged in a position that is offset from the ideal position where they should be arranged, or that the size of the components and the like is smaller than the ideal size. Therefore, in the variable capacity mechanism 30, it is particularly important to increase the available space on the first surface 32d and the second surface 35c.

[0068] Furthermore, the drive ring guide pin portion 42 is fixed to the nozzle ring 32. According to this configuration, by fixing the drive ring guide pin portion 42 to the nozzle ring 32, the position of the flange portion 41 relative to the nozzle ring 32 can be fixed.

[0069] In addition, the second hole 3d is a long hole extending in the radial direction. The diameter of the phasing pin portion 43 is smaller than the width of the second hole. When the supercharger 1 is in operation, high-temperature gas is supplied to the supercharger 1. As a result, the temperature of the components such as the variable capacity mechanism 30 constituting the supercharger 1 rises. If the temperature of the components rises, thermal deformation of the components occurs. The degree of thermal deformation of the components constituting the supercharger 1 with respect to temperature varies. According to the above-mentioned structure, when the phasing pin portion 43 is arranged in the second hole 3d, the radial movement of the phasing pin portion 43 is allowed, thereby allowing radial thermal deformation of the bearing box 3 and the variable capacity mechanism 30.

[0070] Furthermore, the diameter of the phasing pin portion 43 is larger than the diameter of the drive ring guide pin portion 42. This configuration relatively increases the diameter of the phasing pin portion 43, thereby relatively increasing the surface area of the phasing pin portion 43. This reduces wear on the phasing pin portion 43.

[0071] Alternatively, all of the plurality of restricting members 40 may include the flange portion 41, the drive ring guide pin portion 42A, and the phasing pin portion 43A. This configuration more reliably maintains the axial positional relationship between the nozzle ring 32 and the drive ring 35, thereby ensuring structural stability of the supercharger 1 including the variable displacement mechanism 30.

[0072] In addition, the supercharger 1 includes multiple limiting components 40. A plurality of first holes 32e are formed on the first surface 32d, for accommodating the drive ring guide pin portions 42 of each of the multiple limiting components 40. A plurality of second holes 3d are formed on the third surface 3c, for accommodating the phasing pin portions 43 of each of the multiple limiting components 40. According to this structure, the multiple limiting components 40 can more reliably maintain the positional relationship between the nozzle ring 32 and the drive ring 35 in the axial direction. As a result, changes in the positional relationship between the nozzle ring 32 and the drive ring 35 caused by thermal deformation can be suppressed. Therefore, undesirable movement of the variable capacity mechanism 30 that may occur due to changes in the positional relationship between the nozzle ring 32 and the drive ring 35 can be suppressed, thereby reliably exerting the performance of the supercharger 1.

[0073] As mentioned above, when the supercharger 1 is in operation, the components that comprise the supercharger 1 experience varying degrees of thermal deformation due to temperature. Differences in the degree of thermal deformation cause changes in the positional relationship between the components. This change in the positional relationship between the components affects the characteristics of the supercharger 1. According to the above-described structure, even in the event of thermal deformation, the positional relationship between the bearing housing 3 and the variable displacement mechanism 30 is maintained by the constraints imposed by the multiple phasing pins 43 and the multiple second holes 3d. Therefore, the supercharger 1 can achieve desired performance even during operation. Specifically, the nozzle ring 32 of the embodiment expands overall due to thermal deformation. Thermal deformation is isotropic in the circumferential direction and does not vary depending on the orientation. Therefore, the multiple phasing pins 43 and the multiple second holes 3d only allow for radial deformation. Furthermore, thermal deformation creates a gap between the inner circumferential surface 32g of the nozzle ring 32 and the outer circumferential surface of the protrusion 3a of the bearing housing 3. This gap causes the relative positional relationship between the bearing housing 3 and the nozzle ring 32 to change. However, the parallel movement of the variable capacity mechanism 30 is restricted by the multiple phasing pins 43 and the multiple second holes 3d. Furthermore, the directions of movement permitted by a corresponding phasing pin 43 and a corresponding second hole 3d differ from the directions of movement permitted by other phasing pins 43 and other second holes 3d that are different from the corresponding phasing pins 43 and second holes 3d. Therefore, the nozzle ring 32 effectively restricts parallel movement in all directions. In other words, the nozzle ring 32 only permits isotropic expansion or contraction with the center of the nozzle ring 32 as the starting point. As a result, the relative positional relationship between the bearing housing 3 and the variable capacity mechanism 30 can be maintained even in the event of thermal deformation. Therefore, the supercharger 1 can achieve the desired performance even during operation.

[0074] <Second embodiment>

[0075] like Figure 6 as well as Figure 7 As shown, the supercharger 1A of the second embodiment differs from the supercharger 1 of the first embodiment primarily in that a restriction member 40A is provided in place of the restriction member 40, and that the restriction member 40A is fixed to the bearing housing 3A. The remaining structure of the supercharger 1A of the second embodiment is the same as that of the supercharger 1 of the first embodiment, and therefore detailed description thereof will be omitted.

[0076] Instead of the multiple first holes 32e, the first surface 32d of the variable volume mechanism 30A includes multiple first holes 32n. The first holes 32n are elongated holes extending radially. When viewed axially, the radial length of the first holes 32n is greater than the circumferential width of the first holes 32n. When viewed axially, the first holes 32n include a radially extending middle portion and end portions connected to both ends of the radially extending middle portion. Each end portion is, for example, semicircular in shape. The diameter of the semicircle is the same as the circumferential width of the middle portion. The first holes 32n do not penetrate the nozzle ring 32. In other words, the first holes 32n have a bottom surface.

[0077] A plurality of second holes 3f are formed on the third surface 3c of the variable displacement mechanism 30A instead of the plurality of second holes 3d. The cross-sectional shape of the second holes 3f is circular. The second holes 3f do not penetrate the bearing housing 3A. In other words, the second holes 3f have a bottom surface.

[0078] The limiting member 40A is fixed to the bearing housing 3A. The limiting member 40A includes a flange portion 41, a connecting portion 41A, a drive ring guide pin portion 42A, and a phasing pin portion 43A. The diameter of the flange portion 41 is larger than the width of the first hole 32n in the circumferential direction. The diameter of the flange portion 41 is larger than the width of the first hole 32n in the radial direction.

[0079] The connecting portion 41A is provided on the surface 41b of the flange portion 41. The connecting portion 41A is integrally formed with the flange portion 41. The connecting portion 41A has a cylindrical shape. The diameter of the connecting portion 41A is smaller than the diameter of the flange portion 41. The diameter of the connecting portion 41A is larger than the diameter of the second hole 3f. The length of the connecting portion 41A is approximately the same as the distance between the surface 41b of the flange portion 41 and the third surface 3c. The surface 41d of the connecting portion 41A opposite the flange portion 41 abuts the third surface 3c.

[0080] The phase-fixing pin portion 43A is provided on the surface 41d of the connecting portion 41A. The phase-fixing pin portion 43A is formed integrally with the connecting portion 41A. That is, the phase-fixing pin portion 43A is formed integrally with the connecting portion 41A and the flange portion 41. The shape of the phase-fixing pin portion 43A is cylindrical. The diameter of the phase-fixing pin portion 43A is smaller than the diameter of the connecting portion 41A. The length of the phase-fixing pin portion 43A is smaller than the depth of the second hole 3f. The phase-fixing pin portion 43A is arranged in the second hole 3f. The phase-fixing pin portion 43A is fixed to the bearing box 3A. The phase-fixing pin portion 43A is pressed into the second hole 3f. As a result, the position of the flange portion 41 relative to the nozzle ring 32 is fixed. The phase-fixing pin portion 43A is separated from the bottom surface of the second hole 3f.

[0081] The drive ring guide pin portion 42A is provided on the limiting surface 41a of the flange portion 41. The drive ring guide pin portion 42A is integrally formed with the flange portion 41. The drive ring guide pin portion 42A is cylindrical in shape. The diameter of the drive ring guide pin portion 42A is larger than the diameter of the phasing pin portion 43A. The diameter of the drive ring guide pin portion 42A is approximately the same as the diameter of the connecting portion 41A. The drive ring guide pin portion 42A is disposed in the first hole 32n. The drive ring guide pin portion 42A is separated from the bottom surface of the first hole 32n.

[0082] The diameter of the drive ring guide pin portion 42A is smaller than the circumferential width of the first hole 32n. The drive ring guide pin portion 42A is inserted into the first hole 32n. The side surfaces of the drive ring guide pin portion 42A contact the side surfaces of the middle portion of the first hole 32n (side surfaces that face each other in the circumferential direction). The drive ring guide pin portion 42A is movable radially relative to the first hole 32n. In other words, when the drive ring guide pin portion 42A is positioned in the first hole 32n, radial movement of the drive ring guide pin portion 42A is permitted, while movement of the drive ring guide pin portion 42A in other directions is prohibited.

[0083] As described above, in the turbocharger 1A of the second embodiment, the phasing pins 43A are fixed to the bearing housing 3A. With this configuration, the position of the flange 41 relative to the nozzle ring 32 can be fixed by fixing the phasing pins 43A to the bearing housing 3A.

[0084] The first hole 32n is a long hole extending in the radial direction. The diameter of the drive ring guide pin portion 42A is smaller than the width of the first hole 32n. This structure allows for radial thermal deformation of the bearing housing 3A and the variable capacity mechanism 30A, as described above.

[0085] Furthermore, the diameter of the drive ring guide pin portion 42A is larger than the diameter of the phasing pin portion 43A. This configuration increases the diameter of the drive ring guide pin portion 42A, thereby increasing the surface area of the drive ring guide pin portion 42A. This reduces wear on the drive ring guide pin portion 42A.

[0086] The above describes an embodiment of the supercharger of the present invention. The supercharger of the present invention is not limited to the above embodiment. For example, an example is shown in which all of the multiple limiting components 40 have a flange portion 41, a drive ring guide pin portion 42, and a phasing pin portion 43. However, at least one of the multiple limiting components 40 may also have a flange portion 41, a drive ring guide pin portion 42, and a phasing pin portion 43. In other words, two of the three limiting components 40 may also have a flange portion 41, a drive ring guide pin portion 42, and a phasing pin portion 43, while the other limiting component 40 may have a flange portion 41 and a drive ring guide pin portion 42 but not a phasing pin portion 43. Furthermore, one of the three limiting components 40 may also have a flange portion 41, a drive ring guide pin portion 42, and a phasing pin portion 43, while the other two limiting components 40 may have a flange portion 41 and a drive ring guide pin portion 42 but not a phasing pin portion 43.

[0087] Description of Reference Numerals

[0088] 1, 1A…supercharger; 2…rotating shaft; 3, 3A…bearing housing; 3c…third surface; 3d, 3f…second hole; 12…turbine impeller; 30, 30A…variable capacity mechanism; 32…nozzle ring; 32d…first surface; 32e, 32n…first hole; 35…drive ring; 35c…second surface; 40, 40A…limiting component; 41…flange portion; 42, 42A…drive ring guide pin portion (first pin); 43, 43A…phasing pin portion (second pin); AX…rotation axis.

Claims

1. A supercharger, characterized in that: have: a bearing housing that rotatably supports a rotating shaft to which the turbine impeller is fixed; a variable capacity mechanism surrounding the turbine impeller and guiding fluid toward the turbine impeller; and a plurality of limiting components disposed between the bearing housing and the variable capacity mechanism; The variable capacity mechanism has: a nozzle ring surrounding the turbine impeller in a circumferential direction centered on the rotation axis of the rotation shaft; and a drive ring surrounding the nozzle ring in the circumferential direction, The nozzle ring includes a first face opposite the bearing housing, The drive ring includes a second surface opposite to the bearing housing, The bearing housing includes a third surface opposite to the variable capacity mechanism, At least one of the plurality of limiting components has: a flange portion spanning the first surface and the second surface and fixed in position relative to the nozzle ring; a first pin formed integrally with the flange portion and disposed in a first hole formed in the first surface; as well as A second pin is formed integrally with the flange portion and is disposed in a second hole formed in the third surface, and The first pin is fixed to the first hole, and the diameter of the second pin is smaller than the width of the second hole, so that the second pin can move in the second hole in a radial direction intersecting the rotation axis, and The first pin and the second pin extend in an axial direction of the rotation axis, and a diameter of the second pin remains constant along the axial direction and is larger than a diameter of the first pin.

2. The supercharger according to claim 1, characterized in that The cross-section of the first hole is circular.

3. The supercharger according to claim 1, characterized in that The first hole has a bottom surface.

4. The supercharger according to claim 1, characterized in that The second hole is a long hole extending in the radial direction.

5. The supercharger according to claim 1, characterized in that When viewed from the axial direction of the rotation axis, the length of the second hole in the radial direction is greater than the width of the second hole in the circumferential direction.

6. The supercharger according to claim 1, characterized in that The second hole has: a middle portion extending in the radial direction; and end portions, which are connected to both ends of the middle portion in the radial direction, and The end portions are each semicircular in shape.

7. The supercharger according to claim 6, characterized in that The diameter of the semicircle is the same as the width of the middle portion in the circumferential direction.

8. The supercharger according to claim 1, characterized in that The second hole has a bottom surface.

9. The supercharger according to claim 1, characterized in that The outer edge of the flange portion includes a portion located on the side opposite to the rotation axis relative to the outer edge of the nozzle ring body, and The outer edge of the flange portion includes a portion located on a side opposite to the rotation axis relative to an inner edge of the drive ring.

10. The supercharger according to claim 1, characterized in that The thickness of the flange portion is smaller than the distance between the first surface and the third surface.

11. The supercharger according to claim 1, characterized in that The restriction surface of the flange portion abuts against the first surface.

12. The supercharger according to claim 11, characterized in that A surface of the flange portion opposite to the regulating surface is separated from the third surface.

13. The supercharger according to claim 1, characterized in that The thickness of the drive ring is smaller than the distance between the first surface and a guide surface of the nozzle ring flange of the nozzle ring, the guide surface being opposite to the drive ring.

14. The supercharger according to claim 1, characterized in that All of the plurality of restriction members include the flange portion, the first pin, and the second pin.

15. The supercharger according to claim 3, characterized in that The first pin is separated from the bottom surface of the first hole.

16. The supercharger according to claim 8, characterized in that The second pin is separated from the bottom surface of the second hole, and The bottom surface of the second hole extends along the radial direction.

17. The supercharger according to claim 1, characterized in that An outer edge of the main body of the nozzle ring and an inner edge of the driving ring are opposite to each other with a gap therebetween.

18. The supercharger according to claim 1, characterized in that The outer edge of the main body of the nozzle ring and the outer edge of the second pin on the side opposite to the rotation axis are substantially aligned in the axial direction of the rotation axis.

19. The supercharger according to claim 1, characterized in that The inner edge of the second pin on the side of the rotation axis and the inner edge of the first hole on the side of the rotation axis extend in the axial direction of the rotation axis, and The inner edge of the second pin on the side of the rotation axis and the inner edge of the first hole on the side of the rotation axis are not aligned but offset from each other.

20. A supercharger, characterized in that: have: a bearing housing that rotatably supports a rotating shaft to which the turbine impeller is fixed; a variable capacity mechanism surrounding the turbine impeller and guiding fluid toward the turbine impeller; and a plurality of limiting components disposed between the bearing housing and the variable capacity mechanism; The variable capacity mechanism has: a nozzle ring surrounding the turbine impeller in a circumferential direction centered on the rotation axis of the rotation shaft; and a drive ring surrounding the nozzle ring in the circumferential direction, The nozzle ring includes a first face opposite the bearing housing, The drive ring includes a second surface opposite to the bearing housing, The bearing housing includes a third surface opposite to the variable capacity mechanism, At least one of the plurality of limiting components has: a flange portion spanning the first surface and the second surface and fixed in position relative to the nozzle ring; a first pin formed integrally with the flange portion and disposed in a first hole formed in the first surface; as well as A second pin is formed integrally with the flange portion and is disposed in a second hole formed in the third surface, and The second pin is fixed to the second hole, and the diameter of the first pin is smaller than the width of the first hole, so that the first pin can move in the first hole in a radial direction intersecting the rotation axis, and The first pin and the second pin extend in an axial direction of the rotation axis, and a diameter of the first pin remains constant along the axial direction and is larger than a diameter of the second pin.

21. The supercharger according to claim 20, characterized in that The second pin is fixed to the bearing housing.

22. The supercharger according to claim 21, characterized in that The first hole is a long hole extending in a radial direction intersecting the rotation axis.

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