WO2015098826A1

WO2015098826A1 - Compressor and supercharger

Info

Publication number: WO2015098826A1
Application number: PCT/JP2014/083891
Authority: WO
Inventors: 泰治手塚; 中村　敏夫
Original assignee: 三菱重工業株式会社
Priority date: 2013-12-24
Filing date: 2014-12-22
Publication date: 2015-07-02
Also published as: EP3051144B1; KR101844166B1; EP3051144A1; EP3051144A4; CN105814319B; JP6133439B2; JPWO2015098826A1; CN105814319A; KR20160062100A

Abstract

Provided is a compressor (13) having: a compressor impeller (31) secured to a rotor shaft (14); an air-guiding pipe (34) arranged on the outer peripheral side of the compressor impeller (31), the air-guiding pipe (34) guiding air taken in from an air intake port (32) to the compressor impeller (31); a scroll (36) arranged on the outer peripheral side of the air-guiding pipe (34), the scroll (36) guiding compressed air pressurized by the compressor impeller (31); and a containment ring (51) arranged between the air-guiding pipe (34) and the scroll (36).

Description

Compressor and turbocharger

The present invention relates to a supercharger that performs supercharging using exhaust gas discharged from a compressor and an exhaust turbine.

The turbocharger is configured such that a turbine and a compressor are integrally connected by a rotor shaft and are rotatably accommodated in a housing. The exhaust gas is supplied into the housing, and the rotor is driven and rotated by rotating the turbine, thereby driving the compressor. The compressor sucks air from the outside, pressurizes it with an impeller to form compressed air, and supplies this compressed air to a diesel engine or the like. In addition, as such a supercharger, there exist some which were described in patent document 1, for example.

By the way, in such a supercharger, when the impeller bursts, it is required that the burst impeller is not scattered outward in the radial direction, and that the silencer on the exhaust gas intake side is damaged and does not open. . In the conventional turbocharger, an air guide tube is disposed outside the impeller, but since this air guide tube is manufactured by casting, the strength is not sufficient for impact force, and the air guide tube There is a risk of damaging the scroll (vortex chamber) outside the guide tube. As a countermeasure, it is conceivable to increase the strength by increasing the thickness of the air guide cylinder, but as a result, the air guide cylinder will not be damaged, but after the impeller collides with the air guide cylinder, the exhaust gas intake May scatter to the side, causing damage to the silencer and opening of the mouth.

For example, Patent Document 2 discloses a technique for solving such a problem. The exhaust turbine supercharger described in Patent Document 2 includes a turbine housing, a compressor housing, and a bearing housing, and a lubricating oil head tank is provided in the bearing housing, and the lubricating oil head tank is positioned closer to the compressor than the turbine blades. And a compressor-side partition located on the turbine side from the compressor impeller, and an impact-absorbing partition located at a distance from the compressor-side partition to the compressor.

JP 2011-117417 A JP 2001-132465 A

In the exhaust turbine supercharger of Patent Document 2 described above, a turbine side partition is provided on the compressor side from the turbine blades, a compressor side partition is provided on the turbine side, and an interval is provided from the compressor side partition to the compressor side. A shock absorbing partition is provided. In this case, the breakage of the scroll cannot be prevented when the impeller bursts.

This invention solves the subject mentioned above, and aims at providing the compressor and supercharger which can prevent the breakage of the scroll at the time of the burst of an impeller.

In order to achieve the above object, a compressor according to an aspect of the present invention includes an impeller fixed to a rotor shaft, and a fluid that is disposed on an outer peripheral side of the impeller and that is taken in from an intake port. A guide tube that guides the car, a scroll that is disposed on an outer peripheral side of the guide tube and that guides compressed air pressurized by the impeller, and a ring member that is disposed between the guide tube and the scroll , Has.

Therefore, when the impeller bursts, the impeller that is scattered outward in the radial direction or a part of the impeller first collides with the guide cylinder, and the impact force is absorbed by damaging the guide cylinder. Thereafter, the impeller or a part of the impeller collides with the ring member, but since the impact force has been reduced in advance, the ring member is not damaged. Therefore, the impeller or part of the impeller is prevented from scattering in the axial direction, and the opening of the mouth is prevented. As a result, it is possible to prevent the scroll from being damaged when the impeller bursts.

In the compressor according to one aspect of the present invention, the scroll is bolted to a housing, the guide cylinder is bolted to the scroll, and the ring member is bolted to the guide cylinder.

Therefore, it is only necessary to insert both members into the housing with the ring member fastened to the guide tube, and fasten the guide tube to the scroll, thereby improving the assemblability.

In the compressor according to an aspect of the present invention, the ring member has one end in the axial direction sandwiched between the scroll and the guide tube, and a fastening bolt passes through the guide tube and the shaft in the ring member. Screw into one end of the direction.

Therefore, the ring member can be firmly supported.

In the compressor according to an aspect of the present invention, only one end of the ring member in the axial direction is fixed to the guide tube.

Therefore, the assembling property can be improved and the elastic force can be secured to the ring member.

In the compressor according to one aspect of the present invention, the guide cylinder includes a guide cylinder main body having a circulation path in an inner peripheral portion, and a guide ring arranged on the upstream side in the fluid flow direction in the circulation path. The guide ring is bolted to the scroll, the guide tube body is bolted to the guide ring, and the ring member is bolted to the guide ring.

Accordingly, the ring member is fastened to the guide ring, and the guide tube main body is fastened to the guide ring, and these are inserted into the housing, and the guide ring is fastened to the scroll. it can.

In the compressor according to one aspect of the present invention, the guide tube and the scroll are manufactured by casting, and the ring member is manufactured by a general structural rolled steel material.

Therefore, if the guide cylinder has a crushable structure, the impact force can be absorbed by the scattered impeller colliding and being damaged, and when the ring member has ensured ductility, The impact force can be properly absorbed by the elastic force.
In the turbocharger according to one aspect of the present invention, the compressor and the turbine described above are integrally connected by a rotor shaft and are rotatably accommodated in a housing.

According to the compressor and supercharger of the present invention, since the ring member is disposed between the guide cylinder and the scroll, it is possible to prevent the scroll from being damaged when the impeller bursts.

FIG. 1 is a schematic sectional view showing the supercharger of the first embodiment. FIG. 2 is a cross-sectional view of a main part of the supercharger. FIG. 3 is a cross-sectional view of a main part showing a supercharger according to the second embodiment.

Hereinafter, preferred embodiments of a compressor and a supercharger according to the present invention will be described in detail with reference to the accompanying drawings. In addition, this invention is not limited by this embodiment, and when there are two or more embodiments, what comprises combining each embodiment is also included.

[First Embodiment]
FIG. 1 is a schematic cross-sectional view showing a supercharger according to the first embodiment, and FIG. 2 is a main cross-sectional view of the supercharger.

In the first embodiment, as shown in FIG. 1, the supercharger 11 is an exhaust turbine supercharger, for example, a cylinder liner that constitutes a marine diesel engine by being mounted on a marine diesel engine (not shown). The compressed air is supplied to an air supply manifold that communicates with the interior of the air supply.

The turbocharger 11 is configured such that a turbine 12 and a compressor 13 are integrally connected by a rotor shaft 14 and are rotatably accommodated in a housing 15.

The housing 15 has a hollow shape, the rotor shaft 14 is disposed inside, and is rotatably supported by a thrust bearing 21 and

radial bearings

22 and 23. The rotor shaft 14 has a turbine disk 24 fixed to one end portion in the axial direction. The turbine disk 24 has a plurality of turbine blades 25 having an axial flow type provided at a predetermined interval in the circumferential direction. The turbine 12 includes the turbine disk 24 and a plurality of turbine blades 25.

The housing 15 is provided with an exhaust gas inlet passage 26 and an exhaust gas outlet passage 27 with respect to the turbine blade 25. Further, the housing 15 is provided with a turbine nozzle 28 between the inlet passage 26 and the turbine blade 25, and the axial exhaust gas flow statically expanded by the turbine nozzle 28 is guided to the plurality of turbine blades 25. Thus, the turbine 12 can be driven to rotate.

The rotor shaft 14 has a compressor impeller 31 having a plurality of blades 31a provided at predetermined intervals in the circumferential direction fixed to the other end in the axial direction. The compressor 13 is constituted by the compressor impeller 31. The housing 15 is provided with an air intake port 32 and a compressed air discharge port 33 with respect to the compressor impeller 31. The housing 15 is provided with an air guide tube 34 between the compressor impeller 31 and the air intake port 32, while a diffuser 35 and a vortex chamber 36 a are provided between the compressor impeller 31 and the compressed air discharge port 33. A scroll 36 is provided. The air compressed by the compressor impeller 31 is discharged through the diffuser 35 and the scroll 36 (vortex chamber 36a). The housing 15 has a silencer 37 attached to the air intake 32.

Accordingly, the exhaust gas from the marine diesel engine passes through the exhaust gas inlet passage 26 and is statically expanded by the turbine nozzle 28, and the exhaust gas flow in the axial direction is guided to the plurality of turbine blades 25. The turbine 12 is driven to rotate through the turbine disk 24 to which the turbine blades 25 are fixed. The exhaust gas that has driven the plurality of turbine blades 25 is discharged to the outside from the outlet passage 27. On the other hand, when the rotor shaft 14 rotates, the integral compressor impeller 31 rotates and air is sucked through the air intake port 32. The sucked air is pressurized by the compressor impeller 31 to become compressed air, which passes through the diffuser 35 and the scroll 36 and is supplied from the compressed air discharge port 33 to the marine diesel engine.

As shown in FIGS. 1 and 2, in the compressor 13 configured as described above, the rotor shaft 14 is rotatably supported by the housing 15, and the compressor impeller 31 is integrated with the other end portion of the rotor shaft 14. It is fixed to. The scroll 36 is disposed on the outer side in the radial direction of the compressor impeller 31, and the outer peripheral portion is fixed to the housing 15 with a bolt 41. The scroll 36 has a vortex chamber 36a, and a silencer 37 is fixed to a mounting portion 36b extending to the air intake port 32 side by a bolt 42. Further, the scroll 36 is formed with a mounting flange 36c extending from the mounting portion 36b to the inner peripheral side. The air guide tube 34 is formed with a mounting flange 34a extending outward at one end on the air intake port 32 side. The air guide tube 34 is connected by a bolt 43 with a mounting flange 34 a overlapping the air intake port 32 side of the mounting flange 36 c of the scroll 36. The air guide tube 34 is divided into a mounting flange 34 a side and a main body 34 b side, and is connected by a bolt 45 via a liner 44.

In the scroll 36, a ring-shaped guide plate 46 is fixed to the inner peripheral portion by bolts 47, and the turbine nozzle 28 is attached to the guide plate 46. The air guide cylinder 34 has a curved shape along the outer peripheral surface of the compressor impeller 31 with the intermediate portion in the axial direction protruding toward the inner peripheral side, and the tip end is in close contact with the inner peripheral portion of the scroll 36 via the O-ring 48. ing.

In the compressor 13 of this embodiment, a containment ring 51 is disposed between the air guide tube 34 and the scroll 36. The containment ring 51 is bolted to the air guide tube 34. That is, the containment ring 51 has a ring shape in which the inner diameter and the outer diameter are constant in the axial direction, and one end in the axial direction is the outer peripheral surface of the mounting flange 36 c in the scroll 36 and the outer periphery of the mounting flange 34 a in the air guide tube 34. It is pinched by the surface. The containment ring 51 has one end face in the axial direction in close contact with the mounting flange 34a, and the fastening bolt 52 passes through the mounting flange 34a and is screwed into the one end. Therefore, only the one end part in the axial direction of the containment ring 51 is fixed to the end part on the air intake port 32 side of the air guide tube 34.

The air guide tube 34 and the scroll 36 are castings manufactured by casting, and the containment ring 51 is a ring member manufactured by a general structural rolled steel (for example, SS400). That is, the air guide tube 34 and the scroll 36 are manufactured with high precision by casting a complicated shape, but the strength against impact is not sufficient. On the other hand, the containment ring 51 is manufactured from a general structural rolled steel material with a simple shape. In particular, the containment ring 51 is more ductile than the air guide tube 34 and has sufficient strength against impact.

Therefore, when the compressor impeller 31 in the turbocharger 11 bursts for some reason, a part of the bursted compressor impeller 31 is scattered outward in the radial direction. First, a part of the compressor impeller 31 is guided to the air. Collide with the cylinder 34. Since the air guide tube 34 is manufactured by casting, the strength against impact is not sufficient, and since the air guide tube 34 has a crushable structure, it is damaged and the impact force of the compressor impeller 31 is absorbed. Subsequently, the compressor impeller 31 collides with the containment ring 51. Since the containment ring 51 is made of rolled steel for general structure, it has high ductility and sufficient strength against impact, so that it receives and absorbs the impact force of the compressor impeller 31 without being damaged. . Therefore, the scroll 36 is not damaged, and the compressor impeller 31 is not scattered in the axial direction, so that the silencer 37 is prevented from being damaged and the mouth opening is prevented.

As described above, in the turbocharger according to the first embodiment, the turbine 12 and the compressor 13 are integrally connected by the rotor shaft 14 and are rotatably accommodated in the housing 15. 14, a compressor impeller 31 fixed to 14, an air guide cylinder 34 that is disposed on the outer peripheral side of the compressor impeller 31 and guides the air taken in from the air intake port 32 to the compressor impeller 31, and an air guide cylinder 34 The scroll 36 which guides the compressed air which was arrange | positioned at the outer peripheral side of this, and was pressurized by the compressor impeller 31, and the containment ring 51 arrange | positioned between the air guide cylinder 34 and the scroll 36 are provided.

Therefore, when the compressor impeller 31 bursts, the compressor impeller 31 or a part of the compressor impeller 31 scattered outward in the radial direction first collides with the air guide tube 34 and damages the air guide tube 34, thereby causing an impact force. Is absorbed. Thereafter, the compressor impeller 31 or a part thereof collides with the containment ring 51. However, since the impact force is reduced in advance, the containment ring 51 is not damaged. Therefore, the compressor impeller 31 or a part thereof is prevented from being scattered in the axial direction, and the opening of the mouth is prevented. As a result, it is possible to prevent the scroll 36 from being damaged when the compressor impeller 31 is burst.

In the supercharger of the first embodiment, the scroll 36 is bolted to the housing 15, the air guide tube 34 is bolted to the scroll 36, and the containment ring 51 is bolted to the air guide tube 34. . Therefore, in a state where the containment ring 51 is fastened to the air guide tube 34, both are inserted into the housing 15 and the air guide tube 34 is fastened to the scroll 36, so that the assembling property can be improved. In this case, the containment ring 51 can be easily fixed by changing only the air guide tube 34 without changing the scroll 36 or the like.

In the turbocharger according to the first embodiment, the containment ring 51 includes an end portion in the axial direction that is sandwiched between the scroll 36 and the air guide tube 34, and the fastening bolt 52 penetrates the air guide tube 34. 51 is screwed into one end portion in the axial direction. Therefore, the containment ring 51 can be firmly supported on the housing 15 side by clamping the containment ring 51 with the scroll 36 and the air guide tube 34.

In the supercharger of the first embodiment, the containment ring 51 is fixed to the air guide tube 34 only at one end in the axial direction. Therefore, by using the containment ring 51 as a cantilever support, the bolt fastening portion can be reduced and the assemblability can be improved. Further, the containment ring 51 can have an elastic force, and the compressor impeller 31 can be The impact force at the time of collision can be absorbed.

In the supercharger of the first embodiment, the air guide tube 34 and the scroll 36 are cast products manufactured by casting, and the containment ring 51 is a ring member manufactured by using general structural rolled steel. Therefore, if the air guide tube 34 has a crushable structure, the scattered impeller 31 will be properly damaged when it collides, so that the impact force at this time can be absorbed effectively, and the containment ring 51 can be absorbed. When the ductility is ensured, the impact force can be properly absorbed by the elastic force when the scattered compressor impeller 31 collides.

[Second Embodiment]
FIG. 3 is a cross-sectional view of a main part showing a supercharger according to the second embodiment. In addition, the same code | symbol is attached | subjected to the member which has the same function as embodiment mentioned above, and detailed description is abbreviate | omitted.

In the second embodiment, as shown in FIG. 3, the rotor shaft 14 is rotatably supported by the housing 15 by the compressor 61, and the compressor impeller 31 is integrally fixed to the other end portion of the rotor shaft 14. ing. The scroll 36 is disposed on the outer side in the radial direction of the compressor impeller 31, and the outer peripheral portion is fixed to the housing 15 with a bolt 41. The scroll 36 has a vortex chamber 36a, and a silencer 37 is fixed to a mounting portion 36b extending to the air intake port 32 side by a bolt 42. Further, the scroll 36 is formed with a mounting flange 36c extending from the mounting portion 36b to the inner peripheral side.

The air guide cylinder 62 is provided with a recirculation flow path (air circulation path) 63 for preventing surging that tends to occur when the amount of intake air is small. That is, the air guide tube 62 includes an air guide tube main body 64 having a recirculation flow path 63 on the inner peripheral portion, and a guide ring 65 disposed on the upstream side in the air flow direction in the recirculation flow path 63. ing. The air guide tube main body 64 has a curved shape along the outer peripheral surface of the compressor impeller 31 with an intermediate portion in the axial direction protruding toward the inner peripheral side, and a part of the air guide tube main body 64 having a concave shape on the outer peripheral side. A path 63 is formed. The recirculation flow path 63 is provided with an inflow portion 63 a and a discharge portion 63 b with respect to the air passage continuing from the air intake port 32.

The guide ring 65 has a mounting flange 65a extending outward at one end on the air intake port 32 side. The guide ring 65 is connected by a bolt 43 with a mounting flange 65 a overlapping the air intake port 32 side of the mounting flange 36 c of the scroll 36. The air guide tube main body 64 has a proximal end in close contact with the guide ring 65 and is connected by a bolt 66. The scroll 36 has a ring-shaped guide plate 46 fixed to the inner peripheral portion by bolts 47, and the turbine nozzle 28 is attached to the guide plate 46. The air guide tube 62 is in close contact with the inner peripheral portion of the scroll 36 through the O-ring 48 at the tip.

In the compressor 61 of this embodiment, a containment ring 71 is disposed between the air guide tube 62 and the scroll 36. The containment ring 71 is bolted to the air guide tube 62. That is, the containment ring 71 has a ring shape in which the inner diameter and the outer diameter are constant in the axial direction, and one end portion in the axial direction has an inner peripheral surface of the mounting flange 36 c in the scroll 36 and an air guide cylinder main body 64 in the air guide cylinder 62. And the outer peripheral surface of the guide ring 65. Further, the containment ring 71 has one end face in the axial direction in close contact with the mounting flange 65a, and the fastening bolt 52 passes through the mounting flange 65a and is screwed into the one end. Therefore, only one end portion of the containment ring 71 in the axial direction is fixed to the end portion on the air intake port 32 side of the air guide tube 62.

Therefore, when the compressor impeller 31 in the turbocharger 11 bursts for some reason, a part of the bursted compressor impeller 31 is scattered outward in the radial direction. First, a part of the compressor impeller 31 is guided to the air. Collides with the cylinder 62. Since the air guide tube 62 is manufactured by casting, the strength against impact is not sufficient, and since the air guide tube 62 has a crushable structure, it is damaged and the impact force of the compressor impeller 31 is absorbed. Subsequently, the compressor impeller 31 collides with the containment ring 71. Since the containment ring 71 is manufactured from a general structural rolled steel, it has high ductility and sufficient strength against impact, and therefore receives and absorbs the impact force of the compressor impeller 31 without breakage. . Therefore, the scroll 36 is not damaged, and the compressor impeller 31 is not scattered in the axial direction, so that the silencer 37 is prevented from being damaged and the mouth opening is prevented.

Thus, in the supercharger of the second embodiment, the compressor 61 is fixed to the rotor shaft 14 as the compressor 61, and the air intake port 32 is disposed on the outer peripheral side of the compressor impeller 31. An air guide cylinder 62 that guides the air taken in from the compressor impeller 31, a scroll 36 that is arranged on the outer peripheral side of the air guide cylinder 62 and that guides compressed air pressurized by the compressor impeller 31, and an air guide A containment ring 71 disposed between the cylinder 62 and the scroll 36 is provided.

Therefore, when the compressor impeller 31 bursts, the compressor impeller 31 or a part thereof scattered to the outside in the radial direction first collides with the air guide tube 62, and the air guide tube 62 is damaged, thereby causing an impact force. Is absorbed. Thereafter, the compressor impeller 31 or a part thereof collides with the containment ring 71. However, since the impact force has been reduced in advance, the containment ring 71 is not damaged. Therefore, the compressor impeller 31 or a part thereof is prevented from being scattered in the axial direction, and the opening of the mouth is prevented. As a result, it is possible to prevent the scroll 36 from being damaged when the compressor impeller 31 is burst.

In the turbocharger of the second embodiment, the air guide cylinder 62 is disposed on the upstream side of the air flow direction in the recirculation flow path 63 and the air guide cylinder main body 64 having the recirculation flow path 63 on the inner periphery. The guide ring 65 is bolted to the scroll 36, the air guide cylinder body 64 is bolted to the guide ring 65, and the containment ring 71 is bolted to the guide ring 65. Accordingly, the containment ring 71 may be fastened to the guide ring 65, and the air guide cylinder main body 64 may be fastened to the guide ring 65, and these may be inserted into the housing 15 and the guide ring 65 fastened to the scroll 36. Assembling property can be improved.

In this case, the containment ring 71 can be easily fixed by changing only the air guide tube 62 without changing the scroll 36 or the like. Even if the air guide cylinder 62 has the recirculation flow path 63, the containment ring 71 can be properly fixed.

In the above-described embodiment, the containment rings 51 and 71 have a cylindrical shape whose diameter does not change in the axial direction, but may be appropriately set according to the shape of the

air guide tubes

34 and 62, the scroll 36, and the like. For example, it is good also as a shape which provided the shape of a truncated cone cylinder, the shape which combined the cylinder and the truncated cone cylinder, and the rib.

In the above-described embodiment, the supercharger of the present invention is applied to a marine exhaust turbine supercharger. However, the present invention is not limited to this field.

DESCRIPTION OF SYMBOLS 11 Supercharger 12

Turbine

13,61 Compressor 14 Rotor shaft 15 Housing 24 Turbine disk 25 Turbine blade 31 Compressor impeller 32 Air intake port 33 Compressed

air discharge port

34, 62 Air guide cylinder 36 Scroll 37

Silencer

51, 71 Conte Inment ring 63 Recirculation flow path 64 Air guide tube body 65 Guide ring

Claims

An impeller fixed to the rotor shaft;
A guide tube that is arranged on the outer peripheral side of the impeller and guides the fluid taken in from the intake port to the impeller;
A scroll which is arranged on the outer peripheral side of the guide tube and guides compressed air pressurized by the impeller;
A ring member disposed between the guide tube and the scroll;
Having a compressor.
The scroll is bolted to the housing;
The guide tube is bolted to the scroll,
The compressor according to claim 1, wherein the ring member is bolted to the guide tube.
The ring member has one end in the axial direction sandwiched between the scroll and the guide tube, and a fastening bolt passes through the guide tube and is screwed into the one end in the axial direction of the ring member. The compressor described in 1.
The compressor according to claim 2 or 3, wherein only one end portion in the axial direction of the ring member is fixed to the guide tube.
The guide tube has a guide tube main body having a circulation path in an inner peripheral portion, and a guide ring arranged on the upstream side in the fluid flow direction in the circulation path,
The guide ring is bolted to the scroll,
The guide tube body is bolted to the guide ring,
The compressor according to any one of claims 2 to 4, wherein the ring member is bolted to the guide ring.
The guide tube and the scroll are manufactured by casting,
The compressor according to any one of claims 1 to 5, wherein the ring member is manufactured from a general structural rolled steel material.
A turbocharger in which the compressor according to any one of claims 1 to 6 and the turbine are integrally connected by a rotor shaft and are rotatably accommodated in a housing.