WO2016088690A1

WO2016088690A1 - Compressor, supercharger equipped with same and method of adjusting throat passage width of compressor

Info

Publication number: WO2016088690A1
Application number: PCT/JP2015/083512
Authority: WO
Inventors: 白石　啓一
Original assignee: 三菱重工業株式会社
Priority date: 2014-12-02
Filing date: 2015-11-27
Publication date: 2016-06-09
Also published as: CN107002709B; JP2016108956A; KR101965086B1; CN107002709A; JP6621982B2; KR20170074938A

Abstract

The purpose of the present invention is to be able to flexibly handle a variety of specifications while reducing the cost of manufacturing a centrifugal compressor. A compressor (8) comprises: a throat passage (41) that is formed on an outer peripheral side in a radial direction of a compressor impeller (18); a plurality of guide vanes (43) that each have one axial direction end fixed to a passage side surface (92a) of the throat passage (41) and form a diffuser (23); and a spacer plate (45) that has formed therein a plurality of slit holes (47) into which the guide vanes (43) are inserted and that is stacked on the passage side surface (92a). The axial direction height of the guide vanes (43) can be changed by exchanging the spacer plate (45) for a spacer plate of a different thickness. Due to this configuration, a variety of specifications can be flexibly handled by changing the width (W) of the throat passage (41) by appropriately selecting the plate thickness (T) of the spacer plate (45).

Description

Compressor, supercharger equipped with the same, and method for adjusting throat passage width of compressor

The present invention relates to a compressor capable of changing the width of the throat passage and the passage cross-sectional shape, a supercharger provided with the compressor, and a method for adjusting the throat passage width of the compressor.

A centrifugal compressor applied to a compressor in a turbocharger of a large marine diesel engine releases and compresses intake air in a centrifugal direction by a compressor impeller provided integrally with a turbine shaft that is rotationally driven by the exhaust gas of the engine. The air density is increased and supplied to the engine.

Such a centrifugal compressor is equipped with a diffuser. The diffuser has a configuration in which a plurality of guide vanes are fixed in an annular throat passage formed so as to surround the outer peripheral side of the compressor impeller so as to surround the compressor impeller.

As disclosed in Patent Document 1, a large number of guide vanes are provided on the diffuser main plate in order to change the passage area of the compressed air (the width of the diffuser nozzle) by making the passage width in the throat passage of the diffuser variable. The diffuser nozzle is attached to the fixed surface of the throat passage inside the compressor with or without a spacer member, and the passage surface facing this fixed surface is formed with a plurality of grooves into which the tips of the guide vanes enter. Compressors are known.

According to this centrifugal compressor, the width of the throat passage can be adjusted by appropriately selecting the thickness of the spacer member interposed between the back surface and the fixed surface of the diffuser main plate. Thereby, the manufacturing cost of a centrifugal compressor can be reduced, without processing a diffuser nozzle.

JP 50-54909 A

However, even in the centrifugal compressor of Patent Document 1, a disk-shaped diffuser main plate is formed from a steel plate, and a large number of guide vanes are attached to the diffuser main plate, or the diffuser main plate and the guide vanes are integrally cut from the steel ingot. Manufacturing cost was high. In addition, it is difficult to form a plurality of grooves into which the tips of the guide vanes enter the passage surface facing the fixed surface of the diffuser nozzle.

Furthermore, in the structure of Patent Document 1, even though the width of the throat passage can be changed by changing the thickness of the spacer member, the cross-sectional shape of the throat passage cannot be changed, and various engine specifications are available. Could not respond flexibly.

An object of the present invention is to provide a compressor capable of reducing manufacturing costs and flexibly responding to various specifications, a supercharger equipped with the compressor, and a method for adjusting the throat passage width of the compressor.

The compressor according to the first aspect of the present invention includes a throat passage formed on the radially outer peripheral side of the compressor wheel, and a plurality of guide vanes constituting one of the diffuser by fixing one end in the axial direction to the passage side surface of the throat passage. And a spacer plate in which a plurality of slit holes into which the guide vanes are inserted are formed and overlapped on the side surface of the passage.

According to the configuration of the first aspect of the present invention, when the spacer plate is fixed so as to overlap the side surface of the throat passage, each of the plurality of guide vanes provided in the throat passage is formed on the spacer plate. Penetrating through a plurality of slit holes. Then, the width of the throat passage is narrowed by the thickness of the spacer plate, and at the same time, the length of the guide vane is shortened.

Therefore, by appropriately selecting the thickness of the spacer plate, the width of the throat passage can be adjusted to the optimum value without processing the diffuser nozzle, reducing the manufacturing cost of the compressor, and various specifications. Can respond flexibly.

The guide vanes of the compressor of the first aspect may be formed integrally with the side surface of the passage. For example, when the compressor housing in which the throat passage is formed is made of cast iron, the guide vane may be integrally formed with the compressor housing. With this configuration, the guide vanes can be easily formed, and the manufacturing cost of the compressor can be further reduced.

The spacer plate of the compressor of the first aspect may be formed such that the plate thickness on the radially outer peripheral side is smaller than the plate thickness on the radially inner peripheral side. With this configuration, the cross-sectional shape of the throat passage can be changed in the radial direction to obtain an optimum passage shape, and can flexibly respond to various engine specifications.

The supercharger according to the second aspect of the present invention includes any one of the compressors described above.

According to the turbocharger of the second aspect of the present invention, the width of the throat passage is narrowed by the thickness of the spacer plate and at the same time the length of the guide vane is shortened, so the thickness of the spacer plate is appropriately selected. Thus, the width of the throat passage can be adjusted to an optimum value. Therefore, it is possible to flexibly cope with various specifications while reducing the manufacturing cost of the compressor without processing an expensive diffuser nozzle.

The compressor throat passage width adjusting method according to the third aspect of the present invention includes a throat passage formed on the radially outer peripheral side of the compressor wheel, and one end in the axial direction fixed to the passage side surface of the throat passage. A throat passage width adjusting method for a compressor comprising a plurality of guide vanes, wherein a spacer plate formed with a plurality of slit holes into which the guide vanes are inserted is overlapped on a side surface of the passage, and the spacer plate is By changing to a different thickness, the passage width of the throat passage is changed.

According to the compressor throat passage width method according to the third aspect of the present invention, the width of the throat passage is reduced by the plate thickness of the spacer plate by overlapping and fixing the spacer plate on the side surface of the throat passage, The length of the guide vane can be shortened. For this reason, by appropriately selecting the plate thickness of the spacer plate, the width of the throat passage can be adjusted to the optimum value to meet various required specifications.

As described above, according to the compressor according to the present invention, the supercharger including the compressor, and the throat passage width adjusting method of the compressor, it is possible to reduce the manufacturing cost of the compressor and flexibly cope with various specifications. it can.

It is a longitudinal section showing an example of a supercharger in which a centrifugal compressor concerning the present invention was used as a compressor. It is the longitudinal cross-sectional view of the diffuser vicinity which expands the II section of FIG. 1 and shows 1st Embodiment of this invention. It is a perspective view of an inner scroll housing, a guide vane, and a spacer plate. It is a longitudinal cross-sectional view of the diffuser vicinity which shows 2nd Embodiment of this invention. It is a longitudinal cross-sectional view of the diffuser vicinity which shows 3rd Embodiment of this invention. It is a longitudinal cross-sectional view of the diffuser vicinity which shows 4th Embodiment of this invention.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings.

[First Embodiment]
FIG. 1 is a longitudinal sectional view showing an example of a supercharger according to the present invention.
The supercharger 1 of this embodiment is an apparatus that raises the combustion efficiency of a marine large diesel engine by raising the air (gas) supplied to the marine large diesel engine used in the marine vessel to atmospheric pressure or higher. The supercharger 1 includes a turbine shaft 3, a bearing stand 5, an exhaust turbine 6, a centrifugal compressor 8 (compressor), and an intake silencer 10.

The exhaust turbine 6 includes a turbine housing 11 and a turbine impeller 12. The turbine housing 11 is a hollow cylindrical member disposed around the axis of the turbine shaft 3, an exhaust gas passage 14 along the axial direction of the turbine shaft 3, and an exhaust gas inlet 15 that opens in the outer peripheral direction of the turbocharger 1. An exhaust gas outlet 16 is formed, and the turbine impeller 12 is accommodated in the exhaust gas passage 14. The exhaust gas discharged from the marine diesel engine flows from the exhaust gas inlet 15 toward the exhaust gas outlet 16.

The centrifugal compressor 8 includes a compressor housing 9 and a compressor impeller 18. An intake passage 21 is formed in the compressor housing 9. The intake passage 21 includes an intake inlet 22, a diffuser 23 that forms a main part of the present invention, a spiral scroll passage 24, and a compressed gas outlet 25. Is formed.

The compressor wheel 18 is accommodated in the intake passage 21. The compressor impeller 18 is formed of, for example, an aluminum alloy, and a hub 18a that forms the center of the compressor impeller 18 has a shape that increases from the intake upstream side to the downstream side (bearing stand 5 side). A (blade) 18b is projected.

The bearing stand 5 supports the turbine shaft 3 horizontally inside thereof. The turbine shaft 3 is rotatably supported by a pair of

radial bearings

27 and 28 and one thrust bearing 29 and is immovable in the axial direction. A turbine impeller 12 is provided at one end of the turbine shaft 3, and a compressor impeller 18 is provided at the other end coaxially and integrally with the rotation.

The intake silencer 10 is installed on the intake inlet 22 side of the centrifugal compressor 8, and a silencer (not shown) is provided. The silencer absorbs part of the noise generated in the centrifugal compressor 8 and lowers the noise level.

During operation of the large marine diesel engine, on the exhaust turbine 6 side of the turbocharger 1, exhaust gas G of a large, high-temperature marine diesel engine flows from the exhaust gas inlet 15, and this exhaust gas G moves through the exhaust gas passage 14 with an arrow. The turbine impeller 12 is driven to rotate at high speed by flowing in the direction and being discharged from the exhaust gas outlet 16. As a result, the turbine shaft 3 and the compressor impeller 18 integrally rotate at a high speed.

On the centrifugal compressor 8 side, when the compressor impeller 18 rotates, the gas A such as air or gas is sucked into the intake passage 21 through the intake silencer 10 and the intake inlet 22 and compressed by the compressor impeller 18. It is discharged in the centrifugal direction. The discharged gas A is discharged from a compressed gas outlet 25 through a diffuser 23 and a spiral scroll passage 24 and supplied to a large marine diesel engine (not shown).

The compressor housing 9 is disposed on the radially outer side of the compressor wheel 18 and includes, for example, an air guide tube 91, an inner scroll housing 92, and an outer scroll housing 93.

The air guide tube 91 is connected to the inner scroll housing 92 at the position of the intake inlet 22. An intake passage 21 is formed between the air guide tube 91 and the hub 18a of the compressor wheel 18 so that the gas A compressed by the compressor wheel 18 is discharged radially outward.

While the scroll passage 24 is formed between the inner scroll housing 92 and the outer scroll housing 93, the inner scroll housing 92 forms a throat passage 41 between the bearing base 5 as shown in FIG. 2. . The compressed gas discharged from the intake passage 21 is discharged to the scroll passage 28 through the throat passage 41.

Next, the detailed structure of the diffuser 23 according to the present invention will be described.
As shown in FIGS. 2 and 3, the diffuser 23 includes a plurality of guide vanes 43 and a spacer plate 45 in a throat passage 41 formed between the inner scroll housing 92 and the bearing base 5. ing.

The guide vanes 43 are arranged on the radially outer peripheral side of the compressor impeller 18, are installed at equal intervals along the circumferential direction in the throat passage 41, and each has a constant blade cross section along the axial direction of the turbine shaft 3. This is a stationary blade member having a quadratic curved surface extending in a shape.

The guide vane 43 has one end in the axial direction in contact with the end face 92a (passage side face) of the inner scroll housing 92 and the other end in contact with the end face 5a (passage side face) of the bearing stand 5 facing the end face 92a.

In this embodiment, each guide vane 43 is formed integrally with the end surface 92a of the inner scroll housing 92. For example, when the inner scroll housing 92 is made of cast iron, the guide vane 43 is integrally formed with the inner scroll housing 92.

The spacer plate 45 is a hollow disk-shaped member made of, for example, a steel plate, and its inner peripheral hole 46 is fitted to the outer peripheral surface of the air guide cylinder 91 on the air outlet side of the compressor wheel 18 (see FIG. 2, see FIG. A plurality of slit holes 47 into which the guide vanes 43 are inserted are formed along the circumferential direction of the spacer plate 45. These inner peripheral holes 46 and slit holes 47 are formed in the spacer plate 45 by machining, electric discharge machining, or the like.

The spacer plate 45 is overlaid on the end surface 92a of the inner scroll housing 92 forming one side surface in the throat passage 41 and fixed with a plurality of bolts 50. As shown in FIG. 3, the bolt 50 is inserted into a bolt hole 51 formed in the inner scroll housing 92 and screwed into a female screw hole 52 formed in the spacer plate 45. The length of the bolt 50 is set to such a length that the tip of the bolt 50 does not protrude from the female screw hole 52 toward the throat passage 41, so that the flow of compressed gas flowing through the throat passage 41 is not hindered.

In this way, the spacer plate 45 is overlapped with the end surface 92a of the inner scroll housing 92 and fixed with the bolt 50, so that each of the plurality of guide vanes 43 has a plurality of slit holes 47 formed in the spacer plate 45. To penetrate. The spacer plate 45 is not limited to being fixed by the bolt 50, but may be fixed to the end surface 92a by welding or brazing. In this case, for example, the gap between the slit hole 47 of the spacer plate 45 and the guide vane 43 is fixed by spot welding or brazing.

As shown in FIG. 2, R chamfers 54 and 55 are provided on the outer peripheral portion and the inner peripheral portion of the spacer plate 45 so as not to hinder the flow of compressed air discharged from the compressor wheel 18.

In the diffuser 23 configured as described above, the spacer plate 45 is overlaid on the end surface 92a of the inner scroll housing 92 and fixed with the bolts 50, so that each of the plurality of guide vanes 43 is a spacer as described above. It penetrates through a plurality of slit holes 47 formed in the plate 45. For this reason, the width W of the throat passage 41 is reduced by the thickness T of the spacer plate 45, and the substantial axial length of the guide vane 43 is reduced. Therefore, the width of the throat passage 41 can be adjusted to the optimum value by setting the width W of the throat passage 41 to the maximum value in advance and appropriately selecting the thickness T of the spacer plate 45.

Since the spacer plate 45 is a simple plate, it is easy to form a plurality of slit holes 47 in the spacer plate 45, and since the spacer plate 45 is thin and lightweight, it can be easily transported. Further, by preparing several types of spacer plates 45 having different thicknesses, the width of the throat passage can be easily adjusted. In addition, the spacer plate 45 that has not been used in one centrifugal compressor 8 can be diverted to another centrifugal compressor, so that the cost can be reduced. Therefore, it is possible to flexibly cope with various engine specifications while reducing the manufacturing cost of the centrifugal compressor 8.

By forming the guide vane 43 integrally with the end surface 92a of the inner scroll housing 92, the guide vane 43 can be easily formed and the manufacturing cost of the centrifugal compressor 8 can be reduced.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIG.
The diffuser 23A according to the second embodiment is different from the diffuser 23 according to the first embodiment in that the thickness T of the spacer plate 45A installed in the throat passage 41 is not uniform and varies along its radial direction. . In the spacer plate 45A, a slit hole 47A through which the guide vane 43 passes is formed as in the first embodiment. Since the configuration of the other parts is the same as that of the first embodiment, the same reference numerals are given to the respective parts and description thereof will be omitted.

The spacer plate 45A is formed so that the plate thickness T on the radially outer peripheral side is smaller than the plate thickness T on the radially inner peripheral side. By forming the spacer plate 45A in this way, the performance of the centrifugal compressor 8 can be improved by smoothly decelerating the compressed air on the outlet side of the compressor wheel 18 and restoring the pressure of the compressed air.
Of course, the thickness of each part of the spacer plate 45A may be set so as to have another cross-sectional shape as necessary. In this way, the cross-sectional shape of the throat passage 41 can be changed in the radial direction to obtain an optimum passage shape, and can flexibly cope with various engine specifications.

[Third Embodiment]
Next, a third embodiment of the diffuser according to the present invention will be described with reference to FIG.
The diffuser 23B according to the third embodiment is different from the diffuser 23 according to the first embodiment in that a plurality of spacer plates 45B are mounted on the throat passage 41 in an overlapping manner. In each of these spacer plates 45B, slit holes 47B through which the guide vanes 43 pass are formed as in the first embodiment. Since the configuration of the other parts is the same as that of the first embodiment, the same reference numerals are given to the respective parts and description thereof will be omitted.

Thus, even when the plurality of spacer plates 45B are mounted in a stacked manner, the same operations and effects as in the first embodiment can be obtained. In addition, by installing spacer plates 45B having different thicknesses in combination, the spacer plate 45B is not wasted, and the width W of the throat passage 41 can be set more finely to flexibly respond to various engine specifications. Can do.

[Fourth Embodiment]
Next, a fourth embodiment of the present invention will be described with reference to FIG.
In the diffuser 23C of the fourth embodiment, a diffuser main plate 58 to which guide vanes 43 are attached is fixed to an end surface 92a of the inner scroll housing 92 in the throat passage 41 as in the conventional diffuser structure. Thus, the difference from the diffuser 23 of the first embodiment is that the spacer plate 45 is overlapped and fixed by the bolt 50. Since the configuration of the other parts is the same as that of the first embodiment, the same reference numerals are given to the respective parts and description thereof will be omitted.

Thus, by additionally mounting the spacer plate 45, the width W of the throat passage 41 is changed by the thickness T of the spacer plate 45, or the sectional shape of the throat passage 41 is changed by the sectional shape of the spacer plate 45. In this way, the performance of the supercharger 1 can be adapted to changes in engine characteristics or the like.

Therefore, it is possible to repair the centrifugal compressor 8 in which the diffuser 23 is formed by the diffuser main plate 58 to which the guide vanes 43 are attached. That is, the centrifugal compressor 8 can be repaired by opening the compressor housing 9 of the centrifugal compressor 8, then fixing the spacer plate 45 on the diffuser main plate 58, and finally closing the compressor housing 9. Since the spacer plate 45 can be replaced with a plate having a different thickness, the width and cross-sectional shape of the throat passage 41 can be arbitrarily changed.

As described above, the diffuser according to the fourth embodiment can flexibly cope with various specifications by appropriately selecting the thickness T of the spacer plate 45 and adjusting the width W of the throat passage 41 to the optimum value. it can. Further, since the spacer plate 45 is thin and lightweight, it can be easily transported and attached, so that the repair cost of the centrifugal compressor 8 (supercharger 1) can be reduced.

As described above, according to the

diffusers

23, 23A, 23B, and 23C according to the present invention, it is possible to flexibly cope with various specifications while reducing the manufacturing cost of the centrifugal compressor 8.
Moreover, according to the centrifugal compressor 8 provided with

such diffusers

23, 23A, 23B, and 23C, the width and cross-sectional shape of the throat passage 41 can be set by appropriately selecting the plate thickness T of the

spacer plates

45, 45A, and 45B. It can be adjusted to the optimum value. Since the

spacer plates

45, 45A and 45B are thin and lightweight, they can be easily transported, and can be easily diverted to other compressors, so that various specifications can be achieved while reducing the manufacturing cost of the centrifugal compressor 8. Can respond flexibly.
And according to the supercharger 1 provided with such a centrifugal compressor 8, it can be set as the supercharger 1 which can respond to the specification of various engines, reducing the manufacturing cost of the supercharger 1. FIG.

It should be noted that the present invention is not limited to the configuration of each of the embodiments described above, and modifications and improvements can be added as appropriate within the scope of the present invention. It shall be included in the scope of rights of the invention.

For example, in the above-described embodiment, the example in which the present invention is applied to the centrifugal compressor 8 as the compressor of the supercharger 1 attached to the marine diesel engine has been described. The present invention can also be widely applied to centrifugal compressors that compress air, gas, and other fluids.

The slit holes 47 of the

spacer plates

45, 45A, 45B are made loose with respect to the outer peripheral shape of the guide vane 43 so that the slit holes 47 and the guide vanes 43 can be easily fitted to each other. May be improved, or the shape of the slit hole 47 may be unified so that the guide vanes 43 having different angles can be accommodated. After the slit hole 47 and the guide vane 43 are fitted, as described above, the gap between the slit hole 47 and the guide vane 43 is filled by welding or brazing, or an adhesive or filler is filled in the gap. It is conceivable to fill.

The height of the

spacer plates

45, 45A, 45B (the width W of the throat passage 41) is changed by interposing a washer-like spacer member between the

spacer plates

45, 45A, 45B and the passage side surface (92a). It may be.

The

spacer plates

45, 45 </ b> A, 45 </ b> B are not necessarily made of steel and may be formed of a light alloy, a heat resistant resin, a composite material, or the like. In the embodiment, the

spacer plates

45, 45A, 45B are fixed to the end surface 92a of the inner scroll housing 92, but may be fixed to the end surface 5a of the bearing stand 5 facing the end surface 92a.

DESCRIPTION OF SYMBOLS 1 Supercharger 3 Turbine shaft 5 Bearing stand 5a End surface (passage side surface) of a bearing stand
6 Exhaust turbine 8 Centrifugal compressor 9 Compressor housing 18

Compressor impeller

23, 23A, 23B, 23C Diffuser 41 Throat passage 43

Guide vane

45, 45A,

45B Spacer plate

47, 47A, 47B Slit hole 92a End surface of the inner scroll housing (passage side surface )
W Throat passage width T Spacer plate thickness

Claims

A throat passage formed on the radially outer peripheral side of the compressor wheel,
A plurality of guide vanes, one end of which is axially fixed to the side surface of the throat passage to form a diffuser;
A compressor comprising: a spacer plate formed with a plurality of slit holes into which the guide vanes are inserted and overlaid on a side surface of the passage.
The compressor according to claim 1, wherein the guide vane is formed integrally with the side surface of the passage.
The compressor according to claim 1 or 2, wherein the spacer plate is formed such that a plate thickness on the radially outer peripheral side is smaller than a plate thickness on the radially inner peripheral side.
A supercharger comprising the compressor according to any one of claims 1 to 3.
A throat passage formed on the radially outer peripheral side of the compressor wheel,
A throat passage width adjustment method for a compressor, comprising: a plurality of guide vanes, one end in the axial direction of which is fixed to a passage side surface of the throat passage to constitute a diffuser,
A spacer plate formed with a plurality of slit holes into which the guide vanes are inserted is overlaid on the side of the passage,
A compressor throat passage width adjusting method in which the passage width of the throat passage is changed by the spacer plate.