CN110300839A - The exhaust component of rotating machinery, rotating machinery - Google Patents
The exhaust component of rotating machinery, rotating machinery Download PDFInfo
- Publication number
- CN110300839A CN110300839A CN201880003439.6A CN201880003439A CN110300839A CN 110300839 A CN110300839 A CN 110300839A CN 201880003439 A CN201880003439 A CN 201880003439A CN 110300839 A CN110300839 A CN 110300839A
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- China
- Prior art keywords
- flow path
- working fluid
- path portion
- rotor
- downstream
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/30—Exhaust heads, chambers, or the like
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
- F02C3/04—Gas-turbine plants characterised by the use of combustion products as the working fluid having a turbine driving a compressor
- F02C3/045—Gas-turbine plants characterised by the use of combustion products as the working fluid having a turbine driving a compressor having compressor and turbine passages in a single rotor-module
- F02C3/05—Gas-turbine plants characterised by the use of combustion products as the working fluid having a turbine driving a compressor having compressor and turbine passages in a single rotor-module the compressor and the turbine being of the radial flow type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/52—Casings; Connections of working fluid for axial pumps
- F04D29/54—Fluid-guiding means, e.g. diffusers
Abstract
It is an object of the invention to reduce the efficiency for generating the region of removing in flow path and improving the pressure recovery in expanding flow path.Radial turbine (10A) has: rotor (12), is arranged in a manner of it can rotate around central axis (C)；Rotating vane (13), is fixed on the peripheral part of rotor (12)；Shell (11) is set to the peripheral side of rotor (12) and rotating vane (13), and the flow path of working fluid is formed on the inside of it；Reduce flow path portion (16), be set to than rotating vane (13) more by the flow direction of working fluid downstream side position, and towards downstream side and the flow path cross sectional area of working fluid is gradually reduced；And expand flow path portion (17), be set to the downstream side for reducing flow path portion (16), and towards downstream side and the flow path cross sectional area of working fluid is gradually expanded.
Description
Technical field
The present invention relates to a kind of rotating machineries, the exhaust component of rotating machinery.
Background technique
Radial turbine used in turbocharger (centrifugal turbine) or axial-flow turbine, blast furnace axial-flow type drum
The rotating machineries such as blower have shell, are set to the intracorporal rotor of shell in a manner of it can rotate and are set to the peripheral part of rotor
Blade.In this rotating machinery, some has vaned rotor using the working fluid rotation being sent into from outside.Also, also
Some is by sending out working fluid using having vaned rotor from the dynamic rotation of outside transmitting.
However, in the viewpoint of performance, expecting will be high by the flow velocity of the working fluid of blade in this rotating machinery
Efficient be converted to pressure.
Thus, for example, as disclosed in patent document 1, mostly use have in the exhaust flow path of working fluid flow path cross sectional area by
The gradually structure of widened expanding flow path (diffuser).By the way that this expanding flow path is arranged, the workflow of compression can be gradually decreased
The pressure of body is simultaneously expelled in such as atmospheric pressure.
Conventional art document
Patent document
Patent document 1: No. 5040156 bulletins of Japanese Patent No.
Summary of the invention
The invention technical task to be solved
For example, as shown in figure 11, in the case where radial turbine 1 used in turbocharger, working fluid from
The peripheral side of shell 2 is flowed along impeller 3 and changes direction, is discharged from the inner circumferential side of impeller 3 along central axis direction.At this
In the case of, in the downstream side of the central portion 3c of impeller 3, the working fluid that is flowed out from the inner circumferential side of impeller 3 along central axis direction
A part removing and formed removing vortex.The region S1 of the removing vortex is generated substantially not as the stream of working-fluid flow
Road functions.Therefore, in the expanding flow path 4 that side downstream is influenced by the region for generating removing vortex, there are pressure
The impaired situation of the efficiency of recovery.
Also, as shown in figure 12, in the case wheres axial blower 5 etc., exists in shell 6 and be set in shell 6
Rotor 7 between the working fluid that flows the case where the downstream side of movable vane piece 8A or fixed blade 8B are removed.For example, in fixation
The downstream side of blade 8B produces the region S2 of removing when producing removing in the working fluid along the surface flow of rotor 7
Substantially functioned not as the flow path of working-fluid flow.Therefore, in side downstream by the region S2's for generating removing
In the expanding flow path 9 influenced, there is a situation where that the efficiency of pressure recovery is impaired.
The present invention is to complete in light of this situation, can reduce its purpose is to provide one kind and generate stripping in flow path
From region and improve the exhaust component of the rotating machinery of efficiency of pressure recovery in expanding flow path, rotating machinery.
For solving the means of technical task
In order to solve the above problems, the exhaust component of rotating machinery of the invention, rotating machinery is using following means.
Rotating machinery involved in a mode of the invention, has: rotor, by can around center axis rotation in a manner of be arranged；
Rotating vane is fixed on the peripheral part of the rotor；Shell is set to the peripheral side of the rotor and the rotating vane, and
The flow path of working fluid is formed on the inside of it；Flow path portion is reduced, is set to and more leans on the working fluid than the rotating vane
The position in the downstream side of flow direction, and towards downstream side and the flow path cross sectional area of the working fluid is gradually reduced；And expand
Flow path portion is set to the downstream side for reducing flow path portion, and towards downstream side and the flow path cross sectional area of the working fluid by
Flaring is big.
The rotating machinery according to involved in the method, by under the flow direction for more leaning on working fluid than rotating vane
Flow path portion, the flow path constriction of working fluid are reduced in the position setting for swimming side.As a result, in the part of flow path constriction, relative to work
The region that fluid substantially moves about is possible to generate the opposite reduction in region of removing in the downstream side of rotating vane.In this way,
The region that the removing of working fluid is generated in flow path can be reduced.After this diminution flow path portion, expanding flow path portion
The flow path cross sectional area of working fluid is gradually expanded, thus, it is possible to improve the efficiency of the pressure recovery of working fluid.
In above-mentioned rotating machinery, it is also equipped with discharge unit, the discharge unit is towards than the rotor and the rotating vane
Side extends farther downstream, and the working fluid is downstream discharged, if the diminution flow path portion and the expansion flow path portion shape
Cheng Yu in the discharge unit than the flow direction downstream side of the rotor end side farther downstream position, then into one
Step is preferred.
According to this rotating machinery, in the end in the downstream side of rotor, the stripping of working fluid is easy to produce in side downstream
From.In this configuration, by the downstream side than rotor end farther downstream side position setting reduce flow path portion, can
Efficiently reduce the region for generating the removing of working fluid.
In above-mentioned rotating machinery, the shell and the rotor are towards more leaning on the flow direction than the rotating vane
Downstream side extends, if the diminution flow path portion is formed in the shell and the rotor in side farther downstream than the rotating vane
In at least side, then further preferably.
According to this rotating machinery, in shell and rotor into the structure that side is extended continuously farther downstream than rotating vane,
The region for generating the removing of working fluid can be efficiently reduced.
In above-mentioned rotating machinery, it is also equipped with fixed blade, the fixed blade is set to than the rotating vane more on the lower
The position of side is swum, and is extended from the shell towards inner circumferential side, if the diminution flow path portion is formed on the flow direction
It is provided with the region of the fixed blade, then further preferably.
Generation can be reduced in the fixed blade part in the downstream side for being set to rotating vane according to this rotating machinery
The region of the removing of working fluid.
In above-mentioned rotating machinery, it is also equipped with fixed blade, the fixed blade is set to more top than the rotating vane
The position of side is swum, and is extended from the shell towards inner circumferential side, if the diminution flow path portion is set to than the rotating vane more
By the position in the downstream side of the flow direction of the working fluid, then further preferably.
Generation working fluid can be reduced in the part in the downstream side for being set to rotating vane according to this rotating machinery
Removing region.
The exhaust component of rotating machinery involved in a mode of the invention, the rotating machinery have: rotor, with can
Mode around center axis rotation is arranged；Rotating vane is fixed on the peripheral part of the rotor；And shell, it is set to the rotation
The peripheral side of blade, and on the inside of it formed working fluid flow path, wherein the exhaust component of the rotating machinery has: cylinder
The exhaust component main body of shape is arranged in a manner of side extends farther downstream by towards than the rotor and the rotating vane, and shape
At the exhaust flow path that the working fluid is downstream discharged；Flow path portion is reduced, the inner circumferential of the exhaust component main body is formed in
Face, and towards the downstream side of the flow direction of the working fluid and the flow path cross sectional area of the working fluid is gradually reduced；And
Expand flow path portion, be formed in the position of the diminution flow path portion of the inner peripheral surface than exhaust component main body side farther downstream,
And towards downstream side and the flow path cross sectional area of the working fluid is gradually expanded.
The exhaust component of the rotating machinery according to involved in the method, by the way that this exhaust component is arranged, be equivalent to than
Rotating vane more leans on the position in the downstream side of the flow direction of working fluid that diminution flow path portion is arranged.Thereby, it is possible to reduce flowing
The region of the removing of working fluid is generated in road.
Invention effect
The exhaust component of related rotating machinery, rotating machinery according to the present invention can reduce and generate stripping in flow path
From region and improve the efficiency of the pressure recovery in expanding flow path.
Detailed description of the invention
Fig. 1 is to indicate radial turbine used in turbocharger involved in the 1st embodiment of the invention
The cross-sectional view of structure.
Fig. 2 is the stream indicated in radial turbine used in turbocharger involved in the 1st embodiment of the invention
The figure of road surface product.
Fig. 3 is to indicate radial-flow type whirlpool used in turbocharger involved in the variation of the 1st embodiment of the invention
The cross-sectional view of the structure of wheel.
Fig. 4 is to indicate radial-flow type whirlpool used in turbocharger involved in the variation of the 1st embodiment of the invention
The figure of flow path area in wheel.
Fig. 5 is the cross-sectional view for indicating the structure of axial blower involved in the 2nd embodiment of the invention.
Fig. 6 is the cross-sectional view for indicating the structure of axial blower involved in the 3rd embodiment of the invention.
Fig. 7 is the cross-sectional view for indicating the structure of axial blower involved in the variation of the 3rd embodiment of the invention.
Fig. 8 is the cross-sectional view for indicating the structure of axial-flow turbine involved in the 4th embodiment of the invention.
Fig. 9 is the figure for indicating the velocity flow profile in the embodiment of the present invention.
Figure 10 is the figure for indicating the velocity flow profile in comparative example of the invention.
Figure 11 is the cross-sectional view for indicating the structure of radial turbine used in previous turbocharger.
Figure 12 is the cross-sectional view for indicating the structure of previous axial blower.
Specific embodiment
Hereinafter, with reference to attached drawing to an embodiment of the exhaust component of rotating machinery according to the present invention, rotating machinery
It is illustrated.
(the 1st embodiment)
Hereinafter, being illustrated using Fig. 1 to the 1st embodiment of the invention.
As shown in Figure 1, radial turbine used in turbocharger (rotating machinery) 10A have shell 11, rotor 12 and
Rotating vane 13.
The shell of the formation of shell 11 radial turbine 10A.Shell 11 has: turn that be hollow and accommodating rotor 12 inside it
Subshell 11R；And the exhaust component (discharge unit, exhaust component main body) being arranged in a manner of the peripheral side to surround rotating vane 13
15A etc..
Also, the air-breathing (not shown) with working fluids such as the exhaust gas for being taken into internal combustion engine from radial outside is connected on shell 11
The air-breathing shell or static blade of mouth.
Rotor 12 has: the rotation being rotatably freely supported through not shown bearing around central axis C in shell 11
Axis 12s；And it is set to portion wheel disc (disk) 14 of an end in the direction central axis C of rotary shaft 12s.
Wheel pan portion 14 has: being formed in hole (bore) portion 14b of the central portion comprising central axis C；And in the outer of hole portion 14b
Side towards the direction central axis C side and the deviation face 14f that is formed.Deviation face 14f is by outer diameter from the side in the direction central axis C
It is formed towards the convex curve face that the other side is gradually expanded, so that being taken into from the air entry 11a of radial outside towards radially inner side
Working fluid flow direction to the direction central axis C be biased to.
Rotating vane 13 is provided with multiple on the edge deviation face 14f of wheel pan portion 14 around the circumferentially spaced interval of central axis C.
Above-mentioned shell 11 has the shield being arranged in a manner of covering multiple rotating vanes 13 from the side in the direction central axis C
Portion 18.
Exhaust component 15A by with guard section 18 it is continuous in a manner of be set to than rotating vane 13 more lean on working fluid flowing
The downstream side in direction, i.e. the direction central axis C side position.Exhaust component 15A is tubular and is formed on the inside of it from wheel disc
The exhaust for the working fluid that the inner circumferential side (peripheral side of hole portion 14b) in portion 14 is flowed towards the direction central axis C side (downstream side)
Flow path 102.
Exhaust component 15A has the downstream for reducing flow path portion 16 and being set to diminution flow path portion 16 in inner circumferential surface 15f
The expansion flow path portion 17 of side.These reduce flow path portion 16 and expansion flow path portion 17 is formed in exhaust component 15A and turns than being located at
The position of the side farther downstream end face (end) 14g of the hole portion 14b in the flow direction downstream side of son 12.
Flow path portion 16 is reduced to be formed as that the flow path cross sectional area of working fluid is gradually reduced gradually towards downstream side by its internal diameter
It reduces.Expand flow path portion 17 and the downstream side of diminution flow path portion 16 is continuously formed, is formed as through its internal diameter towards downstream side
It is gradually expanded and the flow path cross sectional area of working fluid is gradually expanded.
In such as above-mentioned radial turbine 10A, from the working fluid that air entry 11a is taken into from radial outside towards inside
It is flowed into the flow path 101 of wheel pan portion 14 being biased between face 14f and guard section 18.Pass through the work being flowed into the flow path 101
Make fluid and rotating vane 13 collides, rotor 12 drives the compression for being linked to another end of rotor 12 around center axis rotation
Machine (not shown) etc..Working fluid is from the inner circumferential side (peripheral side of hole portion 14b) of wheel pan portion 14 towards the direction central axis C side
(downstream side) outflow, and be discharged to the outside by the exhaust flow path 102 of the inside of exhaust component 15A.
Here, in exhaust component 15A, along one of the working fluid for being biased to face 14f flowing of wheel pan portion 14
Divide the downstream side removing in the end face 14g of the hole portion 14b of wheel pan portion 14 and generates vortex.As a result, in the end face 14g of hole portion 14b
Downstream side formed generate removing vortex region S21.On the other hand, in exhaust component 15A, along the direction central axis C to
The working fluid of downstream side flowing along the diminution flow path portion 16 for being formed in inner peripheral surface 15f to radially inner side by being biased.Through
The working fluid for having crossed diminution flow path portion 16 is gradually expanded due to flow velocity reduction because in expansion its flow path cross sectional area of flow path portion 17, and from
The outlet of exhaust component 15A is discharged into external such as atmospheric pressure.
In this way, reduce flow path portion 16 by having, it is formed in the center of the exhaust flow path 102 in exhaust component 15A
The radial dimension of region S21 of the generation removing vortex in portion becomes smaller, the peripheral side working fluid of the S21 downstream effluent in the region
The sectional area (hereinafter, being referred to as effective flow path area) of dynamic region S22 is opposite to become larger.
Fig. 2 be the flow path area M1 for indicating exhaust component 15A, by generate removing vortex region S21 except working fluid stream
Effective flow path area M2 of dynamic region S22 and do not have reduce flow path portion 16 when (structure shown in Figure 11) by generate removing rotation
The figure of effective flow path area M0 in the region of the working-fluid flow except the region S21 in whirlpool.As shown in Fig. 2, by having
Flow path portion 16 is reduced, effective flow path area M2 of the region S22 of working-fluid flow becomes larger.
According to such as above-mentioned radial turbine 10A and exhaust component 15A, by more leaning on working fluid than rotating vane 13
The position setting in downstream side of flow direction reduce 102 constriction of flow path of flow path portion 16 and working fluid.It contracts as a result, in flow path
Narrow part is possible to generate removing in the downstream side of rotating vane 13 relative to the region S22 that working fluid substantially moves about
Region S21 opposite reduce.In this way, which the region S21 for generating the removing of working fluid in flow path can be reduced.By this
Kind reduces after flow path portion 16, the flow path cross sectional area of working fluid is gradually expanded expanding flow path portion 17, thus, it is possible to improve
The efficiency of the pressure recovery of working fluid.
Also, flow path portion is reduced by the downstream side setting of the end face 14g in the downstream side of the hole portion 14b in wheel pan portion 14
16, the region S21 for generating the removing of working fluid can be efficiently reduced.
(variation of the 1st embodiment)
As shown in figure 3, exhaust component (discharge unit, row of radial turbine used in turbocharger (rotating machinery) 10B
Gas article body) 15B by with the guard section 18 of shell 11 it is continuous in a manner of be set to than rotating vane 13 more by working fluid
The downstream side of flow direction, i.e. the direction central axis C side position.Exhaust component 15B be tubular and on the inside of it formed from
The exhaust flow path 102 for the working fluid that the inner circumferential side (peripheral side of hole portion 14b) of wheel pan portion 14 is flowed towards downstream side.
Exhaust component 15B has the expansion of straight line flow path portion 20, first in inner circumferential surface 15f from the upstream side toward the downstream side
Flow path portion 21, the second expansion flow path portion 23 for reducing flow path portion 22 and being set to the downstream side for reducing flow path portion 22.These first
Expand flow path portion 21, diminution flow path portion 22 and the second expansion flow path portion 23 to be formed in exhaust component 15B than being located at rotor 12
Flow direction downstream side hole portion 14b the side farther downstream end face 14g position.
Straight line flow path portion 20 has constant internal diameter on the direction central axis C.
First expansion flow path portion 21 is formed as the flow path cross sectional area that working fluid is gradually expanded towards downstream side by its internal diameter
It is gradually expanded.
It reduces flow path portion 22 and is formed as the flow path cross sectional area that working fluid is gradually reduced towards downstream side by its internal diameter
It is gradually reduced.Second expansion flow path portion 23 by with reduce flow path portion 22 downstream side it is continuous in a manner of formed, be formed as passing through it
Internal diameter is gradually expanded towards downstream side and the flow path cross sectional area of working fluid is gradually expanded.
Fig. 4 be the flow path area M11 for indicating exhaust component 15B, by generate removing vortex region S21 except workflow
Body flowing region S22 effective flow path area M12 and do not have reduce flow path portion 22 when (structure shown in Figure 11) will generate
Remove the figure of effective flow path area M0 in the region of the working-fluid flow except the region S21 of vortex.As shown in Fig. 4, lead to
It crosses to have and reduces flow path portion 22, effective flow path area M12 of the region S22 of working-fluid flow becomes larger.
It is identical as the exhaust component 15A of the first embodiment described above in this exhaust component 15B, it can also pass through setting
Flow path portion 22 is reduced to reduce and be possible to generate the region S21 of removing in the downstream side of rotating vane 13, and keeps working fluid real
Effective flow path cross sectional area of the region S22 to move about in matter increases.After this diminution flow path portion 22, expand flow path second
The flow path cross sectional area of working fluid is gradually expanded in portion 23, and thus, it is possible to improve the efficiency of the pressure recovery of working fluid.
(the 2nd embodiment)
Then, the 2nd embodiment of the exhaust component of rotating machinery according to the present invention, rotating machinery is illustrated.Separately
Outside, in the following description, to the first embodiment described above it is common structure mark the same symbol and the description thereof will be omitted.
As shown in figure 5, axial blower (rotating machinery) 10C has shell 31C, rotary shaft (rotor) 32, movable vane piece (rotation
Blade) 33 and fixed blade 34.
Shell 31C is in the tubular extended along the direction central axis C.
Rotary shaft 32 is in the inside of shell 31C by bearing support (not shown) in a manner of it can rotate around central axis C.The rotation
Axis 32 is driven in a manner of it can rotate around central axis C by turbine (not shown) etc..
The cricoid region in section between the inner peripheral surface of these shells 31C and the outer peripheral surface of rotary shaft 32 forms working fluid
Flow path 103.
Movable vane piece 33 is provided with multiple on the peripheral part edge of rotary shaft 32 around the circumferentially spaced interval of central axis C.It is each dynamic
Blade 33 is formed in a manner of extending from the periphery of rotary shaft 32 towards radial outside.
Fixed blade 34 is configured at the downstream side of movable vane piece 33 on the direction central axis C.Fixed blade 34 is in the inside of shell 31C
Edge is provided with multiple around the circumferentially spaced interval of central axis C.Each fixed blade 34 from shell 31C towards inner circumferential side to extend
Mode is formed.
Above-mentioned shell 31C and rotary shaft 32 are towards the downstream for more leaning on flow direction than these movable vane pieces 33 and fixed blade 34
Side extends.In shell 31C, diminution flow path portion is formed in the position of side farther downstream than movable vane piece 33 and fixed blade 34
36C and expansion flow path portion 37.
These reduce flow path portion 36C, expand the inner peripheral surface 31f that flow path portion 37 is formed in shell 31C.Flow path portion 36C is reduced to pass through
The internal diameter of shell 31C is reduced towards downstream side and the flow path cross sectional area of working fluid is gradually reduced.Here, as shown in figure 5, reducing
Flow path portion 36C can be formed in the region for being provided with fixed blade 34 in the flowing direction.
Expand flow path portion 37 and be set to the downstream side for reducing flow path portion 36C, is gradually expanded by the internal diameter of shell 31C towards downstream side
It is big and the flow path cross sectional area of working fluid is gradually expanded.
According to such as above-mentioned axial blower 10C, by the working fluid that have passed through movable vane piece 33, fixed blade 34
The downstream side setting of flow direction reduce the flow path constriction of flow path portion 36C and working fluid.As a result, in the portion of flow path constriction
Point, in the flow path 103 between shell 31C and rotary shaft 32, the sectional area for the region S22 that working fluid substantially moves about is opposite
Become larger.It is possible to generate the opposite reduction of region S21 of removing in the downstream side of movable vane piece 33 as a result,.By this diminution flow path
After portion 36C, the flow path cross sectional area of working fluid is gradually expanded expanding flow path portion 37, thus, it is possible to improve working fluid
The efficiency of pressure recovery.
(the 3rd embodiment)
Then, the 3rd embodiment of the exhaust component of rotating machinery according to the present invention, rotating machinery is illustrated.Separately
Outside, in the following description, to above-mentioned 2nd embodiment it is common structure mark the same symbol and the description thereof will be omitted.
As shown in fig. 6, axial blower (rotating machinery) 10D have shell 31D, rotary shaft (rotor) 32D, movable vane piece 33 and
Fixed blade 34.
Shell 31D is in the tubular extended along the direction central axis C.
Rotary shaft 32D is in the inside of shell 31D by bearing support (not shown) in a manner of it can rotate around central axis C.The rotation
Shaft 32D is driven in a manner of it can rotate around central axis C by turbine (not shown) etc..
The cricoid region in section between the inner peripheral surface of these shells 31D and the outer peripheral surface of rotary shaft 32D forms working fluid
Flow path 103.
Movable vane piece 33 is provided with multiple on the peripheral part edge of rotary shaft 32D around the circumferentially spaced interval of central axis C.It is each dynamic
Blade 33 is formed in a manner of extending from the periphery of rotary shaft 32D towards radial outside.
Fixed blade 34 is configured at the downstream side of movable vane piece 33 on the direction central axis C.Fixed blade 34 is in the inside of shell 31D
Edge is provided with multiple around the circumferentially spaced interval of central axis C.Each fixed blade 34 from shell 31D towards inner circumferential side to extend
Mode is formed.
Above-mentioned shell 31D and rotary shaft 32D is more leaned under flow direction towards than these movable vane pieces 33 and fixed blade 34
Side is swum to extend.In the outer peripheral surface of rotary shaft 32D, contracting is formed in the position of side farther downstream than movable vane piece 33 and fixed blade 34
Small flow path portion 36D.Also, in the inner peripheral surface of shell 31D, expansion is formed in the position of side farther downstream than diminution flow path portion 36D
Big flow path portion 37.
Reduce the flow path cross sectional area that flow path portion 36D expands working fluid by the outer diameter of rotary shaft 32D towards downstream side
It is gradually reduced.Here, as shown in fig. 6, reducing flow path portion 36D is formed in the area for being provided with fixed blade 34 in the flowing direction
Domain.
Expand flow path portion 37 and be set to the downstream side for reducing flow path portion 36D, is gradually expanded by the internal diameter of shell 31D towards downstream side
It is big and the flow path cross sectional area of working fluid is gradually expanded.
According to such as above-mentioned axial blower 10D, by the working fluid that have passed through movable vane piece 33, fixed blade 34
The downstream side setting of flow direction reduce the flow path constriction of flow path portion 36D and working fluid.As a result, in the portion of flow path constriction
Point, in the flow path 103 between shell 31D and rotary shaft 32D, the sectional area phase for the region S32 that working fluid substantially flows
To becoming larger.It is possible to generate the opposite reduction of region S31 of removing in the downstream side of movable vane piece 33 as a result,.It is flowed by this diminution
After road portion 36D, the flow path cross sectional area of working fluid is gradually expanded expanding flow path portion 37, thus, it is possible to improve working fluid
Pressure recovery efficiency.
(variation of the 3rd embodiment)
In addition, diminution flow path portion 36D is set to and is provided with fixed blade in the flowing direction in above-mentioned 3rd embodiment
34 region, but be not restricted to that this.
For example, as shown in fig. 7, can also will be formed in rotary shaft (rotor) 32E's of axial blower (rotating machinery) 10E
Reduce the position that flow path portion 36E is set to side farther downstream than fixed blade 34.
(the 4th embodiment)
Then, the 4th embodiment of the exhaust component of rotating machinery according to the present invention, rotating machinery is illustrated.
As shown in figure 8, axial-flow turbine (rotating machinery) 10F has turbine case 41, rotor 42, fixed blade 43, movable vane piece
(rotating vane) 44 and exhaust casing (shell) 45.
Turbine case 41 is in the tubular extended along the direction central axis C.
Fixed blade 43 is provided with multiple in the interior lateral edge of turbine case 41 around the circumferentially spaced interval of central axis C.Each fixation
Blade 43 is formed in a manner of extending from turbine case 41 towards inner circumferential side.
Rotor 42 around central axis C in a manner of it can rotate by bearing support (not shown).
Movable vane piece 44 is provided with multiple on the peripheral part edge of rotor 42 around the circumferentially spaced interval of central axis C.Each movable vane piece 44
It is formed in a manner of extending from the periphery of rotor 42 towards radial outside.Movable vane piece 44 is configured at fixation on the direction central axis C
The downstream side of blade 43.
Exhaust casing 45 is connect with the downstream side of turbine case 41.Exhaust casing 45 has: positioned at the radial direction of movable vane piece 44
The periphery housing section 45a in outside；And relative to periphery housing section 45a, in the inner circumferential shell that radially inner side interval is arranged
Portion 45b.Inner circumferential housing section 45b is in the tubular that extends along the direction central axis C, and be set to rotor 42 rotary shaft 42s outside
Side.Section rings between the inner peripheral surface of the periphery housing section of these exhaust casings 45 and the outer peripheral surface of inner circumferential housing section 45b
The region of shape forms the exhaust flow path 104 of working fluid.
Above-mentioned exhaust casing 45 extends towards the downstream side than these fixed blades 43 and movable vane piece 44 more by flow direction.
In the outer peripheral surface of inner circumferential housing section 45b, diminution stream is formed in the position of side farther downstream than fixed blade 43 and movable vane piece 44
Road portion 46.Also, in the inner peripheral surface of turbine case 41, expansion stream is formed in the position of side farther downstream than diminution flow path portion 46
Road portion 47.
Reduce the flowing path section that flow path portion 46 expands working fluid by the outer diameter of inner circumferential housing section 45b towards downstream side
Product is gradually reduced.
Expand flow path portion 47 and be set to the downstream side for reducing flow path portion 46, passes through the internal diameter and inner circumferential shell of periphery housing section 45a
The outer diameter of portion 45b is gradually expanded towards downstream side and the flow path cross sectional area of working fluid is gradually expanded.
According to such as above-mentioned axial-flow turbine 10F, by have passed through the working fluid of fixed blade 43, movable vane piece 44
The flow path constriction of flow path portion 46 and working fluid is reduced in the downstream side setting of flow direction.As a result, in the downstream side of movable vane piece 44
It is reduced it is possible that the region for generating removing is opposite.After this diminution flow path portion 46, make workflow expanding flow path portion 47
The flow path cross sectional area of body is gradually expanded, and thus, it is possible to improve the efficiency of the pressure recovery of working fluid.
In addition, in the above-described embodiment, be illustrated radial turbine 10A, 10B and axial blower 10C, 10D,
Axial-flow turbine 10F, but the present invention can also be suitable for the rotating machinery other than the above such as Oblique-flow turbine.Also,
The structure in each portion of radial turbine 10A, 10B, axial blower 10C, 10D, axial-flow turbine 10F also can be set to it is upper
State the difference of structure shown in embodiment and its variation.
As long as also, reduce flow path portion and be set to the position for more leaning on the downstream side of flow direction of working fluid than rotating vane,
The either side in shell side, rotor-side can be set in the convex form for then forming diminution flow path portion, in shell side and can also turn
Convex form is arranged in the two sides of sub- side.
In addition, shell can be made of single component, can also be constituted by combining multiple components.
Embodiment
Effect is had been acknowledged by the structure as shown in the first embodiment described above, therefore, its result described below.
As embodiment, the exhaust component of L-shaped has been used.The exhaust component towards downstream side and what its internal diameter was gradually expanded
The upstream side for expanding flow path portion has diminution flow path portion.
As comparative example, used the upstream side of expanding flow path portion do not have towards downstream side and the diminishing contracting of its internal diameter
The exhaust component of small flow path portion.
To above-described embodiment and comparative example, the velocity flow profile of the inside of exhaust component has been found out by computer analysis.
It the results are shown in Fig. 9 and Figure 10.
As shown in figure 9, being reduced in the embodiment of flow path portion having, compared with comparative example shown in Fig. 10, flowed reducing
Road portion, the low part of the flow velocity of flow path central portion reduce.Therefore, it reduces and generates the region of removing in flow path and in side downstream
Expansion flow path portion improve pressure recovery efficiency.
Symbol description
10A, 10B- radial turbine (rotating machinery), 10C, 10D, 10E- axial blower (rotating machinery), 10F-
Axial-flow turbine (rotating machinery), 11- shell, 12- rotor, 13- rotating vane, the end face 14g- (end), 15A, 15B- exhaust
Component (discharge unit, exhaust component main body), 15f- inner peripheral surface, 16,22,36C, 36D, 36E- diminution flow path portion, 17,37- expansion
Flow path portion, 23- second expand flow path portion (expanding flow path portion), 31C, 31D- shell, 31f- inner peripheral surface, 32,32D, 32E- rotation
Axis (rotor), 33- movable vane piece (rotating vane), 34- fixed blade, 42- rotor, 43- fixed blade, 44- movable vane piece (pivoting leaf
Piece), 45- exhaust casing (shell), C- central axis.
Claims (6)
1. a kind of rotating machinery, which is characterized in that have:
Rotor, by can around center axis rotation in a manner of be arranged；
Rotating vane is fixed on the peripheral part of the rotor；
Shell is set to the peripheral side of the rotor and the rotating vane, and the flow path of working fluid is formed on the inside of it；
Flow path portion is reduced, the position for more leaning on the downstream side of flow direction of the working fluid than the rotating vane is set to,
And towards downstream side and the flow path cross sectional area of the working fluid is gradually reduced；And
Expand flow path portion, be set to the downstream side for reducing flow path portion, and the flow path of the working fluid towards downstream side
Sectional area is gradually expanded.
2. rotating machinery according to claim 1, which is characterized in that be also equipped with:
The work is downstream discharged than the rotor and rotating vane side extension farther downstream in discharge unit, direction
Fluid,
The diminution flow path portion and the expansion flow path portion are formed in the flowing side in the discharge unit than the rotor
The position of the side farther downstream of end downstream.
3. rotating machinery according to claim 1, which is characterized in that
The shell and the rotor towards more leaning on the downstream side of the flow direction to extend than the rotating vane,
The diminution flow path portion is formed in the shell and the rotor at least in side farther downstream than the rotating vane
Side.
4. rotating machinery according to claim 3, which is characterized in that be also equipped with:
Fixed blade is set to the position of side farther downstream than the rotating vane, and extends from the shell towards inner circumferential side,
The diminution flow path portion is formed in the region that the fixed blade is provided on the flow direction.
5. rotating machinery according to claim 3, which is characterized in that be also equipped with:
Fixed blade is set to the position than rotating vane upstream side, and extends from the shell towards inner circumferential side,
The diminution flow path portion is set to the position that the downstream side of flow direction of the working fluid is more leaned on than the rotating vane
It sets.
6. a kind of exhaust component of rotating machinery, the rotating machinery have: rotor, by can around center axis rotation in a manner of set
It sets；Rotating vane is fixed on the peripheral part of the rotor；And shell, it is set to the peripheral side of the rotating vane, and in it
Side forms the flow path of working fluid,
The exhaust component of the rotating machinery is characterized in that having:
The exhaust component main body of tubular is set in a manner of side extends farther downstream by towards than the rotor and the rotating vane
It sets, and forms the exhaust flow path that the working fluid is downstream discharged；
Flow path portion is reduced, is formed in the inner peripheral surface of the exhaust component main body, and towards the flow direction of the working fluid
Downstream side and the flow path cross sectional area of the working fluid are gradually reduced；And
Expand flow path portion, is formed in the position of the diminution flow path portion of the inner peripheral surface than exhaust component main body side farther downstream
Set, and towards downstream side and the flow path cross sectional area of the working fluid is gradually expanded.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2017035465A JP6776154B2 (en) | 2017-02-27 | 2017-02-27 | Radial turbine, exhaust parts of radial turbine |
| JP2017-035465 | 2017-02-27 | ||
| PCT/JP2018/004248 WO2018155189A1 (en) | 2017-02-27 | 2018-02-07 | Rotating machine and exhaust member of rotating machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110300839A true CN110300839A (en) | 2019-10-01 |
Family
ID=63254191
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201880003439.6A Pending CN110300839A (en) | 2017-02-27 | 2018-02-07 | The exhaust component of rotating machinery, rotating machinery |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6776154B2 (en) |
| KR (1) | KR102223293B1 (en) |
| CN (1) | CN110300839A (en) |
| WO (1) | WO2018155189A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11808174B2 (en) | 2020-04-23 | 2023-11-07 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Turbine and turbocharger including the turbine |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3625630A (en) * | 1970-03-27 | 1971-12-07 | Caterpillar Tractor Co | Axial flow diffuser |
| CN101092978A (en) * | 2007-07-30 | 2007-12-26 | 北京航空航天大学 | Synergic action device of preventing breath heavily and expanding stability of airbleed inside stator of multistage axial flow air compresdsor |
| CN103003528B (en) * | 2010-07-15 | 2015-04-08 | 西门子公司 | Exhaust gas diffuser for a gas turbine and a method for operating a gas turbine that comprises such an exhaust gas diffuser |
| US20150211546A1 (en) * | 2014-01-24 | 2015-07-30 | Pratt & Whitney Canada Corp. | Multistage axial flow compressor |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5040156B1 (en) | 1971-05-06 | 1975-12-22 | ||
| JPH07247996A (en) * | 1994-03-11 | 1995-09-26 | Ishikawajima Harima Heavy Ind Co Ltd | Passage form of compressor |
| FR2940413B1 (en) * | 2008-12-19 | 2013-01-11 | Air Liquide | METHOD OF CAPTURING CO2 BY CRYO-CONDENSATION |
| US8328513B2 (en) * | 2009-12-31 | 2012-12-11 | General Electric Company | Systems and apparatus relating to compressor stator blades and diffusers in turbine engines |
| JP6169007B2 (en) * | 2014-01-23 | 2017-07-26 | 三菱重工業株式会社 | Rotor blade and axial flow rotating machine |
-
2017
- 2017-02-27 JP JP2017035465A patent/JP6776154B2/en active Active
-
2018
- 2018-02-07 WO PCT/JP2018/004248 patent/WO2018155189A1/en active Application Filing
- 2018-02-07 CN CN201880003439.6A patent/CN110300839A/en active Pending
- 2018-02-07 KR KR1020197005713A patent/KR102223293B1/en active IP Right Grant
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3625630A (en) * | 1970-03-27 | 1971-12-07 | Caterpillar Tractor Co | Axial flow diffuser |
| CN101092978A (en) * | 2007-07-30 | 2007-12-26 | 北京航空航天大学 | Synergic action device of preventing breath heavily and expanding stability of airbleed inside stator of multistage axial flow air compresdsor |
| CN103003528B (en) * | 2010-07-15 | 2015-04-08 | 西门子公司 | Exhaust gas diffuser for a gas turbine and a method for operating a gas turbine that comprises such an exhaust gas diffuser |
| US20150211546A1 (en) * | 2014-01-24 | 2015-07-30 | Pratt & Whitney Canada Corp. | Multistage axial flow compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| KR102223293B1 (en) | 2021-03-04 |
| KR20190032554A (en) | 2019-03-27 |
| JP2018141399A (en) | 2018-09-13 |
| JP6776154B2 (en) | 2020-10-28 |
| WO2018155189A1 (en) | 2018-08-30 |
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Effective date of registration: 20200414 Address after: No.1, 1-1, shiozhimachi, Nagasaki, Nagasaki, Japan Applicant after: Mitsubishi Heavy Industries Marine Machinery Co., Ltd Address before: Santingmu No. 2 Fan No. 3, Takeshita Pills, the capital of Tokyo, Japan Applicant before: MITSUBISHI HEAVY INDUSTRIES, Ltd. |