CN201212404Y - Impeller wheel of steam turbine - Google Patents
Impeller wheel of steam turbine Download PDFInfo
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- CN201212404Y CN201212404Y CNU2008201131700U CN200820113170U CN201212404Y CN 201212404 Y CN201212404 Y CN 201212404Y CN U2008201131700 U CNU2008201131700 U CN U2008201131700U CN 200820113170 U CN200820113170 U CN 200820113170U CN 201212404 Y CN201212404 Y CN 201212404Y
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- moving vane
- blade face
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Abstract
The utility model discloses a steam turbine impeller which can effectively reduce the turbulent loss of liquid medium and improve the operation efficiency and comprises a static blade, a moving blade and a rotor. The static blade has a cambered blade surface, a blade surface tangent close to a liquid outlet end and the direction of an axis of the rotor form an included angle, and a blade surface tangent opposite to the other end is parallel to the direction of the axis of the rotor; and the moving blade is composed of a planar section, a blade surface which is close to one end of a liquid inlet and parallel to the direction of the axis of the rotor, a planar section with a blade surface which is at an opposite end and forms an included angle with the axis of the rotor, and a cambered section positioned between the two planar sections.
Description
Technical field the utility model relates to a kind of steam turbine, particularly relates to a kind of efficient turbine rotor.
The existing steam turbine of background technique, be all more complicated of its stator or impeller of rotor structure, the blade face tortuosity that has will be used mathematical equation to carry out numerous and diverse computing and obtain, and this not only increases difficulty from designing, and the more important thing is to manufacturing process and has brought bigger difficulty.Particularly existing steam turbine is because its Blade Design reasons in structure is part crescent shape as the blade face, or the blade structure shape of distortion arc, for the blade shape of its mutual correspondences at different levels of multistage turbine, all be easy to generate the turbulent flow phenomenon, this will reduce its operational efficiency greatly.
Model utility content the purpose of this utility model is at above-mentioned the deficiencies in the prior art, and a kind of efficient turbine rotor is provided.This impeller can improve the mobile performance of flowing medium, reduces the generation of turbulent flow, improves the utilization ratio of flowing medium, thereby improves the operational efficiency of steam turbine, and structure tube list, is easy to manufacturing.
The technical solution of the utility model comprises rotor shaft, quiet, the moving vane of some levels, its blade face of described stator blade is an arc, and this arc shaped blade forms an angle by the blade face tangent line and the rotor axis direction of outlet end, and is parallel with rotor axis by the blade face tangent line of entry end; Described moving vane is by forming the planar section of an angle and the formation of the arcuate segment between this two planar section by its blade face of inlet side planar section parallel with rotor axis with by its blade face of outlet side and rotor axis direction.
It highly dwindles described dynamic and static blade successively step by step to final stage from the first order.
Being shaped as of described quiet, moving vane: its final stage is quiet, moving vane is identical rectangle or trapezoidal shape, and first order moving vane is rectangle or is that rectangle, its relative the other end are trapezoidal by outlet end, and all the other stator blades at different levels are that trapezoidal, moving vane is a rectangle.
The wide curved or streamline of blade face, positive and negative two sides, the end of described its outlet end of moving vane rib also or be hypotenuse, the curved or streamline of reverse side blade face, the end corner angle of the relative the other end is also or be hypotenuse; Curved or the streamline of positive blade face, the end of described its outlet end of stator blade corner angle also or be hypotenuse, the curved or streamline of blade face, positive and negative two sides, the end corner angle of the relative the other end is also or be hypotenuse.
The utility model is compared further energy saving with existing impeller, because the above-mentioned shape of dynamic and static blade makes that the phase mutual connection stream on sound blade face is more steady, improves the mobile performance of flowing medium, can effectively avoid the flowing medium percolation to stop up, reduce the turbulent flow loss, improve operational efficiency.The running loss in light weight of its rotor shaft is little, and also further energy saving, and structure tube list is easy to processing and fabricating.
Description of drawings Fig. 1 is the utility model theory structure schematic representation.Fig. 2 is that the right hemihedry part of impeller among Fig. 1 is quiet, the top view structural representation of moving vane.Fig. 3 is the structural drawing of ten grade blade impellers of the utility model 2 * 500MW steam turbine.Fig. 4 is the top view structural representation of quiet, moving vane of the right hemihedry part of impeller among Fig. 3.
Now also the utility model is described in further detail in conjunction with the accompanying drawings by embodiment for embodiment.As shown in Figure 1, be the embodiment of a level Four blade.Reduce step by step successively toward first to fourth grade of blade face height quiet, moving vane 2-1～2-4,1-1～1-4 of fluid input direction respectively from the both sides of rotor shaft orientation flowing channel fluid output side.First profile to third level stator blade 2-1～2-3 (blade face orthographic projection) is shaped as the trapezoidal of rotor axial, second to fourth stage moving vane 1-2～1-4 and the profile (blade face orthographic projection) of fourth stage stator blade 2-4 be shaped as rectangle, the profile of first order moving vane 1-1 (blade face orthographic projection) is shaped as that to be trapezoidal its other end by fluid input one end rectangular.
Rotor shaft 3 its two ends and bearing means 4 corresponding two end portions 3-1 are solid shaft, and impeller mounting portion 3-2 is a hollow shaft between its two ends, forms to be similar to cydariform.
As shown in Figure 2, first to fourth grade of moving vane 1-1～1-4 is respectively by the pelvic outlet plane section 1a that tilts an angle respectively with the rotor axis direction by its blade face of fluid input side plane of inlet section 1b parallel with the rotor axis direction and its blade face, and arcuate segment 1c between this plane of inlet section 1b and pelvic outlet plane section 1a, that its blade face is curved formation; Arcuate segment 1c can form by the connecting part chamfering to pelvic outlet plane section 1a and plane of inlet section 1b.The blade face of first to fourth grade of moving vane 1-1～1-4 pelvic outlet plane section 1a respectively and the angle between the rotor axis direction 11～14 be followed successively by: 45.0,24.1,18.4,15.5 the degree.
The blade face of first to fourth grade of stator blade 2-1～2-4 is an arc, the angle 21～24 that forms between the blade face tangent line at its fluid outlet place of each grade blade and the rotor axis direction is followed successively by 63.4,41.8,33.7,29.0 degree, and the blade face tangent line 21 '～24 ' at fluid input end place is parallel with rotor axis.
The blade face corner angle chamfering streamlining or the hypotenuse of the front of the end fluoran stream surface that leans on fluid outlet of the rotor axial runner direction of moving vane and the reverse side of lee side, the blade face corner angle chamfering of the reverse side of its relative the other end lee side becomes hypotenuse.
The blade face corner angle chamfering in the front of the end fluoran stream surface that leans on fluid outlet of the rotor axial runner direction of stator blade becomes hypotenuse, the blade face corner angle chamfering streamlining or the hypotenuse of the front of the end fluoran stream surface of its relative the other end and the reverse side of lee side.Can reduce flow resistance through the blade after the chamfering like this.
The utility model is executed in the example reality for second kind, as shown in Figure 3, Figure 4, be followed successively by from the blade face tangent line at first to the tenth grade of its fluid outlet place of stator blade 2-1～2-10 and the angle 21～30 between the rotor axis direction: 63.4,41.8,33.7,29.0,25.9,23.6,21.8,20.4,19.2,18.2 degree, the blade face tangent line 21 '～30 ' at fluid input end place is parallel with the rotor axis direction.Be followed successively by from first to the tenth grade of moving vane 1-1～blade face of 1-10 pelvic outlet plane section 1a and the angle 11～20 between the rotor axis direction: 45.0,24.1,18.4,15.5,13.6,12.3,11.3,10.5,9.9,9.3 degree.Above-mentioned angular error can be controlled in ± 0.1 degree scope in.
Stator blade its highly every grade of outlet side and inlet side be followed successively by respectively from first to the tenth grade: 144,76,76,57,57,48,48,42,42,39,39,36,36,33,33,32,32,30,30,26mm.
76,57,48,42,39,36,33,32,30mm its height first order outlet side of moving vane, inlet side are respectively 172,144mm, are followed successively by from second to the tenth grade:.Above-mentioned height error can be controlled in ± the 1mm scope in.
Described width quiet, moving vane is 148mm, and each is quiet, the gap between the moving vane is 2mm.
Blades height has been considered the influence of blade profile to rotor fluid working substance passage sections.
The quantity that every grade blade suggestion is provided with is followed successively by from first to the tenth grade of stator blade: 70,113,140,166,185,203,225,233,252,131.Moving vane is followed successively by: 90,147,154,185,210,233,262,274,300,315.
Every grade blade evenly distributes on turbine blade pitch circle 5 by providing number.
Fluid inlet/outlet pipeline 6,7 diameter D1, the D2 of the rotor of the impeller of steam turbine and corresponding respectively flow velocity V1, the V2 of inlet/outlet pipeline 6,7 in the present embodiment, between the corresponding power W that the diameter D0 of the blade pitch circle 5 of impeller, the rotation speed n of impeller and blade progression N and steam turbine can produce, be 0.8kg/m in flowing medium density
3Corresponding relation under the condition sees Table one.
Table one:
| W(MW) | V1(m/s) | V2(m/s) | D1(m) | D2(m) | D0(m) | N (progression) | N (rev/min) |
| 2×150 | 1130 | 314 | 0.85 | 2×1.14 | 2.00 | 1-3 | 3000 |
| 2×300 | 1570 | 314 | 0.72 | 2×1.14 | 2.00 | 1-6 | 3000 |
| 2×500 | 2010 | 314 | 0.64 | 2×1.14 | 2.00 | 1-10 | 3000 |
Vapour (gas) turbine that above data declaration is provided with this impeller can move under the lower condition of pressure and temperature.
The utility model blade can be selected 2 ± 0.1mm thickness steel plate processing and fabricating for use.
This impeller is applicable to swiftly flowing water vapor or combustion gas vapour (gas) turbine as working medium, except that pressure and the temperature when working of the movement velocity of itself do not have concrete requirement.Vapour (gas) turbine send vapour (gas) by scroll, and it is constant that its flow keeps by every grade of impeller the time.
Claims (7)
1, a kind of turbine rotor, comprise rotor shaft, quiet, the moving vane of some levels is characterized in that its blade face of described stator blade is an arc, this arc shaped blade forms an angle by the blade face tangent line and the rotor axis direction of outlet end, and is parallel with rotor axis by the blade face tangent line of entry end; Described moving vane is by forming the planar section of an angle and the formation of the arcuate segment between this two planar section by its blade face of inlet side planar section parallel with rotor axis with by its blade face of outlet side and rotor axis direction.
2,, it is characterized in that it highly dwindles described dynamic and static blade successively step by step to final stage from the first order according to the described turbine rotor of claim 1.
3, according to claim 1 or 2 described turbine rotors, it is characterized in that being shaped as of described quiet, moving vane: its final stage is quiet, moving vane is identical rectangle or trapezoidal shape, first order moving vane is rectangle or is that rectangle, its relative the other end are trapezoidal by outlet end, and all the other stator blades at different levels are that trapezoidal, moving vane is a rectangle.
4, according to the described turbine rotor of claim 3, it is characterized in that described quiet, moving vane respectively is provided with ten grades respectively, described stator blade is followed successively by from first to the tenth grade by blade face tangent line and the angle between the rotor axis direction of outlet end: 63.4,41.8,33.7,29.0,25.9,23.6,21.8,20.4,19.2,18.2 spend;
Described moving vane is followed successively by from first to the tenth grade by the angle between its blade face of outlet side and the rotor axis direction: 45.0,24.1,18.4,15.5,13.6,12.3,11.3,10.5,9.9,9.3 degree;
Described stator blade its highly every grade of outlet side and inlet side be followed successively by respectively from first to the tenth grade: 144,76,76,57,57,48,48,42,42,39,39,36,36,33,33,32,32,30,30,26mm;
76,57,48,42,39,36,33,32,30mm its height first order outlet side of described moving vane, inlet side are respectively 172,144mm, are followed successively by from second to the tenth grade:.
5, according to the described turbine rotor of claim 3, it is characterized in that described quiet, moving vane respectively is provided with level Four respectively, described stator blade is followed successively by from first to fourth grade with the angle between the rotor axis direction by the blade face tangent line of outlet end: 63.4,41.8,33.7,29.0 spend; Described moving vane is followed successively by from first to fourth grade by the angle between its blade face of outlet side and the rotor axis direction: 45.0,24.1,18.4,15.5 degree.
6,, it is characterized in that described rotor shaft is by the hollow section between solid section constitutes corresponding to solid section of the two ends of bearing part with at these two ends according to the described turbine rotor of claim 1.
7, according to the described turbine rotor of claim 1, it is characterized in that the wide curved or streamline of blade face, positive and negative two sides, the end rib of described its outlet end of moving vane also or be hypotenuse, the curved or streamline of reverse side blade face, the end corner angle of the other end also or be hypotenuse relatively; Curved or the streamline of positive blade face, the end of described its outlet end of stator blade corner angle also or be hypotenuse, the curved or streamline of blade face, positive and negative two sides, the end corner angle of the relative the other end is also or be hypotenuse; Described width quiet, moving vane is 148mm, and each is quiet, the gap between the moving vane is 2mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008201131700U CN201212404Y (en) | 2008-07-12 | 2008-07-12 | Impeller wheel of steam turbine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008201131700U CN201212404Y (en) | 2008-07-12 | 2008-07-12 | Impeller wheel of steam turbine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201212404Y true CN201212404Y (en) | 2009-03-25 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2008201131700U Expired - Fee Related CN201212404Y (en) | 2008-07-12 | 2008-07-12 | Impeller wheel of steam turbine |
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| CN (1) | CN201212404Y (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102213176A (en) * | 2011-05-30 | 2011-10-12 | 高志连 | Same-diameter impeller group working by using fluid power |
| CN102767397A (en) * | 2012-07-09 | 2012-11-07 | 谢信芳 | Planar double-stroke gas turbine |
-
2008
- 2008-07-12 CN CNU2008201131700U patent/CN201212404Y/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102213176A (en) * | 2011-05-30 | 2011-10-12 | 高志连 | Same-diameter impeller group working by using fluid power |
| CN102213176B (en) * | 2011-05-30 | 2012-12-19 | 高志连 | Same-diameter impeller group working by using fluid power |
| CN102767397A (en) * | 2012-07-09 | 2012-11-07 | 谢信芳 | Planar double-stroke gas turbine |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20090325 Termination date: 20110712 |