CN205315052U - Variable -speed turbine and heating system thereof - Google Patents
Variable -speed turbine and heating system thereof Download PDFInfo
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- CN205315052U CN205315052U CN201521039320.4U CN201521039320U CN205315052U CN 205315052 U CN205315052 U CN 205315052U CN 201521039320 U CN201521039320 U CN 201521039320U CN 205315052 U CN205315052 U CN 205315052U
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Abstract
The utility model provides a variable -speed turbine and heating system thereof, including high intermediate pressure cylinder who has the first rotor axle and the low pressure jar that has the the second rotor axle, still include a speed change mechanism, speed change mechanism's output is connected with the first rotor axle, and speed change mechanism's input is connected with the the second rotor axle, when the operation backpressure of steam turbine rose, the steam enthalpy drop (img file='dest_path_image002. TIF'wi='24'he='20' /) of low pressure jar reduced, and speed change mechanism is used for reducing the rotational speed n of the the second rotor axle of low pressure jar, when the operation backpressure of steam turbine reduced, the steam enthalpy drop (img file='518688dest_path_image002. TIF'wi='24'he='20' /) of low pressure jar increased, and speed change mechanism is used for increasing the rotational speed n of the the second rotor axle of low pressure jar. This application changes the rotational speed of steam turbine low pressure jar through speed change mechanism, and the change volume of the change volume that makes low pressure jar rotational speed produced low pressure jar enthalpy drop when changing with the steam turbine operation backpressure is corresponding to make the velocity ratio of low pressure jar all the time in reasonable design scope, and then guarantee steam turbine unit's safe operation, and still improved steam turbine unit's economic nature.
Description
Technical field
This utility model relates to steam turbine power generation field, particularly relates to a kind of variable-speed turbine and heating system thereof.
Background technology
In recent years, China, in order to meet the requirement of energy-saving and emission-reduction, generally closes down little back pressure thermal power plant unit, changes the high-power extraction and condensing unit central heating of employing into. In order to reduce the cold source energy of condenser further, increasing heating load, in the winter time under thermal condition, the backwater of part power plant heat supply network is as the recirculated water of condenser, and the low pressure steam discharge of steam turbine directly heats heating network recirculated water. Owing to the return water temperature of heating network recirculated water is generally 45～50 DEG C, the leaving water temperature of heating network recirculated water is generally 75～85 DEG C, the operation back pressure of the steam turbine corresponding with this Heating Period operating mode is 44～55KPa, therefore the operation back pressure (4.9～11.8KPa) of its steam turbine corresponding with non-heating period operating mode has very big difference, steam turbine operation back pressure value under Heating Period operating mode is far beyond the operational envelope of original Long Turbine Blades.
For the problems referred to above, generally there is following two settling mode at present:
Mode one, using steam turbine in the operation back pressure of Heating Period as design point, adopt shorter blade, but, when non-heating period, the blade of steam turbine is blocking back pressure operation, and economy is very poor.
Mode two, employing interchangeable pair force down rotor design, to adapt to different operation back pressures, but, its cost is very high, need to be equipped with two sets to be applicable to difference and run the rotors of back pressures, and when height runs back pressure or during low operation back pressure, change corresponding rotor there is also operational inconvenience.
Utility model content
The shortcoming of prior art in view of the above, the purpose of this utility model is in that to provide a kind of cost low and run the variable-speed turbine being respectively provided with good safety and economy under back pressure or low operation back pressure at height.
For achieving the above object, this utility model provides a kind of variable-speed turbine, and including having the high intermediate pressure cylinder of the first rotor axle and having the low pressure (LP) cylinder of the second armature spindle, the speed ratio x of described low pressure (LP) cylinder is:In formula: n is the rotating speed of the second armature spindle of low pressure (LP) cylinder, and D is the diameter of the leaf-level of low pressure (LP) cylinder, Δ h is the steam enthalpy drop of low pressure (LP) cylinder, and m is total progression of low pressure (LP) cylinder;Also including a gear, the outfan of described gear is connected with described the first rotor axle, and the input of described gear is connected with described second armature spindle; When the operation back pressure of steam turbine raises, the steam enthalpy drop Δ h of described low pressure (LP) cylinder reduces, and described gear is for reducing the rotating speed n of the second armature spindle of low pressure (LP) cylinder, and the minimizing amount of the rotating speed n of low pressure (LP) cylinder is corresponding with the minimizing amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder; When the operation back pressure of steam turbine reduces, the steam enthalpy drop Δ h of described low pressure (LP) cylinder increases, and described gear is for increasing the rotating speed n of the second armature spindle of low pressure (LP) cylinder, and the increase amount of the rotating speed n of low pressure (LP) cylinder is corresponding with the increase amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder.
Preferably, described gear is the one in change speed gear box, speed regulator, variator, gear-box.
Further, when the exhaust steam pressure of steam turbine reduces or enters the increase of steam flow amount, the steam enthalpy drop Δ h of described low pressure (LP) cylinder increases, described gear is for increasing the rotating speed n of the second armature spindle of low pressure (LP) cylinder, and the increase amount of the rotating speed n of low pressure (LP) cylinder is corresponding with the increase amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder; When the exhaust steam pressure of steam turbine raises or enters the minimizing of steam flow amount, the steam enthalpy drop Δ h of described low pressure (LP) cylinder reduces, described gear is for reducing the rotating speed n of the second armature spindle of low pressure (LP) cylinder, and the minimizing amount of the rotating speed n of low pressure (LP) cylinder is corresponding with the minimizing amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder.
This utility model also provides for a kind of variable-speed turbine heating system, including feed pump steam turbine, the intermediate pressure cylinder of steam turbine and low pressure (LP) cylinder, condenser, secondary heater and resident's heating tube, the steam drain of medium pressure cylinder is connected with the air intake of low pressure (LP) cylinder by pipeline, the described outlet of feed pump steam turbine is connected with the entrance of condenser each through pipeline with the steam drain of low pressure (LP) cylinder, the outlet of described condenser is connected with the import of secondary heater by pipeline, the outlet of described secondary heater is connected by the arrival end of pipeline with resident's heating tube, the port of export of described resident's heating tube is connected with the entrance of condenser by pipeline, whole extraction opening is teased and ridicule during medium pressure cylinder is additionally provided with, this is teased and ridicule during whole extraction opening passes through and tease and ridicule whole extraction line and be connected with the import of secondary heater, the intermediate pressure cylinder of described steam turbine has the first rotor axle, and the low pressure (LP) cylinder of described steam turbine has the second armature spindle, and the speed ratio x of described low pressure (LP) cylinder is:In formula: n is the rotating speed of the second armature spindle of low pressure (LP) cylinder, and D is the diameter of the leaf-level of low pressure (LP) cylinder, Δ h is the steam enthalpy drop of low pressure (LP) cylinder, and m is total progression of low pressure (LP) cylinder; Also including a gear, the outfan of described gear is connected with described the first rotor axle, and the input of described gear is connected with described second armature spindle; When the operation back pressure of steam turbine raises, the steam enthalpy drop Δ h of described low pressure (LP) cylinder reduces, and described gear is for reducing the rotating speed n of the second armature spindle of low pressure (LP) cylinder, and the minimizing amount of the rotating speed n of low pressure (LP) cylinder is corresponding with the minimizing amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder; When the operation back pressure of steam turbine reduces, the steam enthalpy drop Δ h of described low pressure (LP) cylinder increases, and described gear is for increasing the rotating speed n of the second armature spindle of low pressure (LP) cylinder, and the increase amount of the rotating speed n of low pressure (LP) cylinder is corresponding with the increase amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder.
Preferably, tease and ridicule whole extraction line in described and be provided with adjustment valve.
Preferably, described low pressure (LP) cylinder is double fluid low pressure (LP) cylinder.
As it has been described above, the variable-speed turbine that relates to of this utility model and heating system thereof, have the advantages that
The application changes the rotating speed of turbine low pressure cylinder by gear, and the variable quantity of produced low pressure (LP) cylinder enthalpy drop is corresponding when making the variable quantity of low pressure (LP) cylinder rotating speed with steam turbine operation economy, so that the speed ratio of low pressure (LP) cylinder is all the time in rational scope of design, and then the safe operation of guarantee steam-turbine unit, and also improve the economy of steam-turbine unit; Additionally, the application sets up a gear just to reach steam-turbine unit and be respectively provided with the effect of good economic and safety when high back pressure, low back pressure between the first rotor axle and the second armature spindle of low pressure (LP) cylinder of high intermediate pressure cylinder, therefore its cost is also non-normally low. Meanwhile, this variable-speed turbine is applied in Winter heat supply system, to reduce the cold source energy of condenser, increases heat supply network heating load, to meet the requirement of energy-saving and emission-reduction.
Accompanying drawing explanation
Fig. 1 is the structural representation of variable-speed turbine in the application.
Fig. 2 is the structural representation of variable-speed turbine heating system in the application.
Element numbers explanation
1 high intermediate pressure cylinder
11 the first rotor axles
2 low pressure (LP) cylinders
21 second armature spindles
3 gears
4 feed pump steam turbines
5 condensers
6 secondary heater
7 resident's heating tubes
Whole extraction line is teased and ridicule in 8
9 regulate valve
Detailed description of the invention
By particular specific embodiment, embodiment of the present utility model being described below, those skilled in the art the content disclosed by this specification can understand other advantages of the present utility model and effect easily.
Notice, the structure of this specification institute accompanying drawings depicted, ratio, size etc., all only in order to coordinate the disclosed content of description, understand for those skilled in the art and read, it is not limited to the enforceable qualifications of this utility model, therefore do not have technical essential meaning, the adjustment of the modification of any structure, the change of proportionate relationship or size, under not affecting effect that this utility model can be generated by and the purpose that can reach, all should still drop on the disclosed technology contents of this utility model and obtain in the scope that can contain. Simultaneously, in this specification cited as " on ", D score, "left", "right", " centre " and " one " etc. term, it is merely convenient to understanding of narration, and it is not used to limit the enforceable scope of this utility model, the change of its relativeness or adjustment, changing under technology contents without essence, when being also considered as the enforceable category of this utility model.
In steam turbine is through-flow blade design, need to keeping optimum speed ratio, to obtain higher stage efficiency, the speed ratio x1 of every one-level is represented by below equation:In formula: u is the peripheral speed of leaf-level; C is the vapor (steam) velocity of leaf-level leaf grating outlet, and n1 is the rotating speed of steam turbine, and D1 is the diameter of leaf-level, and Δ h1 is the steam enthalpy drop of a cylinder, and m1 is the total progression in a cylinder. Therefore, the speed ratio x of steam turbine mesolow cylinder is:In formula: n is the rotating speed of low pressure (LP) cylinder, D is the diameter of the leaf-level of low pressure (LP) cylinder, and Δ h is the steam enthalpy drop of low pressure (LP) cylinder, and m is total progression of low pressure (LP) cylinder.
Under normal circumstances, the armature spindle of steam turbine high pressure cylinder, the armature spindle of intermediate pressure cylinder, low pressure (LP) cylinder armature spindle be an axle, therefore multiple cylinder has identical rotating speed. But, when steam turbine is run at Heating Period, it runs back pressure and raises, therefore the enthalpy drop Δ h of steam turbine mesolow cylinder can reduce, and therefore, the speed ratio x of low pressure (LP) cylinder deflects away from original design point, so that the stage efficiency of low pressure (LP) cylinder declines.If it addition, the speed ratio x substantial deviation design point of low pressure (LP) cylinder, then low pressure (LP) cylinder blade air blast can be caused to generate heat, thus affecting the safety and reliability that steam-turbine unit runs.
For the problems referred to above, the armature spindle of high intermediate pressure cylinder in steam-turbine unit and the armature spindle of low pressure (LP) cylinder are disconnected by the application and uses gear to connect two roots rotor axles, so that steam-turbine unit is when Heating Period and non-heating period run, low pressure (LP) cylinder has different rotating speeds. Specifically, as shown in Figure 1, the application provides a kind of variable-speed turbine, including there is the high intermediate pressure cylinder 1 of the first rotor axle 11 and there is the low pressure (LP) cylinder 2 of the second armature spindle 21, also include a gear 3, the outfan of described gear 3 is connected with described the first rotor axle 11, and the input of described gear 3 is connected with described second armature spindle 21; When steam-turbine unit runs at Heating Period, then the operation back pressure of steam turbine raises, the steam enthalpy drop Δ h of described low pressure (LP) cylinder 2 reduces, now, maintain the rotating speed of the first rotor axle 11 of high intermediate pressure cylinder, change the gear number gear ratio of gear 3 (namely reduce) of gear 3, reduce the rotating speed n of the second armature spindle 21 of low pressure (LP) cylinder 2 with this, and the minimizing amount of the rotating speed n of low pressure (LP) cylinder 2 is corresponding with the minimizing amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder 2; When steam-turbine unit runs at non-heating period, then the operation back pressure of steam turbine reduces, the steam enthalpy drop Δ h of described low pressure (LP) cylinder 2 increases, now, maintain the rotating speed of the first rotor axle 11 of high intermediate pressure cylinder, change the gear number gear ratio of gear 3 (namely increase) of gear 3, increase the rotating speed n of the second armature spindle 21 of low pressure (LP) cylinder 2 with this, and the increase amount of the rotating speed n of low pressure (LP) cylinder 2 is corresponding with the increase amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder 2.
In the application, second armature spindle 21 of the first rotor axle 11 of the high intermediate pressure cylinder 1 of steam-turbine unit and low pressure (LP) cylinder 2 is disconnected, and by gear 3, the first rotor axle 11 and the second armature spindle 21 are connected, therefore, the rotating speed n of the second armature spindle 21 of steam-turbine unit low pressure (LP) cylinder 2 under difference operation back pressure can be changed by gear 3, and the variable quantity of produced low pressure (LP) cylinder 2 enthalpy drop Δ h is corresponding when making the variable quantity of low pressure (LP) cylinder 2 rotating speed n with steam turbine operation economy, so that the speed ratio x of low pressure (LP) cylinder 2 is all the time in best scope of design, and then ensure efficiency and the safety of low pressure (LP) cylinder blade, thus the safe operation of steam-turbine unit, and also improve the economy of steam-turbine unit. additionally, the application sets up a gear 3 just to reach steam-turbine unit and be respectively provided with the effect of good economic and safety when high back pressure, low back pressure between the first rotor axle 11 and the second armature spindle 21 of low pressure (LP) cylinder 2 of high intermediate pressure cylinder 1, run back pressure compared to steam turbine difference in prior art and need the mode of more exchanging rotor, the cost of the application is non-normally low, and operation is very easy.
Further, the variable-speed turbine that the application relates to also apply be applicable in the thermal power plant unit of high-capacity power, when middle row's amount of drawing gas of unit is bigger, low pressure (LP) cylinder 2 enter steam flow amount reduce, initial steam pressure reduce, then the enthalpy drop Δ h of low pressure (LP) cylinder 2 reduces, now, gear 3 is for reducing the rotating speed n of the second armature spindle 21 of low pressure (LP) cylinder 2, and the minimizing amount of the rotating speed n of low pressure (LP) cylinder 2 is corresponding with the minimizing amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder 2, to reach the speed ratio x maintaining low pressure (LP) cylinder 2 in optimum range, it is ensured that the safety in operation of unit and economy.
In like manner, when the exhaust steam pressure of steam turbine reduces or enters steam flow amount increase (initial steam pressure rising), the steam enthalpy drop Δ h of described low pressure (LP) cylinder 2 increases, then can be increased the rotating speed n of the second armature spindle 21 of low pressure (LP) cylinder 2 by gear 3, and the increase amount of the rotating speed n of low pressure (LP) cylinder 2 is corresponding with the increase amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder 2; When the exhaust steam pressure of steam turbine raises or enters steam flow amount minimizing (initial steam pressure reduction), the steam enthalpy drop Δ h of described low pressure (LP) cylinder 2 reduces, the rotating speed n of the second armature spindle 21 of low pressure (LP) cylinder 2 then can be reduced by gear 3, and the minimizing amount of the rotating speed n of low pressure (LP) cylinder 2 is corresponding with the minimizing amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder 2, the speed ratio x making low pressure (LP) cylinder 2 maintains in optimum range, and the final safety in operation ensureing unit and economy and maintenance low pressure (LP) cylinder 2 have higher efficiency.
Preferably, the first rotor axle 11 of described high intermediate pressure cylinder 1 and the second armature spindle 21 of low pressure (LP) cylinder 2 can coaxial lines, can not also coaxial line, shift to install, therefore described gear 3 can adopt change speed gear box, speed regulator, variator, gear-box etc., and gear 3 has multiple regulation stall, the gear ratio that namely can regulate the second armature spindle 21 to the first rotor 11 has multiple different numerical value.
Further, the application also provides for a kind of variable-speed turbine heating system, as shown in Figure 2, this variable-speed turbine heating system includes feed pump steam turbine 4, the intermediate pressure cylinder of steam turbine and low pressure (LP) cylinder 2, condenser 5, secondary heater 6 and resident's heating tube 7, the steam drain of medium pressure cylinder is connected by the air intake of pipeline with low pressure (LP) cylinder 2, the outlet of described feed pump steam turbine 4 is connected each through the entrance of pipeline with condenser 5 with the steam drain of low pressure (LP) cylinder 2, the outlet of described condenser 5 is connected by the import of pipeline with secondary heater 6, the outlet of described secondary heater 6 is connected by the arrival end of pipeline with resident's heating tube 7, the port of export of described resident's heating tube 7 is connected by the entrance of pipeline with condenser 5, whole extraction opening is teased and ridicule during medium pressure cylinder is additionally provided with, this is teased and ridicule during whole extraction opening passes through and tease and ridicule whole extraction line 8 and be connected with the import of secondary heater 6. described steam turbine is variable-speed turbine described above, therefore the intermediate pressure cylinder of this steam turbine has the first rotor axle 11, and the low pressure (LP) cylinder 2 of this steam turbine has the second armature spindle 21, and the first rotor axle 11 is connected by a gear 3 with the second armature spindle 21, when the operation back pressure of steam turbine raises, the steam enthalpy drop Δ h of described low pressure (LP) cylinder 2 reduces, described gear 3 is for reducing the rotating speed n of the second armature spindle 21 of low pressure (LP) cylinder 2, and the minimizing amount of the rotating speed n of low pressure (LP) cylinder 2 is corresponding with the minimizing amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder 2, when the operation back pressure of steam turbine reduces, the steam enthalpy drop Δ h of described low pressure (LP) cylinder 2 increases, described gear 3 is for increasing the rotating speed n of the second armature spindle 21 of low pressure (LP) cylinder 2, and the increase amount of the rotating speed n of low pressure (LP) cylinder 2 is corresponding with the increase amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder 2.
Variable-speed turbine the application related to is applied in Winter heat supply system, adopt the backwater recirculated water as condenser 5 of heat supply network, the low pressure steam discharge of steam turbine directly heats the recirculated water of heating network, and steam turbine is teased and ridicule whole drawing gas again heat the recirculated water of heating network, to reduce the cold source energy of condenser 5, increase heat supply network heating load, thus meeting the requirement of energy-saving and emission-reduction.Additionally, when the variable-speed turbine in heating system is when Heating Period, it is that high back pressure runs, correspondingly, the rotating speed of the low pressure (LP) cylinder 2 in Heating Period operating mode tubine unit reduces so that the speed ratio x of the low pressure (LP) cylinder 2 in Heating Period operating mode tubine unit is in optimum range; When the variable-speed turbine in heating system is when non-heating period, it is low back pressure operation, correspondingly, the rotating speed of the low pressure (LP) cylinder 2 in non-heating period operating mode tubine unit increases, the speed ratio x of the general low pressure (LP) cylinder 2 made in non-heating period operating mode tubine unit is in optimum range, therefore steam-turbine unit all has good safety and economy under any operating mode.
In the present embodiment, tease and ridicule whole extraction line 8 in described and be provided with adjustment valve 9, in being used for opening or closing, tease and ridicule whole extraction line 8, or for teasing and ridicule the size of the whole amount of drawing gas in regulating; Described low pressure (LP) cylinder 2 is double fluid low pressure (LP) cylinder.
In sum, the application has the advantages that
1, back pressure thermal power plant unit: compared with mode two-spool with prior art, the investment of how a set of low pressure rotor of power plant can be reduced, and without changing time of low pressure rotor and expense for annual twice, therefore the cost of unit can be substantially reduced, save Financial cost and time cost; Compared with prior art directly being blocked blade or adopt short blade, it is possible to be greatly improved the unit economy at non-heating period.
2, solidifying thermal power plant unit is taken out: improve performance driving economy disclosed in heat supply.
3, conventional pure condensate unit: improve the performance driving economy of high back pressure operating mode in summer.
So, this utility model effectively overcomes various shortcoming of the prior art and has high industrial utilization.
Above-described embodiment only illustrative principle of the present utility model and effect thereof, not for restriction this utility model. Above-described embodiment all under spirit of the present utility model and category, can be modified or change by any those skilled in the art. Therefore, art has all equivalence modification or changes that usually intellectual completes under the spirit disclosed without departing from this utility model with technological thought such as, must be contained by claim of the present utility model.
Claims (6)
1. a variable-speed turbine, including having the high intermediate pressure cylinder of the first rotor axle and having the low pressure (LP) cylinder of the second armature spindle, the speed ratio x of described low pressure (LP) cylinder is:In formula: n is the rotating speed of the second armature spindle of low pressure (LP) cylinder, and D is the diameter of the leaf-level of low pressure (LP) cylinder, Δ h is the steam enthalpy drop of low pressure (LP) cylinder, and m is total progression of low pressure (LP) cylinder; It is characterized in that: also including a gear, the outfan of described gear is connected with described the first rotor axle, and the input of described gear is connected with described second armature spindle;
When the operation back pressure of steam turbine raises, the steam enthalpy drop Δ h of described low pressure (LP) cylinder reduces, and described gear is for reducing the rotating speed n of the second armature spindle of low pressure (LP) cylinder, and the minimizing amount of the rotating speed n of low pressure (LP) cylinder is corresponding with the minimizing amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder;
When the operation back pressure of steam turbine reduces, the steam enthalpy drop Δ h of described low pressure (LP) cylinder increases, and described gear is for increasing the rotating speed n of the second armature spindle of low pressure (LP) cylinder, and the increase amount of the rotating speed n of low pressure (LP) cylinder is corresponding with the increase amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder.
2. variable-speed turbine according to claim 1, it is characterised in that: described gear is the one in change speed gear box, speed regulator, variator, gear-box.
3. variable-speed turbine according to claim 1, it is characterized in that: when the exhaust steam pressure of steam turbine reduces or enters the increase of steam flow amount, the steam enthalpy drop Δ h of described low pressure (LP) cylinder increases, described gear is for increasing the rotating speed n of the second armature spindle of low pressure (LP) cylinder, and the increase amount of the rotating speed n of low pressure (LP) cylinder is corresponding with the increase amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder;
When the exhaust steam pressure of steam turbine raises or enters the minimizing of steam flow amount, the steam enthalpy drop Δ h of described low pressure (LP) cylinder reduces, described gear is for reducing the rotating speed n of the second armature spindle of low pressure (LP) cylinder, and the minimizing amount of the rotating speed n of low pressure (LP) cylinder is corresponding with the minimizing amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder.
4. a variable-speed turbine heating system, it is characterized in that: include feed pump steam turbine, the intermediate pressure cylinder of steam turbine and low pressure (LP) cylinder, condenser, secondary heater and resident's heating tube, the steam drain of medium pressure cylinder is connected with the air intake of low pressure (LP) cylinder by pipeline, the described outlet of feed pump steam turbine is connected with the entrance of condenser each through pipeline with the steam drain of low pressure (LP) cylinder, the outlet of described condenser is connected with the import of secondary heater by pipeline, the outlet of described secondary heater is connected by the arrival end of pipeline with resident's heating tube, the port of export of described resident's heating tube is connected with the entrance of condenser by pipeline, whole extraction opening is teased and ridicule during medium pressure cylinder is additionally provided with, this is teased and ridicule during whole extraction opening passes through and tease and ridicule whole extraction line and be connected with the import of secondary heater, the intermediate pressure cylinder of described steam turbine has the first rotor axle, and the low pressure (LP) cylinder of described steam turbine has the second armature spindle, and the speed ratio x of described low pressure (LP) cylinder is:In formula: n is the rotating speed of the second armature spindle of low pressure (LP) cylinder, and D is the diameter of the leaf-level of low pressure (LP) cylinder, Δ h is the steam enthalpy drop of low pressure (LP) cylinder, and m is total progression of low pressure (LP) cylinder; Also including a gear, the outfan of described gear is connected with described the first rotor axle, and the input of described gear is connected with described second armature spindle;
When the operation back pressure of steam turbine raises, the steam enthalpy drop Δ h of described low pressure (LP) cylinder reduces, and described gear is for reducing the rotating speed n of the second armature spindle of low pressure (LP) cylinder, and the minimizing amount of the rotating speed n of low pressure (LP) cylinder is corresponding with the minimizing amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder;
When the operation back pressure of steam turbine reduces, the steam enthalpy drop Δ h of described low pressure (LP) cylinder increases, and described gear is for increasing the rotating speed n of the second armature spindle of low pressure (LP) cylinder, and the increase amount of the rotating speed n of low pressure (LP) cylinder is corresponding with the increase amount of the steam enthalpy drop Δ h of low pressure (LP) cylinder.
5. variable-speed turbine heating system according to claim 4, it is characterised in that: tease and ridicule whole extraction line in described and be provided with adjustment valve.
6. variable-speed turbine heating system according to claim 4, it is characterised in that: described low pressure (LP) cylinder is double fluid low pressure (LP) cylinder.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201521039320.4U CN205315052U (en) | 2015-12-14 | 2015-12-14 | Variable -speed turbine and heating system thereof |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201521039320.4U CN205315052U (en) | 2015-12-14 | 2015-12-14 | Variable -speed turbine and heating system thereof |
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| CN205315052U true CN205315052U (en) | 2016-06-15 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106870021A (en) * | 2015-12-14 | 2017-06-20 | 上海电气电站设备有限公司 | Variable-speed turbine and its heating system |
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2015
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106870021A (en) * | 2015-12-14 | 2017-06-20 | 上海电气电站设备有限公司 | Variable-speed turbine and its heating system |
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