CN218934503U - Novel turbine system of regulation level configuration - Google Patents
Novel turbine system of regulation level configuration Download PDFInfo
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- CN218934503U CN218934503U CN202221822077.3U CN202221822077U CN218934503U CN 218934503 U CN218934503 U CN 218934503U CN 202221822077 U CN202221822077 U CN 202221822077U CN 218934503 U CN218934503 U CN 218934503U
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Abstract
The utility model discloses a novel regulating stage configured steam turbine system, which at least comprises a high-pressure cylinder, a main steam valve, a main steam regulating valve and a steam inlet conduit. Under the rated working condition of the unit, each main steam regulating valve is fully opened, so that partial steam inlet loss is eliminated, and higher rated working condition regulating stage efficiency and wider constant pressure regulating range can be realized. The system also comprises a steam supplementing valve and a steam extraction port, wherein the steam extraction port is connected with the feed water heater through a steam extraction pipeline with a steam extraction regulating valve. When the main steam valve and the main steam regulating valve are in a fully-opened state, if the main steam flow is required to be increased, the main steam pressure can be increased to the upper limit by adopting a sliding pressure mode, and if the main steam flow is still required to be further increased, the steam supplementing valve can be opened or/and gradually closed until the final-stage steam extracting regulating valve or/and the penultimate steam extracting regulating valve are closed.
Description
Technical Field
The utility model belongs to the field of steam turbine generator units, and particularly relates to a novel steam turbine system with adjusting stage configuration.
Background
Under the double-carbon targets that carbon emission in China reaches a peak of carbon reaching and carbon neutralization is realized before year 2060, coal electricity is converted from original dominant energy to a low-carbon guaranteed power supply, wind and light new energy with randomness, gap property and volatility is absorbed as much as possible, and the coal motor group is required to have the capabilities of high efficiency, low carbon, deep peak regulation and flexible load change.
For conventional subcritical units, the boiler drum and the turbine with the regulation stage are generally configured such that their load response, the ability to flexibly change load, is relatively strong, and the regulation stage is indispensable, both from the point of view of safety and economy of unit operation.
The conventional regulating stage configured by the existing steam turbine has low design efficiency for meeting the strength requirement, and bears a larger proportion of enthalpy drop in the high-pressure cylinder of the steam turbine, especially under partial load, the conventional regulating stage further reduces the efficiency and adds the double adverse effects of increasing the acting proportion of the conventional regulating stage, so that the efficiency of the high-pressure cylinder is greatly reduced, and the low-load performance of the steam turbine is seriously affected.
The low operation efficiency of the conventional regulating stage is represented by the following two aspects:
on the one hand, the regulating stage is used as a main means for regulating the load of subcritical, supercritical or even a few supercritical units, and the principle is that the inlet steam flow of the steam turbine is controlled by regulating the area of the nozzle group so as to adapt to the load change. In order to ensure that the turbine can still achieve corresponding output under the summer working condition and the maximum steam inflow of the unit, taking an adjusting stage configured by 4 valve groups as an example, the turbine is often set to be fully opened by 3 valve groups under the rated working condition; in summer, the rated output is achieved by increasing the steam inlet flow of the steam turbine through partially or completely opening the 4 th valve; when the load is reduced, the steam inlet flow of the steam turbine is controlled by reducing the opening degree or the opening quantity of the valves. Once a certain valve-regulating portion is opened, the steam in the passage is throttled, resulting in throttling losses. And the smaller the opening of the valve is, the larger the throttling loss is.
On the other hand, the conventional regulating stage has low self-stage efficiency, and three main reasons are as follows: 1) In actual operation, the conventional adjusting stage needs to consider meeting the strength requirement of bearing larger pressure drop/enthalpy drop, is limited by the current materials and manufacturing process, can only be designed to be short and thick, is difficult to consider the efficiency level, has relatively larger steam leakage proportion of the top steam seal and has larger steam leakage loss; 2) The operation condition of the conventional regulating stage is complex, the pressure ratio of high-load steam in a regulating stage nozzle is generally large and is higher than the critical pressure ratio, and the regulating stage nozzle adopts a convergent nozzle. For a constant pressure operating unit, the pressure ratio of the steam at the regulating stage nozzle gradually decreases with the decrease of the load, and when the pressure ratio at the nozzle is smaller than the critical pressure ratio, a scaling nozzle is needed to meet the further expansion of the steam. Thus, the special requirement for conventional conditioning stages to employ both converging and converging nozzles is typically achieved by providing a chamfer at the nozzle outlet. When the pressure ratio of the steam at the nozzle is greater than or equal to the critical pressure ratio, the beveling only plays a role in guiding; when the pressure ratio of the steam at the nozzle is less than the critical pressure ratio, the steam may further expand at the chamfer portion and the nozzle outlet pressure may further decrease. However, the beveled part (the diverging section) is prone to steam shock wave generation and loss, so that the efficiency of the regulation stage is reduced more; 3) In the conventional regulation stage configuration, the steam turbine always has larger partial steam inlet loss except for the VWO working condition (the partial steam inlet loss is the smallest), and the larger the partial steam inlet degree is, the larger the loss is.
Accordingly, those skilled in the art have been working to develop a novel turbine system with a tuning stage configuration to improve turbine design and operating efficiency, thereby improving the economy of the unit's full operating load.
Disclosure of Invention
In view of the above-mentioned drawbacks of the prior art, the present utility model aims to solve the problem of low efficiency of conventional adjusting stage configuration of a steam turbine, and simultaneously reduce difficulty in designing the blade profile of the nozzle of the adjusting stage, and improve the efficiency of the adjusting stage.
In order to achieve the above purpose, the present utility model provides a steam turbine system configured with a novel adjusting stage, at least comprising a high pressure cylinder configured with a novel adjusting stage, a main steam valve, steam inlet pipes, a nozzle group of a novel adjusting stage, a chamber behind the adjusting stage and a main steam adjusting valve arranged on each steam inlet pipe, wherein steam enters the high pressure cylinder through a plurality of steam inlet pipes after passing through the main steam valve, and the steam turbine system is characterized in that the main steam valve and the main steam adjusting valve are all in a fully-opened state under a rated working condition of a unit; the novel nozzle group of the regulating stage adopts a convergent nozzle type, and the born pressure ratio is higher than the critical pressure ratio.
Further, the high-pressure cylinder also comprises a pressure stage, a steam supplementing valve, a steam supplementing conduit and a steam supplementing port; after the steam does work in the regulating stage, the steam is fully mixed in a cavity behind the regulating stage and then enters the pressure stage to continue to expand and do work; the steam supplementing port is arranged at the chamber behind the regulating stage or is arranged behind any pressure stage of the high-pressure cylinder.
Further, the steam turbine system also comprises a final-stage steam extraction pipeline, a final-stage steam extraction port of the high-pressure cylinder, a feed water heater taking the final-stage steam extraction port of the high-pressure cylinder as a steam source, and a regulating valve on the final-stage steam extraction pipeline; the high pressure cylinder final stage bleed is disposed at the chamber after the regulator stage, or after any pressure stage of the high pressure cylinder.
Further, the novel steam turbine system with the regulating stage configuration further comprises a high-pressure cylinder penultimate steam extraction pipeline, a penultimate steam extraction port, a feed water heater taking the high-pressure cylinder penultimate steam extraction port as a steam source, and a regulating valve on the penultimate steam extraction pipeline; the penultimate steam extraction port of the high pressure cylinder is positioned behind any pressure stage of the high pressure cylinder.
The operation method of the turbine system adopting the novel regulation stage configuration comprises the following steps:
if the load of the unit needs to be reduced, the area of the nozzle group can be regulated by gradually closing down until a part of main steam regulating valve is closed to maintain a constant pressure operation mode, or a sliding pressure operation mode, or an operation mode of combining the constant pressure with the sliding pressure is adopted. The method comprises the following steps:
step 1, when the load of the unit is reduced, maintaining a constant pressure operation mode by sequentially closing down the main steam regulating valve until a part of the main steam regulating valve is closed, and until the pressure drop born by the regulating stage reaches the design limit value; otherwise, when the load of the unit needs to be further increased, the unit is gradually increased by sequentially opening the main gas regulating valves until all the main gas regulating valves are completely opened.
Step 3, when the load of the unit is further reduced, the pressure drop of the regulating stage is correspondingly reduced due to small steam inflow, so that the pressure drop allowance is vacated, and the main steam regulating valves can be further sequentially turned down until the rest part is closed under the condition that the strength limit value of the regulating stage is met, but at least one main steam regulating valve needs to be kept to be opened; otherwise, when the load of the unit continues to rise, part of main steam regulating doors are sequentially opened, and a constant pressure operation mode is maintained.
Step 4, if the unit load still needs to be further reduced, if the unit load enters into the deep peak shaving mode, continuing to adopt a sliding pressure operation mode until the unit load slides to the minimum pressure required by the boiler; otherwise, when the load of the unit needs to be increased, a sliding pressure operation mode is adopted.
When the operation condition of exceeding the rated main steam flow (such as high back pressure in summer) is needed, the main steam valve and the main steam regulating valve are in a fully-opened state, if the main steam flow is needed to be increased, the main steam pressure can be increased to the upper limit by adopting a sliding pressure mode to increase the main steam flow, and if the main steam flow is still needed to be further increased to ensure the rated load, the steam supplementing valve can be opened or/and gradually closed until the final stage steam extraction regulating valve or/and the sub-final stage steam extraction regulating valve are closed. The step 1 specifically further comprises:
step 1.1, if the operation back pressure of the steam turbine is higher than the design value, the output power of the unit is still lower than the rated value under the condition that the main regulating valve of the steam turbine is fully opened and the steam inlet flow is the rated value. At this time, if the turbine inlet flow is required to be further increased to increase the load of the unit, the main steam pressure is increased by adopting a sliding pressure mode until the design upper limit is reached to increase the output of the unit;
and 1.2, after the sliding pressure is increased to reach the design upper limit, if the main steam flow is still required to be further increased to ensure the rated load, a steam supplementing valve opening mode or/and gradual closing mode can be adopted until the final stage steam extraction regulating valve or/and the penultimate stage steam extraction regulating valve is closed.
The novel turbine system with the adjusting stage configuration has the following advantages and technical effects:
(1) Under the rated working condition, all the main steam valves and the main steam regulating valves are in a full-open state, steam enters the regulating stage nozzle group in a nearly full-circumference steam inlet mode, the steam inlet degree of a part of the steam turbine is obviously reduced, the steam inlet loss of the part of the steam turbine is greatly reduced, and the regulating stage efficiency is highest;
(2) Compared with a steam turbine configured by a conventional regulating stage, the novel regulating stage has relatively small pressure drop/enthalpy drop under the same steam inlet flow, does not have a supersonic speed severe working condition, has low requirements on the strength of blades of the regulating stage, can optimize the design of the blade profile of a nozzle and the like, and improves the self efficiency of the regulating stage; meanwhile, the nozzle can be designed as a convergent nozzle, so that the condition that the steam shock wave easily causes the stage efficiency reduction in the traditional regulation stage chamfer part (divergent section) is avoided;
(3) The chamber behind the regulating stage is configured, so that steam behind the regulating stage moving blades can be fully mixed, partial steam inlet loss possibly occurring in the pressure stage can be avoided, part of steam kinetic energy can be converted into pressure energy, and residual speed loss of the regulating stage is reduced;
(4) When the load of the unit is reduced, the steam turbine can operate in a constant pressure mode, a sliding pressure mode or a combined mode, and as the number of the main steam regulating valves is relatively more, the regulating stage efficiency is higher, and the higher rated working condition regulating stage efficiency and the wider constant pressure regulating range can be realized, so that the operation efficiency is better comprehensively realized.
The conception, specific structure, and technical effects of the present utility model will be further described below to fully understand the objects, features, and effects of the present utility model.
Drawings
FIGS. 1 and 2 are schematic diagrams of a turbine system with a novel conditioning stage configuration in accordance with the present utility model.
Fig. 3-6 are illustrations of specific embodiments of the present utility model.
Wherein, 1-main steam pipeline; 2-a main steam regulating valve; 3-a steam inlet conduit; 4-a set of stage-adjusting nozzles; 5-adjusting the stage moving blades; 6-adjusting the post-stage chamber; 7-nozzles of the first pressure stage; 8-a steam supplementing valve; 9-a steam supplementing conduit; 10-a steam supplementing port of the steam turbine; 11-a turbine high pressure cylinder; 12-a steam extraction regulating valve; 13-a high pressure heater; a T-stage; y-pressure stage; v-main steam valve.
Detailed Description
Specific embodiments of the technical scheme of the utility model are described below.
Example 1
Taking a steam turbine provided with four main steam regulating valves as an example, the technical scheme adopted by the utility model is explained. As shown in fig. 1-3. Main steam from the outlet of the boiler superheater is divided into 4 branches through a main steam pipeline and a main steam valve and enters a high-pressure cylinder of the steam turbine, and each branch is controlled by an independent main steam regulating valve.
And under the rated working condition, the four main steam regulating valves are all in a full-open state. Steam enters the regulating stage nozzle group in a mode of almost full-circle steam inlet to expand and accelerate, then enters the regulating stage moving blades and pushes the regulating stage moving blades to do work. When the working condition is operated, partial steam inlet loss of the regulating stage is minimum. Meanwhile, the blades of the adjusting stage nozzle group are designed to be in a tapered shape, so that the blade shape of the adjusting stage nozzle group can be further optimized, and the condition that the steam shock wave easily causes the stage efficiency reduction in the traditional adjusting stage beveling part (a gradually-expanding section) is avoided.
When the load of the unit is reduced, controlling the steam quantity entering the steam turbine by sequentially closing the opening of the main steam regulating valve (comprising I, II, III, IV) one by one, wherein the main steam pressure is kept unchanged during the load reduction process (within a certain load range, for example, a 100% -75% load range) by gradually closing the I, II th valve; thereafter, to avoid excessive pressure drop experienced by the conditioning stage beyond its strength, a sliding pressure mode of operation (e.g., 75% -60% load range) may be employed; when the load is further reduced (for example, in the load range of 60% -40%), the intensity of the regulating stage can still be met because the steam inflow is relatively small, so that the regulating stage can be further closed until the valve III is closed to maintain a constant pressure operation mode, and only the valve IV is kept open (if the influence on equipment heating and the like possibly caused by the fact that only a single valve steam inflow of a steam turbine is considered, the operation of the valve III in a certain opening and a full opening state of the valve IV can also be maintained); when the load is further reduced (for example, below 40%), the sliding pressure mode can be adopted until the pressure reaches the minimum pressure required by the boiler.
In the turbine system with the conventional regulation stage configuration (the main gas regulating valves are also four), under the rated working condition, the main gas regulating valves are opened only three, and the other main gas regulating valve is closed (for example, the main gas regulating valve is closed I and the main gas regulating valve is opened II, III, IV) as a means for increasing the output of the unit, so that during the load reduction process (within a certain load range, for example, 100% -75% of the load range), the valve II is gradually closed and the valve III is closed to maintain the main gas pressure unchanged; and when the load is further reduced (below 75 percent), only a sliding pressure operation mode can be adopted.
Obviously, under the same load, the pressure drop/enthalpy drop born by the regulating stage is relatively small, the severe supersonic speed working condition does not exist, the strength requirement of the regulating stage blade is low, the design such as the nozzle blade profile and the like can be optimized, the self efficiency of the regulating stage can be improved, and the condition that the stage efficiency is reduced due to steam shock waves easily occurring in the inclined cutting part (gradually expanding section) of the traditional regulating stage is avoided, so that the overall efficiency is high. In addition, under low load (for example, 60% -40% load range), because the valve III can be further closed until the valve IV is closed, the valve IV is kept open, a constant pressure operation mode is maintained, compared with a conventional regulation stage sliding pressure operation mode, because the steam pressure parameter is relatively high, and work can be further performed in an efficient novel regulation stage, the work amount can be understood as the newly increased net power, and therefore, the operation efficiency of the unit under low load can be greatly improved.
Of course, in the technical scheme of the utility model, if the load of the unit still needs to be further improved after the four valves are fully opened, the following modes can be adopted:
(1) When the pressure of the main steam is not higher than the operation upper limit value of the pressure of the boiler drum, the main steam pressure is further increased, and the steam turbine operates in an upward sliding pressure mode;
(2) Opening a steam supplementing valve, and enabling a part of main steam flow to enter a certain intermediate stage of a high-pressure cylinder of the steam turbine to do work through the steam supplementing valve, a steam supplementing guide pipe and a steam supplementing port of the steam turbine so as to meet the output of a unit;
(3) By controlling the opening of the steam extraction regulating valve, one, two or more high-pressure heaters are gradually cut off to reduce the steam extraction amount and the steam inlet amount of the high-pressure cylinder of the steam turbine, so that the output of the unit is met.
The three operation modes can be selected according to the actual load demand condition of the unit, and one, two or three modes can be selected to meet the output force of the unit.
In this embodiment, the steam supplementing port and the final stage steam extracting port are both located in the chamber behind the adjusting stage, and under the rated working condition, the final stage steam extracting port and the final stage feedwater heater are normally put into use because the steam supplementing valve is in a closed state, and when the load of the unit needs to be further increased, the steam supplementing valve can be opened, and at this time, the steam supplementing enters the pressure stage through the chamber behind the adjusting stage to continuously apply work to increase the output of the unit. In this embodiment, the operation of the last stage feedwater heater and the steam make-up will have a conflict, and only one of them can be operated, if the last stage feedwater heater has to be disabled once the steam make-up is performed; if the final feedwater heater is to be used, the make-up steam must be shut off.
Example 2
As shown in fig. 4. Main steam from the outlet of the boiler superheater is divided into 4 branches through a main steam pipeline and a main steam valve and enters a high-pressure cylinder of the steam turbine, and each branch is controlled by an independent main steam regulating valve.
Compared with the embodiment 1, the main difference is that the steam supplementing port and the final stage steam extracting port in the embodiment are both positioned after a certain pressure stage (for example, the pressure stage of the fourth stage or the fifth stage, etc.), and the steam supplementing port and the final stage steam extracting port can be positioned after different pressure stages or after the same pressure stage, and if the steam supplementing input and the final stage steam extracting operation of the final stage feedwater heater corresponding to the steam supplementing port and the final stage steam extracting operation are not affected each other after the different pressure stages; if the two are only put into operation after the same pressure level, the final-stage feed water heater has to be stopped once the steam is supplemented; if the final feedwater heater is to be used, the make-up steam must be shut off.
The working principle of this embodiment is the same as that of embodiment 1, and will not be described here again.
Example 3
As shown in fig. 5. Main steam from the outlet of the boiler superheater is divided into 4 branches through a main steam pipeline and a main steam valve and enters a high-pressure cylinder of the steam turbine, and each branch is controlled by an independent main steam regulating valve.
The main difference between the embodiment and the embodiment 1 is that the steam supplementing port is positioned in the cavity behind the regulating stage, the steam extracting port at the final stage is positioned behind the pressure stage, and the input of the steam supplementing and the operation of the final stage feed water heater corresponding to the final stage steam extracting are not affected; therefore, compared with embodiment 1, the method has the advantages that the operation of the two is more flexible, the feeding of the final-stage feedwater heater can be continuously maintained by opening the steam supplementing valve firstly to increase the unit output, if the output force can not meet the requirement after the steam supplementing valve is opened, the final-stage feedwater heater can be further cut to further increase the unit output, and if the required unit output requirement can not be met after the two are combined, the penultimate-stage feedwater heater or a plurality of feedwater heaters can be further cut until the unit output requirement is met.
The working principle of this embodiment is the same as that of embodiment 1, and will not be described here again.
Example 4
As shown in fig. 6. Main steam from the outlet of the boiler superheater is divided into 4 branches through a main steam pipeline and a main steam valve and enters a high-pressure cylinder of the steam turbine, and each branch is controlled by an independent main steam regulating valve.
The main difference between the embodiment and the embodiment 1 is that the final stage steam extraction port is positioned in the cavity behind the regulating stage, the steam supplementing port is positioned behind the pressure stage, and the input of the steam supplementing and the operation of the final stage feed water heater corresponding to the final stage steam extraction are not affected; compared with the embodiment 1, the embodiment has the advantages that the operation of the two is more flexible, the feeding of the final-stage feed water heater can be continuously maintained by opening the steam supplementing valve firstly to increase the unit output, if the output force can not meet the requirement after the steam supplementing valve is opened, the final-stage feed water heater can be further removed to further increase the unit output, and if the two are combined, the required unit output requirement can not be met, the penultimate feed water heater or a plurality of feed water heaters can be further removed until the unit output requirement is met. Compared with embodiment 3, the final stage steam extraction port of this embodiment is located in the chamber behind the adjusting stage, so the corresponding steam extraction pressure is relatively higher, the low load can control the water supply temperature by using the steam extraction adjusting valve on the final stage steam extraction pipeline, and the higher water supply temperature can still be maintained under lower load.
The working principle of this embodiment is the same as that of embodiment 1, and will not be described here again.
The foregoing describes in detail preferred embodiments of the present utility model. It should be understood that numerous modifications and variations can be made in accordance with the concepts of the utility model without requiring creative effort by one of ordinary skill in the art. Therefore, all technical solutions which can be obtained by logic analysis, reasoning or limited experiments based on the prior art by the person skilled in the art according to the inventive concept shall be within the scope of protection defined by the claims.
Claims (4)
1. The steam turbine system with the novel regulation stage configuration at least comprises a novel regulation stage, a high-pressure cylinder provided with the novel regulation stage, a main steam valve, steam inlet pipes, a nozzle group of the novel regulation stage, a cavity behind the regulation stage and a main steam regulating valve arranged on each steam inlet pipe, wherein steam passes through the main steam valve and then enters the high-pressure cylinder through a plurality of steam inlet pipes; the novel nozzle group of the regulating stage adopts a convergent nozzle type, and the born pressure ratio is higher than the critical pressure ratio.
2. The steam turbine system of claim 1, wherein the high pressure cylinder further comprises a pressure stage, a make-up valve, a make-up conduit, and a make-up port; after the novel regulating stage does work, the steam is fully mixed in a cavity behind the regulating stage and then enters the pressure stage to continue to expand and do work; the steam supplementing port is arranged at the chamber behind the regulating stage or is arranged behind any pressure stage of the high-pressure cylinder.
3. The steam turbine system of any one of claims 1-2, further comprising a final stage extraction duct, a final stage extraction port of the high pressure cylinder, a feedwater heater using the final stage extraction port of the high pressure cylinder as a steam source, and a regulating valve on the final stage extraction duct; the high pressure cylinder final stage bleed is disposed at the chamber after the regulator stage, or after any pressure stage of the high pressure cylinder.
4. A novel conditioning stage configured turbine system as recited in claim 3, further comprising a high pressure cylinder penultimate steam extraction duct, a penultimate steam extraction port, a feedwater heater taking said high pressure cylinder penultimate steam extraction port as a steam source, and a conditioning valve on said penultimate steam extraction duct; the penultimate steam extraction port of the high pressure cylinder is positioned behind any pressure stage of the high pressure cylinder.
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