CN112901525B - Control method and control device for power system and power system - Google Patents
Control method and control device for power system and power system Download PDFInfo
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- CN112901525B CN112901525B CN202110076411.9A CN202110076411A CN112901525B CN 112901525 B CN112901525 B CN 112901525B CN 202110076411 A CN202110076411 A CN 202110076411A CN 112901525 B CN112901525 B CN 112901525B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/04—Units comprising pumps and their driving means the pump being fluid-driven
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- 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
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/08—Adaptations for driving, or combinations with, pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/002—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by varying geometry within the pumps, e.g. by adjusting vanes
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- 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
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
- F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
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- Control Of Positive-Displacement Air Blowers (AREA)
- Control Of Turbines (AREA)
Abstract
The present disclosure provides a control method, a device and a power system for a power system, wherein the power system comprises a steam turbine and a compressor, the steam turbine is used for driving the compressor, the compressor comprises an air inlet guide vane valve, and the control method comprises the following steps: acquiring the current rotating speed of the steam turbine; and when the current rotating speed exceeds a first preset range, adjusting the calculated opening degree of the air inlet guide vane valve to enable the current rotating speed to be within the first preset range. The load of the power system and the corresponding actual steam consumption can be adjusted according to the opening degree of the air inlet guide vane valve of the compressor, so that the steam consumption is limited within the maximum steam supply amount, the phenomenon that the turbine stalls to generate trip due to the fact that the maximum steam supply amount is limited and the power of the whole machine is not matched is avoided, and the phenomenon that the compressor surges to cause trip is avoided.
Description
Technical Field
The present disclosure relates to the field of power system control technologies, and in particular, to a control method and a control device for a power system, and a power system.
Background
When the centrifugal compressor driven by the back pressure turbine is used as a stable compressed air supplier, a sufficient amount of steam is required, so that it is not necessary to match the amount of steam, and it is only necessary to provide stable compressed air. However, when the maximum steam supply provided by the outside is limited, that is, the objective of configuring the turbine to drive the centrifugal compressor has been shifted from providing mainly stable compressed air to dynamically adjusting the compressor load, that is, adjusting the load of the back-pressure turbine, thereby ensuring that the overall power of the power system does not exceed the power that the maximum steam supply can provide.
Since the aim of a conventional back-pressure turbine-driven compressor controller is to provide stable compressed air, it is not possible to automatically adapt the steam supply, i.e. to ensure that the overall power does not exceed the power which can be provided by the maximum steam supply.
Disclosure of Invention
In view of the above, embodiments of the present disclosure provide a control method and a control device for a power system, and the power system, so as to solve the problems that the conventional back pressure turbine-driven compressor controller in the prior art aims to provide stable compressed air, so that the steam supply amount cannot be automatically matched, that is, the power that the maximum steam supply amount can provide cannot be guaranteed not to be exceeded by the entire power, and the like.
In one aspect, an embodiment of the present disclosure provides a control method for a power system, where the power system includes a steam turbine and a compressor, the steam turbine is used for driving the compressor, the compressor includes an intake guide vane valve, and the control method includes the following steps:
acquiring the current rotating speed of the steam turbine;
and when the current rotating speed exceeds a first preset range, adjusting the calculated opening degree of the air inlet guide vane valve to enable the current rotating speed to be within the first preset range.
In some embodiments, the first predetermined range is determined by a rated speed of the steam turbine, and the first predetermined range includes a first upper threshold value greater than the rated speed and a first lower threshold value less than the rated speed.
In some embodiments, the difference between the first upper threshold and the first lower threshold and the rated speed is not the same.
In some embodiments, further comprising:
when the current rotating speed exceeds a first preset range, adjusting the calculated opening degree of the air inlet guide vane valve to enable the current rotating speed to be within a second preset range, wherein the second preset range comprises a second upper limit threshold and a second lower limit threshold, the second upper limit threshold is located between the first upper limit threshold and the rated rotating speed, and the second lower limit threshold is located between the first lower limit threshold and the rated rotating speed.
In some embodiments, said adjusting the calculated opening degree of the intake air vane valve so that the current rotation speed is within the first preset range includes:
and adjusting the calculated opening of the air inlet guide vane valve within a third preset range.
In some embodiments, the third preset range is determined by a third upper threshold and a third lower threshold, wherein the third lower threshold is a minimum loading opening degree of the intake vane valve, and the minimum loading opening degree is a minimum opening degree of the intake vane valve that ensures normal operation of the compressor.
In some embodiments, the calculated opening is determined by:
acquiring an actual angle and an angle range of the air inlet guide vane valve;
determining the calculated opening degree based on the actual angle and the angle range.
In some embodiments, the steam turbine is a back pressure steam turbine and the compressor is a centrifugal compressor.
The present disclosure also provides a control device for a power system, the power system including a steam turbine and a compressor, the steam turbine being configured to drive the compressor, the compressor including an intake guide vane valve, the control device being configured to perform the control method according to any one of the above technical solutions.
In some embodiments, the control device is a PLC controller, and the PLC controller is connected to the valve controller of the intake air guide vane valve through an ethernet ring network.
The present disclosure also provides a power system, which includes a steam turbine and a compressor, wherein the steam turbine is used for driving the compressor, and the power system includes the control device in any one of the above technical solutions.
The load of the power system and the corresponding actual steam consumption can be adjusted according to the opening of the air inlet guide vane valve of the compressor, so that the steam consumption is limited within the maximum steam supply amount, the phenomenon that the turbine stalls to trip due to the fact that the maximum steam supply amount is limited and the power of the whole machine is not matched is avoided, the phenomenon that the compressor surges to trip is avoided, the problem of limitation of the maximum steam supply amount is solved, and the whole machine can be more flexibly matched with the working condition of the steam supply amount.
In addition, the embodiment of the disclosure can perform operation adjustment according to the steam consumption through control optimization of the steam turbine driving compressor in the power system, namely, when the steam consumption of the corresponding load reaches the maximum steam supply amount, the output power of the compressor is limited, and the load is prevented from exceeding the limit of the maximum steam supply amount on the power; when the load of the whole machine is reduced, the ballast limitation can be automatically removed, and the function of the compressor in the general sense is realized, so that stable compressed air is provided.
Drawings
In order to more clearly illustrate the embodiments of the present disclosure or the technical solutions in the prior art, the drawings needed to be used in the description of the embodiments or the prior art will be briefly introduced below, it is obvious that the drawings in the following description are only some embodiments described in the present disclosure, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
FIG. 1 is a system schematic of a power system provided by an embodiment of the present disclosure;
fig. 2 is a schematic flow chart of a control method according to an embodiment of the disclosure;
fig. 3 is a control schematic diagram of a control method according to an embodiment of the disclosure;
fig. 4 is a schematic flow chart of a control method according to an embodiment of the disclosure;
fig. 5 is a schematic diagram of a control device according to an embodiment of the disclosure.
Reference numerals are as follows:
10-a steam turbine; 20-a compressor; 30-an air inlet guide vane valve; 40-a controller; 50-a processor; 60-IO module; 70-touch screen.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present disclosure more clear, the technical solutions of the embodiments of the present disclosure will be described below clearly and completely with reference to the accompanying drawings of the embodiments of the present disclosure. It is to be understood that the described embodiments are only a few embodiments of the present disclosure, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the described embodiments of the disclosure without any inventive step, are within the scope of protection of the disclosure.
Unless otherwise defined, technical or scientific terms used herein shall have the ordinary meaning as understood by one of ordinary skill in the art to which this disclosure belongs. The use of "first," "second," and similar terms in this disclosure is not intended to indicate any order, quantity, or importance, but rather is used to distinguish one element from another. The word "comprising" or "comprises", and the like, means that the element or item listed before the word covers the element or item listed after the word and its equivalents, but does not exclude other elements or items. The terms "connected" or "coupled" and the like are not restricted to physical or mechanical connections, but may include electrical connections, whether direct or indirect. "upper", "lower", "left", "right", and the like are used merely to indicate relative positional relationships, and when the absolute position of the object being described is changed, the relative positional relationships may also be changed accordingly.
To maintain the following description of the embodiments of the present disclosure clear and concise, a detailed description of known functions and known components is omitted from the present disclosure.
A first embodiment of the present disclosure provides a control method for a power system, as shown in fig. 1, where the power system includes a steam turbine 10 and a compressor 20 that are connected to each other, the steam turbine 10 is a rotary power machine that consumes externally supplied steam, such as a boiler, and converts energy into mechanical work, and the compressor 20 is a fluid machine that delivers gas and increases the pressure of the gas, so that the steam is supplied as intake air to the steam turbine 10 to do work and is discharged, and the steam is supplied to the steam turbine 10 to output kinetic energy, thereby driving a variable-capacity compression motion in the compressor 20, and finally generating a required compressed gas, thereby achieving the overall operation of the power system. Generally, the steam turbine 10 receives a maximum amount of externally supplied steam to operate at a rated rotational speed under the condition that the load of the power system is constant.
In one embodiment, the steam turbine 10 is a back pressure steam turbine, and the compressor 20 is a centrifugal compressor, and the back pressure steam turbine is coupled to the centrifugal compressor via a transmission mechanism such as a reduction gear box and a coupling to transmit kinetic energy to drive the centrifugal compressor.
Further, the compressor 20 has an intake portion, an intake Guide Vane valve 30 is disposed in the intake portion, the intake Guide Vane valve 30 is used for controlling the movement of an Intake Guide Vane (IGV), and the calculated opening degree of the intake Guide Vane valve 30 determines the intake air amount of the intake portion of the compressor 20, for example, the calculated opening degree of the intake Guide Vane valve 30 can be controlled by a controller 40 on the compressor 20.
In the operation of the power system, the load of the compressor 20 is related to the load of the power system, the load of the power system is related to the actual steam consumption of the power system when the rotation speed of the steam turbine 10 is not changed, the actual steam consumption for maintaining the normal operation of the power system is larger when the load of the power system is larger, and the actual steam consumption is also changed when the rotation speed of the steam turbine 10 is changed and the load of the power system is not changed. Therefore, the control method for the power system according to the embodiment of the present disclosure can control the actual steam consumption by controlling the load of the power system, and in order to ensure the normal operation of the power system, especially in the case of the current rotation speed of the steam turbine 10 changing, the actual steam consumption of the steam turbine 10 needs to be adjusted in such a way that the maximum steam supply provided by the outside is not exceeded, and meanwhile, the problems of surging the compressor 20 and stopping the power system are not caused.
As shown in fig. 2, the control method for a power system of the embodiment of the present disclosure includes the steps of:
and S101, acquiring the current rotating speed of the steam turbine.
In the operation of the power system, the steam turbine 10 is used for performing work by externally input steam such as a boiler to drive the compressor 20, and it is known that the current rotation speed of the steam turbine 10 is directly related to the actual steam consumption, generally speaking, the steam turbine 10 operates at the rated rotation speed, the corresponding steam consumption when the steam turbine operates at the rated rotation speed at full load is the maximum steam supply, and the fluctuation of the current rotation speed of the steam turbine 10 means the actual steam consumption changes. Therefore, in this step, a current rotation speed of the steam turbine 10 is first obtained, and an operating state of the steam turbine 10, which is related to the actual steam consumption, is determined from the current rotation speed.
S102, when the current rotating speed exceeds a first preset range, adjusting the calculated opening degree of the air inlet guide vane valve to enable the current rotating speed to be within the first preset range.
After the current rotation speed of the steam turbine 10 is obtained in the step S101, a judgment is made between the current rotation speed and a rated rotation speed, for example, specifically, when the current rotation speed exceeds a first preset range, the calculated opening degree of the intake guide vane valve 30 is adjusted so that the current rotation speed is within the first preset range.
Specifically, if the current rotation speed of the steam turbine 10 is within the first preset range, it may be considered that the steam turbine 10 basically operates in a rated or normal state, and when the current rotation speed exceeds the first preset range, that is, when the operation state of the steam turbine 10 is greatly changed, in order to avoid that the actual steam consumption of the power system is greater than the maximum steam supply amount, it is necessary to adjust the load of the power system so that the current rotation speed of the steam turbine 10 is restored to the normal range, and to operate the power system in a normal state, for example, when the current rotation speed of the steam turbine 10 is too low, that the actual steam consumption of the power system exceeds the maximum steam supply amount, and when the current rotation speed is too high, a shutdown of the steam turbine 10 or the compressor 20 in the power system may be caused, and therefore, the current rotation speed of the steam turbine 10 needs to be adjusted to a suitable range.
In the power system according to the embodiment of the present disclosure, the outside supplies steam to the steam turbine 10 to enable the steam turbine 10 to perform work and transmit kinetic energy to the compressor 20 to drive the operation of the compressor 20, so that the output power of the compressor 20 is directly related to the load of the power system and the actual steam consumption corresponding to the load. During the operation of the power system, the load or output of the compressor 20 is in a positive correlation with the opening degree of the intake guide vane valve 30 in the intake portion of the compressor 20, and therefore, the output of the compressor 20 can be adjusted by the calculated opening degree of the intake adjusting valve 30, so that the operation of the steam turbine 10 can be controlled based on the output of the compressor 20, and finally the load variation of the power system is controlled, for example, when the actual steam consumption amount of the power system exceeds the maximum steam supply amount, the output of the compressor 20 can be controlled based on the calculated opening degree of the intake guide vane valve 30 of the compressor 20, and thus the load of the power system is adjusted, so that the current rotation speed of the steam turbine 10 is adjusted to an appropriate range so that the actual steam consumption amount does not exceed the maximum steam supply amount.
Further, when determining between the current rotational speed of the steam turbine 10 and the first predetermined range, the first predetermined range is determined by the rated rotational speed of the steam turbine 10, and the first predetermined range includes a first upper threshold greater than the rated rotational speed and a first lower threshold less than the rated rotational speed, that is, the first upper threshold in the first predetermined range is greater than the rated rotational speed, and the first lower threshold is less than the rated rotational speed, wherein, taking fig. 3 as an example, the first upper threshold is 101% of the rated rotational speed, and the first lower threshold is 99% of the rated rotational speed.
If the current rotation speed exceeds the first preset range, specifically, if the current rotation speed is less than a first lower threshold of the first preset range, the actual steam consumption of the power system is considered to exceed the maximum steam supply amount, which requires adjusting the load of the power system based on the output power of the compressor 20, so that the current rotation speed of the steam turbine 10 is adjusted to be within the first preset range, and adjusting the actual steam consumption of the power system so that the actual steam consumption does not exceed the maximum steam supply amount, specifically, adjusting the output power of the compressor 20 by adjusting the calculated opening degree of the intake guide vane valve 30 of the compressor 20, so as to reduce the load of the power system and the actual steam consumption, so that the rotation speed of the steam turbine 10 can return to the rated rotation speed again; when the current rotating speed is greater than a first upper threshold of the first preset range, under the condition that the load of the power system is not changed, the turbine 10 or the compressor 20 may be stopped, and therefore, the load of the power system needs to be adjusted, so that the current rotating speed of the turbine 10 is adjusted to be within the first preset range; therefore, in both cases, it is necessary to adjust the load of the power system by adjusting the calculated opening of the intake guide vane valve 30 of the compressor 20 so that the current rotational speed of the steam turbine 10 is restored to the first preset range, so that the opening limit of the intake guide vane valve 30 to the compressor 20 can be released in this case.
In a preferred embodiment, when the current rotation speed exceeds a first preset range, the calculated opening degree of the intake air guide vane valve 30 is adjusted so that the current rotation speed is within a second preset range, the second preset range includes a second upper threshold and a second lower threshold, the second upper threshold is between the first upper threshold and the rated rotation speed, and the second lower threshold is between the first lower threshold and the rated rotation speed. Here, for example, if the first predetermined range is 99% to 101%, the second predetermined range may be 99.5% to 100.5%, that is, the second predetermined range is within the first predetermined range, so that the current rotational speed may be adjusted more finely so that the current rotational speed is within a range closer to the rated rotational speed.
The second preset range is the most stable working range of the compressor, and the operation performance of the compressor is the best within the preset range, so that the current rotating speed is within the second preset range by adjusting the calculated opening degree of the intake guide vane valve 30, the compressor can operate most stably, and the controller can be prevented from frequently adjusting the rotating speed.
For adjusting the calculated opening degree of the intake louver valve 30, the load of the compressor 20 is related to the calculated opening degree of the intake louver valve 30 in the intake portion of the compressor 20, when the opening degree of the intake louver valve 30 is larger, the intake air amount per unit time of the compressor 20 is larger, so that the load or output power of the compressor 20 is larger, and correspondingly, when the opening degree of the intake louver valve 30 is smaller, the intake air amount per unit time of the compressor 20 is smaller, so that the load or output power of the compressor 20 is smaller.
Further, the step of adjusting the calculated opening degree of the inlet guide vane valve 30 to make the current rotation speed of the steam turbine 10 within the first preset range aims at adjusting the air intake amount of the compressor 20 to make the current rotation speed of the steam turbine 10 return to the first preset range by adjusting the load of the power system, and comprises: the calculated opening degree of the intake guide vane valve 30 is adjusted within a third preset range. The third preset range is determined by a third upper threshold and a third lower threshold, where the third upper threshold may be set to 100% at most, the third lower threshold is the minimum loading opening of the intake vane valve 30, and the minimum loading opening is the minimum opening of the intake vane valve 30 that ensures normal operation of the compressor 20, and may be set to 30%, for example. The third preset range here is used to limit the adjustment range of the intake guide vane valve 30.
The minimum loading opening is mainly explained, the minimum loading opening is the minimum opening for preventing the compressor 20 from surging, if the compressor 20 supplies gas to a pipe network during the normal operation of the power system, since the pipe network is pressurized, and if the intake guide vane valve 30 is in a fully closed state, the outlet pressure of the compressor 20 is reduced to be very low due to the fact that the gas cannot be sucked by the compressor 20, and thus the gas in the pipe network flows backwards into the compressor 20 to cause surging, therefore, the opening of the intake guide vane valve 30 is ensured to be greater than a certain value during the operation of the power system to ensure that the outlet pressure of the compressor 20 has the ability to resist the backflow of the pipe network pressure to prevent surging. In practical use, the minimum loading opening is obtained by measurement when the power system is debugged in the field, for example, the power system is started according to a set pressure value, when the calculated opening of the intake guide vane valve 30 is tested at 30%, whether the exhaust pressure of the compressor 20 reaches a set value before the surge occurs is checked, if the exhaust pressure can be reached successfully, the calculated opening of the intake guide vane valve 30 is reduced to 25%, for example, and then the test is performed until the surge occurs in the compressor 20, and the minimum loading opening is determined.
Specifically, as shown in fig. 4, the calculated opening degree of the intake guide vane valve 30 may be obtained by:
s201, acquiring an actual angle and an angle range of the air inlet guide vane valve.
In this step, since it is necessary to obtain the calculated opening degree of the intake guide vane valve 30, which is determined by conversion based on the actual angle of the intake guide vane valve 30 and the angle range, the angle range of the intake guide vane valve 30 is related to the design parameter of the valve body thereof, and the actual angle of the intake guide vane valve 30 can be controlled by a controller or the like in the compressor 20 to vary within the angle range. In the disclosed embodiment, the angle of the inlet guide vane valve 30 ranges from 0 ° to 85.6 °.
And S202, determining the calculated opening degree based on the actual angle and the angle range.
After the actual angle and the angle range of the intake louver valve 30 are acquired through step S201, the calculated opening degree of the intake louver valve 30 may be determined by conversion through the following equation:
calculated opening (%) =100-100 (actual angle/85.6 °).
The calculated opening degree here generally refers to a range of 0% to 100%, and in order to ensure the normal operation of the compressor 20, after the obtaining of the calculated opening degree of the intake guide vane valve 30, the method further includes: and adjusting the calculated opening to be larger than a minimum loading opening, wherein the minimum loading opening is the minimum opening of the air inlet guide vane valve 30 for ensuring the normal operation of the compressor 20, so that the compressor 20 can be ensured to operate continuously and stably without breakdown and the like.
The air inlet guide vane valve 30 mainly comprises a valve rod and vanes, wherein the angle of the valve rod is controlled by a valve controller, and when the angle of the valve rod is 0 degrees, namely the actual angle is 0 degrees, the vanes are fully opened, namely the calculated opening degree is 100 percent; when the angle of the valve stem is 85.6 °, i.e. the actual angle is 85.6 °, the vanes are fully closed, i.e. the calculated opening is 100%.
The range of the physical opening degree is determined according to actual conditions, the actual angle of the valve rod can be rotated to 90 degrees, however, the rotation is too large, the closing between the blades is very tight, the vacuumizing is caused, then the valve cannot be opened, and therefore the valve is generally rotated to 85.6 degrees, the valve is prevented from being closed to death, and the valve cannot be opened when a machine needs to be loaded.
The disclosed embodiments can limit the actual output power of the compressor and the load of the power system by adjusting the calculated opening of the intake guide vane valve of the compressor in the case where the required actual steam consumption of the power system exceeds the maximum steam supply amount provided from the outside, and can also prevent the shutdown of the steam turbine or the compressor due to the increase in the rotation speed of the steam turbine in order to prevent the actual steam consumption from being greater than the maximum steam supply amount and the compressor surge that may occur due to the decrease in the rotation speed of the steam turbine.
According to the embodiment of the disclosure, the load of the power system and the corresponding actual steam consumption can be adjusted according to the opening of the air inlet guide vane valve of the compressor, so that the steam consumption is limited within the maximum steam supply, the turbine stalling caused by the maximum steam supply limitation and the complete machine power mismatching is avoided from generating trip, and the compressor surge caused trip is also avoided, thereby solving the problem of the maximum steam supply limitation, and enabling the complete machine to be capable of more flexibly matching the steam supply working condition.
A second embodiment of the present disclosure provides a control apparatus for a power system, as shown in fig. 1, the power system including a steam turbine 10 and a compressor 20, the steam turbine 10 being configured to drive the compressor 20, the compressor 20 including an intake guide vane valve 30, the control apparatus being configured to perform any of the control methods in the first embodiment of the present disclosure.
As shown in FIG. 5, the control device employs a PLC controller, such as the Allen-Bradley series of Rockwell automation; the processor (CPU) 50 adopts a 1756-L72 processor, and the IO module 60 for redundant configuration adopts a 1715-series redundant IO configuration module; the touch screen 70 is a Panel View Plus 7 series 10 inch screen.
The control device is connected with other controllers by an Ethernet ring network, for example, two servo valve controllers of the compressor, in one embodiment, the air inlet guide vane valve and the air release valve are hung on the ring network by a ring network module, and the control device of the compressor can perform opening control and state monitoring by an Ethernet/IP protocol. Wherein the Inlet Guide Vane Valve is used for controlling an Inlet Guide Vane (IGV), and the Blow Valve (BOV) is used for executing gas Blow operation control.
The embodiment of the disclosure can adjust the load of the power system and the corresponding actual steam consumption according to the opening of the air inlet guide vane valve of the compressor, thereby ensuring that the steam consumption is limited within the maximum steam supply, avoiding the trip caused by the stall of the steam turbine due to the mismatch of the maximum steam supply limit and the power of the whole machine, and avoiding the trip caused by the surge of the compressor, thereby solving the problem of the limitation of the maximum steam supply and enabling the whole machine to be more flexibly matched with the working condition of the steam supply.
A third embodiment of the present disclosure provides a power system that employs the control apparatus of the second embodiment.
Moreover, although exemplary embodiments have been described herein, the scope thereof includes any and all embodiments based on the disclosure with equivalent elements, modifications, omissions, combinations (e.g., of various embodiments across), adaptations or alterations. The elements of the claims are to be interpreted broadly based on the language employed in the claims and not limited to examples described in the present specification or during the prosecution of the application, which examples are to be construed as non-exclusive. It is intended, therefore, that the specification and examples be considered as exemplary only, with a true scope and spirit being indicated by the following claims and their full scope of equivalents.
The above description is intended to be illustrative, and not restrictive. For example, the above-described examples (or one or more versions thereof) may be used in combination with each other. For example, other embodiments may be used by those of ordinary skill in the art upon reading the above description. In addition, in the foregoing detailed description, various features may be grouped together to streamline the disclosure. This should not be interpreted as an intention that a non-claimed disclosed feature is essential to any claim. Rather, the subject matter of the present disclosure may lie in less than all features of a particular disclosed embodiment. Thus, the following claims are hereby incorporated into the detailed description as examples or embodiments, with each claim standing on its own as a separate embodiment, and it is contemplated that the embodiments can be combined with each other in various combinations or permutations.
The scope of the disclosure should be determined with reference to the appended claims, along with the full scope of equivalents to which such claims are entitled. The above embodiments are merely exemplary embodiments of the present disclosure, which is not intended to limit the present disclosure, and the scope of the present disclosure is defined by the claims. Various modifications and equivalents of the disclosure herein disclosed may occur to persons skilled in the art and are intended to be included within the spirit and scope of the disclosure.
Claims (11)
1. A control method for a power system including a turbine for driving a compressor to compress air and the compressor including an intake air guide vane valve, the control method comprising the steps of:
acquiring the current rotating speed of the steam turbine;
when the current rotating speed exceeds a first preset range, adjusting the calculated opening degree of the air inlet guide vane valve to enable the current rotating speed to be within the first preset range;
the actual steam consumption of the steam turbine does not exceed the maximum steam supply provided by the outside by adjusting the load of the power system.
2. A control method according to claim 1, characterized in that said first preset range is determined by the rated speed of the turbine; the first preset range includes a first upper threshold value greater than the rated rotation speed and a first lower threshold value less than the rated rotation speed.
3. The control method according to claim 1, characterized in that the first upper threshold value and the first lower threshold value are different from the difference between the rated rotational speed.
4. The control method according to claim 1, characterized by further comprising:
and when the current rotating speed exceeds a first preset range, adjusting the calculated opening degree of the air inlet guide vane valve to enable the current rotating speed to be within a second preset range, wherein the second preset range comprises a second upper limit threshold and a second lower limit threshold, the second upper limit threshold is located between the first upper limit threshold and the rated rotating speed, and the second lower limit threshold is located between the first lower limit threshold and the rated rotating speed.
5. The control method according to claim 1, wherein the adjusting the calculated opening degree of the intake guide vane valve so that the current rotation speed is within the first preset range includes:
and adjusting the calculated opening of the air inlet guide vane valve within a third preset range.
6. The control method according to claim 5, wherein the third preset range is determined by a third upper threshold and a third lower threshold, wherein the third lower threshold is a minimum loading opening degree of the intake vane valve, and the minimum loading opening degree is a minimum opening degree of the intake vane valve that ensures normal operation of the compressor.
7. The control method according to claim 1, wherein the calculated opening degree is determined by:
acquiring an actual angle and an angle range of the air inlet guide vane valve;
determining the calculated opening degree based on the actual angle and the angle range.
8. The control method according to claim 1, wherein the steam turbine is a back pressure steam turbine, and the compressor is a centrifugal compressor.
9. A control apparatus for a power system, the power system including a turbine for driving a compressor, and the compressor including an intake guide vane valve, the control apparatus being configured to perform the control method according to any one of claims 1 to 8.
10. The control device of claim 9, wherein the control device is a PLC controller, and the PLC controller is connected to the valve controller of the inlet guide vane valve through an ethernet ring network.
11. A power system comprising a turbine and a compressor, the turbine being arranged to drive the compressor, characterised by comprising a control device according to claim 9 or 10.
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| CA2544366A1 (en) * | 2006-05-19 | 2006-07-31 | Sandy Albert Clancy | A natural gas compressor and a system for operating the same |
| CN1987689A (en) * | 2005-12-19 | 2007-06-27 | 本田技研工业株式会社 | Control apparatus |
| CN106337789A (en) * | 2016-09-13 | 2017-01-18 | 山东康宏电力有限公司 | Light-collecting amplification solar photo-thermal power generation system and method |
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| CN111075516A (en) * | 2019-12-06 | 2020-04-28 | 浙江浙能技术研究院有限公司 | Adaptive parameter change control system and method for steam turbocharger |
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| CN1987689A (en) * | 2005-12-19 | 2007-06-27 | 本田技研工业株式会社 | Control apparatus |
| CA2544366A1 (en) * | 2006-05-19 | 2006-07-31 | Sandy Albert Clancy | A natural gas compressor and a system for operating the same |
| CN106337789A (en) * | 2016-09-13 | 2017-01-18 | 山东康宏电力有限公司 | Light-collecting amplification solar photo-thermal power generation system and method |
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