WO2005021976A1 - 圧縮機の制御装置 - Google Patents
圧縮機の制御装置 Download PDFInfo
- Publication number
- WO2005021976A1 WO2005021976A1 PCT/JP2004/012366 JP2004012366W WO2005021976A1 WO 2005021976 A1 WO2005021976 A1 WO 2005021976A1 JP 2004012366 W JP2004012366 W JP 2004012366W WO 2005021976 A1 WO2005021976 A1 WO 2005021976A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- compressor
- control
- operation value
- control device
- value
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/22—Fuel supply systems
- F02C7/236—Fuel delivery systems comprising two or more pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C9/00—Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
- F02C9/26—Control of fuel supply
- F02C9/38—Control of fuel supply characterised by throttling and returning of fuel to sump
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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
- F04D27/02—Surge control
- F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
-
- 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
- F04D27/02—Surge control
- F04D27/0246—Surge control by varying geometry within the pumps, e.g. by adjusting vanes
Definitions
- the present invention relates to a compressor control device for compressing fuel gas.
- a fuel gas supply device for a gas turbine including a control means for adjusting a fuel gas supply amount to a gas turbine so as to maintain a discharge pressure of a fuel gas compressor within a set range.
- a bypass valve is provided between the suction flow path and the discharge flow path of the compressor, and the opening degree of the bypass valve is determined based on a signal from a pressure detector that detects the discharge pressure. By controlling the discharge pressure, the discharge pressure is maintained within a set range.
- Patent Document 1 Patent No. 3137498
- An object of the present invention is to provide a control device for a compressor that can obtain good controllability in an operating state.
- the present invention provides an inflow amount adjusting means for adjusting an inflow amount of fuel gas into a compressor, and returns fuel gas discharged from the compressor to an inlet side of the compressor.
- Control valve for operating the compressor at a predetermined operating point, and a control means for controlling the inflow amount adjusting means and the recycle valve based on the control operation value.
- the control means generates, when the control operation value is equal to or greater than a predetermined value, a signal that increases with an increase in the operation value as a control signal of the inflow amount adjustment means.
- Signal generation means, and second control signal generation means for, when the control operation value is less than the predetermined value, generating a signal that decreases as the operation value increases as a control signal for the recycle valve, Characterized by having ing.
- an inlet guide valve provided at an inlet of the compressor or a drive source for rotating the compressor can be used.
- the first control signal generating means when the control operation value is less than the predetermined value
- the value of the minimum opening signal is changed according to the pressure of the fuel gas flowing into the compressor.
- control operation value a value obtained by adding a feedforward operation value to a feedback control operation value can be used.
- the operation value for feedback control is formed based on a pressure difference of a fuel gas discharged from the compressor, and the operation value for feedforward control is based on a load of the compressor. Can be formed.
- the operation value for feedback control includes a discharge flow rate set value corresponding to a pressure deviation of the fuel gas. Based on the deviation from the amount of fuel gas flowing into the header tank May be set.
- the valve control means may be configured to track the operation value for feedback control to a predetermined value when a load is interrupted, and to rapidly open the recycle valve.
- the valve control means compares the anti-surge signal generating means with the anti-surge signal and the control signal of the recycle valve, and selectively outputs a higher signal of the signals to the recycle valve. It may further include high-order selecting means for outputting.
- a value obtained by adding a feedforward operation value to a feedback control operation value as the control operation value for an arbitrary one of the compressors is used.
- the feedforward operation value is used as the control operation value for the machine.
- the recycle valve which is connected only with the inlet guide valve, is also used for controlling the discharge pressure of the compressor. Therefore, all operation states (when the load is cut off, when the compressor and the gas turbine trip, during normal operation) , Etc.), a good control result can be obtained. In addition, since the inlet guide valve and the recycle valve are operated in the split range, control interference by these valves is avoided.
- highly responsive pressure control can be achieved by a combination of feedforward control and feedback control. Furthermore, since the higher control of discharge pressure control and anti-surge control is selectively applied to the recycle valve, interference between these controls is also avoided.
- FIG. 1 is a block diagram showing a first embodiment of a control device for a compressor according to the present invention.
- FIG. 2 is a graph showing the relationship between discharge flow rate and discharge pressure using the IGV opening as a parameter.
- FIG. 3 is a graph illustrating a function of a load command that defines a valve opening operation value.
- FIG. 4 is a graph exemplifying a function of a valve opening operation value that defines an IGV opening.
- FIG. 5 is a graph illustrating a function of a valve opening operation value that defines an RCV opening.
- FIG. 6 is a characteristic diagram illustrating a relationship between a discharge flow rate and a discharge pressure using the rotation speed of the compressor as a parameter.
- FIG. 7 is a block diagram showing a second embodiment of the control device for the compressor according to the present invention.
- FIG. 8 is a block diagram showing a third embodiment of a control device for a compressor according to the present invention.
- FIG. 9 is a block diagram showing a fourth embodiment of a control device for a compressor according to the present invention.
- FIG. 1 shows a first embodiment of the present invention.
- an inlet guide valve (hereinafter referred to as IGV) 5 is interposed between the inlet of the compressor 1 and the fuel gas supply line 3, and the outlet of the compressor 1 is connected to the fuel gas supply line.
- a recycling valve (hereinafter referred to as RCV) 7 is interposed between the system and 3.
- RCV7 has a structure that is more responsive than IGV5.
- the compressor 1 compresses a fuel gas (in this example, a constant-pressure fuel gas) supplied from the gas supply line 3 via the IGV 5. Fuel gas compressed by the compressor 1 is supplied to a gas turbine 15 via a check valve 9, an on-off valve 11, and a header tank 13, where it is burned.
- a fuel gas in this example, a constant-pressure fuel gas supplied from the gas supply line 3 via the IGV 5.
- Fuel gas compressed by the compressor 1 is supplied to a gas turbine 15 via a check valve 9, an on-off valve 11, and a header tank 13, where it is burned.
- Curves a, b, and c in FIG. 2 illustrate the relationship between the discharge flow rate and the discharge pressure of the compressor 1 when the opening degree of the IGV 5 is 20%, 50%, and 100%, respectively.
- the set pressure SV is P
- the flow rate required from the gas turbine 15 is F
- compressor 1 operates at operating point A.
- a minimum opening of the IGV5 (in this example, an opening of 20%) is set so that the opening of the IGV5 does not become smaller than the minimum opening. I have to.
- the discharge flow amount is not reduced after the IGV 5 reaches the minimum opening. Therefore, as described later, when the IGV 5 reaches the minimum opening, the opening is maintained and a part of the fuel gas discharged from the compressor 1 is supplied to the fuel supply line 3 through the RCV 7. To return to.
- the required flow rate of the fuel gas is, for example, F shown in FIG.
- Discharge flow can be reduced only up to the discharge flow rate F (> F) based on the opening of 20%.
- the feed gas is supplied to the turbine 15 side.
- the operating point of compressor 1 is A
- the load command unit 17 gives an output command to the function generator 19.
- This output command is given as a load factor when the maximum load of the gas turbine 15 is set to 100%.
- the function generator 19 converts the output instruction into an operation value MV based on a function as illustrated in FIG. 3, and outputs a signal corresponding to the operation value MV.
- the output signal of 9 is input to the adder 21 as an operation signal for feedforward control.
- the details of the operation value MV will be described later.
- the pressure regulator 23 sets the set pressure S
- the signal corresponding to the operation value MV of 1 1 is supplied to the adder 21 as the operation signal for feedback control.
- the adder 21 executes an operation of adding the above operation values MV and MV, and
- MV is obtained, and a signal corresponding to the manipulated value MV is applied to function generators 27 and 29.
- the required opening of IGV5 and RCV7 can be predicted from the relationship shown in Figure 2.
- the signal indicating the operation value MV defines the predicted required opening of IGV5 and RCV7.
- the function generator 27 for example, operates based on the function illustrated in FIG.
- the IGV opening is maintained at 20% (corresponding to the minimum opening) until the operating value MV becomes
- a valve control signal that linearly increases the IGV opening from 20% to 100% as it increases from 50% is formed, and this valve control signal is output to IGV5.
- the function generator 29 adjusts the RCV opening, for example, until the operation value MV becomes 50%.
- FIG. 2 shows a surge line d for the compressor 1 and a surge control line e set with a margin for anti-surge.
- the surge line d and the surge control line e are both functions of the opening of the IGV5.
- the function generator 33 includes a function indicating the surge control line e and the function generator
- Device 35 corresponds to the deviation between the set flow SV and the actual discharge flow PV detected by the flow meter 37.
- Operation value MV and outputs a signal corresponding to the operation value MV to the high-order selection section 31.
- the high-order selection unit 31 includes a signal indicating the operation value MV output from the function generator 29 and a function
- the operation value MV output from the generator 33 is compared with the signal indicating the operation value MV.
- the opening of IGV5 is set to 50%, and the relationship based on the manipulated value MV (MV) is
- the output of the number generator 29 sets the opening of RCV7 to 0%. Since the opening degrees of the IGV5 and the RCV7 are set by the feedforward control, the discharge pressure of the compressor 1 quickly approaches the set value P. And finally, the operation value
- the above-mentioned discharge pressure is set to the set value P with high accuracy by feedback control based on MV (MV).
- the opening of the IGV5 is set to the minimum opening of 20%
- the opening of RCV7 is set so that the fuel gas from FF is recycled to the fuel supply line 3 side.
- the discharge pressure of the compressor 1 is quickly brought close to the target value P by the opening degree setting of the IGV5 and RCV7 by the feedforward control.
- the point becomes point A.
- An output command requesting the minimum flow rate at which fuel combustion in one bin 15 can be maintained) is output from the load command unit 17.
- the final operating point of the compressor 1 is A because the control is performed.
- the compressor 1 is operated in a state where surging is avoided.
- the opening of the IGV5 becomes larger than the minimum opening (20%), and the fuel gas having the flow rate FF is recycled through the RCV7.
- the RCV7 which is not only the IGV5, is also used for controlling the discharge pressure.
- the fluctuation of the discharge pressure of the compressor 1 can be suppressed, that is, the controllability of the discharge pressure can be improved.
- the command signal for the discharge pressure of RCV7 is set to zero, and the discharge pressure is controlled only by the IGV5.
- the operation value MV is less than 50%
- the IGV5 is maintained at the minimum opening (20%) and the discharge pressure is controlled only by the RCV7, that is, since the IGV5 and the RCV7 are operated in the split range, the interference of the discharge pressure control by the IGV5 and the RCV7 occurs. Is avoided.
- the discharge pressure is controlled by a combination of the feedforward control and the feedback control, highly responsive pressure control becomes possible, and therefore, even when a sudden load request is made to the gas turbine 15, In addition, fluctuations in the discharge pressure can be suppressed. Furthermore, since higher control of discharge pressure control and anti-surge control is selectively applied to RCV7, interference between these controls is also avoided.
- the split point of IGV5 and RCV7 is set to 50%.
- This split point is not limited to 50%. That is, since the slopes of the functions shown in FIGS. 4 and 5 define the control gains of IGV5 and RCV7, respectively, the split point may be changed to change these gains. For example, if the split point is larger than 50%, the operation time of the IGV5 with poor response can be shortened, and the operation stability of RCV7 with good response can be improved. In short, the above split point can be appropriately set so as to improve the controllability of the IGV5 and RCV7 in consideration of the dynamic characteristics and the like.
- Curves a ', b' and c 'in Fig. 6 show the relationship between the discharge flow rate and the discharge pressure of the compressor 1 when the rotation speed of the compressor 1 is set to 60%, 80% and 100%, respectively. This is an example. As is clear from the comparison between FIG. 6 and FIG. 2, the discharge pressure can be controlled by operating the number of rotations of the compressor 1 instead of operating the opening degree of the IGV 5.
- FIG. 7 shows a second embodiment of the present invention configured to control the discharge pressure by controlling the number of revolutions of the compressor 1.
- the second embodiment is different from the second embodiment in that the IGV is eliminated, and a function generator 27 ′ corresponding to the function generator 27 shown in FIG.
- the point that the number is controlled by the output of this function generator 27 'and the number of rotations detector 41 that detects the number of rotations of the compressor 1 are provided, and the function generator corresponding to the function generator 33 in Fig. 2 is provided.
- the third embodiment differs from the first embodiment in that the output of the rotation speed detector 41 is added to 33 '.
- the rotation speed is detected by the rotation speed detector 41.
- FIG. 8 shows a third embodiment of the present invention.
- the third embodiment is different from the third embodiment in that a flow controller 43 and an adder 45 are interposed between an adder 21 and a pressure controller 23, and a flow meter for detecting an inlet flow and an outlet flow of the header tank 13, respectively. 47 and 49 are provided, and the outputs of these detectors 47 and 49 are added to the flow controller 43 and the adder 45, respectively. This is different from the first embodiment in that point.
- the adder 45 indicates a signal (feedback signal) corresponding to the deviation of the discharge pressure and the outlet flow rate of the header tank 13, that is, the required fuel supply amount of the turbine 15.
- Signal (feedforward signal) and the sum is used as the set flow rate SV.
- the flow controller 43 controls the set flow SV and the input of the header tank 13.
- the deviation from the outlet flow (actual discharge flow) is calculated, and the deviation is subjected to PI processing to form the flow operation value MV '.
- the control for eliminating the deviation in the flow rate of the fuel gas into and out of the header tank 13 is executed.
- the pressure of the supplied fuel gas is further stabilized.
- the configuration shown in FIG. 7 in which the discharge pressure is controlled by operating the rotation speed of the compressor 1 can also be applied to the control device of the third embodiment.
- the fuel gas pressure at the inlet of the header tank 13 is detected by the pressure gauge 25, but the fuel gas pressure in the header tank 13 is detected by the pressure gauge 25. You may make it.
- the control device controls the discharge pressure of the two compressors 1A and IB.
- FIG. 9 elements having the same configuration and function as those shown in FIG. 1 are denoted by common or corresponding reference numerals. Also, the elements corresponding to the elements such as the IGV5 and RCV7, the function generators 27, 29, and 33, the high-order selection unit 31, and the flow controller 35 shown in Fig. 1 are provided on the compressor 1A and IB sides in the figure. Although they are provided, they are omitted in the figure.
- Switch elements 51A and 51B are provided between 23 'and the adder 21A, respectively. Further, the pressure of the fuel gas in the header tank 13 is detected by the pressure gauge 25, and the pressure is measured.
- the load command unit 17 During normal operation, the load command unit 17 'outputs the selection signal S of the logic level [H].
- switch elements 51A and 51B are configured to be opened by the signal of the logic level [H], as shown in the figure, the switch element 51A to which the selection signal S is directly input is opened.
- both of the compressors 1A and 1B are provided with, for example, the operating point A shown in FIG. 2 by the feedforward control. And the estimation of the feedforward control function is wrong.
- compressor 1A is at operating point A
- compressor B is at operating point A.
- the load command unit 17 'outputs a selection signal S of a logic level [L] based on a trip occurrence signal from a higher-level control device (not shown), and as a result, the switch element 51A is closed.
- the switch element 51A is opened.
- the pressure feedback control is transferred to the control system of the compressor B side to the control system of the compressor A side, so that the pressure of the fuel gas in the header tank 13 maintains the value before the compressor 1B trips. It will be controlled as follows.
- the force that causes only one of the control system on the compressor A side and the control system on the compressor B side to execute the pressure feedback control is executed in the above, there is a possibility that those controls may interfere with each other.
- the load command section 17 when a load shedding signal is input to the load command section 17 from a higher-level control device (not shown), the load command section 17 outputs an operation value switching signal S to the pressure regulator 23 ′.
- the pressure regulator 23 ′ changes the operation value MV to a large value such that the RCV7 is rapidly opened.
- the tracking data to be changed is output as the operation value MV, and as a result, RCV7
- the quick opening operation is performed with good response, and the pressure fluctuation at the time of load interruption is further suppressed.
- Such a tracking operation can be applied to the first to third embodiments.
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- Combustion & Propulsion (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Physics & Mathematics (AREA)
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- Control Of Positive-Displacement Air Blowers (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
Abstract
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Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP04772322.6A EP1662147B1 (en) | 2003-08-28 | 2004-08-27 | Control unit for compressor |
CN2004800235618A CN1836109B (zh) | 2003-08-28 | 2004-08-27 | 压缩机的控制装置 |
US10/567,018 US7556473B2 (en) | 2003-08-28 | 2004-08-27 | Control unit for compressor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003304269A JP4191563B2 (ja) | 2003-08-28 | 2003-08-28 | 圧縮機の制御方法 |
JP2003-304269 | 2003-08-28 |
Publications (1)
Publication Number | Publication Date |
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WO2005021976A1 true WO2005021976A1 (ja) | 2005-03-10 |
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ID=34269265
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2004/012366 WO2005021976A1 (ja) | 2003-08-28 | 2004-08-27 | 圧縮機の制御装置 |
Country Status (6)
Country | Link |
---|---|
US (1) | US7556473B2 (ja) |
EP (1) | EP1662147B1 (ja) |
JP (1) | JP4191563B2 (ja) |
CN (1) | CN1836109B (ja) |
TW (1) | TWI249002B (ja) |
WO (1) | WO2005021976A1 (ja) |
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JPH08254197A (ja) | 1995-03-17 | 1996-10-01 | Mitsubishi Heavy Ind Ltd | 圧縮機制御システム |
EP0871853B1 (en) * | 1996-01-02 | 2004-01-02 | Woodward Governor Company | Surge prevention control system for dynamic compressors |
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2004
- 2004-08-27 US US10/567,018 patent/US7556473B2/en not_active Expired - Fee Related
- 2004-08-27 TW TW093125860A patent/TWI249002B/zh not_active IP Right Cessation
- 2004-08-27 EP EP04772322.6A patent/EP1662147B1/en not_active Expired - Fee Related
- 2004-08-27 WO PCT/JP2004/012366 patent/WO2005021976A1/ja active Application Filing
- 2004-08-27 CN CN2004800235618A patent/CN1836109B/zh not_active Expired - Fee Related
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1659294A2 (en) * | 2004-11-17 | 2006-05-24 | Mitsubishi Heavy Industries, Ltd. | Compressor control unit and gas turbine power plant including this unit |
EP1659294A3 (en) * | 2004-11-17 | 2012-10-31 | Mitsubishi Heavy Industries Compressor Corporation | Compressor control unit and gas turbine power plant including this unit |
CN102518598A (zh) * | 2011-12-31 | 2012-06-27 | 北京时代科仪新能源科技有限公司 | 离心式空压机及其控制方法和*** |
Also Published As
Publication number | Publication date |
---|---|
TW200512373A (en) | 2005-04-01 |
TWI249002B (en) | 2006-02-11 |
US7556473B2 (en) | 2009-07-07 |
EP1662147A1 (en) | 2006-05-31 |
JP2005076461A (ja) | 2005-03-24 |
JP4191563B2 (ja) | 2008-12-03 |
EP1662147A4 (en) | 2011-08-24 |
CN1836109B (zh) | 2010-05-26 |
EP1662147B1 (en) | 2016-10-05 |
US20070110587A1 (en) | 2007-05-17 |
CN1836109A (zh) | 2006-09-20 |
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