US20030161731A1 - Process for controlling a plurality of turbo engines in parallel or tandem operation - Google Patents

Process for controlling a plurality of turbo engines in parallel or tandem operation Download PDF

Info

Publication number
US20030161731A1
US20030161731A1 US10/371,136 US37113603A US2003161731A1 US 20030161731 A1 US20030161731 A1 US 20030161731A1 US 37113603 A US37113603 A US 37113603A US 2003161731 A1 US2003161731 A1 US 2003161731A1
Authority
US
United States
Prior art keywords
accordance
machine
controllers
controller
variable
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US10/371,136
Other languages
English (en)
Inventor
Wilfried Blotenberg
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
MAN Energy Solutions SE
Original Assignee
MAN Turbomaschinen AG GHH Borsig
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by MAN Turbomaschinen AG GHH Borsig filed Critical MAN Turbomaschinen AG GHH Borsig
Assigned to MAN TURBOMASCHINEN AG GHH BORSIG reassignment MAN TURBOMASCHINEN AG GHH BORSIG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WILFRIED BLOTENBERG
Publication of US20030161731A1 publication Critical patent/US20030161731A1/en
Assigned to MAN TURBO AG reassignment MAN TURBO AG CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: MAN TURBOMASCHINEN AG
Abandoned legal-status Critical Current

Links

Images

Classifications

    • 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
    • F04D27/0269—Surge control by changing flow path between different stages or between a plurality of compressors; load distribution between compressors

Definitions

  • the present invention pertains to a process for controlling a plurality of turbo engines cooperating in a station in parallel or tandem operation for observing at least one process variable that is preset by the station and is common to all turbo engines, wherein each turbo engine with the drive machine forming it forms a machine unit, with which a machine controller is associated.
  • a process for operating a plurality of turbocompressors connected in parallel, which are provided each with a surge limit control to prevent surge, is described in EP-B 0 132 487.
  • the turbocompressors are controlled jointly by load distribution controllers and individually by a pressure controller each.
  • the load distribution controllers control the setting of the compressors among each other such that there are equal distances between the working point and the blow-off line for all compressors. Only one of the compressors is controlled by its pressure controller, whereas the others are adjusted by the load distribution control.
  • a higher-level master controller also called master controller
  • the master controller has a higher-level task. It determines the necessary adjusting commands for the individual machine units from the required total capacity (desired pressure or desired flow of all compressors). Especially in the case of plants of an asymmetric design, the master controller calculates different manipulated variables for the individual machine controllers. According to the pertinent state of the art, it is emphasized time and time again that there must be only one controller for distributing the load among different compressors, which controller processes only one set point and only one actual value, because conflicts may otherwise arise in the downstream machine controllers.
  • Each machine unit needs an unambiguous manipulated variable, which is coordinated with the other manipulated variables such that no conflicts can arise.
  • the flow may be measured at a single point only.
  • the pressure may likewise be measured at a single point only. There may also be only a single set point for the common pressure or flow controller. Observing this rule is particularly important especially in case of use as a pressure controller for the final pressure or the suction pressure.
  • the basic object of the present invention is to simplify the control of this type, to increase the availability of the individual controllers and to avoid colliding interactions between the controllers.
  • a process for controlling a plurality of turbo engines cooperating in a station in parallel or tandem operation to observe at least one process variable, which is preset by the station and is common to all turbo engines.
  • Each turbo engine with the drive machine forming it forms a machine unit, with which a machine controller is associated.
  • a master controller affecting all turbo engines for controlling the process variable is done away with in the process according to the present invention by the functionality of this process variable controller being divided among the individual machine controllers.
  • the algorithm for the distribution of the load among the individual compressors which takes place exclusively in the master controller according to the known state of the art, is embodied according to the present invention in every individual machine controller.
  • the flow, the final pressure, the suction pressure, the pressure ratio, the temperature, the level in a tank, the power of the drive machine or the load distribution of the compressors can be used as the process variable individually or in a combination. Since storage space and computing power are available to a sufficient extent with modern hardware, there are no restrictions in this respect.
  • an existing station can be expanded by additional machine units without problems. Only a machine unit with a machine controller is to be added, which machine controller contains the same control and regulation as each of the existing machine units. No investment, operating or maintenance costs arise due to the use of the process according to the present invention.
  • the elimination of the master controller is likewise unlikely to lead to disturbances in operation in a station. Since there are no higher-level and lower-level controllers, colliding interactions between different controllers are eliminated.
  • the process according to the present invention is applicable to the parallel operation, the tandem operation and the combined parallel and tandem operation of the turbo engines in a station.
  • FIG. 1 is a system diagram of a control system for compressors in parallel operation according to the state of the art
  • FIG. 2 is a system diagram of a control system in tandem operation according to the state of the art
  • FIG. 3 is a signal flow diagram for the control system according to FIG. 1 or 2 ;
  • FIG. 4 is a system diagram of a control system for compressors in parallel operation according to the present invention.
  • FIG. 5 is a system diagram of a control system for compressors in tandem operation according to the present invention.
  • FIG. 6 is a system diagram of a system for surge limit control according to the state of the art
  • FIG. 7 is a signal flow diagram for the control system according to FIG. 4 or 5 ;
  • FIG. 8 is a system diagram of a control system for compressors in parallel operation according to another embodiment of the present invention.
  • FIG. 9 is a system diagram of a control system for compressors in parallel and tandem operation
  • FIG. 10 is a system diagram of a control system for compressors in parallel and tandem operation, where the control of one of the compressors is faded in;
  • FIG. 11 is a control system for compressors in parallel and tandem operation, where the control of one of the compressors is faded in, according to another embodiment of the present invention.
  • FIG. 1 shows three compressors 1 , 2 , 3 in parallel operation, which are driven by a turbine 4 , 5 , 6 each acting as a drive machine.
  • One compressor each forms a machine unit with a drive machine.
  • the three machine units are integrated within one station, which may in turn be part of a pipeline system or is bound in a process.
  • the delivery capacity of the compressor 1 , 2 , 3 can be varied by varying the speed of the turbines.
  • the turbines may also be replaced with motors with a fixed speed, and adjustable guide vanes are used with the adjusting drives 7 , 8 , 9 in the compressors 1 , 2 , 3 or butterfly valves are used in front of the compressors (not shown) in this application.
  • the compressors 1 , 2 , 3 are connected by inlet lines 10 , 11 , 12 to a suction-side bus bar 13 , which in turn has a connection to a suction-side process 14 or to a pipeline or to a gas storage unit.
  • the compressors 1 , 2 , 3 are connected via outlet lines 15 , 16 , 17 to a pressure-side bus bar 18 , which in turn has a connection to a pressure-side process 19 or to a pipeline or to a gas storage unit.
  • a station governor level which presets as the set point presetter 20 the set points for the operation of the station, is superordinate to the entire station.
  • the actual capacity of the mechanical equipment usually the final pressure or the suction pressure of the compressor plant or the flow, is measured with a sensor 22 and transmitted as an actual value via a signal line 23 to a master controller 24 .
  • the master controller 24 has a higher-level task. It determines the necessary adjusting commands for the individual machine units from the required total capacity (desired pressure or desired flow) of all three compressors 1 , 2 , 3 . Especially in the case of plants of an asymmetric design, the master controller 24 calculates different manipulated variables for the individual machine controllers 28 , 29 , 30 .
  • FIG. 2 shows the case of application for three compressors 1 , 2 , 3 in tandem operation.
  • the design of this station extensively corresponds to that of the station shown in FIG. 1 for the parallel operation. The difference is only that the first compressor 1 is connected to the inlet line 11 and, via the outlet line 15 , to the second compressor 2 , and this is connected via the outlet line 16 and the inlet line 12 to the third compressor 3 .
  • the suction-side bus bar 13 is not present, and the process 14 is connected directly to the inlet line 10 acting as a suction line.
  • the pressure-side bus bar is likewise absent, and the outlet of the third compressor 3 is connected directly to the process 19 via the outlet line 17 .
  • Each unit controller 41 , 42 , 43 has a converter 44 , 45 and 46 for the input variable and another input converter (not shown) for the actual value of the machine, typically the speed of the drive turbine 4 , 5 , 6 , or the position of the inlet guide vanes in guide vane-controlled compressors.
  • the difference between the actual value of the machine and the set point of the machine is formed in the comparison units 47 , 48 and 49 and is sent to the respective unit controllers 41 , 42 and 43 .
  • the machine controller usually contains an additional control function.
  • a pressure control circuit may be designed such that flow controllers, which control the particular flow through the individual machines, are subordinated to the master pressure controller. Speed controllers, which will then control the speed, are in turn subordinated to these flow controllers.
  • the flow controller associated with the machines is part of the respective unit controller 41 , 42 , 43 in these applications.
  • FIG. 6 shows a block diagram of a typical surge limit control for a compressor with variable suction pressure.
  • a compressor 53 is equipped with a suction line 54 and a delivery line 55 .
  • a blow-by valve 56 in a blow-by line 57 may be opened in a controlled manner when needed, thus increasing the flow through the compressor when the gas consumption by the process is smaller than the minimum allowable compressor flow.
  • a blow-by valve 56 also called surge limit control valve, is actuated via a control line 58 by the surge limiter 59 , whose input variables are the inlet pressure measured with the sensor 60 , the inlet flow measured with the sensor 61 , the final pressure measured with the sensor 62 , and the inlet temperature measured with the sensor 63 .
  • the surge limiter 59 is usually embodied within the same controller hardware as the machine controller (it is an essential part of the machine controller), signals such as compressor flow as well as pressure before and after the compressor are available within the machine controller and can thus be also used for the load distribution controller and the capacity controller.
  • FIGS. 4 and 5 show the control process according to the present invention for three compressors 1 , 2 , 3 integrated to form a station in parallel operation and in tandem operation.
  • the compressors 1 , 2 and 3 are coupled with turbines 4 , 5 and 6 as drive machines and are driven by these.
  • the delivery capacity of the compressor 1 , 2 , 3 can be varied by varying the speed of the turbine.
  • the drive turbines may also be replaced with motors with a fixed speed, and adjustable guide vanes with the adjusting drives 7 , 8 , 9 are used in the compressors 1 , 2 , 3 or butterfly valves are used in front of the compressors (not shown) in this case of application.
  • the compressors 1 , 2 , 3 shown in FIG. 4 are connected by the inlet lines 10 , 11 , 12 to the suction-side bus bar 13 , which in turn has a connection to the suction-side process 14 or to a pipeline or to a gas storage unit.
  • the compressors 1 , 2 , 3 are connected via the outlet lines 15 , 16 , 17 to the pressure-side bus bar 18 , which in turn has a connection to a pressure-side process 19 or to a pipeline or to a gas storage unit.
  • the first compressor 1 of the compressors 1 , 2 , 3 connected in tandem is connected to the inlet line 11 and, via the outlet line 15 , to the second compressor 2 .
  • This is connected to the third compressor 3 via the outlet line 16 and the inlet line 12 .
  • the process 14 is directly connected to the suction line 10
  • the outlet of the third compressor 3 is directly connected to the process 19 via the outlet line 17 .
  • the master controller is eliminated in the control process according to the present invention.
  • the total set point is sent, instead, to each of the machine controllers 28 , 29 , 30 from the set point presetter 20 of the station directly via the signal line 21 .
  • the actual value is likewise sent directly to each machine controller 28 , 29 , 30 via the signal line 23 , so that each machine controller 28 , 29 , 30 can perform the necessary calculations on its own and can adjust the downstream control units just as if a common, higher-level master controller were used.
  • FIG. 7 shows the signal flow diagram for a parallel or tandem connection of three compressors 1 , 2 , 3 according to the present invention.
  • the station set point of the set point presetter 20 is divided, sent in parallel to three converters 64 , 65 , 66 , and passed on to the comparison units 70 , 71 , 72 .
  • the actual value from the signal line 23 is sent to three converters 67 , 68 , 69 and passed on to the comparison units 70 , 71 , 72 .
  • the set point is divided among the individual machine units, comprising the compressors 1 , 2 , 3 and the turbines 4 , 5 , 6 .
  • the difference between the set point and the actual value is formed in the comparison units 70 , 71 , 72 and is sent to an amplifier 73 , 74 , 75 each to the controllers 76 , 77 , 78 of the units.
  • the unit controllers 76 , 77 , 78 adjust in turn the turbine speed or the guide vanes of the respective compressor 1 , 2 or 3 via the converters 79 , 80 and 81 .
  • the converters 67 , 64 , the percentage setter 35 , the comparison unit 70 , the amplifier 73 , the unit controller 76 , and the converter 79 are common parts of the machine controller 28 , which is associated with the machine unit, which is formed by the turbine 4 and the compressor 1 .
  • the converters 68 , 65 , the percentage setter 36 , the comparison unit 71 , the amplifier 74 , the unit controller 77 , and the converter 80 are common parts of the machine controller 29 , which is associated with the machine unit, which is formed by the turbine 5 and the compressor 2 .
  • the converters 69 , 66 , the percentage setter 37 , the comparison unit 72 , the amplifier 75 , the unit controller 78 , and the converter 81 are common parts of the machine controller 30 , which is associated with the machine unit, which is formed by the turbine 5 and the compressor 3 .
  • the actual value and the set point of the process variable may be any variables as inputs of the converters 67 through 66 . They are frequently the flow through the compressors, the pressure before or after the station, but they may also be the load distribution of the compressors in tandem or parallel operation. The pressure ratio of the entire station or a temperature or a liquid level in a tank is also conceivable.
  • the essential difference between the state of the art according to FIG. 3 and the present invention according to FIG. 7 is that the master controller 24 shown in FIG. 3 with the elements 31 through 40 may be eliminated altogether, and its function is divided among the machine controllers 28 , 29 , 30 , which are present anyway.
  • the elements 31 through 34 have been eliminated without replacement and are replaced with three elements 64 , 70 and 76 ; 65 , 71 and 77 as well as 66 , 72 and 78 each.
  • the converters 38 through 46 are eliminated.
  • it is much more essential that the functionalities being shown are auxiliary functions embodied purely in software in the machine controllers which are already present anyway.
  • This station controller 34 increases its power by a percentage that corresponds to an increase in the pressure ratio by 10% from 90 bar to 99 bar, and an increase in the output signal from 45% to 50% shall be assumed here as an example.
  • Each of the three machine units increases its power by the same extent until the measured actual value corresponds to the set point.
  • the function will be the following in a system according to the present invention according to FIG. 7.
  • the actual value on the signal line 23 is 90 bar and the set point on the signal line 21 is 99 bar.
  • all three unit controllers (capacity controllers) 76 , 77 and 78 receive the same deviation of 9 bar.
  • Each of the three unit controllers 76 , 77 and 78 reacts in exactly the same way as the master controller 24 in FIG. 3.
  • Each of the three machine units increases its power by the same extent until the measured actual value corresponds to the set point.
  • the final pressure is always controlled in the compressors in tandem operation with variable suction pressure such that the controlled variable is the pressure ratio over the entire station, i.e., the tandem connection of all compressors.
  • the ratio of the pressure ratios of the individual compressors is also the variable to be controlled for the unit controllers in the case of compressors in tandem operation, which are run at constant flow.
  • This problem is solved according to the present invention by the use of a load distribution controller.
  • This load distribution controller acts in addition to the unit controller 76 through 78 (capacity controller) and uses the same machine controller 28 , 29 , 30 . Only the function of the load distribution controller will be described below with the use of the prior-art functional groups. The combination of capacity controller and load distribution controller will be subsequently described.
  • This load distribution controller has exactly the same design as the unit controller 76 through 78 (capacity controller) according to FIG. 7. However, the set point of a load distribution control is the set point of the load percentage of the compressor and the actual value is the current load.
  • the distance between the working point and the stability limit is usually the controlled variable in the case of compressors in parallel operation, and the pressure ratio is usually the controlled variable in compressors in tandem operation.
  • the actual value for each machine unit is the particular pressure ratio of the particular compressor
  • the set point is the set point of the percentage contributed by the particular compressor to the total pressure ratio.
  • the actual value of the pressure ratio can be determined by dividing the final pressure obtained for the surge limit control by the suction pressure measured for the surge limit control.
  • the total pressure ratio is calculated by dividing the station's outlet pressure by the station's inlet pressure. All compressors are usually operated with the same pressure ratio in tandem operation, so that the set point is one third of the total station pressure ratio for every individual load distribution controller. Should the ratio be different for individual machines, a scaling factor may be taken into account within the set point formation. Should the load percentage of the individual machine units depend on additional process variables, variable scaling factors may be introduced.
  • the load distribution algorithm calculates a partial load for each of the compressors and, in the case of compressors in parallel operation, e.g., a preset percentage of the total flow. In tandem operation, the algorithm presets, e.g., a fixed, preset percentage of the total required pressure ratio. The unit controller of each compressor now adjusts the individual machine unit to this value.
  • the machine unit 1 In the equalized state, the machine unit 1 operates in a stable manner with a load that is too low by 6.66%, and the machine units 2 and 3 operate in a stable manner with a load that is too high by 3.33%.
  • the consequence of this is an imbalance of all three compressors. However, this is smaller than the individual error of the machine unit in question.
  • the system even operates robustly when the set point and the actual value for each machine unit are determined separately and there are greater deviations between the set points and the actual values of the individual controllers as a result.
  • a disturbance in a common actual value measurement affects the operation of all machine units in the station. This also applies to a disturbance in the set point setter.
  • the actual value measurement can be associated with every individual machine unit according to this process.
  • FIG. 8 shows, e.g., an arrangement with individual actual value measurement.
  • the actual value (final pressure after the compressors, before the compressors or flow through the compressors) can be measured in the respective outlet lines 15 , 16 and 17 with sensors, which are connected to converters 90 , 91 and 92 .
  • the individual actual values are then sent via the converters 69 , 64 and 65 to the comparison units 70 , 71 and 72 according to FIG. 7 and are sent to the machine controllers 28 , 29 , 30 . It is also possible to preset the set point individually. Thus, all necessary functionalities are now individually associated with each machine unit. Conversion errors of the set point and actual value determination are compensated in the same manner with the use of the control process according to the present invention as capacity controllers (flow controllers, pressure controllers).
  • each of the actual value measurements can be associated with one machine unit, and the converters can be supplied with auxiliary energy from the control box of the respective associated machine unit. Furthermore, the corresponding units of the other machine units are active even in case of total failure of set point or actual value converters of one machine unit, and they reduce as a result the negative effects of this failure. It is also possible to form the set point and the actual value separately for each machine unit. It is advantageous that there are no common components any more and only identical machine systems without higher-level system parts are used.
  • the above-described case shall be mentioned as an example with the use of the unit controller as a pressure controller.
  • the desired final pressure is 99 bar.
  • the compressors 1 through 3 shall contribute each one third of the total power currently needed.
  • Each turbine 4 through 6 shall contribute for this 20% of the total available power each.
  • the turbine 6 runs up to its maximum power because of the missing actual value and contributes 33% of the total power as a result.
  • the pressure rises as a result in the pressure-side bus bar 18 and so does consequently the final pressure of all compressors 1 , 2 and 3 .
  • the two intact measuring means in the compressor outlet lines 15 and 16 of the compressors 1 and 2 notice this increase and reduce the power of the compressors 1 and 2 to the extent that the final pressure of all three compressors 1 , 2 , 3 will again correspond to the set point of 99 bar.
  • a station that is controlled according to the state of the art by means of a master controller brings all compressors to 100% power in this case of operation. The same thing happens in case of failure of a set point.
  • a master controller brings all machines to zero and the entire station ceases to offer any power any longer.
  • the power of the compressor whose set point drops to zero will drop the zero, the other two compressor controls notice this deviation and eliminate it by increasing their own power, so that the operation of the station as an entirety is not affected.
  • Another possibility is to preset the set point individually and differently for the load distribution for each of the compressors. This may be necessary, e.g., when there is an asymmetry in the machine units. For example, machine units of various sizes may operate together in one station. The factor must be adapted to the size of the machine units in this case.
  • Another possibility is for an optimizing algorithm to determine a combination of the machine load of the individual machine units that is optimal for the particular working point.
  • optimizing algorithms are described, e.g., in EP-B 0 431 287, which was mentioned in the introduction. If the present invention is applied to this prior-art process, a higher-level computer and master controller may be eliminated even in the prior-art process if the algorithm is programmed in each machine controller.
  • Another need for interfering with the selection of the load distribution among the individual machine units may also be encountered, e.g., when a limit of the permissible operating range is reached at one of the components. If, e.g., gas turbines of various designs are used as drive machines for compressors, one of the gas turbines may have reached, e.g., the maximum exhaust gas temperature, while the other gas turbines still have reserves for adjustment.
  • the present invention offers two approaches to solving this problem.
  • One approach is that the factor for the splitting of the load among the machine units that are not at the limit is changed such that the factors are increased at the ratio of the machine units that are no longer available.
  • the factor for the machine operating at the limit is set to zero as long as the machine is being operated at the limit.
  • the process according to the present invention also compensates this process without this intervention. Since the unit being operated at the limit does not offer any power any longer, the capacity controller determines a deviation from the set point and increases the power of the other unit such that the process variable to be controlled will exactly correspond to the set point.
  • the control unit and the point of intervention for all these offsetting factors are the percentage setters 35 through 37 and the addition of a fixed value to the summing units 70 through 72 .
  • FIGS. 9 through 11 show three parallel-connected compressors of the low-pressure stage (LP-A, LP-B, LP-C) with three parallel-connected compressors of the medium-pressure stages (MP-A, MP-B, MP-C) and three parallel-connected compressors of the high-pressure stage (HP-A, HP-B, HP-C) connected in tandem.
  • the control system for the compressor MP-B is enlarged in FIGS. 10 and 11.
  • the usual compressors are equipped with an identical control system. Each compressor is provided with a surge limit control, which was already described in connection with FIG. 6.
  • a machine controller 85 is associated with each machine unit comprising a compressor and a turbine.
  • a sensor for determining the actual value of the final pressure of the station is arranged in the pressure-side bus bar 18 .
  • the measured value is sent to a converter 86 , which is connected to a comparison unit 88 via a signal line 87 .
  • the set point of the final pressure is sent to this comparison unit 88 by the set point presetter.
  • a sensor for determining the actual value of the flow of the station is arranged in the pressure-side bus bar 18 .
  • the measured value is sent to a converter 89 , which is connected to a comparison unit 91 via a signal line 90 .
  • the set point of the flow is sent to this comparison unit 91 by the set point presetter.
  • a sensor for determining the actual value of the suction pressure of the station is arranged in the suction-side bus bar 13 .
  • the measured value is sent to a converter 92 , which is connected to a comparison unit 94 via a signal line 93 .
  • the set point of the suction pressure is sent to this comparison unit 94 by the set point presetter.
  • the signal line 93 of the suction pressure and the signal line 87 of the final pressure are led to a computing site 95 , in which the total pressure ratio is calculated.
  • the pressure ratio may be additionally rated with a fixed factor or even a factor that depends on other variables.
  • the factor is 1 ⁇ 3 in the first approach, i.e., all three compressors are loaded equally.
  • a signal line 96 which is led to a computing site 97 , is branched off after the converter 62 for the final pressure of the compressor MP-B.
  • a signal line 98 which is likewise led to a computing site 97 , is branched off after the converter 61 for the suction pressure of the compressor MP-B.
  • the pressure ratio of an individual compressor is determined in the computing site 97 .
  • the computing sites 95 and 97 are connected to a comparison unit 99 , in which the individual pressure ratio of this compressor MP-B is compared with its percentage set point relative to the total pressure ratio (which is rated with a factor).
  • a signal line 100 is led from the surge limiter 59 to a computing site 101 .
  • the signal line 100 carries a signal containing the distance of the working point of an individual compressor.
  • the corresponding signals of the other parallel-connected compressors are sent to the computing site 101 .
  • the mean value of the distance of the working points is determined in the computing site 101 .
  • the mean value of the distances is compared with the individual value of a compressor in a comparison unit 102 .
  • the comparison units 88 , 91 , 94 are connected to a summing unit 104 via signal lines, in which a changeover switch 103 each is arranged.
  • the comparison units 99 , 102 are connected to a summing unit 106 via signal lines, in which a changeover switch 105 each is arranged.
  • the summing units 104 are also connected to the summing unit 106 .
  • the summing units 104 , 106 are connected to the machine controller 85 , which belongs to a machine unit and performs the functions of a capacity, final pressure, suction pressure, flow and load distribution controller.
  • the control system shown in FIG. 11 also contains additionally a maximum selection means 109 and a minimum selection means 110 in order to limit the speed and the load of the drive machine or other variables.
  • the capacity control and the load distribution control of the station are performed by a single machine controller each which is associated with each machine unit. Deviations for the capacity control, the load distribution control in parallel operation and the load distribution control in tandem operation are formed by the machine controller.
  • Three different capacity control algorithms can be selected in this control system. Since the capacity controller can control only one variable, the other two deviations of the capacity control are switched to zero via the switches 103 . A mutual interlocking is meaningful here. If, e.g., the flow control shall be active, the deviation for the suction pressure control and the final pressure control is switched to zero. As an alternative, the set point for the non-active controller may also be switched to the actual value. This also causes the deviation to become zero.
  • the compressors in tandem are called the low-pressure (LP) compressor, medium-pressure (MP) compressor and high-pressure compressor (HP).
  • the parallel-connected compressors are called A, B, C. It shall be assumed that the plant is in the flow control mode and all compressors are in operation.
  • the flow set point shall be 2% greater in parallel operation than the actual value, and compressor LP-A shall deliver exactly 1 ⁇ 3 of the total mass flow, compressor LP-B 5% too little, and compressor LP-C 5% too much.
  • Compressor MP-A and compressor MP-B shall deliver 30% of the mass flow and compressor MP-C shall deliver 40%.
  • Each of the HP compressors shall deliver an equal mass flow.
  • compressor LP-A shall be loaded 2% too low, compressor MP-A shall be loaded correctly, and compressor HP-A shall be loaded 2% too high.
  • Compressor LP-B is loaded correctly, compressor MP-B is loaded 3% too high, and compressor HP-B 3% too low.
  • Compressor LP-C shall be loaded at a rate of 29%, MP-C at 36%, and HP-C at 35%.
  • each machine controller receives an unambiguous adjusting command in the necessary direction in order to reach the optimum.
  • An interaction between the different requirements is ruled out by design.
  • additional algorithms may be added as well.
  • the drive machines of one or more compressors may reach, e.g., a power limit. This can be additionally processed in the algorithm such that the deviation of the machine controllers of the drive machines, which are being operated at the limit, are brought to zero (as in manual operation). These drive machines will then not participate in a further power increase any longer.
  • the difference between the optimal adjusting difference according to the above table and the actual effective difference can be added to the deviation of the other parallel and tandem compressors. This intervention is thus optimally compensated as well.
  • the process also functions, of course, for a plurality of limiting controllers per machine unit.
  • the limiting controllers may be switched, as is shown in FIG. 11, via an extreme value selection means (maximum selection or minimum selection means).
  • maximum selection or minimum selection means In addition to the above-described deviations, deviations for the distances of the working points from the limits are formed, e.g., from the maximum speed and the minimum speed in FIG. 11.
  • the formation of another deviation each for a maximum limitation and a minimum limitation are shown.
  • the deviations for limitations to maxima are switched to a minimum selection, and the deviations for a minimum limit act on a maximum selection.
  • the effective deviation for the machine controller is thus either the deviation according to the above algorithm or the distance of the working point from the limit when this distance is shorter.
  • the output of the max/min selection means 109 / 110 also always controls the machine unit in case of conflicting requirements of capacity or load distribution controllers primarily such that the limit is not exceeded in steady-state operation.
  • the power of compressor LP-C shall be increased by a deviation of 6.3%.
  • the drive turbine shall be 3% below the maximum operating speed.
  • the effective deviation is thus limited to 3%.
  • the deviation of the speed limiting control becomes zero and prevents any positive deviation on the machine controller via the minimum selection. Only negative deviations in the direction of a speed reduction can occur.
  • the controller of the unit reduces the speed.
  • controller adjustment time is to be adapted individually, this can be achieved in a simple manner.
  • the variable that is the leading variable can be identified from a comparison of the individual inputs of the maximum and minimum selection with the output.
  • the position of the changeover switch for the deviations of the capacity controllers and the load distribution controllers makes it possible to determine which of these controllers is in operation.
  • a selection matrix can now determine which controller adjustment time shall be effective at which controller combination.
  • the controller time constant effective in the machine controller can now be accurately adjusted adaptively as is required by the selection matrix.
  • FIG. 11 shows an application with a total of nine control circuits. If such a system were composed of nine individual controllers according to the state of the art, extensive adjustments and mutual interlocking, which would prevent individual non-active controllers from running into saturation, would be necessary. Furthermore, there is a risk that the nine controllers will mutually dynamically affect each other. All these drawbacks are circumvented according to the present invention. There is only one machine controller per machine unit. Any adjustment can be eliminated, and an interaction between controllers cannot occur, either. The machine controllers of the other compressors cannot mutually affect each other, because all machine controllers are set to the same parameters for the same controlled variables. Since all load distribution controllers are optimized with the same parameters, they have the same time characteristic. Consequently, it cannot happen that individual machines run in different directions and consequently against each other.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
US10/371,136 2002-02-28 2003-02-20 Process for controlling a plurality of turbo engines in parallel or tandem operation Abandoned US20030161731A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10208676.1 2002-02-28
DE10208676A DE10208676A1 (de) 2002-02-28 2002-02-28 Verfahren zum Regeln von mehreren Strömungsmaschinen im Parallel- oder Reihenbetrieb

Publications (1)

Publication Number Publication Date
US20030161731A1 true US20030161731A1 (en) 2003-08-28

Family

ID=27675112

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/371,136 Abandoned US20030161731A1 (en) 2002-02-28 2003-02-20 Process for controlling a plurality of turbo engines in parallel or tandem operation

Country Status (5)

Country Link
US (1) US20030161731A1 (de)
EP (1) EP1340919B1 (de)
AT (1) ATE325951T1 (de)
DE (2) DE10208676A1 (de)
ES (1) ES2262901T3 (de)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004041661A1 (de) * 2004-08-27 2006-03-30 Siemens Ag Verfahren zur optimalen Steuerung von Pumpstationen und Pumpen in einer Pipeline und entsprechendes Computerprogramm-Erzeugnis
US20070189905A1 (en) * 2006-02-13 2007-08-16 Ingersoll-Rand Company Multi-stage compression system and method of operating the same
US20070199606A1 (en) * 2003-09-11 2007-08-30 Ormat Technologies Inc. Method Of And Apparatus For Pressurizing Gas Flowing In A Pipeline
US20080131258A1 (en) * 2005-02-11 2008-06-05 Helmut Liepold Method for Optimizing the Functioning of a Plurality of Compressor Units and Corresponding Device
US20100198640A1 (en) * 2003-06-11 2010-08-05 Kabushiki Kaisha Toshiba Electric-power-generating-facility operation management support system, electric-power-generating-facility operation management support method, and program for executing operation management support method on computer
US20120230840A1 (en) * 2009-11-12 2012-09-13 Rolls-Royce Plc Gas compression
WO2013087524A1 (en) 2011-12-15 2013-06-20 Nuovo Pignone S.P.A. Method for controlling a plurality of machines, control system and plant
US20160187893A1 (en) * 2014-12-31 2016-06-30 Ingersoll-Rand Company System and method using parallel compressor units
US20160265798A1 (en) * 2015-03-09 2016-09-15 Lennox Industries Inc. Sensor coupling verification in tandem compressor units
WO2016177879A1 (en) * 2015-05-07 2016-11-10 Nuovo Pignone Tecnologie Srl Method and apparatus for compressor system pressurization
CN111927814A (zh) * 2020-08-19 2020-11-13 蘑菇物联技术（深圳）有限公司 一种基于边缘计算的离心空压机组节能的方法
US11162492B2 (en) 2008-12-23 2021-11-02 Kaeser Kompressoren Se Method for controlling a compressor installation

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT502998B1 (de) * 2006-01-11 2008-05-15 Leobersdorfer Maschf Hochdruck-kompressor sowie dessen verwendung und verfahren zu dessen betrieb
DE102008064491A1 (de) * 2008-12-23 2010-06-24 Kaeser Kompressoren Gmbh Simulationsgestütztes Verfahren zur Steuerung bzw. Regelung von Druckluftstationen
DE102009017613A1 (de) 2009-04-16 2010-10-28 Siemens Aktiengesellschaft Verfahren zum Betrieb mehrerer Maschinen
DE102011079732B4 (de) * 2011-07-25 2018-12-27 Siemens Aktiengesellschaft Verfahren und Vorrichtung zum Steuern bzw. Regeln eines Fluidförderers zum Fördern eines Fluides innerhalb einer Fluidleitung
US9527683B2 (en) 2011-07-25 2016-12-27 Siemens Aktiengesellschaft Method and device for controlling and/or regulating a fluid conveyor for conveying a fluid within a fluid line

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4580947A (en) * 1984-01-11 1986-04-08 Hitachi, Ltd. Method of controlling operation of a plurality of compressors
US4640665A (en) * 1982-09-15 1987-02-03 Compressor Controls Corp. Method for controlling a multicompressor station
US5347467A (en) * 1992-06-22 1994-09-13 Compressor Controls Corporation Load sharing method and apparatus for controlling a main gas parameter of a compressor station with multiple dynamic compressors
US5743715A (en) * 1995-10-20 1998-04-28 Compressor Controls Corporation Method and apparatus for load balancing among multiple compressors
US5820349A (en) * 1995-09-14 1998-10-13 Copeland Corporation Rotary compressor with reverse rotating braking
US5971711A (en) * 1996-05-21 1999-10-26 Ebara Corporation Vacuum pump control system
US6126401A (en) * 1998-08-12 2000-10-03 Computer Graphics Systems Development Corporation Hybrid electric/hydraulic drive system
US6164901A (en) * 1998-06-26 2000-12-26 Ghh Borsig Turbomaschinen Gmbh Method and device for operating turbocompressors with a plurality of controllers that interfere one with each other
US6233954B1 (en) * 1999-04-28 2001-05-22 Ingersoll-Rand Company Method for controlling the operation of a compression system having a plurality of compressors
US6318965B1 (en) * 1999-04-13 2001-11-20 Degree Controls, Inc. Intelligent internal fan controller
US6398505B1 (en) * 1999-06-03 2002-06-04 Fujitsu Limited Cooling apparatus and cooling system for realizing efficient cooling
US6471486B1 (en) * 1997-10-28 2002-10-29 Coltec Industries Inc. Compressor system and method and control for same
US6685438B2 (en) * 2001-08-01 2004-02-03 Lg Electronics Inc. Apparatus and method for controlling operation of reciprocating compressor

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA926978A (en) * 1971-06-29 1973-05-22 Trans-Canada Pipe Lines Limited Control system for compressors operating in parallel
FR2324911A1 (fr) * 1975-09-18 1977-04-15 Rateau Sa Dispositif de regulation du fonctionnement d'un ensemble de n turbo-compresseurs
JPS623198A (ja) * 1985-06-28 1987-01-09 Hitachi Ltd タ−ボ圧縮機の容量制御装置
US5343384A (en) * 1992-10-13 1994-08-30 Ingersoll-Rand Company Method and apparatus for controlling a system of compressors to achieve load sharing
BE1011122A3 (nl) * 1997-04-22 1999-05-04 Atlas Copco Airpower Nv Besturingsinrichting van een compressorinstallatie.

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4640665A (en) * 1982-09-15 1987-02-03 Compressor Controls Corp. Method for controlling a multicompressor station
US4580947A (en) * 1984-01-11 1986-04-08 Hitachi, Ltd. Method of controlling operation of a plurality of compressors
US5347467A (en) * 1992-06-22 1994-09-13 Compressor Controls Corporation Load sharing method and apparatus for controlling a main gas parameter of a compressor station with multiple dynamic compressors
US5820349A (en) * 1995-09-14 1998-10-13 Copeland Corporation Rotary compressor with reverse rotating braking
US5743715A (en) * 1995-10-20 1998-04-28 Compressor Controls Corporation Method and apparatus for load balancing among multiple compressors
US5971711A (en) * 1996-05-21 1999-10-26 Ebara Corporation Vacuum pump control system
US6471486B1 (en) * 1997-10-28 2002-10-29 Coltec Industries Inc. Compressor system and method and control for same
US6164901A (en) * 1998-06-26 2000-12-26 Ghh Borsig Turbomaschinen Gmbh Method and device for operating turbocompressors with a plurality of controllers that interfere one with each other
US6126401A (en) * 1998-08-12 2000-10-03 Computer Graphics Systems Development Corporation Hybrid electric/hydraulic drive system
US6318965B1 (en) * 1999-04-13 2001-11-20 Degree Controls, Inc. Intelligent internal fan controller
US6233954B1 (en) * 1999-04-28 2001-05-22 Ingersoll-Rand Company Method for controlling the operation of a compression system having a plurality of compressors
US6398505B1 (en) * 1999-06-03 2002-06-04 Fujitsu Limited Cooling apparatus and cooling system for realizing efficient cooling
US6685438B2 (en) * 2001-08-01 2004-02-03 Lg Electronics Inc. Apparatus and method for controlling operation of reciprocating compressor

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100198640A1 (en) * 2003-06-11 2010-08-05 Kabushiki Kaisha Toshiba Electric-power-generating-facility operation management support system, electric-power-generating-facility operation management support method, and program for executing operation management support method on computer
US8219439B2 (en) * 2003-06-11 2012-07-10 Kabushiki Kaisha Toshiba Electric-power-generating-facility operation management support system, electric-power-generating-facility operation management support method, and program for executing operation management support method on computer
US20070199606A1 (en) * 2003-09-11 2007-08-30 Ormat Technologies Inc. Method Of And Apparatus For Pressurizing Gas Flowing In A Pipeline
US7950214B2 (en) * 2003-09-11 2011-05-31 Ormat Technologies Inc. Method of and apparatus for pressurizing gas flowing in a pipeline
DE102004041661B4 (de) * 2004-08-27 2006-06-14 Siemens Ag Verfahren zur optimalen Steuerung von Pumpstationen und Pumpen in einer Pipeline und entsprechendes Computerprogramm-Erzeugnis
DE102004041661A1 (de) * 2004-08-27 2006-03-30 Siemens Ag Verfahren zur optimalen Steuerung von Pumpstationen und Pumpen in einer Pipeline und entsprechendes Computerprogramm-Erzeugnis
US20080131258A1 (en) * 2005-02-11 2008-06-05 Helmut Liepold Method for Optimizing the Functioning of a Plurality of Compressor Units and Corresponding Device
US7676283B2 (en) 2005-02-11 2010-03-09 Siemens Aktiengesellschaft Method for optimizing the functioning of a plurality of compressor units and corresponding device
US20070189905A1 (en) * 2006-02-13 2007-08-16 Ingersoll-Rand Company Multi-stage compression system and method of operating the same
US11162492B2 (en) 2008-12-23 2021-11-02 Kaeser Kompressoren Se Method for controlling a compressor installation
US20120230840A1 (en) * 2009-11-12 2012-09-13 Rolls-Royce Plc Gas compression
US9022747B2 (en) * 2009-11-12 2015-05-05 Rolls-Royce Plc Gas compression
WO2013087524A1 (en) 2011-12-15 2013-06-20 Nuovo Pignone S.P.A. Method for controlling a plurality of machines, control system and plant
US10545485B2 (en) 2011-12-15 2020-01-28 Nuovo Pignone S.P.A. Method for controlling a plurality of machines, control system and description
US20160187893A1 (en) * 2014-12-31 2016-06-30 Ingersoll-Rand Company System and method using parallel compressor units
US20160265798A1 (en) * 2015-03-09 2016-09-15 Lennox Industries Inc. Sensor coupling verification in tandem compressor units
US10684032B2 (en) * 2015-03-09 2020-06-16 Lennox Industries Inc. Sensor coupling verification in tandem compressor units
US11054162B2 (en) * 2015-03-09 2021-07-06 Lennox Industries Inc. Sensor coupling verification in tandem compressor units
WO2016177879A1 (en) * 2015-05-07 2016-11-10 Nuovo Pignone Tecnologie Srl Method and apparatus for compressor system pressurization
CN107532605A (zh) * 2015-05-07 2018-01-02 诺沃皮尼奥内技术股份有限公司 用于压缩机系统增压的方法和设备
US10724531B2 (en) 2015-05-07 2020-07-28 Nuovo Pignone Tecnologies SRL Method and apparatus for compressor system pressurization
CN111927814A (zh) * 2020-08-19 2020-11-13 蘑菇物联技术（深圳）有限公司 一种基于边缘计算的离心空压机组节能的方法

Also Published As

Publication number Publication date
EP1340919B1 (de) 2006-05-10
DE50303267D1 (de) 2006-06-14
EP1340919A3 (de) 2004-01-07
EP1340919A2 (de) 2003-09-03
ATE325951T1 (de) 2006-06-15
DE10208676A1 (de) 2003-09-04
ES2262901T3 (es) 2006-12-01

Similar Documents

Publication Publication Date Title
US20030161731A1 (en) Process for controlling a plurality of turbo engines in parallel or tandem operation
US6551068B2 (en) Process for protecting a turbocompressor from operating in the unstable working range
US4560319A (en) Method and apparatus for controlling at least two parallel-connected turbocompressors
US6164901A (en) Method and device for operating turbocompressors with a plurality of controllers that interfere one with each other
US8977518B2 (en) Device and method for performing a functional test on a control element of a turbo engine
CN102177322B (zh) 发动机
EP1939431A2 (de) Verfahren und Vorrichtungen zur Ermöglichung der Brennstoffsteuerung von Gasturbinen
US6293766B1 (en) Process for operating a compressor with a downstream user, and unit operating according to this process
JP2011241782A (ja) ガスタービン燃料の制御機構及びガスタービン
US6406268B1 (en) Control of a compressor unit
US4178762A (en) Efficient valve position controller for use in a steam turbine power plant
JPH01151727A (ja) ガスタービンの制御方法及びその装置
CN115539210A (zh) 控制燃气涡轮功率装置的方法和燃气涡轮功率装置
CN111828952A (zh) 电、汽动给水泵并列运行时汽包水位的控制方法
JPH0333495A (ja) 復水ポンプ制御装置
CN110307138B (zh) 一种关于能量效率的多压缩机系统的设计、测量和优化方法
CN116792305A (zh) 空压站的控制系统
CN104074843A (zh) 具有转速可调的驱动机的液压装置和用于其的控制方法
CN113739437A (zh) 一种多台压缩机并联运行的动态负荷分配控制方法
RU2298653C2 (ru) Способ регулирования частоты вращения турбины, подключенной посредством генератора к электрической сети энергоснабжения (варианты) и устройство для его осуществления (варианты)
US4178763A (en) System for minimizing valve throttling losses in a steam turbine power plant
US20130039781A1 (en) Anticipation logic for a surge control valve utilized with load compressor
EP1078204A1 (de) Brennstoffzuführung zu einem brennerelement
CN114076004B (zh) 一种中压供热系统及中压供热方法
CN111148887B (zh) 蒸汽涡轮机控制

Legal Events

Date Code Title Description
AS Assignment

Owner name: MAN TURBOMASCHINEN AG GHH BORSIG, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:WILFRIED BLOTENBERG;REEL/FRAME:013809/0813

Effective date: 20030207

AS Assignment

Owner name: MAN TURBO AG, GERMANY

Free format text: CHANGE OF NAME;ASSIGNOR:MAN TURBOMASCHINEN AG;REEL/FRAME:016195/0869

Effective date: 20040929

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION