JPH0814191A - Fluid machine system control device and its control method - Google Patents

Abstract

PURPOSE:To reduce power consumption, enhance system reliability and move an operation point at a high speed by obtaining a system without generating transitional pressure fluctuation or flow rate fluctuation at the time of operation point movement of a fluid machine and capable of conducting operation to the vicinity of a surge line. CONSTITUTION:This device comprises a turbo-type blower or compressor 1, a drive source 4, a flow rate control device 2, compressed gas consuming equipment 3 and a fluid piping 5, and is provided with a detector 6 of a physical quantity in a system, a signal processor 7, an operating state detector 8 of the compressed gas consuming equipment 3 and a system operation parameter determining apparatus 9. It is also provided with a simulator 10 for simulating physical quantity fluctuation at the time of operation point movement, and a controller 11 for controlling a set value of the flow rate control device 2. When a change of an external load 12 is detected, a step for simulating the physical quantity fluctuation at the time of operation point movement and a step for calculating a change of the set value of the flow rate control device 2 are repeated, and when the pressure fluctuation is estimated not more than a threshold value, movement of the operation point is started.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a controller of a fluid mechanical system and a control method thereof, and more particularly to, for example, a turbo fan or compressor system and an operation control method thereof.

[0002]

2. Description of the Related Art In a fluid machine, for example, a system such as a plant equipped with a turbo type blower or a compressor (hereinafter referred to as a turbo type blower or compressor system), it is necessary to reduce the flow rate from the design point. When the flow rate becomes lower than a certain level, a large-scale backflow occurs in the system, and an unstable phenomenon such as turning stall or surging occurs. Generally,
Jing should not occur under practical conditions because the entire flow in the turbo blower or compressor system will flow backwards and will impose a heavy load on the system.

Regarding the avoidance of surging of the conventional turbo fan or compressor system, see, for example, Japanese Patent Laid-Open No. 2-1.
A compressor flow control device described in Japanese Patent Publication No. 19698 is known. FIG. 38 is a diagram showing the surging line and the surging avoidance control line described in the above publication. In FIG. 38, the horizontal axis represents the flow rate and the vertical axis represents the discharge pressure.
The performance curve is shown by a solid line, and the surging line and the surging avoidance control line are shown by broken lines.

The compressor flow rate control device disclosed in Japanese Patent Laid-Open No. 2-119698 has a system pressure,
Using a polytropic head that has detected the temperature and calculated based on the detected pressure and temperature, set the surging avoidance setting flow rate of the flow rate controller provided on the bypass line in parallel with the surging line as shown in FIG. A means is disclosed to prevent the compressor flow rate from becoming less than the flow rate at which surging occurs.

Further, in the method of controlling a centrifugal compressor described in Japanese Patent Laid-Open No. 63-230999, sizing is performed on a vane angle plane determined by the angles of an inlet guide vane and a diffuser vane. If the measured vane angle is within the surging area, the sag line that defines the area is set in advance, and the vane angle is controlled to eliminate the surging. If the vane angle set for the target flow rate is directed to the surging region, a vane angle for avoiding surging is determined and the flow rate is controlled so as to avoid surging. It is disclosed.

Further, in the method of controlling a centrifugal compressor described in Japanese Patent Laid-Open No. 1-200955, a functional relationship between a suction temperature of a fluid sucked into the compressor and a minimum rotation speed capable of avoiding surge is set. Every time, the suction speed is used to set the minimum number of revolutions of the compressor that can avoid surging, and the compressor is operated at the minimum number of revolutions or higher, and the inlet guide base is set.
There is disclosed a method for controlling the flow rate by controlling the angle of the drain and diffuser vanes.

[0007]

When the operating point of the blower or compressor rapidly moves, transient pressure fluctuations and flow rate fluctuations occur in the system, and a large load is applied to the blower or compressor system. In addition to a problem in terms of system strength, surging may occur even though the flow rate is higher than the set operating limit. On the other hand, in the current turbo-type blower or compressor system, it is required to speed up the movement of the operating point, and the above-mentioned prior art has not disclosed a control method for such high-speed movement of the operating point.

Further, in the above-mentioned prior art, the vane angle and flow rate for starting the surging avoidance control are set to be larger than the vane angle and flow rate for generating surging with a margin, and the consumption is reduced. Power loss was great and uneconomical.
Furthermore, the surging line changes due to changes in suction temperature, characteristics of compressed gas consuming equipment, etc., and if the surging line can be changed according to the operating environment of the system, reliable surging can be avoided. , It becomes possible to operate the blower or compressor near the flow rate of surge generation,
At the time of partial load, it is not necessary to use the bypass control described in the above-mentioned prior art, and the loss of power consumption can be reduced.

The present invention has been made to solve the above-mentioned problems of the prior art, and a first object of the present invention is to predict pressure fluctuations and flow rate fluctuations occurring in a fluid mechanical system,
Since the operating point is moved, it is possible to suppress pressure fluctuations and flow rate fluctuations during movement of the operating point, reduce the load on the fluid mechanical system, and enable high-speed movement of the operating point. To provide a method.

A second object of the present invention is to control a fluid mechanical system capable of making an accurate surging determination by detecting pressure fluctuations and flow rate fluctuations during surging in a fluid mechanical system and starting suppression control. An object is to provide an apparatus and a control method thereof. Furthermore, a third object of the present invention is to change the operating limit according to the operating environment of the fluid machine, and also to cope with changes in the operating limit due to performance deterioration of the system and changes over time, and a safe operating point movement. It is an object of the present invention to provide a control device for a fluid mechanical system and a control method thereof that can set an accurate operating limit.

Further, a fourth object of the present invention is to provide a control device of a fluid mechanical system and a control method thereof, which can further speed up the prediction of movement of the operating point in the fluid mechanical system and can suppress sudden pressure fluctuations. To do. That is, an object of the present invention is to provide a system capable of operating up to the vicinity of a surging line without causing a transient pressure fluctuation or flow rate fluctuation when the operating point of a blower or a compressor is moved. To do.

[0012]

In order to achieve the above first object, the configuration of the first invention relating to the control device of the fluid machine system of the present invention is a fluid machine, a drive source of the fluid machine, and a system. A flow rate control device for adjusting the flow rate of the fluid inside, a compressed gas consuming device on the demand side of the compressed gas related to the fluid, and a fluid pipe, and a physical quantity detector in the system, a detector of the operating state of the drive source, and In a control device for a fluid machine system including an operating state detector for the compressed gas consuming device, a simulator for simulating a physical quantity change when the operating point of the fluid machine moves, and a controller for controlling a set value of the flow rate control device. It is equipped with.

More specifically, in the above configuration,
It is provided with a set value storage device of the flow rate control device, and is further provided with a simulator for controlling the set value of the flow rate control device.

In order to achieve the above first object, the configuration of the first invention relating to the control method of the fluid machine system of the present invention is provided with the above control device, and the operating state of the fluid machine at a predetermined operating point is set. In the control method of the fluid mechanical system that detects the operating state of the compressed gas consuming device and controls the flow rate control device according to the external load fluctuation, when the change of the external load is detected, the physical quantity change when moving the operating point is simulated. And the step of calculating the change in the set value of the flow rate control device are repeated, and the operating point movement is started when the pressure fluctuation is predicted to be equal to or less than a predetermined threshold value.

In order to achieve the above-mentioned second object, the configuration of the second invention relating to the controller of the fluid machine system of the present invention is to adjust the fluid machine, the drive source of the fluid machine, and the fluid flow rate in the system. A flow rate control device, a compressed gas consuming device on the demand side of the compressed gas related to the fluid, and a fluid pipe, and a physical quantity detector in the system, a drive source operating state detector, and the compressed gas consuming device. In a controller of a fluid machine system including an operating state detector, a simulator that simulates a physical quantity change after the operating point of the fluid machine is moved, a device that suppresses a physical quantity change during surging, and a physical quantity change in the system is determined. The decision device to
And a controller for controlling the set value of the flow rate control device.

Further, more specifically, in the above configuration,
It is provided with a controller of a drive source of a fluid machine.

In order to achieve the above-mentioned third object, the configuration of the third invention relating to the controller of the fluid machine system of the present invention is to adjust the fluid machine, the drive source of the fluid machine, and the fluid flow rate in the system. A flow rate control device, a compressed gas consuming device on the demand side of the compressed gas related to the fluid, and a fluid pipe, and a physical quantity detector in the system, a drive source operating state detector, and the compressed gas consuming device. In a controller of a fluid machine system including an operating state detector, a simulator that simulates an operating state of the fluid machine, a storage device that stores an operating environment of the fluid machine, and an operating limit that is changed according to the operating environment. And a device for doing so.

Further, more specifically, in the above configuration,
It is provided with a device for storing the operating parameters of the fluid machine, further, a surging suppression control device, a determiner for determining a physical quantity variation in the system, a controller for changing the set value of the flow rate control device, The controller is provided with a drive source of the fluid device.

In order to achieve the above-mentioned third object, the configuration of the third invention relating to the control method of the fluid mechanical system of the present invention is provided with the above-mentioned control device, and the operating state of the fluid machine at a predetermined operating point and Detecting the operating state of the compressed gas consuming device, in the control method of the fluid mechanical system to control the flow rate control device according to the external load fluctuation, after the data of the operating parameters of the system or the parameters of the operating environment is accumulated, The operating limit is changed without simulating the operating state.

Further, in order to achieve the above-mentioned fourth object, the configuration of the fourth invention relating to the controller of the fluid machine system of the present invention is a fluid machine, a drive source of the fluid machine, and a fluid flow rate in the system. A flow rate control device for adjusting the flow rate, a compressed gas consuming device on the demand side of the compressed gas related to the fluid, and a fluid pipe, and a physical quantity detector in the system, a drive source operating state detector, and the compressed gas consumption. A controller of a fluid mechanical system including an operating state detector of equipment includes a plurality of arithmetic units coupled to each other so that information can be exchanged with each other, and a controller for controlling a set value of the flow rate controller. It is a thing.

[0021] More specifically, in the above configuration,
A surging suppressor, a determiner for determining a physical quantity variation in the system, and a controller for a drive source of the fluid machine, and a storage device for the operating environment of the fluid machine and a system operation. A parameter storage device and an operation limit changing device are provided.

Further, in order to achieve each of the above objects, the structure of the fourth invention relating to the control method of the fluid mechanical system of the present invention is provided with the above-mentioned control device and is connected so that information can be exchanged with each other. A plurality of arithmetic units are used to simulate the operating state and to control the flow rate of the flow rate control device.

In more detail, in addition to the above, the flow rate control of the flow rate control device and the surging suppression control are performed to determine the physical quantity variation in the system.
Further, a plurality of computing units coupled to each other to exchange information are used to store the operating environment of the fluid mechanical system, store operating parameters of the system, and change the operating limit. is there.

[0024]

The function of each of the above technical means is as follows.
The operating state of the fluid mechanical system can be simulated based on a differential equation that describes the flow state in the system. In the first aspect of the present invention, it is possible to predict and suppress pressure fluctuations and flow rate fluctuations that occur during movement of the operating point by simulation, so it is possible to move the operating point without transient pressure fluctuations and flow rate fluctuations. As a result, the load on the fluid mechanical system can be reduced, and the reliability of the system can be improved.

Further, according to the second aspect of the invention, since the change in the set value of the flow rate control device can be set according to the operating environment of the fluid machine, it is possible to prevent surging caused by the influence of the inertial force of the gas. If the system model used for simulating the operating state of the fluid mechanical system is set to the safe side, the flow rate of surging may be predicted to be higher than the actual flow rate. On the other hand, by detecting the pressure fluctuation or flow rate fluctuation actually occurring in the system,
If the surging is determined, it is possible to accurately determine the occurrence of the surging, and it is possible to operate near the operating limit and reduce energy loss.

As in the third aspect of the invention, if the change in the operating limit of the fluid mechanical system is stored, the operating limit can be set depending on the temperature, pressure and flow rate. As a result, the fluid machine can be operated in the vicinity of the operating limit, and energy saving can be realized. Further, as in the fourth aspect, if the operating state is predicted by the arithmetic units connected in parallel, the operating state can be predicted and the control speed can be increased. As a result, it is possible to deal with a sudden change and improve the reliability of the system.

[0027]

Embodiments of the present invention will be described below with reference to FIGS. 1 to 37. First, an embodiment of the first invention will be described. [Embodiment 1-1] FIG. 1 is a system diagram showing a control configuration of a blower or compressor system according to a first embodiment of the first invention, and FIG. 2 is a performance curve of the blower or compressor and movement of an operating point. 3 is a diagram showing the relationship between the pressure and the flow rate at the time, FIG. 3 is a diagram showing the transient pressure fluctuation when the operating point moves, and FIG. 4 is a flowchart showing the operation control method in the system of FIG.
FIG. 5 is a diagram showing changes in set values of the flow rate control device, and FIG.
FIG. 7 is a diagram showing a change in the set value of the flow rate control device, FIG. 7 is a diagram showing a pressure fluctuation when the first embodiment of the first invention is implemented, and FIG. 8 is a first embodiment of the first invention. It is a diagram which shows the relationship of the pressure and the flow rate at the time of implementation.

FIG. 1 shows a blower or compressor system according to a first embodiment of the present invention, in which 1 is a turbo blower or compressor relating to a fluid machine, and 2 is a flow rate in the system. A flow control device such as a valve for adjusting
Reference numeral 3 denotes a compressed gas demand side, for example, a compressed gas consuming device such as an air turbine, 4 denotes a blower or a drive source for the compressor 1, and 5 denotes piping for connecting each constituent element in the system. .

Further, 6 is a detector of pressure, flow rate, and temperature which are physical quantities in the system such as a pressure sensor, thermocouple, and electromagnetic flow meter, 7 is a signal processor from the detector, 8
Is the operating state detector of the compressed gas consuming device 3, and 9 is the operation of the turbo blower or the compressor system based on the set value of the flow rate control device 2, the operating state of the drive source 4 and the operating state of the compressed gas consuming device 3. Setting device for setting parameters, 1
0 is a simulator for simulating the movement of the operating point, 11 is a controller for controlling the set value of the flow rate control device 2, and 12 is an external load connected to the compressed gas consuming device 3.

In FIG. 2, the horizontal axis represents the flow rate and the vertical axis represents the pressure.
The performance curve C1 of the turbo blower or the compressor 1 is shown, point A shows the operating point of the flow rate Qa, and point B shows the operating point of the flow rate Qb. Further, in FIG. 3, the horizontal axis represents time and the vertical axis represents pressure, showing transient pressure fluctuations when the operating point moves, and ΔP represents a threshold value. When the operating point is to be moved from A to B near the discharge pressure maximum point in the performance curve of the turbo blower or the compressor 1, the operating point is as shown in FIG. 2 due to the influence of the inertial force of the gas in the system. Without moving on the curve C1, the locus shown by the curve arrow is taken, and the operation on the lower flow rate side than the surging line occurs momentarily, and the pressure fluctuation shown in FIG. 3 occurs. Such pressure fluctuations impose a heavy load on the blower or compressor system, which causes a problem in strength. Further, when the inertial force is large, surging may occur.

In the first embodiment of the first aspect of the invention, a simulator 10 for simulating physical quantity fluctuations when the operating point moves and a controller 11 of the flow rate control device are provided to suppress pressure fluctuations when the operating point moves. Is. The control method of the blower or compressor system in the first embodiment will be described below with reference to FIG.

The pressure, the flow rate, and the temperature, which are the physical quantities in the system at the current operating point A shown in FIG. 2, are calculated by the detector 6 and the signal processor 7 (step A1), and the calculated pressure, flow rate, The operating state of the turbo blower or the compressor 1 at point A is calculated based on the temperature (step A2). The operating state detector 8 of the compressed gas consuming device detects the operating state of the compressed gas consuming device 3 (step A3).

The rotational speed or driving force of the drive source 4 and the set value of the flow rate control device 2 are detected, and the operating parameters of the system are set by the setter 9 together with the operating state of the compressed gas consuming device 3 detected in step A3 ( Step A4).
The load condition of the external load 12 is detected by the setter 9, and when a load change is detected, a new operating point (point B in FIG. 2) of the turbo blower or the compressor 1 is calculated (step A5).

After the operating point B after the movement is calculated, the pressure, the flow rate, the temperature in the system detected by the detector 6 and the operating parameters of the system obtained by the setter 9 are used to move to the operating point B. The movement is simulated by the simulator 10 (step A6), and it is determined whether or not pressure fluctuation and flow fluctuation occur when moving to the point B (step A7). In the simulation of movement of the operating point, the change in the set value of the flow rate control device stored in the simulator 10 (see FIG. 5) is used.

5 and 6, the horizontal axis represents time and the vertical axis represents the flow control device set value, and the solid line shows the change in the flow control device set value at the start and end of movement of the operating point. As a result of the simulation, when it is predicted that a pressure fluctuation equal to or larger than the threshold value ΔP shown in FIG. 3 will occur, the change in the set value of the flow control device for mitigating the predicted pressure fluctuation is stored in the simulator 10. The calculation is performed using the model of the system, and the operations of steps A6 and A7 are repeated until the pressure fluctuation is predicted to be less than or equal to the threshold value.

When the pressure fluctuation becomes equal to or less than the threshold value shown in FIG. 7 due to the change of the set value of the flow rate control device shown in FIG. 6, the controller 11 controls the set value of the flow rate control device, and FIG. The movement from the point A to the point B shown is performed (step A8), and transient pressure fluctuations and flow rate fluctuations at the time of moving the operating point from the point A to the point B are suppressed.

[Embodiment 1-2] FIG. 9 is a system diagram showing a control configuration of a blower or compressor system according to a second embodiment of the first invention, and FIG. 10 is an operation control method in the system of FIG. FIG. 11 is a diagram showing a pressure fluctuation when the second embodiment of the first invention is carried out.
In FIG. 9, the same reference numerals as those in FIG. 1 are the same parts as those in the previous embodiment, and the description thereof will be omitted. Also, FIG.
The numbers of step Nos. 1 to 5 in 0 are the same as those in FIG. 4 and indicate the same steps.

In the second embodiment, the system shown in FIG. 1 described in the first embodiment is additionally provided with a storage device 13 for setting value change of the flow rate control device. The operation control method of the turbo blower or compressor system in the second embodiment will be described below with reference to FIG. Similar to the first embodiment, control is performed from detection of pressure, flow rate, and temperature (step B1) to detection of external load (step B5).

When the change of the external load 12 is detected, the setting of the flow control device from the point A to the point B (see FIG. 2) stored in the storage device 13 of the set value change of the flow control device 2. A value change is input (step B6), the movement to the operating point B is simulated by the simulator 10 (step B7), and it is determined whether or not pressure fluctuations and flow fluctuations occur when moving to the operating point B. (Step B
8). When it is predicted that the pressure fluctuation above the threshold value will occur, the change in the set value of the flow rate control device 2 is calculated as in the first embodiment, and the pressure fluctuation below the threshold value is controlled in steps B7 and B8. Repeat until predicted.

In the second embodiment, since the storage device 13 for the set value change of the flow control device 2 is provided and the change of the set value of the flow control device at the time of moving the operating point in the past is stored, the transient pressure fluctuation. The calculation time of the set value change of the flow rate control device can be shortened because the set value change calculation of the flow control device is started from the stage of the change of the set value which does not occur or the pressure fluctuation smaller than that of the first embodiment shown in FIG. The change decision can be speeded up.
Further, in the second embodiment, the threshold value of pressure fluctuation can be made smaller, and the transient pressure fluctuation can be made smaller than in the first embodiment.

[Embodiment 1-3] FIG. 12 is a system diagram showing a control configuration of a blower or compressor system according to a third embodiment of the first invention, and FIG. 13 is an operation control method in the system of FIG. It is a flowchart showing. 12
In FIG. 5, the same reference numerals as those in FIGS. Also, the numbers in Steps Nos. 1 to 8 in FIG. 13 are the same as those in FIG. 10 and indicate the same steps.

In the third embodiment, a simulator 14 for changing the set value of the flow rate control device 2 is newly provided in the system [Embodiment 1-2] shown in FIG. The operation control method of the third embodiment will be described with reference to FIG. In the third embodiment, a simulation of the set value control of the flow rate control device using the simulator 14 (step C9) is added to the above second embodiment.

In the simulator 14 for controlling the set value of the flow control device, the model of the turbo blower or the compressor system is changed according to the operating state, and the change in the set value of the flow control device is made more accurate than in the second embodiment. calculate. In changing the model, for example, the valve resistance and the piping frictional resistance are changed according to the operating state. Needless to say, the same effect can be obtained by providing the system of FIG. 1 according to the first embodiment with the simulator 14 for controlling the set value of the flow rate control device.

[Embodiment 1-4] FIG. 14 is a system diagram showing a control configuration of a blower or compressor system according to a fourth embodiment of the first invention, and FIG. 15 shows simulation intervals in the control of FIG. The diagram shown in FIG. 16 and FIG. 16 are diagrams showing pressure fluctuations when the control of FIG. 14 is executed.

In the fourth embodiment of the first invention, the step D2 is carried out at the interval of time Δt (simulation interval) shown in FIG. 15 even during movement of the operating point, as in the third embodiment.
From step D11, the operation control is performed. After the control from step D2 to step D11, it is determined whether the operating point after Δt has reached a predetermined operating point (step D1
2) If not, step D1 to step D1
The control of 0 is repeated. If the predetermined operating point has been reached, the control ends.

According to the fourth embodiment, the movement of the operating point can be finely controlled, and as shown in FIG. 16, the pressure fluctuation is smaller than that in the third embodiment, and the operating point can be moved at a high speed. The system shown in FIGS. 1 and 9 [Embodiments 1-1 and 2].
Even if the fourth embodiment is applied, the pressure fluctuation is small and the operating point can be moved at high speed.

Next, an embodiment of the second invention will be described. [Embodiment 2-1] FIG. 17 is a system diagram showing a control configuration of a blower or compressor system according to a first embodiment of the second invention, and FIG. 18 is a flowchart showing an operation control method in the system of FIG. FIG. 19 is a diagram showing a movement of an operating point when operation control is performed in the system of FIG. 17, FIG. 20 is a diagram showing pressure fluctuations during surging in the system of FIG. 17, and FIG. 21 is induced by control suppression. 22 is a diagram showing the generated pressure fluctuation and the pressure fluctuation during surging.
[Fig. 4] is a diagram showing an actually detected pressure fluctuation during surging. In FIG. 17, the same reference numerals as those in FIG.
Since it is the same part as the previous embodiment, its explanation is omitted.

In the first embodiment of the second invention, as shown in FIG. 17, the simulator 15 for pressure fluctuations after movement of the operating point is performed.
And a suppression control device 16 for pressure fluctuation during surging and a pressure fluctuation determination device 17 in the system. The operation control method of the turbo blower or compressor system shown in FIG. 17 will be described below with reference to FIG.

The pressure, the flow rate, and the temperature, which are the physical quantities in the system, at the current operating point A on the performance curve shown in FIG. 19 are calculated by the detector 6 and the signal processor 7 (step E1) and calculated. The operating state of the turbo blower or the compressor 1 at the operating point A is calculated based on the pressure, the flow rate, and the temperature (step E2). The operating state detector 8 of the compressed gas consuming device detects the operating state of the compressed gas consuming device 3 (step E3).

The rotational speed or driving force of the drive source 4 and the set value of the flow rate control device 2 are detected, and the operating parameters of the system are set by the setter 9 together with the detected operating state of the compressed gas consuming device 3 (step E4). . The load condition of the external load 12 is detected by the setting device 9, and when a load change is detected, a new operating point (point B in FIG. 19) of the turbo blower or the compressor 1 is calculated (step E5).

The state at the point B is simulated by the simulator 15 (step E6).
It is determined whether or not the pressure fluctuation shown in (1) occurs (step E7). In the judgment of surging, when it is predicted that a pressure fluctuation larger than the threshold value (ΔP) shown in FIG. 20 has occurred for a time longer than the set time (T),
Judge as surging.

When it is predicted that a pressure fluctuation will occur, the fluctuation for suppressing the predicted pressure fluctuation during surging shown in FIG. 21 is controlled by the suppression controller 16 and the flow rate control device of the pressure fluctuation during surging. While inducing using the controller 11, the operating point is moved to the point B (step E
8). After moving to the point B, the detector 6 detects the actual pressure fluctuation (step E9), and the pressure fluctuation determiner 17 uses the detected pressure fluctuation to actually generate the pressure fluctuation during the surging. Is determined (step E1)
0).

Since the pressure fluctuation of the surging generated in the blower or the compressor system can be predicted by the simulation, the actual pressure fluctuation is detected by performing the surge in about one cycle of the pressure fluctuation shown in FIG. Can be determined. As a result of the judgment, when it is judged that the pressure fluctuation at the time of surging is generated, the controller 11 controls the set value of the flow rate control device 2 to operate from the point B to the point C shown in FIG. The point is moved to avoid surging (step E11).

When the movement from the point B to the point C is performed, a safer movement of the operating point can be realized by adding suppression control for suppressing the pressure fluctuation generated during the movement in addition to the operating point movement control. In this embodiment, since the actual pressure fluctuation is determined to determine the surging, accurate surging can be determined, and since surging suppression control can be performed, safe surging can be avoided.

[Embodiment 2-2] FIG. 23 is a system diagram showing the control configuration of the blower or compressor system according to the second embodiment of the second invention. In FIG. 23, components having the same reference numerals as those in FIGS. 1 and 17 are the same as those in the above-mentioned respective embodiments, and therefore their explanations are omitted. In the second embodiment of the second invention, the controller 18 of the drive source 4 is newly added to the system [Embodiment 2-1] shown in FIG. Similar to the flow chart of FIG. 18, when the control up to step E10 is performed and the occurrence of surging is actually detected, the controller 18 of the drive source 4 changes the rotation speed of the drive source or the change in the set value of the flow rate control device. One or both of the driving forces is controlled to move to point D in FIG. 19 while suppressing surging. This allows the system to operate at the same flow rate as at point B.

In the embodiment of the system shown in FIGS. 17 and 23, since the actual pressure fluctuation can be detected and judged,
It is also possible to deal with the occurrence of surging that could not be predicted by the turbo blower or compressor system model stored in the simulator 11. In the above-mentioned embodiments, the method of suppressing the pressure fluctuation and avoiding the surging is described, but the same effect can be obtained even with the fluctuation of the flow rate during the surging.

Next, an embodiment of the third invention will be described. [Embodiment 3-1] FIG. 24 is a system diagram showing a control configuration of a blower or compressor system according to a first embodiment of the third invention, and FIG. 25 is a flow chart showing an operation control method in the system of FIG. 26 is a diagram showing the movement of the operating point when the operation control is executed in the system of FIG. 24, and FIG. 27 is a diagram showing the pressure fluctuation when surging does not occur. In FIG. 24, the same symbols as those in FIG. 1 are the same parts as those in the previous embodiment, and the description thereof will be omitted.

In the first embodiment of the third invention, as shown in FIG. 24, an operating environment storage device 19 for setting an operating limit according to the operating environment and an operating limit storage device 20 are provided. There is something. 24, with reference to FIG.
The control method of the system will be described. The pressure, flow rate, and temperature at the current operating point A on the performance curve shown in FIG. 26 are calculated by the detector 6 and the signal processor 7 (step F
1) Based on the calculated pressure, flow rate, and temperature, the operating state of the turbo blower or compressor at point A is calculated (step F2).

The operating state detector 8 of the compressed gas consuming equipment detects the operating state of the compressed gas consuming equipment 3 (step F3). The rotation speed or driving force of the drive source 4 and the set value of the flow rate control device are detected, and the operating parameters of the system are set by the setter 9 together with the detected operating state of the compressed gas consuming device 3 (step F4). The load state of the external load 12 is detected by the detector 9, and when a load change is detected, a new operating point of the turbo blower or the compressor 1 is detected.
(Point B in FIG. 26) is calculated (step F5).

Then, the operating limit in the current operating environment is set by collating with the storage device 20 (step F6), and the point B is the operating limit in the current operating environment (surging line, f
It is determined whether the flow rate is lower than (t, p, Q) (step F7). When the flow rate is lower than the operating limit, the simulator 16 simulates the operating state after moving the operating point, that is, the state at point B (step F).
8). By the simulation, at the point B, FIG.
It is determined whether or not the pressure fluctuation shown in (6) occurs (step F9).

When it is predicted by the simulation that the pressure fluctuation does not occur at the working point B as shown in FIG. 27, the suction pressure at the working limit stored in the working environment storage device 19, The operating environment such as temperature is changed to the operating environment at point B (step F10), and the operating limit stored in the operating limit storage device 20 is changed to point B (step F11). Thereafter, the controller 11 changes the set value of the flow rate control device to move the operating point from the point A to the point B (step F12).

When the occurrence of surging is predicted,
The operating point after movement is changed to the operating point on the larger flow rate side than the current operating limit (point C in FIG. 26) (step F13) to prevent the occurrence of surging. In this embodiment, since the storage device 19 for operating environment and the storage device 20 for operating limit are provided, the operating limit of the turbo fan or the compressor can be changed according to the operating environment.

[Embodiment 3-2] FIG. 28 is a system diagram showing the control configuration of the blower or compressor system according to the second embodiment of the third invention. In FIG. 28,
The same reference numerals as 4 denote the same parts as those in the previous embodiments, and thus the description thereof will be omitted. In the embodiment shown in FIG. 28,
The system [embodiment 3-1] shown in FIG. 24 is newly provided with a storage device 21 for operating parameters of a turbo blower or compressor system. Along with the control of changing the operating environment (step F10) in the flowchart of FIG. 25, the operating parameter storage device 21 is used to set the flow rate controller at the operating limit, the operating state of the drive source 4, and the compressed gas consuming device 3. By storing the operating state, it is possible to set the operating limit more accurately than in the first embodiment of the third invention.

[Embodiment 3-3] FIG. 29 is a system diagram showing a control configuration of a blower or compressor system according to a third embodiment of the third invention, and FIG. 30 is a secular change of the blower or compressor system. FIG. 6 is a diagram showing changes in a performance curve and a surging line according to FIG. In FIG. 29, FIG.
The same reference numerals as those of Nos. 4 and 28 are the same as those of the previous embodiments, and thus the description thereof will be omitted. In FIG. 30, the horizontal axis represents the flow rate and the vertical axis represents the pressure, the performance curve of the specifications of the blower or the compressor is shown by the solid line, and the performance curve after aging is shown by the thick solid line.

The embodiment shown in FIG. 29 is a combination of the system [embodiment 2-2] shown in FIG. 23 and the system [embodiment 3-1 and 2] shown in FIG. 24 or 28. By performing the combination, the surging suppression control can be performed even when the operation limit moves to the large flow rate side due to the secular change of the turbo blower or the compressor system shown in FIG. 30, and the wider flow rate range can be achieved. It is possible to set the operating limit in.

[Embodiment 3-4] FIG. 31 is a diagram showing a surging line according to the operating environment. As the fourth embodiment of the third invention, according to the operation control of the system shown in FIG. 24 or FIG. 29 [Embodiment 3-1 and 3],
Since the change in the operating limit is stored as shown in FIG. 31, it is possible to set the operating limit according to the operating environment without simulating the operating state after the data of the operating limit is accumulated. It is also possible to predict changes in operating limits.

Next, an embodiment of the fourth invention will be described. [Embodiment 4-1] FIG. 32 is a system diagram showing a control configuration of a blower or compressor system according to a first embodiment of the fourth invention, FIG. 33 is a diagram showing sudden flow rate fluctuations, and FIG.
FIG. 33 is a diagram showing suppressed pressure fluctuations in the system of FIG. 32. In FIG. 32, the same symbols as those in FIG. 1 are the same parts as those in the previous embodiment, and therefore the description thereof will be omitted.

In the system of the first embodiment of the fourth invention,
The calculator 22 is connected in parallel. That is, a simulator for operating point movement related to the arithmetic unit 22 coupled in parallel and a detector 6 arranged at a plurality of places in the system are provided, and pressures detected by the plurality of detectors 6 are
Since physical quantities such as flow rate and temperature are used, pressure fluctuations in the flow rate control device 2, pressure fluctuations in the turbo blower or compressor 1, and pressure fluctuations in the compressed gas consuming device 3 are connected to the constituent devices. It is possible to separately simulate the pressure fluctuation in the pipe 5 that is present.

Further, the information in each flow path is sent to each computing unit (22-1 to 2-2) via the computing unit controller 22-0.
2-n). Therefore, the movement of the operating point can be simulated more quickly and in detail than in the first embodiment of the first invention. In the embodiment of the system shown in FIG. 32, since the prediction of the movement of the operating point can be speeded up, it is possible to deal with the sudden pressure fluctuation as shown in FIG. 33, and the sudden pressure fluctuation as shown in FIG. 34. Can be suppressed.

[Embodiment 4-2] FIG. 35 is a system diagram showing a control configuration of a blower or compressor system according to a second embodiment of the fourth invention. In FIG. 35, the same reference numerals as those in FIG. 32 denote the same parts as those in the previous embodiment,
The description is omitted. The system shown in FIG.
[Example 4-1] of FIG. 17 and FIG.
17 is carried out in combination with the embodiment of the system [Embodiment 2-1 and 2], the pressure fluctuation in the turbo blower or the compressor system in the surging state is shown in FIG.
Alternatively, high-speed and accurate prediction can be performed at more positions than the embodiment of the system in FIG. 23, and reliable suppression control can be performed.

[Embodiment 4-3] FIG. 36 is a system diagram showing a control configuration of a blower or compressor system according to a third embodiment of the fourth invention. In FIG. 36, the same reference numerals as those in FIG. 35 denote the same parts as in the previous embodiment,
The description is omitted. The system shown in FIG.
System [Example 4-1] of FIGS.
The working state of the system can be accurately predicted by carrying out in combination with the embodiment of the system [Embodiment 3-1, 2,3]. This makes it possible to set an accurate operating limit.

[Embodiment 4-4] FIG. 37 is a system diagram showing a control configuration of a blower or compressor system according to a fourth embodiment of the fourth invention. In FIG. 37, those having the same reference numerals as those in FIG. 32 are the same parts as in the previous embodiment,
The description is omitted. The system shown in FIG. 37 is an arithmetic unit 23 that can perform simulation and control in parallel.
The operation unit 23 performs simulation of the operating state and control of the flow rate control device.

In the embodiment shown in FIG. 37, in FIGS.
The system can be simplified and the operating point can be moved at a higher speed than the respective systems shown in FIG. 1 [Embodiments 1-1, 2, 3] or the embodiment of the system [Embodiment 4-1] shown in FIG. Can be measured.

[Embodiment 4-5] As a fifth embodiment of the fourth invention, in addition to the fourth embodiment of the fourth invention,
If the surging suppression control and the pressure fluctuation detection in the system are also performed by the arithmetic unit and the controller 23 connected in parallel, the equipment can be further simplified and the surging suppression control can be speeded up. You can

[Embodiment 4-6] Further, as a sixth embodiment of the fourth invention, in addition to the fifth embodiment of the fourth invention, the arithmetic unit and controller 23 coupled in parallel are provided.
By storing the operating environment of the system, storing operating parameters, and changing the operating limit, it is possible to further simplify the equipment and speed up the changing of the operating limit.

In each of the above embodiments, the pressure, the flow rate, and the temperature are detected. However, by changing the model of the simulator 11, two or one of the pressure, the flow rate, and the temperature can be detected. Thus, it is possible to obtain the same effect as that of the above embodiment. Although the pressure fluctuation predicted by the simulation is used as the determination condition, the same effect as that of the above-described embodiment can be obtained by using the flow fluctuation predicted by the simulation or both the pressure fluctuation and the flow fluctuation. it can. Further, in each of the above embodiments, the turbo blower or the compressor system has been described.
The present invention is not limited to this, and may be applied to controllers of other fluid mechanical systems.

[0077]

As described in detail above, according to the first aspect of the present invention, the pressure fluctuation and flow rate fluctuation occurring in the fluid mechanical system are predicted and the operating point is moved. It is possible to provide a control device for a fluid mechanical system and a control method thereof that can suppress flow rate fluctuations, reduce the load on the fluid mechanical system, and enable high-speed movement of the operating point.

According to the second aspect of the present invention, the control device for the fluid mechanical system can detect the pressure variation and the flow rate variation at the surging time in the fluid mechanical system and start the suppression control so that the surging can be accurately determined. And its control method can be provided. Furthermore, according to the third aspect of the present invention, the operating limit can be changed according to the operating environment of the fluid machine, and the operating limit can be changed due to deterioration of system performance or aging, so that safe operating point movement and accurate movement can be achieved. It is possible to provide a control device for a fluid mechanical system and a control method therefor capable of setting various operating limits.

Further, according to the fourth aspect of the invention, the prediction of the movement of the operating point in the fluid mechanical system can be further speeded up,
It is possible to provide a control device and a control method for a fluid mechanical system capable of suppressing sudden pressure fluctuations. That is, according to the present invention, it is possible to provide a system in which transient pressure fluctuations or flow rate fluctuations do not occur when the operating point of a blower or a compressor is moved, and the system can be operated near the surging line. it can.

[Brief description of drawings]

FIG. 1 is a system diagram showing a control configuration of a blower or compressor system according to a first embodiment of the first invention.

FIG. 2 is a diagram showing a relationship between a performance curve of a blower or a compressor and pressure and flow rate when an operating point is moved.

FIG. 3 is a diagram showing a transient pressure fluctuation when the operating point moves.

4 is a flowchart showing an operation control method in the system of FIG.

FIG. 5 is a diagram showing a change in set value of the flow rate control device.

FIG. 6 is a diagram showing a change in set value of a flow rate control device.

FIG. 7 is a diagram showing pressure fluctuations when the first embodiment of the present invention is implemented.

FIG. 8 is a diagram showing a relationship between pressure and flow rate when the first embodiment of the present invention is carried out.

FIG. 9 is a system diagram showing a control configuration of a blower or compressor system according to a second embodiment of the first invention.

10 is a flowchart showing an operation control method in the system of FIG.

FIG. 11 is a diagram showing pressure fluctuations when the second embodiment of the first invention is implemented.

FIG. 12 is a system diagram showing a control configuration of a blower or compressor system according to a third embodiment of the first invention.

13 is a flowchart showing an operation control method in the system of FIG.

FIG. 14 is a system diagram showing a control configuration of a blower or compressor system according to a fourth embodiment of the first invention.

FIG. 15 is a diagram showing a simulation interval in the control of FIG.

16 is a diagram showing a pressure fluctuation when the control shown in FIG. 14 is executed.

FIG. 17 is a system diagram showing a control configuration of a blower or compressor system according to the first embodiment of the second invention.

18 is a flowchart showing an operation control method in the system of FIG.

19 is a diagram showing movement of an operating point when operation control is executed in the system of FIG.

20 is a diagram showing pressure fluctuations during surging in the system of FIG.

FIG. 21 is a diagram showing pressure fluctuations induced by control suppression and pressure fluctuations during surging.

FIG. 22 is a diagram showing an actually detected pressure fluctuation during surging.

FIG. 23 is a system diagram showing a control configuration of a blower or compressor system according to a second embodiment of the second invention.

FIG. 24 is a system diagram showing a control configuration of a blower or compressor system according to the first embodiment of the third invention.

25 is a flowchart showing an operation control method in the system of FIG.

FIG. 26 is a diagram showing movement of an operating point when operation control is executed in the system of FIG. 24.

FIG. 27 is a diagram showing pressure fluctuations when surging does not occur.

FIG. 28 is a system diagram showing a control configuration of a blower or compressor system according to a second embodiment of the third invention.

FIG. 29 is a system diagram showing a control configuration of a blower or compressor system according to a third embodiment of the third invention.

FIG. 30 is a diagram showing changes in the performance curve and the surging line due to aging of the blower or compressor system.

FIG. 31 is a diagram showing a surging line according to an operating environment.

FIG. 32 is a system diagram showing a control configuration of the blower or compressor system according to the first embodiment of the fourth invention.

FIG. 33 is a diagram showing a sudden flow rate variation.

FIG. 34 is a diagram showing suppressed pressure fluctuations in the system of FIG. 32.

FIG. 35 is a system diagram showing a control configuration of a blower or compressor system according to a second embodiment of the fourth invention.

FIG. 36 is a system diagram showing a control configuration of a blower or compressor system according to a third embodiment of the fourth invention.

FIG. 37 is a system diagram showing a control configuration of a blower or compressor system according to a fourth embodiment of the fourth invention.

FIG. 38 is a diagram showing a surging line and a surging avoidance control line.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Turbo fan or compressor, 2 ... Flow control device, 3 ... Compressed gas consuming device, 4 ... Drive source, 5 ... Piping, 6
... Detector, 7 ... Signal processor, 8 ... Compressed gas consuming equipment operating state detector, 9 ... System operating parameter setter,
10 ... Simulator for moving operating point, 11 ... Controller for flow control device, 12 ... External load, 13 ... Storage device for changing set value of flow control device, 14 ... Simulator for changing set value of flow control device, 15 ... Operating point Pressure fluctuation simulator after movement, 16 ... Pressure fluctuation suppression control device during surging, 17 ... Pressure fluctuation determination device, 18 ... Drive source controller, 19 ... Operating environment storage device, 20 ... Operation limit storage device, 21 ... System operating parameter storage device, 22
... arithmetic unit connected in parallel, 23 ... arithmetic unit and controller connected in parallel.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Hiroshi Mukai 502 Jinritsu-cho, Tsuchiura-shi, Ibaraki Prefecture Hiritsu Manufacturing Co., Ltd.Mechanical Research Institute (72) Kyo Takatsu 603, Jinritsu-cho, Tsuchiura-shi, Ibaraki Hiritsu Manufacturing Co., Ltd. Tsuchiura factory

Claims (17)

[Claims] 1. A system comprising a fluid machine, a drive source of the fluid machine, a flow rate control device for adjusting a fluid flow rate in the system, a compressed gas consuming device on the demand side of compressed gas related to the fluid, and a fluid pipe. In a controller of a fluid mechanical system including a physical quantity detector, a drive source operating state detector, and a compressed gas consuming equipment operating state detector, a physical quantity fluctuation when the operating point of the fluid machine is moved is simulated. And a controller for controlling the set value of the flow rate control device. 2. The control device for a fluid mechanical system according to claim 1, further comprising a set value storage device for the flow rate control device. 3. The controller for the fluid mechanical system according to claim 1, further comprising a simulator for controlling a set value of the flow rate controller. 4. A control device for a fluid machine system according to claim 1, wherein the operating state of the fluid machine and the operating state of the compressed gas consuming device at a predetermined operating point are detected, and an external load fluctuation is detected. In the control method of the fluid mechanical system for controlling the flow rate control device according to the above, when a change in the external load is detected, a step of simulating a change in the physical quantity when the operating point moves, and a change in the set value of the flow rate control device are calculated. The method for controlling a fluid mechanical system is characterized in that the operating point movement is started when the pressure fluctuation is predicted to be equal to or less than a predetermined threshold value. 5. A system comprising a fluid machine, a drive source of the fluid machine, a flow rate control device for adjusting the fluid flow rate in the system, a compressed gas consuming device on the demand side of compressed gas related to the fluid, and a fluid pipe. In a controller of a fluid machine system including a physical quantity detector, a drive source operating state detector, and a compressed gas consuming apparatus operating state detector, a physical quantity variation after movement of an operating point of the fluid machine is simulated. Fluid machine system comprising: a simulator for controlling a physical quantity variation during surging; a determiner for determining a physical quantity variation in the system; and a controller for controlling a set value of the flow rate control device. Control device. 6. The control device for a fluid machine system according to claim 5, further comprising a controller for a drive source of the fluid machine. 7. A system comprising a fluid machine, a drive source for the fluid machine, a flow rate control device for adjusting a fluid flow rate in the system, a compressed gas consuming device on the demand side of compressed gas related to the fluid, and a fluid pipe. In the controller of the fluid machine system including a detector of the physical quantity in, a detector of the operating state of the drive source and a detector of the operating state of the compressed gas consuming device, a simulator simulating the operating state of the fluid machine, A control device for a fluid machine system, comprising: a storage device that stores an operating environment of a fluid machine; and a device that changes an operating limit according to the operating environment. 8. The control device for a fluid machine system according to claim 7, further comprising a device for storing an operation parameter of the fluid machine. 9. The control device for a fluid mechanical system according to claim 7, wherein a surging suppression control device, a determination device that determines a physical quantity variation in the system, and a set value of the flow rate control device are changed. A controller for a fluid mechanical system, comprising: a controller for controlling the fluid device and a controller for a drive source of the fluid device. 10. A control device for a fluid machine system according to claim 7, wherein the operating state of the fluid machine and the operating state of the compressed gas consuming device at a predetermined operating point are detected, and an external load fluctuation is detected. In the control method of the fluid mechanical system that controls the flow control device according to the above, after the data of the operating parameter of the system or the parameter of the operating environment is accumulated, the operating limit is changed without simulating the operating state. And a method for controlling a fluid mechanical system. 11. A system comprising a fluid machine, a drive source for the fluid machine, a flow rate control device for adjusting a fluid flow rate in the system, a compressed gas consuming device on the demand side of compressed gas related to the fluid, and a fluid pipe. In a controller of a fluid mechanical system including a physical quantity detector, a drive source operating state detector, and a compressed gas consuming device operating state detector, a plurality of devices are connected so as to exchange information with each other. A controller for a fluid machine system, comprising: a computing unit and a controller that controls a set value of the flow rate controller. 12. The control device for a fluid machine system according to claim 11, further comprising a surging suppressor, a determiner for determining a physical quantity variation in the system, and a controller for a drive source of the fluid machine. A control device for a characteristic fluid mechanical system. 13. A control device for a fluid machine system according to claim 12, wherein the storage device stores an operating environment of the fluid machine, and a storage device for operating parameters of the system.
A control device for a fluid mechanical system, comprising: an operating limit changing device. 14. A system comprising a fluid machine, a drive source for the fluid machine, a flow rate control device for adjusting a fluid flow rate in the system, a compressed gas consuming device on the demand side of compressed gas related to the fluid, and a fluid pipe. In a controller of a fluid mechanical system including a physical quantity detector, a drive source operating state detector, and the compressed gas consuming device operating state detector, a plurality of devices are connected so as to exchange information with each other. A controller for a fluid mechanical system, characterized in that it is provided with a computing unit. 15. A control device for a fluid mechanical system according to claim 14, wherein the operating state is simulated by using a plurality of arithmetic units coupled to each other so that information can be exchanged with each other, and A method for controlling a fluid mechanical system, characterized by performing flow rate control. 16. A flow rate control device, comprising the control device for a fluid mechanical system according to claim 14, simulating an operating state by using a plurality of arithmetic units coupled to each other so that information can be exchanged with each other. A method for controlling a fluid mechanical system, characterized in that the flow rate control and surging suppression control are performed to determine a physical quantity variation in the system. 17. A fluid machine system control device according to claim 15 or 16, wherein the fluid machine system is operated by using a plurality of computing units coupled to each other so as to exchange information with each other. A method for controlling a fluid mechanical system, comprising storing an environment, operating parameters of a system, and changing an operating limit.