JPH0510300A - Compressor equipment for plants - Google Patents

Abstract

(57) [Summary] [Object] The present invention compensates for a deterioration in the performance of a high-pressure stage compressor, prevents the deterioration of the capacity of the entire apparatus, and does not use external energy for the main driving machine of the apparatus. It is characterized by improving energy efficiency. According to the present invention, a low pressure stage of a compressor device comprising a low pressure stage and a high pressure stage is constituted by a variable static vane type axial flow compressor, and the static vanes of the axial flow compressor are automatically angled. It is characterized in that the discharge pressure or discharge air volume of the compressor device is kept constant.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a plant compressor device.

[0002]

2. Description of the Related Art Conventionally, as shown in FIG. 4, a compressor device of a plant is constituted by only a centrifugal compressor as both a low pressure stage compressor 1 and a high pressure stage compressor 2, and therefore these compressor devices are used. No. 1 intercooler 3, No. 2 intercooler 4 and No. 3 intercooler 5 installed on the However, there is a problem in that it is not possible to maintain the compression capacity of the above, and the production volume of the plant is reduced, or the compressor device is frequently cleaned.

Further, the main drive unit of the conventional compressor device is the steam turbine 7 using the external steam source from the boiler 6 or the like, or the electric motor, and there is a problem that the plant energy efficiency is not good. In addition, in FIG.
A high pressure stage compressor 2, a low pressure stage compressor 1 and a gas expander 8 are provided directly connected to the steam turbine 7, and a post cooler 1 is provided between the discharge port of the high pressure stage compressor 2 and the plant 9.
0 and the plant 9 and the gas expander 8 are connected via a control valve 11, a heater 12 and a shutoff valve 13.

A suction air filter 14 and a suction throttle valve 15 are provided at the suction port of the low-pressure compressor 1, while steam from the boiler 6 passes through a main steam valve 16 and a steam control valve 17. The steam introduced into the steam turbine 7 and discharged from the steam turbine 7 is returned to the boiler 6 via the condenser 18 and the condensate pump 19 and circulated.

As described above, in the case of the conventional plant compressor apparatus which is composed of only the centrifugal compressor, if the compressor rotational speed is increased with respect to the performance deterioration of the high-pressure stage compressor 2, it will be somewhat increased. However, the amount of economically designed compressor device is generally only a few percent, and further deterioration of performance cannot be coped with. It is also inefficient.

As described above, FIG. 5 shows a compressor performance curve of the conventional compressor device for controlling the rotation speed, and the compressor performance at the time of cleaning is shown by a solid line A in the figure.
For example, the compressor performance at the time of pollution when it decreases by about 5% is shown by broken lines B and C in the figure. In other words, if the compressor rotation speed remains constant, the discharge flow rate decreases by about 5%, so it is necessary to increase the rotation speed by several percent in order to compensate for this.

However, since this margin of the number of rotations is not so large in view of economical design of the compressor,
It is impossible to deal with the performance deterioration of 4 to 5% or more.
Further, in general, the efficiency of the compressor is greatly reduced when the speed is increased. In addition, in the conventional compressor device in which the main drive is operated at a constant speed by an electric motor, it is possible to perform constant discharge pressure control by compressor suction throttle valve control in anticipation of performance degradation in advance, but in this case, However, there is a problem that the suction throttle loss is large and the energy efficiency is not good.

That is, when the compressor blades are preliminarily operated in a suction throttle state in consideration of when the blades of the compressor are contaminated, the solid line A shows the compressor performance during cleaning at a constant rotation speed in the diagram of FIG. The compressor performance at the time of contamination is shown by the broken line B, and the compressor performance in the throttled state is shown by the alternate long and short dash line D. The compressor device is made quite large, and the compressor is reduced by 5 to 10% during cleaning. It must be used in this condition, resulting in a significant loss of power to the compressor system.

[0009]

SUMMARY OF THE INVENTION The present invention has been made in order to solve the problems of the above-mentioned conventional compressor device. When the high-pressure stage compressor is contaminated and its performance deteriorates, the automatic A compressor unit for a plant, which can compensate for it, prevent the deterioration of the capacity of the compressor unit as a whole, and maximize the plant energy efficiency without using external energy for the main drive unit of the compressor unit. It is intended to provide.

[0010]

That is, the compressor apparatus for a plant of the present invention comprises a variable static vane type axial flow compressor for the low pressure stage of a compressor comprising a low pressure stage and a high pressure stage, and When the performance deteriorates due to the occurrence of stage contamination, the stator vanes of the axial flow compressor are automatically angled through the automatic variable stator control mechanism, etc., and the discharge pressure or the discharge air volume of the compressor device is held constant. In this case, the deterioration of the performance of the high pressure stage can be automatically compensated while the rotation speed of the compressor remains constant.

It is also desirable that a low-pressure mixed steam turbine utilizing low-pressure saturated steam generated in the plant is used as the main drive unit of the above-mentioned compressor device.
In this case, providing a drain separator on the steam inlet pipe of the low-pressure air-fuel mixture steam turbine is a preferable configuration in order to prevent an obstacle due to the drain.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a system diagram of a compressor device for a plant according to the present invention. The compressor device of this embodiment has substantially the same configuration as that of the conventional system shown in FIG. 4, and the same parts are designated by the same part numbers in FIGS. 1 and 4, and the description thereof is given here. Is omitted.

First, in the compressor device of the present invention, of the low-pressure stage compressor 1A and the high-pressure stage compressor 2, the low-pressure stage compressor 1A is composed of a variable stator vane type axial flow compressor, The variable operation of the stationary blade is hydraulically operated by the variable blade operation cylinder 20. Therefore, No. 1 intercooler 3, N
o.2 The high-pressure stage compressor 2 (for example, the centrifugal compressor in this embodiment) after the intercooling by the intercooler 4 and the No. 3 intercooler 5 is contaminated, and the performance of the high-pressure stage compressor 2 is reduced. The reduced amount is automatically compensated for the variable stator vane of the low-pressure stage compressor 1A by an automatic variable stator vane control mechanism or the like while keeping the number of revolutions of the compressor device constant, thereby preventing the deterioration of the capacity of the entire compressor device. I am trying.

That is, the stator vanes of the axial flow compressor, which is the low-pressure stage compressor 1A, are automatically driven by a stator vane variable mechanism controller or the like in response to a signal from either the compressor discharge pressure regulator or the discharge air flow regulator. It is possible to change the angle and maintain the discharge pressure or the discharge air volume constant. As described above, the performance curve of the compressor when the low pressure stage compressor 1A is the variable vane axial flow compressor is as shown in Fig. 2. By varying the vane angle with respect to the design air volume, A blow operation range of ± 20% or more can be obtained.

Therefore, even if the high-pressure compressor 2 becomes dirty and the performance of the compressor deteriorates, it is possible to maintain the predetermined air volume without difficulty by changing the angle of the vane of the low-pressure compressor 1A. In addition, a solid line A in the drawing shows a state at the time of cleaning, and a broken line B shows a state at the time of contamination, and the performance curves at the vane blade angles of −10 °, −5 °, 0 °, + 5 °, + 10 °, respectively. Is shown.

Next, in the compressor device according to the present invention, for example, three types of low-pressure saturated steam generated in the plant 9 in the main drive machine are respectively provided with the drain separator 22 and the control valve 23. A low-pressure mixed steam turbine 7A (a two-stage mixed steam turbine in this embodiment) that operates by using the saturated steam that is sent by the interposed steam inlet pipe 28 is adopted, thereby maximizing plant energy efficiency. I try to raise it.

On the other hand, when low-pressure saturated steam is used in the plant compressor device, the steam inlet pipe 28 of the turbine is used.
The operation of the turbine is often hindered by the drain generated in the drain separator 2 as described above.
Since 2 is provided in the inlet pipe 28, it is possible to prevent an obstacle due to drainage. In FIG. 1, the low-pressure mixed steam turbine 7A and the high-pressure stage compressor 2 are connected by a speed increasing gear 21, and a control valve 11, a front heater 12A and a cutoff are provided from the plant 9 to the gas expander 8. The gas expander 8 is communicated with the plant 9 via the intermediate heater 24 and the extraction control valve 25.

Next, FIG. 3 is a control system diagram of the compressor device of FIG. 1, in which FT is a flow rate transmitter, TT is a temperature converter, PT is a pressure transmitter, and FY is a temperature / pressure compensator. , FIC is a constant air flow controller, and PIC is a constant air pressure controller. In the figure, 30 is a Venturi tube, and a changeover switch 31 is provided between the constant air flow rate controller FIC and the constant wind pressure controller PIC, and the current passing through this changeover switch 31 causes the electric oil converter (E / H) 32, the hydraulic pressure from the hydraulic unit 34 and the oil pump 33 is switched to operate the variable stationary blade operating cylinder 20 of the low-pressure stage compressor 1A.

[0019]

As described above, according to the compressor apparatus for a plant of the present invention, even if the blades of the compressor stage after the intermediate cooling are deteriorated in performance due to dirt or the like, the number of rotations of the compressor is reduced. There is an effect that the deterioration of the performance of the compressor as a whole can be prevented by automatically compensating for the deterioration of the performance at a low pressure stage while keeping it constant.

Further, in the compressor device of the present invention, since the low-pressure saturated steam generated in the plant is used as the power source of the main driving device, the effect that the energy efficiency of the plant can be maximized is obtained. is there. Further, since the drain separator is provided in the inlet pipe of the low-pressure saturated steam to the mixed steam turbine, there is also an advantage that the trouble due to the drain during the operation of the turbine can be prevented.

[0021]

[Brief description of drawings]

FIG. 1 is a system system diagram of a compressor device for a plant according to the present invention.

FIG. 2 is a compressor performance curve diagram of the compressor device according to the present invention.

FIG. 3 is a control system diagram of a compressor device according to the present invention.

FIG. 4 is a system diagram of a conventional compressor device.

FIG. 5 is a compressor performance curve diagram in the case of a conventional rotation speed control compressor.

FIG. 6 is a compressor performance curve diagram in the case of conventional rotation speed constant and suction throttle control.

[Explanation of symbols]

1A low pressure stage compressor 2 High pressure stage compressor 7A Low pressure mixed steam turbine 9 plants 20 Variable vane operating cylinder 22 Drain separator 28 Steam inlet pipe

Continued front page    (72) Inventor Toshiaki Masaoka             6-1-2 Waki, Waki-cho, Kuga-gun, Yamaguchi Prefecture             Mitsui Petrochemical Industry Co., Ltd. (72) Inventor Toko Abiko             6-1-2 Waki, Waki-cho, Kuga-gun, Yamaguchi Prefecture             Mitsui Petrochemical Industry Co., Ltd.

Claims (3)

[Claims] 1. A low pressure stage of a compressor device comprising a low pressure stage and a high pressure stage is constituted by a variable static vane type axial flow compressor, and the static vanes of the axial flow compressor are automatically changed in angle to produce a compressor. A compressor device for a plant that maintains a constant discharge pressure or discharge air volume. 2. The compressor device for a plant according to claim 1, wherein a low-pressure mixed steam turbine utilizing low-pressure saturated steam generated in the plant is used as a main drive device of the compressor device. 3. The compressor device for a plant according to claim 2, wherein a drain separator is provided in the steam inlet pipe of the low-pressure mixed steam turbine.