JP2831320B2 - Gas turbine driven pump - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

TECHNICAL FIELD The present invention relates to, for example,
The present invention relates to a centrifugal pump, a centrifugal pump, a mixed flow pump, an axial pump, and the like widely used in nuclear power plants, thermal power plants, steelworks, chemical factories, and the like, and relates to a gas turbine drive pump using a gas turbine as a prime mover.

[0002]

2. Description of the Related Art FIG. 5 shows an example of a conventional gas turbine drive pump. This is one in which a gas turbine 2 is disposed above a spiral pump 1 which is an example of a pump, and a pump drive shaft 3 connected to an impeller 1a of the spiral pump 1 extends in a vertical direction. Gas turbine 2
The gas generator 2a and the output part 2b containing the output turbine are arranged concentrically and horizontally, and the output shaft 4a extending horizontally from the output part 2b is connected to the pump drive shaft 3 via the bevel gear reducer 5. Linked and linked.

In the above configuration, the gas turbine 2
Sucks air into the gas generator 2a, compresses the sucked air, burns fuel with the compressed air to generate high-temperature and high-pressure gas, and uses the high-temperature and high-pressure gas to drive the output turbine in the output section 2b at high speed. The impeller 1a is rotated via the output shaft 4a, the bevel gear reducer 5, and the pump drive shaft 3. Thereby, the suction port 6a of the centrifugal pump 1
, The liquid is sucked into the vortex pump chamber 6 in the direction of arrow A,
The sucked liquid receives centrifugal force by the impeller 1a and is fed in a direction of arrow B from the outlet 6b.

[0004]

In the conventional configuration described above, the use state of the centrifugal pump 1 includes a standby operation, which is a light load operation, in addition to the normal operation. The load is not always constant. That is, when the rotational speed of the centrifugal pump 1 is decelerated or accelerated to change the pump operating point to continue the stable pump continuous operation, the fluctuation range of the load increases.

However, the gas turbine 2 is a high-speed rotation type prime mover, and it is not advisable to continue the low-load operation at the lower limit of the rotation speed in terms of the operation efficiency. In other words, continuing to operate the gas turbine 2 in a low-speed state with low energy efficiency, for example, when the rated output of the gas turbine 2 is 以下 or less of the rated output is sufficient, continuously operating the gas turbine with a large rated output results in a large energy loss. .

SUMMARY OF THE INVENTION The present invention solves the above-mentioned problems, and can increase the number of gas turbines, for example, two or more, and shorten the total length of each gas turbine.
Moreover, it is an object of the present invention to provide a gas turbine drive pump capable of reducing the occupation range on a plane.

[0007]

In order to solve the above-mentioned problems, a gas turbine drive pump according to the present invention is arranged such that an output portion having a built-in output turbine is arranged vertically with respect to a gas generator arranged horizontally. A gas turbine drive pump that drives the pump using a two-shaft gas turbine that has been arranged, a plurality of gas turbines are arranged in parallel in upper and lower positions, and the output shaft of the upper gas turbine is directed downward. , The output shaft of the lower gas turbine is arranged upward, and the output shaft of each gas turbine and the input shaft of the speed reducer, which are positioned in parallel, are linked and connected via a parallel gear unit, The pump drive shaft is connected to the output shaft.

Further, the output shafts of a plurality of gas turbines are connected to a parallel gear unit via a clutch. In addition, each intake duct of the plurality of gas turbines is collectively connected to one main intake duct, and each exhaust duct is collectively connected to one main exhaust duct.

In the above configuration, since the upper and lower gas turbines are positioned so as to overlap each other on a plane, arranging a plurality of gas turbines does not increase the occupied area.

[0010] Each clutch is operated in accordance with the operating state of the pump and load fluctuations to control the input of each gas turbine to the reduction gear. As a result, the number of gas turbines contributing to the driving of the pump is adjusted, and only the necessary gas turbines are controlled in rotation speed to maintain a stable operation state. It is possible to follow a load change that shifts to operation in multiple stages. Also, since the input to the speed reducer is the sum of the output of each gas turbine with the clutch connected,
It can also cope with high output operation such as high head operation and low head large water flow operation of the pump.

By connecting each intake duct of a plurality of gas turbines to one main intake duct and connecting each exhaust duct to one main exhaust duct, it is possible to save duct space. .

[0012]

Embodiments of the present invention will be described below with reference to the drawings. Since the configuration of the main part of the pump is the same as that described in FIG. 5, the same reference numerals are given and the description is omitted. In FIGS. 1 to 4, a plurality of gas turbines 20 for driving the spiral pump 1 are provided above a pump drive shaft 3 extending in a vertical direction of the spiral pump 1.
0,300 (two in this embodiment) are arranged in parallel at the upper and lower positions of the steel plate base 7.

Each of the gas turbines 200, 300 has a gas generator 200a, 300a disposed horizontally, and output turbines 214, 314 bent perpendicularly to the gas generators 200a, 300a and disposed vertically.
Output units 200b, 300b incorporating (described in detail below)
And

The upper gas turbine 200 has an output section 200.
b, the output shaft 214a faces downward, and in the lower gas turbine 300, the output shaft 314a of the output section 300b faces upward. Each of the gas turbines 200 and 300 is connected to the pump drive shaft 3 via a parallel gear unit 400 having a plurality of input shafts (a pair in this embodiment) and a speed reducer 8 connected to an output shaft 401 of the parallel gear unit 400. The output shafts 214a and 314a of the gas turbines 200 and 300 are connected to each other via the clutches 9 and 9, respectively.
And the output shaft 8 a of the speed reducer 8 is connected to the pump drive shaft 3.

The parallel gear unit 400 includes an output shaft 401
And a pair of driven gears 404 and 404 mounted on the input shafts 402 and 402. The driven gears 404 and 404 are driven gears at opposing positions. 403 is engaged.

As shown in FIGS. 3 and 4, the gas turbine 2
Reference numerals 00 and 300 denote two-shaft gas turbines, and gas generators 200 a and 300 a are fixed on bases 210 and 310 via support frames 211 and 311, respectively, and air sucked from intake ports 212 and 312. Is compressed into a combustion chamber by a compressor, and high-temperature and high-pressure gas generated by burning fuel in the combustion chamber is discharged from the exhaust ports 213 and 313. (Not shown) is driven to rotate.

The output sections 200b and 300b pass the high-temperature and high-pressure gas discharged from the gas generators 200a and 300a through the scroll flow passage SF in the scroll casings 215 and 315 to form the moving blades 2 of the output turbines 214 and 314.
The output shafts 214a and 314a are rotated at a high speed by ejecting them toward the 14b and 314b.

The scroll casings 215, 315
The exhaust ports 213 and 313 of the gas generators 200a and 300a are arranged concentrically with the output shafts 214a and 314a.
Gutter portions 215a, 315a communicating with the rotor blades 215a, 315a, and rotor blades 214b, 3
It has annular exhaust ports 215b and 315b opposed to 14b, and changes the direction of the high-temperature and high-pressure gas discharged from the gas generators 200a and 300a to a right angle.

Reference numeral 216 denotes a cylindrical exhaust duct connected to the annular exhaust port 215b of the school casing 215.
Reference numeral 6 denotes a scroll-shaped exhaust duct connected to the annular exhaust ports 215b and 315b of the scroll casings 215 and 315.
5,315, the output frame 21
A bearing device for rotatably supporting 4,314 is incorporated. 218, 318 are scroll casings 215, 3
15 is a fixing member for fixing the base 15 to the bases 210 and 310.
219, 319 are gas generators 200a, 300
a of each of the intake ducts 21 of the gas turbines 200 and 300.
9, 319 are collectively connected to one main intake duct 11, and each exhaust duct 216, 316 is collectively connected to one main exhaust duct 12.

In the above configuration, each gas turbine 2
In 00 and 300, the gas generators 200a and 300
The high-temperature and high-pressure gas generated in the exhaust ports 213 and 31
3 and flows out into the scroll flow channel SF in the horizontal direction. The high-temperature and high-pressure gas that has flowed into the scroll passage SF spreads annularly along the inner surface of the scroll passage SF, and changes its direction to a right angle to change the output turbine 21.
4, 314 are ejected to the rotor blades 214b, 314b to rotate the output shafts 214a, 314a at high speed. Each of the gas turbines 200 and 300 transmits the output to the pump drive shaft 3 via the clutches 9 and 9 and the speed reducer 8, and rotates the impeller 1a via the pump drive shaft 3. As a result, liquid is sucked in the direction of arrow A from the suction port 6a of the centrifugal pump 1 into the spiral pump chamber 6, and the sucked liquid is subjected to centrifugal force by the impeller 1a to move in the direction of arrow B from the discharge port 6b. Pumped.

At this time, the input of each gas turbine 200, 300 to the speed reducer 8 is controlled by operating each clutch 9, 9 in accordance with the operating state of the centrifugal pump 1 and the load fluctuation. Thereby, the number of the gas turbines 200 and 300 contributing to the driving of the centrifugal pump 1 is adjusted, and the number of the gas turbines 200 and 300 is reduced to one as needed, and the rotation speed control is performed, so that the gas turbines 200 and 300 are stabilized. It is possible to follow the load fluctuation of the centrifugal pump 1 in multiple stages while maintaining the operation state.

Since the input to the speed reducer 8 is the sum of the outputs of the gas turbines 200 and 300 to which the clutches 9 and 9 are connected, the pump operates in a high-output operation such as a high-head operation or a low-head large-water operation. It can also respond when performing.

Each of the gas turbines 200 and 300 includes a gas generator 200a, 300a and an output turbine 214, 3
Since the output units 200b and 300b incorporating the P.14 are arranged at right angles to each other, the total length can be shortened, and the occupied area can be reduced by the shortened length. Therefore, a space for disposing a plurality of gas turbines 200 and 300 can be easily secured even in an existing pump station.

The upper and lower gas turbines 200 and 300
Are located so as to overlap each other on a plane, so that even when the plurality of gas turbines 200 and 300 are arranged, the occupied area does not increase. Further, since each intake duct 219, 319 of each gas turbine 200, 300 is collectively connected to one main intake duct 11, each exhaust duct 216, 316 is collectively connected to one main exhaust duct 12. Therefore, the duct space can be saved.

[0025]

As described above, according to the present invention, since the upper and lower gas turbines are positioned so as to overlap each other on a plane, the arrangement of a plurality of gas turbines does not increase the occupied area. By operating the clutch, the number of gas turbines contributing to the drive of the pump is adjusted, and by controlling the rotation speed of each necessary gas turbine, the operating state of the pump is maintained while maintaining a stable operating state. In addition, the output of the prime mover can be adjusted in multiple stages according to the load fluctuation, and the driving force of the pump can be finely adjusted in a wide range. By connecting each intake duct of a plurality of gas turbines to one main intake duct and collectively connecting each exhaust duct to one main exhaust duct, it is possible to save duct space.

[Brief description of the drawings]

FIG. 1 is a schematic diagram showing a gas turbine drive pump according to an embodiment of the present invention.

FIG. 2 is a schematic diagram showing a connection structure between a gas turbine and a pump according to the embodiment.

FIG. 3 is a side view of the upper gas turbine in the embodiment.

FIG. 4 is a side view of a lower gas turbine in the embodiment.

FIG. 5 is a schematic view of a conventional gas turbine drive pump.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Centrifugal pump (pump) 8 Reduction gear 9 Clutch 200, 300 Gas turbine 214a, 314a Output shaft 400 Parallel gear unit

──────────────────────────────────────────────────続 き Continuation of front page (72) Inventor Takafumi Nakagawa 3-1-1, Higashikawasaki-cho, Chuo-ku, Kobe-shi, Hyogo Kawasaki Heavy Industries, Ltd. Kobe Plant (56) References JP-A-5-321876 (JP, A JP-A-7-102995 (JP, A) JP-A-4-76231 (JP, A) (58) Fields investigated (Int. Cl. ⁶ , DB name) F04D 25/02 F02C 7/36

Claims (3)

(57) [Claims] 1. A gas turbine drive pump in which a pump is driven by using a two-shaft gas turbine in which an output section having a built-in output turbine is arranged vertically with respect to a gas generator arranged in a horizontal direction. A plurality of gas turbines are arranged in parallel at the upper and lower positions, the output shaft of the upper gas turbine is arranged downward, the output shaft of the lower gas turbine is arranged upward, and An output shaft of each gas turbine and an input shaft of a speed reducer, which are linked to each other via a parallel gear unit, and a pump drive shaft is connected to an output shaft of the speed reducer. 2. The gas turbine drive pump according to claim 1, wherein each of output shafts of the plurality of gas turbines is connected to a parallel gear unit via a clutch. 3. The gas turbine according to claim 1, wherein each intake duct of the plurality of gas turbines is collectively connected to one main intake duct, and each exhaust duct is collectively connected to one main exhaust duct. A gas turbine driven pump as described.