JPH02199230A - Biaxial gas turbine - Google Patents

Abstract

PURPOSE:To make it possible to change an output shaft in rotating direction with ease by constituting an intermediate shaft to be capable of being moved, on which both the first gear driven by a power turbine and the second gear meshed with the third gear of the output shaft are stationarily fitted. CONSTITUTION:When reversely rotated, a high speed pinion gear 40 rotating integrally with a power turbine shaft 15 makes an output shaft 17 rotate reversely by way of the first gear 44, an intermediate shaft 45, the second gear 49, an idler gear 50 and the third gear 54. In this case, the positional relation thetaamong the gears 49, 50, and 54 is set to be -20 deg.<=theta<=100 deg. so that the idler gear 50 is not subjected to excessive force. In the second place, when the output shaft 17 is normally rotated, the bearing position of the intermediate shaft 45 is relocated to the other positions pre-determined in advance of a gear box main body and a gear box cover so that the rotation of a high speed pinion gear 40 is transmitted to the output shaft 17 by way of the first gear 44, the intermediate shaft 45, the second gear 49 and the third gear 54. In this case, the idler gear 50 is removed. Thus, the output shaft can thereby be easily changed in the rotational direction.

Description

[Detailed description of the invention] (Industrial application field) The present invention relates to a two-shaft gas turbine.

(Prior Art) In conventional two-shaft gas turbines, the rotation direction of the output shaft of the reducer is determined at the design stage and cannot be changed at the assembly stage.

(Problems to be Solved by the Invention) A two-shaft gas turbine is not a constant-speed engine like a single-shaft gas turbine, but is a variable-speed engine. etc., it is very suitable for general industrial machinery. However, when driving, for example, a pump or the like with a two-shaft gas turbine, the required rotational direction of the output shaft is not uniquely determined, but is determined depending on the equipment such as the pump. Therefore, if the rotational direction of the output shaft of the gas turbine is constant as in the past, two types of gas turbines with different rotational directions must be designed and manufactured, which is poor in mass production.

(Means for Solving the Problems) In order to solve the above problems, the two-shaft gas turbine of the present invention includes a first gear driven by a power turbine shaft in a gear box of a reduction gear, and a first gear driven by a power turbine shaft. a second gear fixed to the intermediate shaft; and a third gear fixed to the output shaft and meshing with the second gear. When the shaft is configured to be movable, and an idler gear is detachably interposed between the second gear and the third gear when the intermediate shaft is moved, and the intermediate shaft is moved. A straight line connecting the center of the second gear and the center of the idler gear is drawn, and a straight line connecting the center of the idler gear and the third gear is M, and the line formed by the straight line M is The angle θ is set to −20″≦θ≦100° with the straight line as a reference and the rotation direction of the idler gear as the positive direction.

(Operation) During reverse rotation, the rotation of the power turbine shaft is transmitted to the output shaft via the first gear, intermediate shaft, second gear, idler gear, and third gear. During forward rotation, the rotation of the power turbine shaft is transmitted to the output shaft via the first gear, the intermediate shaft, the second gear, and the third gear, so that the output shaft rotates in the opposite direction to that during reverse rotation. Rotate.

(Example) Hereinafter, an example of the present invention will be described based on FIGS. 1 to 6.

FIG. 6 is a front view of a two-shaft gas turbine according to an embodiment of the present invention. Reference numeral 1 designates a platform that also serves as an oil pan for storing lubricating oil. a gas generator 2 that generates high-temperature, high-pressure combustion gas; an output turbine 3 that extracts rotational power from the combustion gas generated by the gas generator 2; and an output turbine 3 that decelerates the rotational power extracted by the output turbine 3 to a predetermined rotation speed. The reduction gears 4 are arranged in this order from the left side to the right side. An auxiliary equipment gear box 5 is attached to the left side surface of the gas generator 2, which accommodates bearings, gears, etc. of various auxiliary equipment.

FIG. 1 is a longitudinal sectional front view of a two-shaft gas turbine according to an embodiment of the present invention. By mixing with fuel and burning it, high temperature and
A combustor 8 that produces high-pressure combustion gas, a high-pressure turbine rotor 9 that is rotationally driven by the combustion gas and rotates the impeller 7, and a high-pressure turbine rotor 9 that is located downstream of the high-pressure turbine rotor 9 and operates in the same way as the high-pressure turbine rotor 9. The turbine is equipped with a low-pressure turbine rotor 10 and the like. The output turbine 3 includes a power turbine rotor 12 located downstream of the low-pressure turbine rotor 10 and rotated by combustion gas, and a power turbine rotor 12 that is located downstream of the low-pressure turbine rotor 10 and rotates the combustion gas, that is, the exhaust gas after driving the power turbine rotor 12, without generating a vortex. It includes an exhaust differential user 13 for deceleration, an exhaust duct 14 for releasing exhaust gas, a power turbine shaft 15 that rotates integrally with the power turbine rotor 12, and the like. The reducer 4 includes an output shaft 17 and a plurality of gears that reduce the rotational power of the power turbine shaft 15 to a predetermined rotational speed and transmit it to the output shaft 17. Inside the auxiliary equipment gear box 5, a plurality of gears and the like for driving various auxiliary equipment such as the fuel pump 19 and the cover actuator 20 are arranged.

The outer shell of the reducer 4 is constituted by a gear box 22, and the gear box 22 is connected to the pedestal 1 by bolts (not shown) that are screwed into a plurality of bolt holes 23 screwed into the top wall of the pedestal 1. is firmly fixed. The outer shell of gas generator 2 is
A main casing 25 that covers the high-pressure turbine rotor 9 and the low-pressure turbine rotor 10, an intake housing 26 that covers the impeller 7, and a combustor outer cylinder 27 that covers the combustor 8.
The combustor outer cylinder 27 is fixed to the main casing 25 with a plurality of bolts. The main casing 25 and the gear box 22 are connected by a number of bolts via a semi-cylindrical support 29 in which a number of holes are formed.
It is located on the inner circumference side. The lower end of a wide steel plate 32 as a support member is fixed to the left side of the base 1 by a plurality of bolts 33, and the upper end of the steel plate 32 is fixed to the lower end of the intake housing 26 and the main casing 25 by a plurality of bolts 34. It is fixed to the part.

That is, the steel plate 32 is arranged in a direction perpendicular to the turbine axis direction, and the high temperature section 35 consisting of the gas generator 2 and the output turbine 3 is elastically supported by the steel plate 32 so that it can be displaced only in the turbine axis direction. has been done.

The gear box 22 of the reducer 4 includes a gear box body 38 and a gear box body 38, as shown in detail in FIG.
A gear box cover 39 is bolted to the gear box cover 39. The right end of the power turbine shaft 15 penetrates into the gear box 22, and a high speed pinion gear 40 is spline-fitted to the outer periphery. high speed pinion gear 40
The outer periphery of both ends is rotatably supported by bearings 41 and 42, and teeth 43 are formed on the outer periphery of the central portion in the axial direction. The teeth 43 of the high-speed pinion gear 40 mesh with a first gear 44, and the first gear 44 is fitted and fixed to the outer periphery of the intermediate shaft 45 near the left end. The intermediate shaft 45 is rotatably supported by bearings 46 and 47 on the outer periphery of both ends.
The bearing 46 is housed in a recess on the inner surface of the gear box body 38, and the bearing 47 is housed in four parts on the inner surface of the gear box cover 39. A second gear 49 is formed on the outer periphery of the intermediate shaft 45 near the right end, and the second gear 49 meshes with the idler gear 50 . The idler gear 50 is rotatably supported on the inner periphery of both ends by bearings 52 and 53 that are fitted and fixed to the outer periphery of both ends of a shaft 51 bolted to the inner surface of the gear box cover 39. It meshes with 54.

The third gear 54 has a flange 5 integrally formed on the left end of the output shaft 17 which is rotatably supported by bearings 55 and 56.
It is bolted to the outer periphery of 7.

In addition, in Figures 1 and 2, the vertical positional relationship of each gear is shown slightly different from the actual one to make it easier to understand, and the actual position is as shown in Figure 3. It is a relationship.

The positional relationship between the second gear 49, the idler gear 50, and the third gear 54 is as shown in FIG. When the straight line connecting the center of the gear 50 and the center of the third gear 54 is M, and the angle θ between the straight line and the straight line M is based on the straight line and the rotation direction of the idler gear 50 is the positive direction, -20'' ≦θ≦ ioo'.

As shown in FIG. 2, the gear box 22 of the reducer 4 is formed with a lubricating oil supply passage 59 for supplying lubricating oil to each gear, bearing, etc. in the gear box 22. 59 is supplied with lubricating oil stored in the platform 1 by a lubricating oil pump (not shown). The lubricating oil supply passage 59 includes a lubricating oil supply hole 60a formed in the gear box body 38 and a lubricating oil supply hole 60 formed in the gear box cover 39.
b, and these lubricating oil supply holes 60a.

60b is the first gear 44, the second gear 49, the bearing 46.
This is for supplying lubricating oil to 47 etc. A plurality of first oil injection nozzles 61 for injecting lubricating oil to the bearings 46 are screwed into the gear box main body 38, and the inner surface of the gear box main body 38 is for injecting lubricating oil to the bearings 46. A second oil injection nozzle 62 for this purpose is bolted. Lubricant oil is supplied to the first oil injection nozzle 61 from a lubricant oil supply hole 60a through a hole 63 formed in the gear box body 38 and the vibro 4, and lubricant oil is supplied to the second oil injection nozzle 62. Lubricating oil is supplied from the hole 60a through a hole 65 formed in the gear box body 38. A third oil injection nozzle 67 having a plurality of injection ports for injecting lubricating oil to the bearing 47 is bolted to the outer surface of the gear box cover 39, and a second oil injection nozzle 67 is bolted to the inner surface of the gear box cover 39. A fourth oil injection nozzle 68 having a plurality of injection ports for injecting lubricating oil to the gear 49 is bolted. Lubricating oil is supplied to the third oil injection nozzle 67 from the lubricating oil supply hole 60b through six holes formed in the gear box cover 39, and to the fourth oil injection nozzle 68 from the lubricating oil supply hole 60b. Hole 7 formed in gear box cover 39
Lubricating oil is supplied through 0.

The above state indicates a reverse rotation state of the output shaft 17, and by changing the position of the intermediate shaft 45, the output shaft 17 can be brought into a forward rotation state. That is, a bearing 46 is provided on the inner surface of the gear box body 38 and the gear box cover 39.
, 47 are provided at one other location in addition to the position shown in FIG.
7 and supporting the intermediate shaft 45, the third
As shown by imaginary lines in the figure, the four second gears and the third gear 54 directly mesh with each other. In this case, the idler gear 50 is unnecessary and is therefore removed together with the shaft 51. Also the fifth
As shown in the figure, the first oil injection nozzle 61 and the third oil injection nozzle 67 are moved to positions corresponding to the changed intermediate shaft 45, and the first oil injection nozzle 61 is placed in the original position. Instead, a blind plug 72 is screwed together, and a blind cover 73 is bolted in place of the third oil injection nozzle 67. Also, the second oil injection nozzle 62
And the fourth oil injection nozzle 68 changes the direction of the injection port. That is, as shown in FIG. 3, the lubricating oil supply holes 60a and 60b are formed at positions that are equal distances from both the axis of the intermediate shaft 45 during reverse rotation and the axis of the intermediate shaft 45 during forward rotation. Therefore, the position of the intermediate shaft 45 can be changed simply by changing the attachment of the first oil injection nozzle 61 and the third oil injection nozzle 67 or changing the orientation of the second oil injection nozzle 62 and the fourth oil injection nozzle 68. can be dealt with.

Next, the operation will be explained. During reverse rotation, the rotation of the high-speed pinion gear 40, which rotates integrally with the power turbine shaft 15,
The signal is transmitted to the output shaft 17 via the first gear 44 , intermediate shaft 45 , second gear 49 , idler gear 50 , and third gear 54 . During forward rotation, the rotation of the high-speed pinion gear 40 that rotates together with the power turbine shaft 15 is transmitted to the output shaft 17 via the first gear 44, the intermediate shaft 45, the second gear 49, and the third gear 54. Therefore, the output shaft 17
rotates in the opposite direction when rotating in reverse. During reverse rotation, the positional relationship between the second gear 49, idler gear 50, and third gear 54 was set to satisfy -20°≦θ≦100°, so as shown in Fig. 4. , the resultant force Fh of the gear reaction force Fa acting on the center of the idler gear 50
(F≦Pa.

When changing from the reverse rotation state to the normal rotation state, the intermediate shaft 45 is changed in position together with the bearings 46, 47, etc., and the idler gear 50 is removed together with the shaft 51 etc. In addition, the positions of the first oil injection nozzle 61 and the third oil injection nozzle 67, the blind plug 72, and the blind cover 73 are exchanged, and the orientation of the injection ports of the second oil injection nozzle 62 and the fourth oil injection nozzle 68 is changed. change. When changing from the normal rotation state to the reverse rotation state, the operation is performed in the reverse order to the above.

In this way, the rotation direction of the output shaft 17 can be easily changed during assembly or after production is completed, so there is no need to design and manufacture two types of two-shaft gas turbines with different rotation directions, which improves mass production. It is possible to reduce manufacturing costs by improving the performance. In addition, since the resultant force F of the gear reaction force Pa applied to the center of the idler gear 50 can be made smaller than the gear reaction force Pa, an excessive force is not applied to the idler gear 50, and smooth power transmission can be maintained well. At the same time, wear and damage to the idler gear 50 and the like can be favorably reduced. In addition, the lubricating oil supply holes 60a and 60b are connected to the intermediate shaft 4 during forward rotation.
5 and the axis of the intermediate shaft 45 during reverse rotation, the attachment of the first oil injection nozzle 61 and the third oil injection nozzle 67 may be changed or It is possible to change the position of the intermediate shaft 45 by simply changing the orientation of the oil injection nozzle 62 and the fourth oil injection nozzle 68, making the work easier and reducing costs by sharing parts. .

(Effects of the Invention) As explained above, according to the present invention, the rotation direction of the output shaft can be easily changed during assembly or even after production is completed, so two types of two-shaft gas turbines with different rotation directions can be used. There is no need for designing and manufacturing, and manufacturing costs can be reduced by improving mass productivity. Also, when rotating in reverse,
Since the positional relationship between the second gear, idler gear, and gear ff13 is set to satisfy -20@≦θ≦100@, the resultant force F of the gear reaction force Pa applied to the center of the idler gear is Since the force Pa can be made smaller than the force Pa, an excessive force is not applied to the idler gear, and smooth power transmission can be maintained well, and at the same time, wear and damage to the idler gear etc. can be favorably reduced.

In addition, if the lubricating oil supply hole is placed at a position equidistant from both the axis of the intermediate shaft during forward rotation and the axis of the intermediate shaft during reverse rotation, the attachment and orientation of the oil injection nozzle can be changed. You can easily change the position of the intermediate shaft by simply changing the position of the intermediate shaft.
By sharing parts, costs can be reduced.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional front view of a two-shaft gas turbine according to an embodiment of the present invention, FIG. 2 is an enlarged sectional view of the reduction gear part of the two-shaft gas turbine, and FIGS. 3 and 4 are the reduction gear parts of the same two-shaft gas turbine. Fig. 5 is a cross-sectional view of the main parts of the gear box during forward rotation of the reducer, and Fig. 6 is a front view of a two-shaft gas turbine according to an embodiment of the present invention. . 4... Reducer, 15... Power turbine shaft, 17...
...output shaft, 22...gear box, 44...first
gear, 45...intermediate shaft, 46.47...bearing, 4
9... Second gear, 50... Idler gear, 54...
...Third gear, 60g, 60b...Lubricating oil supply hole Patent applicant Yanmar Diesel Co., Ltd. Figure 2/N

Claims (1)

[Claims] 1. A first gear driven by a power turbine shaft, an intermediate shaft to which the first gear is fixedly installed, and an intermediate shaft to which the first gear is fixedly installed in the gear box of the reduction gear. a second gear fixed to the output shaft and meshing with the second gear, the intermediate shaft is configured to be movable, and when the intermediate shaft is moved, the third gear An idler gear interposed between the second gear and the third gear is detachably provided, and a straight line connects the center of the second gear and the center of the idler gear when the intermediate shaft is moved. is L, the straight line connecting the center of the idler gear and the center of the third gear is M, and the angle θ between the straight line L and the straight line M is based on the straight line L and the rotation direction of the idler gear is the positive direction. , -20°≦θ≦100°. 2. A lubricating oil supply hole formed in the gear box to supply oil to the intermediate shaft bearing and the first and second gears is provided at a position equidistant from the axis both before and after the intermediate shaft moves. A two-shaft gas turbine according to claim 1, characterized in that: