JPH0155339B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a gas turbine speed reducer used in a small, movable, single-shaft gas turbine generator.

The frequency of commercial AC power in Japan is 50 hertz in eastern Japan and 60 hertz in western Japan, so alternators must be operated at rotational speeds that match the respective frequencies. Therefore, in a gas turbine generator, it is conceivable to change the power frequency by changing the rotational speed of the gas turbine, but in particular, when a single-shaft gas turbine is operated at a rotational speed other than the rated rotational speed, the output decreases significantly.

It is also possible to use a transmission to switch the frequency of AC power, but this would reduce the friction between the transmission's shift fork and the side of the gear, since the rotational speed of a gas turbine is extremely high, unlike an engine. As it becomes larger, it causes a loss of rotational energy and a decrease in durability.

This invention was made in view of the above-mentioned disadvantages, and an object of the present invention is to provide a gas turbine reducer that can change the rotational speed of the output shaft, has little loss of rotational energy, and has high durability. do.

An embodiment of the present invention will be described below with reference to the drawings.

In FIG. 1, reference numeral 1 denotes an input shaft to which rotational output from a gas turbine 2 is transmitted, and is supported via a bearing 4 mounted in a case 3. As shown in FIG. A first input gear 5 and a second input gear 6 having different numbers of teeth are fixed to the input shaft 1, and the number of teeth of the first input gear 5 is equal to the number of teeth of the second input gear 6. To a lesser extent, the first input gear 5 is for a power frequency of 50 Hertz and the second input gear 6 is for a power frequency of 60 Hertz.

Reference numeral 7 denotes an output shaft that transmits the driving force from the input shaft 1 to the alternator 8, and the output shaft 7 is connected to a first output gear 10 and a second output gear 11 via a rotatable bearing 9. The first output gear 10 and the second output gear 11 are set to always mesh with the first input gear 5 and the second input gear 6, respectively.

14 is a third output gear, which is connected to the first and second output gears.
The output shaft 7 is integrally formed between the output gears 10 and 11 in the axial direction 13. Therefore, the third output gear 14 rotates together with the output shaft 7.

12 is a ring gear, and the third output gear 14
It is arranged coaxially with the output shaft 7 so as to always engage with the outer periphery of the output shaft 7. This ring gear 12 is slidable in the axial direction 13 of the output shaft 7, and by shifting in the axial direction 13 of the output shaft 7, the first output gear 10
Alternatively, the second output gear 11 is selectively engaged.

Reference numeral 15 denotes a lock mechanism for setting the position of the ring gear 12 in the axial direction 13. In FIG. 2 showing this lock mechanism, the third output gear 1
A storage hole 16 is provided in the radial direction of the housing 4 .
The compression coil spring 17 installed in the storage hole 16 has a ball (engager) in contact with its upper part.
18 is pressed to cause the ball 18 to protrude from the storage hole 16. On the other hand, in the ring gear 12, only one tooth on the inner circumference is cut out as shown by the line 30 to form locking grooves 19, 19, and the balls 18 are inserted into the locking grooves 19, 19. The protruding part is inserted. The ball 18 therefore engages the ring gear 12 and the third output gear 14 in the axial direction 13. That is, the ball 18 is interposed between the left locking groove 19 provided in the ring gear 12 and the storage hole 16 provided in the third output gear 14.
The position of the ring gear 12 is such that the first output gear 10 and the third output gear 14 are connected to prevent the ring gear 12 from moving in the axial direction 13. Furthermore, if the ring gear 12 is shifted to the left in the axial direction 13 and the balls 18 are interposed between the locking groove 19 and the storage hole 16 on the right side of the ring gear 12, the second output gear 11 and the third Since the output gear 14 of the output shaft 7 is connected to the output gear 14, the rotation speed of the output shaft 7 is changed. The ring gear 12 is provided with a pair of insertion holes 35 passing through it in the radial direction. These insertion holes 35 are for the ring gear 1
Depending on the shift position of the operating rod 2, one of them faces the ball 18, and the operating rod 2, which will be described later,
5 is the hole into which it is inserted.

Reference numeral 20 in FIG. 1 is a shift fork for shifting the ring gear 12 in the axial direction 13 of the output shaft 7; When the shift lever 23 fixed to the fork 20 is shifted in the axial direction 13, the ring gear 12 is shifted accordingly, and the connection between the first output gear 10 or the second output gear 11 and the output shaft 7 can be selected. can do. As shown in FIG. 3, the shift fork 20 is engaged only when selecting the first output gear 10 and the second output gear 11, and is engaged with the ring gear 12 so that it can be removed during operation. It is set to be removable.

Next, the operation of the above embodiment will be explained.

In order to obtain an output with an AC frequency of 50 hertz from the alternating current generator 8, the ring gear 12 may be set as shown in FIG. That is, in this case, when the gas turbine 2 is operated at the rated rotation speed,
The driving force is transmitted from the input shaft 1 to the first input gear 5 and the first
is transmitted to the output gear 10, the ring gear 12, and the third output gear 14, the output shaft 7 is rotated at a predetermined rotational speed, and an AC frequency of 50 Hz is obtained from the alternator 8.

Next, to convert to an AC frequency of 60 hertz,
With the gas turbine 2 stopped, the operating rod 25 is inserted through the through hole 24 provided in the case 3 as shown in FIG. 2, and its protrusion 26 is inserted into the insertion hole 35 of the ring gear 12. The ball 18 housed in the storage hole 16 is pressed against the spring 17 and lowered to near the tooth bottom 27 of the third output gear 14.
At this time, the stepped portion 29 of the operating rod 25
By contacting the outer peripheral surface of the ring gear 2, the protrusion 26 is prevented from entering too deeply and interfering with the movement of the ring gear 12 in the axial direction. In this state, the shift lever 23 is rotated in the direction of arrow 28 as shown in FIG. Shift the ring gear 12 to the left in the axial direction 13 as shown in FIG.
The ball 18 is engaged with the first and third output gears 14, and the ball 18 is pressed by a spring into the locking groove 19 on the right side of the ring gear 12, and when the upper hemisphere is inserted and the ring gear 12 is fixed, the gear switching is completed. Ru.

Next, rotate the shift lever 23 in the direction of the arrow 31 to move the shift fork 20 from the ring gear 12.
When the engagement is released and the gas turbine 2 is operated at the rated rotation speed, the driving force is transferred from the input shaft 1 to the second input gear 6, the second output gear 11, the ring gear 12, and the third output gear 14. The output shaft 7 is rotated at a predetermined rotational speed, and an alternating current frequency of 60 hertz is obtained from the alternator 8.

That is, according to the above embodiment, since the transmission is inserted between the gas turbine 2 and the alternator 8, even if the gas turbine 2 is always operated at a constant rated rotation speed, the gears of the transmission do not change. Different AC power frequencies can be obtained by switching. Furthermore, since the shift fork 20 can be disengaged from the ring gear 12 during operation, there is no friction in their contact areas, which facilitates maintenance and eliminates loss of rotational energy.

By the way, since the shift fork 20 is not engaged with the ring gear 12 during operation, it is necessary to prevent the ring gear 12 from shifting in the axial direction 13. On the other hand, during the switching operation, the ring gear 12 is not engaged with the ring gear 12.
must be movable. In contrast, in this transmission, the ball 18 shown in FIG. 2 protrudes from the storage hole 16, and the ring gear 12 and the third output gear 14
By engaging in the axial direction of the ball 18, it is possible to prevent the ring gear 12 from shifting in the axial direction 13. On the other hand, since the insertion hole 35 is provided, the engagement of the ball 18 can be controlled by the operating rod 25. Can be released from outside. In other words, by ball 18 and ring gear 1
2 can be prevented from shifting, while the provision of the insertion hole 35 makes it possible to release the engagement of the ball 18, allowing positioning and switching operations to be performed.

As described above, according to the present invention, the power frequency can be switched without reducing the output of the gas turbine, and the third output shaft and the ring gear rotate together with the ring gear. Since the gear and the third output shaft are fixed in the axial direction, it can be operated with the shift fork removed, so there is no wear between the shift fork and the ring gear, making maintenance easy and durable. In addition, it is possible to provide a gas turbine speed reducer with good rotational energy loss.

[Brief explanation of drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention, FIG. 2 is an enlarged sectional view showing essential parts of the embodiment, and FIG. 3 is a side view showing the gear switching operation of the embodiment. 1... Input shaft, 5... First input gear, 6...
Second input gear, 7... Output shaft, 10... First output gear, 11... Second output gear, 12... Ring gear, 13... Axial direction, 14... Third output gear , 16... Storage hole, 17... Compression coil spring, 18... (engager) ball, 20... Shift fork.

Claims (1)

[Claims] 1 The first shaft is fixed to the input shaft and has a different number of teeth.
and a second input gear, and first and second output gears that are rotatably mounted on the output shaft and always mesh with the first and second input gears, respectively;
A third output gear is disposed between the first and second output gears in the axial direction and rotates together with the output shaft; a ring gear that selectively engages the first output gear or the second output gear by shifting in the direction; a storage hole bored in the radial direction of the third output gear; an engager that is pressed by a compression coil spring attached to the hole and protrudes from the storage hole and engages in the axial direction of the ring gear and the third output gear to prevent the ring gear from shifting; and a diameter of the ring gear. A pair of insertion holes are formed to penetrate in the direction, one of which faces the engager according to the shift position of the ring gear, and a shift fork that shifts the ring gear in the axial direction of the output shaft. . A gas turbine speed reducer, wherein the shift fork is configured to be freely engageable and detachable from a ring gear.