JPS629730B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to gas turbine equipment, and particularly to improvements in a gas turbine starting system and driven rotor rotation device.

The prior art will be explained with reference to FIG.

The gas turbine equipment shown in this figure includes a starting power source 1, a torque converter 2 which is a fluid transmission,
clutch 3, auxiliary drive device 4, gas turbine 5,
A generator 6, a turning device 7 that is a driven rotor rotation device, and an oil tank 8 that constitutes a fluid pressure supply device.
, main oil pump 9, auxiliary oil pump 10, check valve 12
A forward circuit 11 that pressurizes and supplies oil to the torque converter 2 through a filling pump 13, a return side circuit 14 of the torque converter 2, and an oil supply circuit 15 that supplies lubricating oil to each bearing. When starting the gas turbine 5, first the starting power source 1
At the same time as the engine is started, a clutch 3, which is engaged only during startup, is forcibly engaged by a hydraulic cylinder or the like. The power of the starting power source 1 is transmitted to the gas turbine 5 and the generator 6 via the torque converter 2, which is adjusted in advance to have a constant rotation, and via the clutch 3 and the auxiliary drive device 4.
accelerates until it reaches self-sustaining rotation.

When the gas turbine 5 starts self-sustaining operation, the clutch 3 is switched to cut off the power,
At the same time, the starting power source 1 stops.

The turning device 7 is installed on the rear side of the generator 6 or attached to the output shaft of the auxiliary drive device 4 or the torque converter 2.
In both cases, the gas turbine 5 is rotated at low speed,
It is operated to prevent thermal deformation of the rotor, cool it, etc. when the gas turbine 5 is stopped.

However, in this prior art, since the clutch 3 is a pawl type clutch, it is not possible to react when the gas turbine 5 is desired to be restarted immediately after the combustion has been stopped. This is because the clutch 3 is a jaw type clutch, so the jaw on the auxiliary drive device 4 side is the torque converter 2.
This is because the pawls of the clutch 3 cannot engage with each other unless the rotation speed is slower than that of the side pawls, or unless the auxiliary drive device 4 side completely stops. Normally, even if combustion in the gas turbine is stopped, the rotor continues to rotate for 10 to 20 minutes due to inertia, and the disadvantage is that the gas turbine cannot be restarted during this time.

Further, gas turbine power generation equipment is generally assembled on a beam, and the beam is transported and installed together. Therefore, for convenience of transportation, the area on the beam is also limited. Then,
It is important to downsize the equipment used in gas turbine power generation equipment, and determining the placement of each equipment is not easy.

However, the conventional driven rotor rotation device 7
It is composed of an electric motor 70 and a reduction gear device 71, and power transmission from the electric motor 70 to the reduction gear device 71 is performed mechanically, so the electric motor 70 and the reduction gear device 71 cannot be placed separately. ,
The drawback was that it took up quite a lot of space on the beam.

The object of the present invention is to
It is an object of the present invention to provide gas turbine equipment that can be restarted immediately if necessary, and that can install a rotational drive source of a driven rotor rotation device such as a gas turbine rotor at an arbitrary position.

A feature of the present invention is that a driven rotor rotation device is directly connected to a synchronous clutch, and the driven rotor rotation device rotates the driven rotor at a low speed via the output shaft of the synchronous clutch when switching the power of the synchronous clutch. In addition, the synchronous clutch is configured to idle when switching power transmission, the driven rotor rotation device is connected to a rotational drive source using fluid pressure, and the rotational drive source is connected to a fluid pressure supply device of the fluid transmission. It's about connecting. With this configuration, the rotational drive source of the driven rotor rotation device can be installed at any position, and the entire driven rotor rotation device can be downsized.

Hereinafter, the present invention will be explained based on the drawings.

2 to 6 show an embodiment of the present invention, in which a starting power source 1, a torque converter 2 which is a fluid transmission connected thereto, an auxiliary drive device 4, a gas turbine 5, a power generator Hydraulic supply device that is a fluid pressure supply device to the torque converter 2; an outgoing circuit 1 that supplies oil under pressure to the torque converter 2
1. The return side circuit 14, an oil supply circuit 15 for supplying lubricating oil to each bearing, connected to the torque converter 2 via an input shaft 160, and connected to the auxiliary drive device 4 via an output shaft 167. A synchronous clutch 16, a driven rotor rotation device 17 directly connected to the synchronized clutch 16, and a rotation drive circuit connected to the hydraulic pressure supply device for rotating the driven rotor rotation device 16.

As the starting power source 1, a prime mover such as an electric motor or a diesel engine is used.

Oil is supplied to the inside of the torque converter 2 from a hydraulic pressure supply device through an outgoing circuit 11.

As shown in FIG. 2, the hydraulic pressure supply device includes an oil tank 8, a main oil pump 9, and an auxiliary oil pump 1.
0.

The outgoing circuit 11 that supplies oil to the torque converter 2 passes the oil sucked in by the main oil pump 9 and the auxiliary oil pump 10 of the hydraulic supply system through a check valve 12, as shown in FIG. The fuel is sent to a filling pump 13, and the pressure is increased by the filling pump 13, so that the inside of the torque converter 2 can be filled.

The torque converter 2 is shown in FIGS. 3 and 4.
As shown in the figure, when the input shaft 21 is rotated by the starting power source 1, the pump impeller 22 attached to the input shaft 21 is rotated, and the oil filled inside the torque converter 2 is rotated in the centrifugal direction. The turbine impeller 24 attached to the output shaft 23 is rotated by this oil, and power is transmitted to the output shaft 23. Furthermore, the oil that has passed through the turbine impeller 24 has its flow direction changed by the guide vanes 25 and is sucked into the pump impeller 22 again. The rotation speed of the output shaft 23 can be controlled by changing the angle of the guide vanes 25 using a vane control device 26. The blade control device 2
6 is operated by a hydraulic cylinder 27 etc. shown in FIG.

The synchronizing clutch 16 includes an input shaft 160 and a stopper 16, as shown in FIGS.
2, a slider 163, and an output shaft 167 are combined. A male screw gear 161 is formed in one half of the input shaft 160 on the output shaft 167 side, and a shoulder portion 160' is provided in the axially intermediate portion. The stopper 162 is attached to the end face of the male screw gear 161. The slider 163 has a female screw gear 16 on its inner peripheral surface.
4, a first clutch tooth 165 is formed at one end in the axial direction on the outer periphery, and a ratchet 166 is formed at the other end. Further, the slider 163 is meshed with the male screw gear 161 via a female screw gear 164, and the slider 163 is engaged with the male screw gear 161 through a female screw gear 164.
is moved in the direction of arrow a in FIG. 5 when the rotation of the input shaft is relatively faster than the rotation of the output shaft, and on the contrary, is moved in the direction of arrow b in the figure when it is slower. The output shaft 167 has a second clutch tooth 168 formed at one end of its inner peripheral surface, and a pawl 16 that can engage with the ratchet 166 at the other end.
9 is attached. Then, the output shaft 1
The axial position of 67 is fixed, and the slider 163
moves in the direction of arrow a in FIG. 5, the first and second clutch teeth 165 and 168 engage, power is transmitted from the input shaft 160 to the output shaft 167, and the slider 163 moves in the direction of arrow b in FIG. When the clutch moves to the position, the first and second clutch teeth 165, 168 are disengaged, and the power is cut off. are arranged so that they can mesh with each other.

As clearly shown in FIGS. 5 and 6, the driven rotor rotating device 17 includes a worm 170,
It is configured to include a worm wheel 171, a stopper 173, a slider 174, and an output shaft 167 of the synchronous clutch 16. The worm wheel 171 has a female threaded gear 172 formed in one half of its inner peripheral surface on the output shaft 167 side of the synchronous clutch 16, and has a shoulder 171' in the middle. The stopper 173 is attached to the end face of the female screw gear 172. The slider 174 has a male screw gear 175 formed on its outer circumferential surface, a third clutch tooth 176 formed at one end of its inner circumference, and a pawl 17 formed at the other end.
7 is provided. The slider 174 is meshed with a female screw gear 172 via a male screw gear 175, and these female and male screw gears 172, 17
5, the slider 174 connects the synchronous clutch 1
When the worm wheel rotation is relatively faster than the output shaft rotation in 6, the worm wheel is moved in the direction of arrow c in Fig. 5,
On the other hand, when it is slow, it is moved in the direction of arrow d in the figure.
On the outer periphery of the output shaft 167, a fourth
Clutch teeth 178 are formed at the other end, and a ratchet 179 is formed at the other end. When the slider 174 moves in the direction of arrow c in FIG. 5, the third and fourth clutch teeth 176 and 178 engage, and power is transmitted from the worm 170 and the worm wheel 171 to the output shaft 167.
When the slider 174 moves in the direction of arrow d in FIG.
The structure is such that the power is cut off when the Further, the ratchet 179 and the pawl 177 are aligned so that the third and fourth clutch teeth 176 and 178 mesh with each other.

The synchronous clutch 16 and the driven rotor rotating device 17 are housed in a single housing 180 and are combined into a unit, and bearings 181 and 182 are incorporated at key points.

As shown in FIG. 2, the rotational drive circuit of the driven rotor rotation device 17 includes a high-pressure oil generating pump 18, a check valve 19, and a hydraulic motor 20, and a main oil pump 9 and an auxiliary oil pump. The oil sucked through the pump 10 is increased in pressure by the high-pressure oil generation pump 18 and sent to the hydraulic motor 20 through the check valve 19.
The hydraulic motor 20 is configured to rotationally drive the worm 170 of the driven rotor rotation device 17.

In the gas turbine equipment configured as described above, when the starting power source 1 is activated immediately if necessary after the gas turbine 5 is stopped, the power is transmitted to the input shaft 160 of the synchronous clutch 16 via the torque converter 2.

The input shaft 160 is driven, and the synchronous clutch 1
When the rotational speed of the input shaft 160 of 6 is relatively faster than the rotational speed of the output shaft 167, the synchronous clutch 16 operates as follows. First, the ratchet teeth 166 provided to align the meshing positions of the first clutch teeth 165 and the second clutch teeth 168 mesh with the pawl 169, and the slider 163
The first clutch tooth 165 formed in the output shaft 1
The second clutch tooth 168 formed in the second clutch tooth 67 is brought into engagement with the second clutch tooth 168 . The operation during this time is carried out within the rotation angle of one ratchet tooth 166, so it is extremely short. Furthermore, the friction torque generated by the friction force between the male screw gear 161 and the female screw gear 164 is extremely small compared to the torque required to rotate the driven machine at increased speed.
Rotation of the slider 163 is stopped by a pawl 169. Then, due to the screw action of the male and female screw gears 161 and 164, the slider 163 moves in the direction of the arrow a in FIG. 5 until it comes into contact with the shoulder 160'.
The second clutch teeth 165, 168 are fully engaged. Since the male and female screw gears 161 and 164 have large leads, the slider 163 can move in a short time until it comes into contact with the shoulder 160'. By engaging the synchronous clutch 16, power is transmitted from the input shaft 160 to the output shaft 167, and the auxiliary drive device 4, gas turbine 5, and generator 6 can be started in a short time.

In this way, in the synchronous clutch 16, the engagement and disengagement of the clutch teeth is automatically determined only by the relative rotational speed difference between the synchronous clutch 16, the input shaft 160, and the output shaft 167, and therefore the hydraulic cylinder, etc. No forced engagement device is required. Furthermore, the clutch teeth can be engaged even when the input shaft 160 and the output shaft 167 are rotating.

During the above-mentioned startup, the driven rotor rotation device 17
The slider 174 has been moved to a position where it comes into contact with the stopper 173, and the third clutch tooth 176 formed on the slider 174 and the synchronous clutch 1
It is separated from the fourth clutch tooth 178 formed on the output shaft 167 of No. 6. Further, the pawl 177 of the driven rotor rotation device 17 does not engage with the ratchet 179 and rotates idly.

Then, when the gas turbine 5 becomes independent and rotates at the rated speed, the output shaft 167 of the synchronous clutch 16 is rotationally driven by the gas turbine 5 via the auxiliary drive device 4, so that the input shaft rotation is relatively faster than the output shaft rotation. slider 16 of synchronous clutch 16.
3 is moved in the direction of arrow b in FIG. 5 by the action of the male and female screw gears 161 and 164 until it abuts against the stopper 162, and the first and second clutch teeth 16
5,168 will be withdrawn. In this state, the pawl 169 of the synchronized clutch 16 does not engage with the ratchet 166 and rotates idly.

Also in this case, the third and fourth clutch teeth 176, 178 of the driven rotor rotating device 17 are disengaged.

At the time when the starting power source 1 is stopped and the gas turbine 5 is stopped, the hydraulic pressure supply device to the torque converter 2, the high pressure oil generation pump 18,
Oil is sent to the hydraulic motor 20 through the check valve 19, and the worm 170 of the driven rotor rotating device 17 is fed.
Rotate. The worm wheel 171 is rotationally driven by the rotation of the worm 170, and the worm wheel rotation drives the output shaft 1 of the synchronous clutch 16.
67, the driven rotor rotation device 17 operates as follows. That is, a pawl 177 provided on the slider 174 engages with a ratchet 179 formed on the output shaft 167, and a third clutch tooth 176 formed on the slider 174 engages with a fourth clutch tooth 178 formed on the output shaft 167. are aligned so that they interlock.
Then, due to the action of the female and male screw gears 172 and 175, the slider 174 is moved in the direction of arrow c in FIG.
It is moved until it comes into contact with the shoulder 171', and at this position the third and fourth clutch teeth 176 and 178 are engaged. As a result, the power decelerated by the worm 170 and the worm wheel 171 is transferred to the output shaft 1.
67, and the auxiliary drive device 4, which is a driven machine,
The rotors of the gas turbine 5 and the generator 6 are rotated at low speed.

In this case, since the starting power source 1 is stopped, the slider 163 of the synchronous clutch 16 has been moved to a position where it abuts against the stopper 162, and the first and second clutch teeth 165, 168 are disengaged. , the ratchet 166 and the pawl 169 do not engage, and the pawl 169 rotates idly.

Then, when the gas turbine 5 becomes independent and shifts to the rated rotation, the output shaft 167 of the synchronous clutch 16 is rotated at high speed through the auxiliary drive device 4, and when the worm wheel rotation becomes relatively slower than the output shaft rotation, The slider 174 is moved in the direction of arrow d in FIG.
The power between them is cut off.

Further, in this state, the first and second clutch teeth 165 and 168 of the synchronous clutch 16 are also disengaged.

Note that the synchronous clutch 16 has an output shaft 167.
In addition, it has a structure in which power can be transmitted only from the input shaft 160 and the worm wheel 171, and the input shaft 160
and the worm wheel 171, and from the output shaft 167 to the input shaft 160 and the worm wheel 1.
No power is transmitted to 71.

Next, FIG. 7 shows another embodiment of the present invention, in which a first oil amount control device 29 and a first orifice 30 are connected between the synchronous clutch 16 and the auxiliary drive device 4. A second oil amount control device 31 and a second orifice 3 are attached to the outgoing circuit 13 that supplies the torque converter 2.
6 is attached.

The first oil amount control device 29 is installed in the middle of an oil passage 28 that supplies oil to the inside of the synchronous clutch 16, and controls the oil passage 28 when the clutch teeth of the synchronous clutch 16 are engaged by an external electric signal or the like. When the clutch teeth of the synchronous clutch 16 are disengaging, the oil passage 28 is closed. Also, the first
The orifice 30 is installed so as to bypass the first oil flow control device 29, and the synchronous clutch 16
Only the necessary amount of oil is supplied to the inside of the system. This eliminates power loss caused by the output shaft 167 stirring oil inside the synchronous clutch 16.

On the other hand, the second oil amount control device 31 is installed just before the filling pump 13 for supplying oil to the torque converter 2, and opens the circuit when the filling pump 13 is in operation by an external electric signal or the like, and also closes the circuit when the filling pump 13 is in operation. 1
3 is stopped, the circuit can be controlled to close. Further, the second orifice 32 is installed so as to bypass the oil amount control device 31, and supplies only the necessary amount of oil to the torque converter 2 via the filling pump 13. This prevents the filling pump 13 from operating as a hydraulic motor while the filling pump 13 is stopped, and eliminates unnecessary rotation of the starting power source 1.

In addition, in Fig. 1, Fig. 2, and Fig. 7,
Identical members are given the same reference numerals and explained.

The present invention has the configuration described above, and uses a synchronous clutch as the clutch that transmits or interrupts the power of the starting power source to the driven machine, and also connects the driven machine rotor rotation device to the synchronous clutch. This is directly connected to a rotary drive source using fluid pressure, and the rotary drive source is connected to the fluid pressure supply device of the fluid transmission, so that restarting power can be immediately applied as necessary after the gas turbine is stopped. In addition, there is an effect that the rotational drive source can be installed at an arbitrary position, and there is also an advantage that the entire driven rotor rotation device can be miniaturized.

[Brief explanation of the drawing]

FIG. 1 is a system diagram of conventional gas turbine equipment, FIG. 2 is a system diagram of an embodiment of the present invention, FIG. 3 is an enlarged vertical sectional front view of a torque converter, and FIG. 4 is an enlarged partially cutaway side view of the same. FIG. 5 is an enlarged longitudinal sectional front view of a portion of the synchronous clutch and the driven rotor rotating device, FIG. 6 is a partially cutaway side view of the same, and FIG. 7 is a system diagram of an embodiment different from the above. 1... Starting power source, 2... Torque converter which is a fluid transmission, 4... Auxiliary machine drive device, 5... Gas turbine, 6... Generator, 8-13... Hydraulic pressure supply which is a fluid pressure supply circuit to the fluid transmission. components that make up the circuit,
16... Synchronous clutch, 160 to 169... Members constituting the synchronous clutch, 17... Driven rotor rotation device, 170 to 179... Driven rotor rotation device, 18, 19... Consists of rotational drive circuit of driven machine rotation device member, 20...A hydraulic pump which is a rotational drive source using fluid pressure.

Claims (1)

[Claims] 1 A starting power source, a fluid transmission connected to the starting power source, and a fluid transmission installed between a driven machine including a gas turbine and the fluid transmission, and capable of transmitting or interrupting the power of the starting power source to the driven machine. and a driven rotor rotation device, and a synchronous clutch is used for the clutch to directly connect the driven rotor rotation device to the synchronous clutch, and when the power of the synchronous clutch is switched off, the output of the synchronous clutch is The driven rotor is configured to rotate at a low speed via the shaft and can idle when switching the power transmission of the synchronous clutch, and the driven rotor rotation device is connected to a rotational drive source using fluid pressure, and the driven rotor is connected to a rotational drive source using fluid pressure. is connected to a fluid pressure supply device of the fluid transmission.