RU2397344C1 - Gas turbine engine turning and starting gear - Google Patents

Abstract

FIELD: engines and pumps.

SUBSTANCE: reduction gear is mounted between drive engine (electric motor, ICE) and compressor rotor, said reduction gear consisting of simple three-link planetary gear (PG) and four-stage three-axle aligned gearbox (GB) made up of three pairs of engaged gears. Five clutches allows operating PG in three operating conditions: total torque, when the latter is transferred to two links and is taken off the third link; torque is transferred to sun gear and take off pinion frame with epicyclic gear wheel locked, and direct PG gear.

EFFECT: reliable start of GTE, simplified starting device due to integration of two devices.

2 dwg, 1 tbl

Description

The invention relates to a start-up system for gas turbines (gas turbine units) used to drive the blowers for transporting gas through gas pipelines, drive power plants and vehicles.

Well-known gas turbines with shaft-turning and starting devices (1. Mogilnitsky IP, Steshenko VN Gas turbine units in the oil and gas industry. M: Nedra, 1971. - 160 pp. 2. Atlas of structures and diagrams. Gas turbine units. / Under the editorship of Shubenko-Shubin. - M.: Mechanical Engineering, 1976).

These devices are functionally separated and complex. Initially, a shaft-turning device is triggered, which provides the output of the rotor with a large inertial mass from the rest state. Then, a starting device is included in the work, which should provide the compressor rotor speed sufficient to supply air with parameters that realize the launch of the combustion chamber and turbine. As a starting device, a turbo-expander is often used, for the operation of which a high pressure of gas taken from the main pipeline is necessary.

To combine two functions in one technical device, it is possible to use a simple three-link PM (planetary mechanism) based on patent RU No. 2053135 C1, B60K 17/08. Author V.I.Nekrasov. (01/27/96. Bull. No. 3).

The gear according to patent No. 2053135 provides seven gears. Three transmissions are implemented by PM in a summing mode with a constant rotation speed of the sun gear and a variable rotation frequency of the carrier, the power flow is removed from the epicyclic wheel. The change in the carrier speed relative to the speed of the sun gear is provided by a four-stage three-shaft coaxial gearbox (gearbox), consisting of three pairs of interlocked gears and two switching clutches. Four gears are implemented by three pairs of gears KP and the PM carrier.

The technical solution according to patent No. 2053135 cannot provide a reliable start-up of gas turbines without using the energy of the gas flow from the main gas pipeline, since the placement of gear ratios in the range is not optimal.

The objective of the invention is to provide a reliable start-up of gas turbines without using the energy of the gas flow from the main gas pipeline.

The technical result is achieved by improving the technical solution for the patent No. 2053135.

The achievement of the technical result is ensured by the fact that the shaft-turning and starting device of the gas turbine installation contain a drive motor, a gearbox and an overrunning clutch of the compressor rotor, while the gearbox contains a three-shaft coaxial gearbox with three pairs of interlocked gears and a simple three-link planetary mechanism, three gears are fixed on the intermediate shaft of the box gears located parallel to the input shaft, on which two gears are freely mounted, between them the first gear is fixed on the shaft the crown with a three-position switching clutch, a tubular output shaft with a freely installed gear is freely installed, on the first gear ring of this shaft between the gears of the second and third rows there is a three-position switching clutch, a double two-position clutch is installed on the second gear ring of this shaft, a second one is fixed next to it the gear rim of the input shaft and the gear rims of the drive shaft of the sun gear and the tubular shaft of the planetary gear carrier are located, the satellites located on the axle drove, engaged with the sun gear mounted on the end of the input shaft, as well as with the epicyclic wheel, which is mounted on the output tubular shaft with a gear rim, next to it are the gear rim of the output shaft of the dropper and the gear rim of the output shaft of the gearbox with a two-shaft two-position switching clutch, a single-shaft, two-position clutch is mounted on the gear rim of the wall of the gear housing next to the gear rim of the tubular shaft of the epicyclic wheel.

Placing a double two-position switching clutch on the shafts between the gearbox and the PM, as well as the coupling between the gear housing wall and the ring gear of the tubular shaft of the epicyclic wheel, allows for the reliable start-up of the gas turbine with optimal gear ratios in the U ^b _ah = K + 1 mode range.

Where U is the gear ratio, the index at the top indicates the stopped link PM “b” is the epicyclic wheel, the indices at the bottom “ah” are the links of the input (sun gear) and output (carrier) of the power flow. K = Z _b / Z _a is the internal parameter PM equal to the ratio of the number of teeth of the epicyclic wheel to the number of teeth of the sun gear.

Figure 1 shows the kinematic diagram of the gearbox. In the lower part of the gearbox, the numbers of gear pairs for the table are shown in circles.

Figure 2 shows the radiation diagram of the gear ratios provided by the gearbox in figure 1. On the beam diagram, the gear ratios (U) are shown by an uneven scale at the bottom of the horizontal. A uniform scale of gear ratios on a logarithmic scale (lq U) is shown in the upper part of this horizontal line, while the beam characterizing the gear ratio does not change its magnitude.

Under the diagram on the right is a table of gears, the status of the clutch gears for these gears and the gearbox elements included. Theoretically, the gearbox provides 11 gears: 4 gears (11, 10, 8 and 7) in gearbox mode when transmitting torque via the PM carrier, 4 gears (6-3) when using PM in K + 1, 3 gears mode (9, 2 and 1) when the PM is in the summing mode. Transmissions form 5 stages (11-9, 8-5, 4-3, 2 and 1st gear) with almost the same intervals between them, which will ensure reliable start-up of the gas turbine.

In the bearings of the gearbox housing 1 (see Fig. 1) there is an input shaft 2 of the gearbox, on which the first gear ring 3 and the second gear ring 4 are fixed. On the input shaft 2, the tubular output shaft 5 of the gearbox is freely located, at the ends of which the first 6 and second 7 toothed crowns. Parallel to input 2 and output 5 shafts, an intermediate shaft 8 is mounted on which gears 9-11 are fixed. Gears 9 and 10 of the intermediate shaft 8 are engaged with gears 12 and 13 freely mounted on the input shaft 2 near the first gear ring 3, on which the three-position switching clutch 14 (A) is located. The gear 11 is engaged with the gear 15 freely mounted on the tubular output shaft 5 of the gearbox. On the first gear ring 6 of the tubular output shaft 5 between the gears 13 and 15 there is a three-position switching clutch 16 (B). Next to the ring gear 4 is the ring gear 17, mounted on a gear shaft 18 of the sun gear 19 mounted coaxially to the input shaft 2 of the gearbox. The sun gear 19 is engaged with the satellites 20 mounted on the axles of the carrier 21, on the tube shaft 22 of which the ring gear 23 is located, located next to the gear rim 17 of the shaft 18 of the drive of the sun gear 19. On the second gear rim 7 of the tubular output shaft 5, there is a dual on / off clutch 24 (C). A gear ring 26 is fixed to the output shaft 25 of the carrier 21. An epicyclic wheel 27 engaged with the satellites 20 is fixed to the tubular output shaft 28, at the end of which a gear ring 29 is located adjacent to the gear ring 26 of the output shaft 25 of the carrier 21. On the housing wall 1, next to the ring gear 29 is the ring gear 30 on which the on-off single-clutch shift clutch 31 (D) is mounted. Coaxial with the output shaft 25 of the carrier 21 is the output shaft 32 of the gearbox, a ring gear 33 is fixed on it, on which a two-position two-crown switching clutch 34 (E) is installed.

The operation of the gearbox is as follows.

1st gear

Couplings A, D and E are in the left position (L), couplings B and C are in the right (P) - see the table under figure 2. The sun gear 19 receives direct drive from the input shaft 2 along the inner gear rim of the clutch 24 (C). The carrier 21 receives a drive through a pair of gears 1 and 3 with a rotation speed lower than the sun gear 19.

From the drive motor (electric motor, ICE - internal combustion engine) through the input shaft 2 (see figure 1), through the gear ring 3 and the coupling 14 (A), the torque is supplied to a pair of gears 1 (12-9), then through the intermediate shaft 8 for a pair of gears 3 (11-15), then along clutch 16 (B) to the first gear ring 6 and the tubular output shaft 5, the second gear ring 7, along the outer gear rings of the coupling 24 (C) to the ring gear 23 and tubular the shaft 22 of the carrier 21, on the satellites 20 the power flows from the sun gear 19 and the carrier 21 are added up and removed from the epicyclic wheel 27 along the tubular output shaft 28 to the ring gear 29, then through the coupling 34 (E) to the ring gear 33 and the output shaft 32 of the gearbox (see the upper position of the couplings C, D and E in figure 1)

In the beam diagram (see FIG. 2), beam 1 from volume 0 is directed downward to the right in the middle horizontal, then beam 3 goes upward to the level IqU = 0.47, with U = 2.95. Two beams are directed to a point on the upper horizontal equal to 2.07: one of t.0 from the rotation speed of the sun gear 19, the second from the rotation frequency of the carrier 21.

The rotation frequency of the epicyclic wheel 27 and the output shaft of the gearbox 32, as well as the gear ratio of the gearbox are determined as follows:

n _b = u ^h _ba n _a + u ^a _bh n _h = -n _a / c + n _h (k + 1) / k = -3000 / 2 + 3000 / 2.95 * 3/2 = 25.4 r / min; u ₁ = 3000 / 25.4 = 118.1; lq 118.1 = 2.07.

2nd gear

We switch clutch A to the right position - instead of a pair of gears 1 (12-9), we include a pair of gears 2 (13-10), the gear ratio of which is slightly lower than the first pair.

From the input shaft 1 through the gear ring 3 and the clutch 14 (A), the torque is supplied to a pair of gears 2 (13-10), to the intermediate shaft 8 and then as in first gear.

On the beam diagram, rays 2 and 3 belong to this transmission. Ray 3 reaches the level lqU = 0.45, with U = 2.818.

n _b = -3000 / 2 + 3000 / 2.818 * 3/2 = 96.9 rpm; u ₂ = 3000 / 96.9 = 31; lq 31 = 1.49.

3rd gear

Return clutch A to the left position, change the position of couplings C, D and E to the opposite. In this case, the PM switches to K + 1 mode. The epicyclic wheel 27 is stopped by the tubular shaft 28, the ring gear 29, the clutch D on the ring gear 30 of the gear housing 1 wall.

Prior to the ring gear 7 of the output tubular shaft 5, the torque is supplied as in first gear. Then, along the outer gear rims of the clutch C in the left position, on the gear rim 17, the drive shaft 18 of the sun gear 19, which rotates the satellites 20 relative to the stopped epicyclic wheel 27. The satellites 20 rotate the carrier 21 three times slower than the sun gear (at K = 2), on the shaft 25, the torque is supplied to the ring gear 26, through the coupling E in the right position (see the lower position of the couplings C, D and E in figure 1) to the ring gear 33 and the output shaft 32 of the gearbox.

In the beam diagram, this transmission is represented by beams 1 and 3, then a flat beam U ^b _ah = K + 1 to the upper horizontal to the level lqU = 0.47 + 0.477 = 0.947, with U ₃ = 8.85.

4th gear

Switch clutch A to the right position. Instead of a pair of gears 1, a pair of gears 2 works.

Prior to the ring gear 7 of the output tubular shaft 5, the torque is supplied in both second gear and then in the previous gear.

In the beam diagram, this transmission is represented by rays 2 and 3, then a flat beam U ^b _ah = K + 1 to the upper horizontal to the level lqU = 0.45 + 0.477 = 0.927, with U ₄ = 8.455.

5 gear

We switch the couplings A and B from the right to the left - we turn on the gears pair 1 and 2.

To the intermediate shaft 8, the torque is supplied in both 1st and 3rd gears. From the intermediate shaft 8 through a pair of gears 2 (10-13) through the clutch 16 (B), the torque is supplied to the ring gear 6 of the tubular output shaft 5 of the gearbox, then as in the 3rd and 4th gears.

In the beam diagram, this transmission is represented by rays 1 and 2, then a flat beam U ^b _ah = K + 1 to the upper horizontal to the level lqU = 0.02 + 0.477 = 0.497, with U ₅ = 3.14.

6th gear

We switch clutch A to the right position - direct transmission in gearbox, gears are out of operation.

Torque from the input shaft 2 along the ring gear 3 and clutch A is supplied to the gear housing 13, then as in the previous gear.

In the beam diagram, this transmission is represented by a flat beam U ^b _ah = K + 1 to the upper horizontal to the level lqU = 0.477, with U ₆ = 3.0.

7th gear

We switch clutches A and D to the left position, and couplings B and C to the right, - PM is turned off, only gearbox gears work, as in 1st and 3rd gears.

In the beam diagram, this transmission is represented by beams 1 and 3, then a vertical beam to the upper horizontal to the level lqU = 0.47, with U ₇ = 2.95.

8 gear

We switch clutch A from the left to the right position - the gearbox works as in 2nd and 4th gears.

In the beam diagram, this transmission is represented by rays 2 and 3, then a vertical beam to the upper horizontal to the level lqU = 0.45, with U ₈ = 2.818.

9 gear

We switch couplings A, B and E from the right position to the left, PM in the summing mode.

To the sun gear 19, the torque is transmitted, as in 1st and 2nd gears, and to the carrier 21, as in 5th gear.

In the beam diagram, this transmission is shown by rays 1 and 2 to the level lqU = 0.02, with U = 1.047, then the beam to the upper horizontal to the level lqU = 0.03, while U ₉ = 1.072, the beam from t .0:

n _b = -3000 / 2 + 3000 / 1,047 * 3/2 = 2798 rpm; u ₉ = 3000/2798 = 1.072.

10 gear

We switch the clutch E from the left position to the right - PM is switched off from work.

Torque is supplied to the ring gear 7 of the tubular output shaft 5 of the gearbox, as in the previous gear, then on carrier 21, as in the 7th and 8th gears.

In the beam diagram, this transmission is represented by beams 1 and 2, then a vertical beam to the upper horizontal to the level lqU = 0.02, with U ₁₀ = 1.047.

11 gear

We switch clutch A from the left position to the right - there is a direct transmission in the gearbox. When changing the parameters of gears KP and PM, the gear ratios will change.

Designations:

1 - gear housing

2 - input shaft KP,

3 - the first gear rim of the input shaft of the gearbox,

4 - the second gear rim of the input shaft of the gearbox.

5 - tubular output shaft KP,

6 - the first gear rim of the output shaft of the gearbox,

7 - the second gear rim of the output shaft of the gearbox,

8 - the intermediate shaft of the gearbox,

9-11 - gears of the intermediate shaft,

12, 13 - gears of the input shaft of the gearbox,

14 (A) is a three-position switching clutch on the first gear ring 3 of the input shaft 2 of the gearbox,

15 - gear output tubular shaft 5,

16 (B) is a three-position switching clutch on the first gear ring 6 of the output tubular shaft 5 of the gearbox,

17 - the gear crown of the shaft 18,

18 - the drive shaft of the sun gear PM,

19 - sun gear PM,

20 - satellites drove PM,

21 - drove PM,

22 - a tubular shaft drove 21 PM,

23 - the gear rim of the tubular shaft 22,

24 (C) - dual on-off clutch switching the second gear ring 7 of the tubular output shaft 5 KP,

25 - the output shaft drove 21,

26 - the gear rim of the output shaft 25 drove 21,

27 - epicyclic wheel PM,

28 - tubular output shaft of the epicyclic wheel 27,

29 - the ring gear of the tubular output shaft 28,

30 - a gear rim of the wall of the housing 1 of the gearbox,

31 - two-position single-shaft clutch gear ring gear 30,

32 - output shaft of the gearbox,

33 - gear ring of the output shaft 32,

34 (E) - two-position two-axle clutch for switching the gear ring 33 of the output shaft 32.

Claims (1)

A shaft-turning and starting device of a gas turbine installation, comprising a drive motor, a gearbox and an overrunning clutch of the compressor rotor, characterized in that the gearbox contains a three-shaft coaxial gearbox with three pairs of interlocked gears and a simple three-link planetary gear, three gears are mounted on the intermediate shaft of the gearbox parallel to the input shaft, on which two gears are freely mounted, between them on the shaft is fixed the first gear ring with a three-position clutch In addition, a tubular output shaft with a freely installed gear is freely installed, on the first gear ring of this shaft between the gears of the second and third rows there is a three-position switching clutch, on the second gear ring of this shaft there is a double two-position clutch, a second gear ring of the input shaft is fixed next to it and there are gear rims of the drive shaft of the sun gear and the tubular drive shaft of the planetary gear carrier, the satellites located on the axles of the carrier are engaged with the sun pole and also with an epicyclic wheel, which is mounted on the output tubular shaft with a gear ring, next to it are the gear ring of the output shaft of the carrier and the gear ring of the output shaft of the gearbox with a two-shaft two-position switching clutch, a single-shaft two-position clutch is mounted on the gear ring of the wall of the gear case with the ring gear of the tubular shaft of the epicyclic wheel.

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