RU2581269C1 - Engine turning and starting device of gas turbine plant - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: engine turning and starting device of gas turbine plant comprises drive motor, reduction gear and overrunning clutch compressor rotor. Gearbox contains specialised coaxial gearbox with pairs of inter-engaged gears and simple three-link planetary mechanism. At the input shaft gearbox two gears are freely installed between them is fixed first gear rim with three position clutch, and a tubular output shaft with freely mounted gears. On the front end of the tubular output shaft is fixed gear rim with three position clutch, at the second rim of this shaft there is a double two-position clutch with internal freely installed gear rim. Near the second ring gear of the tubular shaft are the second ring gear input shaft, toothed rims of drive shaft of the Sun gear and tubular shaft drive carrier of planetary gear. Satellites located on axles, engaged with Sun gear, as well as with epicyclic wheel, which is fixed on the output tubular shaft with rim next to it there is a rim of the output shaft of carrier. Two-position clutch is installed on the rim of the wall of the gearbox casing near the rim of the tubular shaft epicyclic wheel. Coaxially to the output shaft of carrier reduction gear output shaft is arranged with ring gear and two-position of double clutch. At the input shaft near the first ring gear of the tubular output shaft freely installed gear. Two gears are located on axis installed parallel to the input shaft. Gears between blocks of two-position shift collar is arranged with oppositely turned half-couplings, interconnected general shift yoke.

EFFECT: invention allows increasing the number and range of gear ratio turning gear and starting device.

1 cl, 2 dwg

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. 2053136 C1, B60K 17/08. Author V.I. Nekrasov. (January 27, 1996. Bull. No. 3).

The gearbox according to patent No. 2053136 provides eight gears that are transformed by PM in the summing mode, with a constant speed of the sun gear and a variable speed 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 an eight-stage three-shaft pine gearbox (gearbox), consisting of four pairs of interlocked gears and three switching clutches.

The technical solution according to patent No. 2053136 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.

For a shaft-turning and starting device of a gas turbine, reverse gears are not required.

; 3 - прямая передача в ПМ.The technical solution for VPU according to patent No. 2397344 C1 F02C 7/26 (Authors V.I. Nekrasov and I.A. Ivanov. Bull. No. 23 of 08.20.2010) contains a three-shaft 4-speed gearbox and a simple three-link planetary mechanism, which provide 11 gears located on five steps. Placing a double on / off clutch on the shafts between the gearbox and the PM, as well as the couplings between the wall of the gear case and the ring gear of the tubular shaft of the epicyclic wheel, allows the PM to be implemented in three modes: 1 - summing; 2 - mode $$U_{\text{ah}}^{\text{b}}=K+\mathrm{one}$$

; 3 - direct transmission to the PM.

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 - internal PM parameter, equal to the ratio of the number of teeth of the epicyclic wheel to the number of teeth of the sun gear.

This device has limited capabilities due to the insufficient range of gear ratios and the number of stages.

The objective of the invention is to expand the operational capabilities of the VPU (shaft-turning and starting device) GTU due to a significant increase in the number of gears and gear ratios.

The technical result is achieved by improving the technical solution for the patent No. 2397344.

The achievement of the technical result is ensured by the fact that the shaft-turning and starting devices 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 pairs of interlocked gears and a simple three-link planetary gear, two gearboxes are freely mounted on the input shaft of the gearbox gears, between them the first gear ring with a three-position switching clutch is fixed, and a tubular output shaft with a free position a gear on it, on the front end of this shaft a gear ring with a three-position switching clutch is fixed, on the second gear ring of this shaft there is a double two-position clutch with an internal freely mounted gear ring, next to the second gear ring of the tubular shaft there are a second gear ring of the input shaft, gear the crowns of the drive shaft of the sun gear and the tubular drive shaft drove the planetary mechanism; the satellites located on the axles of the carrier are engaged with the sun gear, as well as with the epicyclic wheel, which is mounted on the output tubular shaft with a gear rim, next to it is the gear rim of the output shaft of the carrier, a two-position clutch is mounted on the gear rim of the gearbox wall next to the gear the crown of the tubular shaft of the epicyclic wheel, coaxial with the output shaft of the carrier, is the output shaft of the gearbox with a gear ring and a two-position two-gear clutch, the device is characterized in that a gear is freely mounted on the input shaft next to the first gear rim of the tubular output shaft, two gear units are located on an axis mounted parallel to the input shaft, on the gears between the blocks there is a two-position switching clutch with oppositely deployed coupling halves interconnected by a common switching fork.

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

In FIG. 2 is a radial diagram of the gear ratios provided by the gearbox of FIG. 1. On the beam diagram, the gear ratios (U) are reflected by an uneven scale at the bottom of the horizontal. A uniform scale of gear ratios on a logarithmic scale (lqU) 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.

In the bearings of the gearbox housing 1 (see Fig. 1) is located the 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, axis 8 is installed, on which two gear units 9-12 are freely mounted. The gears 9, 10 and 11 of the axis 8 are engaged with gears 13, 14 and 15 freely mounted on the input shaft 2, between the gears 13 and 14 there is a first gear ring 3 on which a three-position switching clutch 16 (A) is installed. On the gear rims of the gears of the two middle rows (10-14 and 11-15), a double two-position switching clutch B is installed with oppositely deployed coupling halves 17 and 18 interconnected by the switching fork 19. A gear 20 is freely mounted on the tubular output shaft 5, engaged with the gear 12 of the axis 8. On the first gear rim 6 of the tubular output shaft 5 between the gears 15 and 20 there is a three-position switching clutch 21 (C). Next to the second gear ring 4 of the input shaft 2, there is a ring gear 22 mounted on a gear 23 of the sun gear 24 mounted coaxially to the input shaft 2 of the gearbox 24. The sun gear 24 is engaged with the satellites 25 mounted on the axles of the carrier 26, on the tubular shaft 27 of which the gear is fixed crown 28 located next to the ring gear 22 of the shaft 23 of the sun gear 24 drive. On the second ring gear 7 of the tubular output shaft 5, there is a double on-off shift clutch 29 (D) with an internal ring gear, freely installed oval regarding the coupling. A gear ring 31 is fixed to the output shaft 30 of the carrier 26. An epicyclic wheel 32 engaged with the satellites 25 is fixed to the tubular output shaft 33, at the end of which a gear ring 34 is located adjacent to the gear ring 31 of the output shaft 30 of the carrier 26. On the housing wall 1, next to the ring gear 34, there is a ring gear 35 on which a two-position single-shaft shift clutch 36 (E) is mounted. Coaxial with the output shaft 30 of the carrier 26 is the output shaft 37 of the gearbox, a gear ring 38 is fixed on it, on which a two-position two-crown switching clutch 39 (F) is installed.

The operation of the gearbox is as follows.

The planetary mechanism (PM), installed at the output of the gearbox, provides three options for operation:

The 1st variant of PM operation is a summing mode (∑), while the E and F couplings are in the left position (L), and the D clutch is in the right position (P).

The torque from the gearbox to the PM comes in two ways: the first from the input shaft 2 to the second gear ring 4, along the inner gear ring of the coupling 29 (D) to the gear ring 22 of the shaft 23 of the sun gear 24; the second is a tubular output shaft 5, its second gear rim 7, along the outer gear rims of the clutch 29 (D) to the gear rim 28 and the tubular shaft 27 of the carrier 26. On satellites 25, the power flows from the sun gear 24 and carrier 26 are added up and removed from the epicyclic wheels 32 along the tubular output shaft 33 to the ring gear 34, then along the coupling 39 (F) to the ring gear 38 and the output shaft 37 of the gearbox (see the upper position of the couplings D, E and F in Fig. 1).

This version of the PM is used in seven gears: 1, 2, 11, 12, 17, 22 and 23 (see table).

, при этом муфты Е и F находятся в правом положении (П), а муфта D - в левом (Л).II variant of PM operation - mode $$U_{\text{ah}}^{\text{b}}=K+\mathrm{one}$$

, while the couplings E and F are in the right position (P), and the clutch D is in the left (L).

Torque from the gearbox to the PM comes from the ring gear 7 of the tubular output shaft 5 through the outer ring gears of the clutch D in the left position to the ring gear 22, the sun gear drive shaft 23, which rotates the satellites 25 relative to the epicyclic wheel 32 stopped by the clutch E. Satellites 25 the carrier 26 is rotated three times slower than the sun gear (at K = 2), the torque is applied to the ring gear 31 through the shaft 30, along the coupling F in the right position (see the lower position of the couplings D, E and F in Fig. 1) by ring gear 38 and gearbox output shaft 37.

This option PM is used in eight gears: 3-8 and 13, 15.

The 3rd option of PM operation is direct transmission, while the D and F couplings are in the right position (P), and the E clutch is in the left (L) position.

The torque from the gearbox to the PM comes from the ring gear 7 of the tubular output shaft 5 through the outer ring gears of the coupling D in the right position on the ring gear 28 and the tube shaft 27 drove 26, along the output shaft 30 drove 26, on the ring gear 31, through the coupling 39 (F) to gear ring 38 and gearbox output shaft 37.

This option PM is used in eight gears: 9, 10, 14, 16, 18-21.

Four rows of gears KP, indicated by numbers in circles, provide 8 transmission options on the tubular output shaft 5.

1st option - the 2nd and 4th pairs of gears are working, while the couplings A and C are in the right position (P), and the clutch B is in the left (L).

From the drive motor (electric motor, ICE - internal combustion engine) through the input shaft 2 (see Fig. 1), through the gear ring 3 and the coupling 16 (A), the torque is supplied to the pair of gears 2 (14-10), then through the coupling half 18 to the second block of gears of the axis 8 and a pair of gears 4 (12-20), then along the clutch 21 (C) to the first gear ring 6 and the tubular output shaft 5.

In the beam diagram (see Fig. 2), beam 2 from t. 0 is directed down to the right in the middle horizontal, then beam 4 is moved up to the right lqU = 0.475, with U = 2.985, then a vertical beam, which corresponds to the 9th gear gearbox.

This option of the gearbox provides three gear reducers: 1, 3 and 9.

2nd option - the 3rd and 4th pairs of gears work, while all three couplings A, B and C are in the right position (P).

From the input shaft 2 along the gear ring 3, clutch A, gear 14 and half-coupling 17 (B), the torque is supplied to a pair of gears 3 (15-11), to the second gear block of the axis 8 and further as in the 1st embodiment.

On the beam diagram, rays 3 and 4 belong to this transmission. Ray 4 reaches the level lqU = 0.46, with U = 2.885, then a vertical beam, which corresponds to the 10th gear of the gearbox.

This option of the gearbox provides three gear reducers: 2, 4 and 10.

3rd option - all four pairs of gears work, while clutches B and C are in the right position (P), and clutch A is in the left (L).

From the drive shaft 2 through the clutch A and a pair of gears 13-9, the torque is supplied to the first gear block of the axis 8, then through a pair of gears 10-14, through the coupling half 17, then as in the 2nd embodiment.

In the beam diagram, this transmission is represented by rays: 1 - vertically down, 2 - left up, 3 - right down and 4 - right up, which go to the level lqU = 0.24 in the middle horizontal (U = 1,738), then a vertical ray, which corresponds to the 14th gear of the gearbox.

This option of the gearbox provides three gear reducers: 5, 11 and 14.

4th option - the 1st and 4th pairs of gears are working, while the couplings A and B are in the left position (L), and the coupling C is in the right (P).

From the drive shaft 2 through the clutch A and a pair of gears 13-9, the torque is supplied to the first block of gears of the axis 8, through the coupling half 18 to the second block of gears of the axis 8, then through the pair of gears 12-20.

In the beam diagram, this transmission is represented by beams 1 and 4 to the middle horizontal to the level lqU = 0.225 (U = 1.68), then a vertical beam, which corresponds to the 16th gear of the gearbox.

This option of the gearbox provides three gear reducers: 6, 12 and 16.

5th option - the 2nd and 3rd pairs of gears work, while the couplings B and C are in the left position (L), and the coupling A is in the right (P).

Until the second block of gears of the axis 8, the torque is supplied as in the 1st embodiment, then through the gears 11-15, to the coupling C and the tubular output shaft 5.

In the beam diagram, this transmission is represented by rays 2 and 3 to the middle horizontal to the level lqU = 0.015 (U = 1.035), then a vertical beam, which corresponds to the 18th gear of the gearbox.

This option of the gearbox provides three gear reducers: 7, 17 and 18.

6th option - direct transmission to the gearbox to the sun gear 24 along the drive shaft 2, the inner gear ring of the coupling D and the shaft 23, while the couplings A, B and C are in the neutral position (H).

On the beam diagram represented T. 0, is used in the 8th gear of the gearbox.

7th option - the 1st and 2nd pairs of gears are working, while the couplings A and C are in the left position (L), and the coupling B is in the right (P).

From the drive shaft 2 through the coupling A and a pair of gears 13-9, the torque is supplied to the first gear block of the axis 8, then through a pair of gears 10-14, the coupling half 17, gear 15, the coupling C to the tubular output shaft 5.

In the beam diagram, this transmission is represented by beams 1 and 2 to the middle horizontal to the level lqU = -0.225 (U = 0.596), then a vertical beam, which corresponds to the 20th gear transmission.

This option of the gearbox provides three gear reducers: 13, 20 and 22.

8th option - the 1st and 3rd pairs of gears work, while all three couplings A, B and C are in the left position (L).

From the drive shaft 2 through the coupling A and a pair of gears 13-9, the torque is supplied to the first gear block of the axis 8, through the coupling half 18, then through a pair of gears 11-15, the coupling C to the tubular output shaft 5.

In the beam diagram, this transmission is represented by beams 1 and 3 to the middle horizontal to the level lqU = -0.24 (U = 0.575), then a vertical beam, which corresponds to the 21st gear transmission.

This option of the gearbox provides three gear reducers: 15, 21 and 23.

Gearboxes are formed by options KP and PM

1st gear - 1.I (1st option in gearbox and 1st option in PM)

Clutches B, E and F are in the left position (L), couplings A, C and D are in the right position (P) - see the table under FIG. 2. The sun gear 24 receives a direct drive from the input shaft 2 along the inner gear ring of the clutch 29 (D). The carrier 26 receives a drive through a pair of gears 2 and 4 with a rotation speed lower than the sun gear 24.

In the beam diagram (Fig. 2), two beams are directed to a point on the upper horizontal, to the level lqU = 2.6, one of t. 0 from the rotation speed of the sun gear 24, the second from the rotation frequency of carrier 26.

The rotation frequency of the epicyclic wheel 32 and the output shaft of the gearbox 37, as well as the gear ratio of the gearbox are determined as follows:

; u₁=3000/7,5=400; lq400=2,6. $$n_b=u_{ba}^h{n}_a+u_{bh}^a{n}_h=-n_a/\mathrm{to}+n_h(\mathrm{to}+\mathrm{one})/\mathrm{to}=-3000/2+3000/\mathrm{2,985}*3/2=7.5\mathrm{about}b/m\mathrm{and}n$$

; u ₁ = 3000 / 7.5 = 400; lq400 = 2.6.

A slight change in the gear ratio of the gearbox leads to a significant change in the gear ratio of the gearbox. For example, U = 2.99;

; u₁=3000/5=600; lq600=2,778. Если lqU>3,0, то направление вращения выходного вала 37 изменяется на обратное. $$n_b=-n_a/\mathrm{to}+n_h(\mathrm{to}+\mathrm{one})/\mathrm{to}=-3000/2+3000/2.99*3/2=5\mathrm{about}b/m\mathrm{and}n$$

; u ₁ = 3000/5 = 600; lq600 = 2.778. If lqU> 3.0, then the direction of rotation of the output shaft 37 is reversed.

2nd gear - 2.I

Clutch B is switched to the right position - instead of a pair of gears 2 (14-10), a pair of gears 3 (15-11) is included in the operation, the gear ratio of which is slightly lower than that of the first pair.

From the input shaft 1 along the gear ring 3 and the coupling half 17 (B), the torque is supplied to a pair of gears 3 (15-11), to the second gear block of the axis 8 and then as in first gear.

On the beam diagram, rays 3 and 4 belong to this transmission. Ray 4 reaches the level lqU = 0.46, with U = 2.885.

n _b = -3000 / 2 + 3000 / 2.886 * 3/2 = 60 rpm; u ₂ = 3000/60 = 50; lq50 = 1.7.

A significant step of gear ratios at the output of the gearbox q = 600/50 = 12 is provided by an insignificant step inside the gearbox q = 2,985 / 2,8846 = 1,035, which allows shifting gears practically without breaking the power flow.

3rd gear - 1.II

. Эпициклическое колесо 32 остановлено трубчатым валом 33, зубчатым венцом 34, муфтой Е на зубчатом венце 35 стенки корпуса редуктора 1.Clutch B is returned to the left position, the positions of couplings D, E and F are reversed. In this case, the PM goes into mode $$U_{ah}^b=K+\mathrm{one}$$

. The epicyclic wheel 32 is stopped by the tubular shaft 33, the ring gear 34, the clutch E on the ring gear 35 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 D in the left position, on the gear rim 22, the drive shaft 23 of the sun gear 24, which rotates the satellites 25 relative to the stopped epicyclic wheel 32. The satellites 25 rotate the carrier 26 three times slower than the sun gear (at K = 2), on the shaft 30, the torque is supplied to the ring gear 31, along the clutch F in the right position (see the lower position of the clutches D, E and F in Fig. 1) to the ring gear 38 and the output shaft 37 of the gearbox.

к верхней горизонтали на уровень lqU=0,475+0,477=0,952, при этом U₃=8,96.In the beam diagram, this transmission is represented by rays 2 and 4, then a gentle beam $$U_{ah}^b=K+\mathrm{one}$$

to the upper horizontal to the level lqU = 0.475 + 0.477 = 0.952, with U ₃ = 8.96.

4th gear - 2.II

Clutch B is in the right position. Instead of a pair of gears 2, a pair of gears 3 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.

к верхней горизонтали на уровень lqU=0,46+0,477=0,937, при этом U₄=8,65.In the beam diagram, this transmission is represented by rays 3 and 4, then a gentle beam $$U_{ah}^b=K+\mathrm{one}$$

to the upper horizontal to the level lqU = 0.46 + 0.477 = 0.937, while U ₄ = 8.65.

5th gear - 3.II

Clutch A is switched from right to left - all pairs of gears are turned on.

From the drive shaft 2 through the clutch A and a pair of gears 13-9, the torque is supplied to the first gear block of the axis 8, then through a pair of gears 10-14, through the coupling half 17, then as in 4th gear.

к верхней горизонтали на уровень lqU=0,24+0,477=0,717, при этом U₅=5,21.In the beam diagram, this transmission is represented by rays: 1 - vertically down, 2 - left up, 3 - right down and 4 - right up, then a gentle beam $$U_{ah}^b=K+\mathrm{one}$$

to the upper horizontal to the level lqU = 0.24 + 0.477 = 0.717, while U ₅ = 5.21.

6th gear - 4.II

Clutch B is switched to the left position, the 1st and 4th pairs of gears are working. The torque to the first block of gears comes in as in the previous gear, then through the coupling half 18 to the second block of gears in axis 8, then in a pair of gears 12-20 as in the previous gear.

к верхней горизонтали на уровень lqU=0,225+0,477=0,702, при этом U₆=5,04.In the beam diagram, this transmission is represented by beams 1 and 4, then a flat beam $$U_{ah}^b=K+\mathrm{one}$$

to the upper horizontal to the level lqU = 0.225 + 0.477 = 0.702, with U ₆ = 5.04.

7th gear - 5.II

Clutch A is switched from the left position to the right, and clutch C is from the right position to the left, the 2nd and 3rd pairs of gears are working, the PM works as in 3-6th gears.

In the beam diagram, this transmission is represented by rays 2 and 3, then a gentle beam to the upper horizontal to the level lqU = 0.015 + 0.477 = 0.492, with U ₇ = 3.1.

8th gear - 6.II

Clutches A, B and C are switched to neutral position, PM in mode $$U_{ah}^b=K+\mathrm{one}$$

Torque enters the sun gear 24 directly through the input shaft 2, then as 3-7th gears.

In the beam diagram, this transmission is represented by a flat beam from t. 0 to the upper horizontal to the level lqU = 0.477, with U ₈ = 3.0.

9th gear - 1.III

Clutches A, C and D are switched to the right position, and couplings B and E are to the left, in the PM the direct gear, gears of the gearbox work as in the 1st and 3rd gears.

In the beam diagram, this transmission is represented by rays 2 and 4, then a vertical ray to the upper horizontal to the level lqU = 0.475, with U ₉ = 2.985.

10th gear - 2.III

Clutch B is switched from the left position to the right, in the PM direct transmission.

To the sun gear 24, the torque is transmitted by pairs of gears 3 and 4, as in 2nd and 4th gears.

In the beam diagram, this transmission is shown by rays 3 and 4 to the level lqU = 0.02, with U = 1.047, then the beam to the upper horizontal to the level lqU = 0.46, while U ₁₀ = 2.88, the beam also arrives from t. 0.

11th gear - 3.I

Clutches A and F are switched from the right to the left. All four pairs of gears are turned on, the PM operates in a summing mode.

Torque is applied to carrier 26 for all four pairs of gears in both 5th gear and further in 1st and 2nd gears.

In the beam diagram, this transmission is represented by rays 1, 2, 3, and 4, which reach the level lqU = 0.24 on the middle horizontal (U = 1.738), then the summing mode n _b = -3000 / 2 + 3000 / 1,738 * 3 / 2 = 1089.2 rpm; U ₁₁ = 3000 / 1089.2 = 2.754. lqU ₁₁ = 0.44.

12th gear - 4.I

Clutch B is switched from the right to the left. The 1st and 4th pairs of gears are turned on, the PM operates in a summing mode.

Torque is applied to carrier 26 through the 1st and 4th gear pairs, as in the 6th gear, then in the 1st, 2nd and 11th gears.

In the beam diagram, this transmission is represented by rays 1 and 4, which reach the level lqU = 0.225 on the middle horizontal (U = 1.68), then the summing mode n _b = -3000 / 2 + 3000 / 1.68 * 3/2 = 1178.6 rpm; U ₁₂ = 3000 / 1178.6 = 2.545. lqU ₁₁ = 0.406.

13th gear - 7.II

.Clutches B, E and F are switched from the left position to the right, and the clutch D from the right position to the left. 1st and 2nd pairs of gears are included, PM in mode $$U_{ah}^b=K+\mathrm{one}$$

.

Torque is applied to carrier 26 on the 1st and 2nd gear pairs, then as on the 2nd-8th gears.

к верхней горизонтали на уровень lqU=-0,225+0,477=0,252, при этом U₁₃=1,79.In the beam diagram, this transmission is represented by rays: 1 - vertically down, 2 - left up, then a gentle beam $$U_{ah}^b=K+\mathrm{one}$$

to the upper horizontal to the level lqU = -0.225 + 0.477 = 0.252, with U ₁₃ = 1.79.

14th gear - 3.III

Clutches C and D and F are switched from the left position to the right, and the clutch E from the right position to the left. All four pairs of gears are included, in PM direct transmission.

Torque is applied to carrier 26 as in 5th and 11th gears, then as in 9th and 10th gears.

In the radiation diagram, this transmission is represented by rays 1, 2, 3, and 4, which reach the level lqU = 0.24 in the middle horizontal (U ₁₄ = 1.738), then the vertical ray.

15th gear - 8.II

.Clutches B, C and D are switched from the right position to the left, and the clutch E from the left position to the right. 1st and 3rd pairs of gears are included, PM in mode $$U_{ah}^b=K+\mathrm{one}$$

.

Torque is applied to carrier 26 on the 1st and 3rd gear pairs, then as 3rd-8th and 13th gears.

к верхней горизонтали на уровень lqU=-0,24+0,477=0,237, при этом U₁₅=1,726.In the beam diagram, this transmission is represented by rays: 1 - vertically down, 3 - left up, then a gentle beam $$U_{ah}^b=K+\mathrm{one}$$

to the upper horizontal to the level lqU = -0.24 + 0.477 = 0.237, while U ₁₅ = 1.726.

16 transmission - 4.III

Clutch D is switched from left to right, and clutch E is from right to left. The 1st and 4th pairs of gears are included, in the PM direct transmission.

Torque enters carrier 26 on the 1st and 4th gear pairs in both 6th and 12th gears, and then in 10th, 11th and 14th gears.

In the beam diagram, this transmission is represented by beams 1 and 4, which reach the level lqU = 0.225 on the middle horizontal (U ₁₆ = 1.68), then a vertical beam.

17th gear - 5.I

Clutch A is switched from left to right, and couplings C and F from right to left. The 2nd and 3rd pairs of gears are included, PM in the summing mode.

Torque is transmitted to carrier 26 through the 2nd and 3rd pairs of gears as in 7th gear, then as 1st, 2nd, 11th and 12th gears.

In the radiation diagram, this transmission is represented by rays 2 and 3, which reach the level lqU = 0.015 (U = 1.035) in the middle horizontal, then the summing mode n _b = -3000 / 2 + 3000 / 1,035 * 3/2 = 2848 rpm ; U ₁₇ = 3000/2848 = 1.053. lqU ₁₇ = 0.023.

18th gear - 5.III

Clutch F is switched from left to right. The 2nd and 3rd pairs of gears are included, in the PM direct transmission.

In the radiation diagram, this transmission is represented by rays 2 and 3, which reach the level lqU = 0.015 (U ₁₈ = 1.035), then a vertical beam.

19th gear - direct - 6.III

Clutch B is switched from left to right. In KP and PM direct transmission. lqU = 0; U ₁₉ = 1.0.

On the beam diagram, one vertical ray from t. 0 up.

20th gear - 7.III

Clutch A is switched from the right to the left. The 1st and 2nd pairs of gears are included, in the PM direct transmission.

In the beam diagram, this transmission is represented by rays 1 and 2 to the level lqU = -0.225 (U ₂₀ = 0.596), then a vertical beam.

21 assists - 8.III

Clutch B is switched from the right to the left. The 1st and 3rd pairs of gears are included, in the PM direct transmission.

In the radiation diagram, this transmission is represented by rays 1 and 3 to the level lqU = -0.24 (U ₂₀ = 0.575), then a vertical beam.

22th gear - 7.I

Clutch B is switched from left to right, and clutch F from right to left. The 1st and 2nd pairs of gears are included, PM in the summing mode.

In the beam diagram, this transmission is represented by rays 1 and 2 to the level lqU = -0.225 (U = 0.596), then the rays to the upper horizontal to the level lqU = -0.305, with U ₂₂ = 0.496.

n _b = -3000 / 2 + 3000 / 0.596 * 3/2 = 6050 rpm; u ₂₂ = 3000/6050 = 0.496.

23 gear - 8.I

Clutch B is switched from the right to the left. The 1st and 3rd pairs of gears are included, PM in the summing mode.

In the beam diagram, this transmission is represented by rays 1 and 3 to the level lqU = -0.24 (U = 0.575), then the rays to the upper horizontal to the level lqU = -0.324, with U ₂₃ = 0.474.

n _b = -3000 / 2 + 3000 / 0.575 * 3/2 = 6326 rpm; u ₂₃ = 3000/6326 = 0.474.

The gearbox can provide 23 gears, which form 9 gear units with a wide distribution in the range: 1st and 2nd blocks in one gear, 3rd block - 3rd and 4th gears, 4th block - 5- I and 6th gear, 5th block - 7-12th gear, 6th block - 13-16th gear, 7th block - 17-19th gear, 8th block - 20 and 21st gears and 9th block - 22nd and 23rd gears. For the considered case: 1 - 400; 2 to 50; 3-8.96.8.65; 4-5.21, 5.04; 5-3.1, 3.0, 2.985, 2.88, 2.754, 2.545; 6 - 1.79, 1.738, 1.726, 1.68; 7 - 1,053, 1,035, 1,0; 8 - 0.596, 0.575; 9 - 0.496, 0.474. Such a distribution of gears across the blocks will ensure reliable start-up of the gas turbine and dynamic balancing of the gas turbine rotors. When choosing the GTU rotor acceleration algorithm — the gearshift order, it is necessary to take into account the small step between the 2nd and 3rd pairs of gears, which allows switching between these pairs of gears with clutch B with virtually no interruption in the power flow.

Designations:

1 - gear housing;

2 - input shaft gearbox;

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 tubular output shaft of the gearbox;

7 - the second gear rim of the tubular output shaft of the gearbox;

8 - axis gears KP;

9-12 - gears combined in two blocks, freely mounted on axis 8;

13-15 - gears freely mounted on the input shaft 2 of the gearbox;

16 (A) - three-position switching clutch on the first gear ring 3 of the input shaft 2 of the gearbox;

17, 18 - oppositely deployed coupling halves of a double on-off switching clutch B;

19 - switching fork of the coupling halves 17 and 18;

20 - gear, freely mounted on the tubular output shaft 5;

21 (C) - three-position switching clutch on the first gear ring 6 of the tubular output shaft 5 of the gearbox;

22 - gear ring of the shaft 23,

23 - the drive shaft of the sun gear PM,

24 - sun gear PM,

25 - satellites drove PM,

26 - drove PM,

27 - a tubular shaft drove 26 PM,

28 - the ring gear of the tubular shaft 27,

29 (D) - dual on-off switching clutch with an internal freely mounted gear ring of the second gear ring 7 of the tubular output shaft 5 of the gearbox,

30 - the output shaft drove 26,

31 - the gear ring of the output shaft 30 drove 26,

32 - epicyclic wheel PM

33 - tubular output shaft of the epicyclic wheel 32,

34 - the gear rim of the tubular output shaft 33,

35 - gear ring of the wall of the housing 1 of the gearbox,

36 (E) - two-position single-shaft clutch switching gears 35,

37 - output shaft of the gearbox,

38 - gear ring of the output shaft 37,

39 (F) - two-position two-axle clutch for switching the gear ring 38 of the output shaft 37.

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, the gearbox containing a three-shaft coaxial gearbox with pairs of interlocked gears and a simple three-link planetary mechanism, two gears are freely mounted on the input shaft of the gearbox, the first gear is fixed between them gear ring with a three-position switching clutch, and a tubular output shaft with a gear freely located on it, fixed to the front end of this shaft a gear ring with a three-position shift clutch is mounted, a double two-position clutch with an internal freely mounted gear ring is installed on the second gear ring of this shaft, a second gear ring of the input shaft, gear rings of the sun gear drive shaft and the carrier shaft of the drive carrier are located next to the second gear ring of the tubular shaft planetary gear; the satellites located on the axles of the carrier are engaged with the sun gear, as well as with the epicyclic wheel, which is mounted on the output tubular shaft with a gear rim, next to it is the gear rim of the output shaft of the carrier, a two-position clutch is mounted on the gear rim of the gearbox wall next to the gear the crown of the tubular shaft of the epicyclic wheel, coaxial with the output shaft of the carrier, is the output shaft of the gearbox with a gear ring and a two-position two-gear switching clutch, characterized in that at the input A gear is freely mounted on the shaft next to the first gear rim of the tubular output shaft, two gear units are located on an axis mounted parallel to the input shaft, on the gears between the blocks there is a two-position switching clutch with oppositely deployed coupling halves interconnected by a common switching fork.

Images