RU2583476C1 - 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. Reduction gear comprises gearbox with three 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 gear rim with three position clutch. Gear rim with three position clutch tubular output shaft is fixed on the front end, located between second and third rows of gears. At the second rim tubular output shaft there is a double two-position clutch, nearby it are rims Sun gear drive shaft 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. At the output of the second three-link planetary mechanism, and the gear box is misaligned. Parallel to the inlet shaft there is a secondary shaft with freely mounted unit of two gears and tubular output shaft with freely mounted gears with secured on secondary shaft three rims. First rim and three position clutch is fixed on the end face between housing and a unit of gears, second toothed rim is fixed between the rims of the tubular gearbox output shaft and tubular input shaft of carrier first, third gear rim is located between the rims of the tubular output shaft of the first planetary gear and tubular input shaft of carrier second planetary mechanism. Cage with five-way rim is freely installed at the output of the secondary shaft and the input shaft drive Sun gear of the second planetary mechanism. Reduction gear output shaft is fixed on the carrier of the second planetary mechanism.

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.

Known gas turbines with shaft-turning and starting devices (VPU). (1. Mogilnitsky I.P., Steshenko V.N. Gas-turbine units in the oil and gas industry. - M .: Nedra, 1971. - 160 pp. 2. Atlas of structures and schemes. Gas-turbine units. / Ed. Shubenko- Shubina. - M.: Mechanical Engineering, 1976.)

These devices are functionally separated and complex. First, the VPU (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 a compressor rotor speed sufficient to supply air with parameters that enable the combustion chamber and turbine to start. 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 two-shaft non-axial gearbox (KP) and a simple three-link planetary gear (PM) based on RU patent No. 2047506 C1, B60K 17/08. Author V.I. Nekrasov (10.11.95. Bull. No. 31).

The gear according to patent No. 2047506 provides 22 forward gears and 6 reverse gears. Four gears are implemented by PM in the summing mode, with a constant speed of the sun gear and a variable speed of the carrier or epicyclic wheel, the power flow is removed from the epicyclic wheel or carrier. The change in the rotational speed of the carrier or epicyclic wheel relative to the rotational speed of the sun gear is provided by a four-stage two-shaft non-axial gearbox consisting of three pairs of interlocked gears and three switching clutches. PM in each gearbox implements 5 forward gears and reverse gear.

The technical solution according to patent No. 2047506 has a complex PM drive with three coaxially placed shafts, it cannot provide the output of a massive rotor from a standstill and reliable start-up of a gas turbine without using the gas flow energy from the main gas pipeline, since the gear ratio of the low gear is small, the gear ratio range is insufficient, and the placement of gear ratios over the range is not optimal.

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

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 dated 08/08/2010) contains a three-shaft 4-speed gearbox and a simple three-link planetary mechanism, which provide 11 gears located in five steps.

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 device of the gas turbine installation consists of a drive motor, a gearbox and a freewheel clutch of the compressor rotor, while the gearbox contains a gearbox with three pairs of interlocked gears and a simple three-link planetary gear, two are freely mounted on the input shaft of the gearbox gears, between them a gear ring with a three-position switching clutch is fixed, a gear ring with a three-position tubular switching clutch the output shaft is mounted on the front end located between the second and third rows of gears, a double two-position clutch is installed on the second gear rim of this shaft, next to it are the 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 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 wall of the gearbox housing next to the gear rim of the tubular shaft of the epicyclic wheel, the difference is that the output is equipped with a second three-link planetary gear, the gearbox is misaligned, a secondary shaft with freely mounted block of two gears is located parallel to the input shaft a tubular output shaft with a gear freely located on it, with three gear rims fixed to the secondary shaft, the first gear rim with a three-position clutch An exception is fixed at the end between the housing and the gear block, the second gear ring is fixed between the gear rims of the tubular output shaft of the gearbox and the tubular input shaft of the carrier of the first planetary gear, the third gear ring is located between the gear rims of the tubular output shaft of the first planetary gear and the tubular input shaft of the carrier of the second planetary gear, a cage with a five-position gear ring is freely installed at the output of the secondary shaft and the second gear shaft of the sun gear drive a planetary mechanism, gear output shaft is mounted on the carrier of the second planetary gear.

The installation of the second PM with two operating modes significantly expands the range of gear ratios of the gearbox and provides reliable output from standstill and start-up of gas turbines of various masses by choosing the optimal gear ratio algorithm over a significant gearbox range.

In FIG. Figure 1 shows the kinematic diagram of the gearshift and launcher (VPU) gearbox of a gas turbine unit, consisting of an off-axis two-shaft four-speed gearbox and two three-link planetary gears (PM). In the lower part of the KP, the numbers of gear pairs for the table of the radiation diagram of FIG. 2.

In FIG. 2 shows a beam diagram of the gear ratios provided by the gearbox of FIG. 1. On the ray diagram, the gear ratios (U) are given in a uniform logarithmic scale (lq U), while the beam characterizing the gear ratio does not change its value. Point 0 on the lower horizontal indicates the input of torque into the gearbox, three beams 2, 1 and 3 go out from this point, corresponding to the gear ratios of the pairs of gears: U ₂ = 1.32; lq 1.32 = 0.12; U ₁ , = 1.68; lq 1.68 = 0.225; U ₃ = 3.16; lq 3.16 = 0.5. At the output of the gearbox we get four gears with gear ratios: U _kp1 = U ₁ × (1 / U ₂ ) × U ₃ = 1.68 × 1 / 1.32 × 3.16 = 4.02; lq 4.02 = 0.605; U _kn2 = U ₃ = 3.16; lq 3.16 = 0.5; U _cp3 = U ₁ = 1.68; lq 1.68 = 0.225; U _kn4 = U ₂ = 1.32: lq 1.32 = 0.12.

; lq 0,38=-0,42; 2. $$U_{пм1}^{\text{'}}=U_{hb}^a=К/\left(К+1\right)=\mathrm{1,62}/\mathrm{2,62}=\mathrm{0,62}$$

; lq 0,62=-0,21; 3. U_пм1п=U=1,0; lq 1,0=0,0; 4. $$U_{пм1м}=U_{ah}^b=К+1=\mathrm{2,62}$$

; lq 2,52=0,42; а также две передачи в суммирующем режиме, где U - передаточное число, индекс вверху указывает на остановленное звено ПМ «b» - эпициклическое колесо, индексы внизу «ah» - звенья входа (солнечная шестерня) и выхода (водило) потока мощности. К=Z_b/Z_a - внутренний параметр ПМ, равный отношению числа зубьев эпициклического колеса к числу зубьев солнечной шестерни.The rays of the gear ratios provided by the first planetary mechanism (PM 1) with the internal parameter K ₁ = 1.62 are shown in the middle part of the diagram. This PM implements four transmission options: 1. $$U_{Pm\mathrm{one}}^{"}=U_{ha}^b=\mathrm{one}/\left(\mathrm{TO}+\mathrm{one}\right)=\mathrm{one}/2.62=0.38$$

; lq 0.38 = -0.42; 2. $$U_{Pm\mathrm{one}}^{\text{'}\text{'}}=U_{hb}^a=\mathrm{TO}/\left(\mathrm{TO}+\mathrm{one}\right)=\mathrm{1,62}/2.62=0.62$$

; lq 0.62 = -0.21; 3. U _pm1n = U = 1.0; lq 1.0 = 0.0; four. $$U_{Pm\mathrm{one}m}=U_{ah}^b=\mathrm{TO}+\mathrm{one}=2.62$$

; lq 2.52 = 0.42; as well as two gears in the summing mode, 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.

n_h=-n_a/к+n_h(к+1)/к=-1000/1,62+1000/(4,02/1,68)×2,62/1,62=56,6 об/мин; U_пм1=1000/56,6=17,7; lq 17,7=1,25. На выходе 1-го ПМ получаем 18 передач: по четыре варианта на каждой из 4-х передач КП и две суммирующие передачи.The summarizing PM mode is ensured by applying torque to the sun gear and the carrier at the output of the torque from the epicyclic wheel. If at the entrance to the 1st PM the rotation speed of the sun gear n _a = 1000 rpm, then at the output we get

n _h = -n _a / k + n _h (k + 1) / k = -1000 / 1.62 + 1000 / (4.02 / 1.68) × 2.62 / 1.62 = 56.6 r / min; U _pm1 = 1000 / 56.6 = 17.7; lq 17.7 = 1.25. At the output of the 1st PM we get 18 transmissions: four variants in each of the 4 gears of the gearbox and two summing transmissions.

; lq 6=0,78. На выходе редуктора имеем 36 вариантов передач, которые позволяют выбрать оптимальный алгоритм передаточных чисел для вывода из состояния покоя ГТУ различной массы и разгона их до пускового режима, исключая резонансные частоты низших порядков.In the upper part of the diagram, the rays of gear ratios of the 2nd PM are presented, which implements two transmission options: 1. U = 1,0 - vertical beams; 2. $$U_{ah}^b={\mathrm{TO}}_2+\mathrm{one}=6$$

; lq 6 = 0.78. At the output of the gearbox, we have 36 transmission options that allow you to choose the optimal gear ratio algorithm for outputting various masses of gas turbines from idle state and accelerating them to the starting mode, excluding lower-order resonant frequencies.

Above the diagram is a table of gears, the state of the shift clutches during these gears and the included elements of an off-axis gearbox and two PM.

The input shaft 2 is located in the supports of the casing 1 of the VPU gearbox (see Fig. 1), the secondary shaft 3 of the non-coaxial twin-shaft gearbox and the sun gear of the first PM (PM1), the shaft of the second sun gear of the second PM (PM2), output gear shaft 5. On the secondary shaft 3, there is a tubular output shaft KP 6. On the input shaft 2, gear 7 and the gear block 8 and 9 are freely mounted, and on the secondary shaft 3 the gear block 10 and 11 is also freely mounted, engaged with gears 7 and 8 of the input shaft 2, respectively A gear 12 is freely mounted on the tubular output shaft 6, engaged with the gear 9 of the input shaft 2. A three-position clutch 14 (A) of the secondary shaft is mounted on the gear rim 13 mounted on the front end of the secondary shaft 3 between the housing 1 and the gear block 10, 11 . On the gear ring 15, mounted on the input shaft 2 between the gear 7 and the gear block 8 and 9, a three-position clutch 16 (B) of the input shaft is installed. A gear ring 17 is fixed on the tubular output shaft 6 between the gears 11 and 12, on which the three-position coupling 18 (C) of the tubular output shaft is located, and a two-position gear ring 19 is mounted on the output of the tubular output shaft 6, on which the two-position coupling 20 (D) is located KP exit. At the output of the secondary shaft 3, the sun gear 21 of the first PM, the gear rim 22 of the inlet of the sun gear 21 and the gear rim 23 of the output of the sun gear 21 are fixed. The sun gear 21 is engaged with the satellites 24, the axes of which are installed in the carrier 25. At the entrance of the carrier 25, a tubular input a shaft 26 with a gear rim 27, and at the output a tubular output shaft 28 with a gear rim 29. The satellites 24 are engaged with the epicyclic wheel 30 of the first PM, a tubular shaft 32 with a gear rim 33 is fixed on the casing 31 of this wheel. A gear is mounted on the wall of the housing 1 the fourth crown 34, on which the on-off clutch 35 (E) of the stop of the epicyclic wheel PM1 is located. Between the shafts 3 and 4, a ferrule 36 with a five-position gear ring is freely mounted, on which are located the three-position clutch 37 (F) of the output of the first PM for selective connection with the gear rims 23, 29 and 33, as well as the two-position clutch 38 (G) of the input of the second PM. The sun gear 39 of the second PM is fixed to the output of the shaft 4, a ring gear 40 is fixed at the input of this shaft next to the yoke 36. The sun gear 39 is engaged with the satellites 41 mounted on the axles of the carrier 42, which is mounted on the output shaft 5, on the tubular shaft 43 of the drive the carrier 42 has a gear ring 44 fixed. The satellites 41 are engaged with the epicyclic wheel 45 of the second PM, this wheel is fixed on the housing 1.

The operation of the gearbox is as follows.

The first (lowest) gear in a two-shaft misaligned gearbox is provided by the serial connection of all three pairs of gears (see Fig. 2 below) - beam 1 from t. 0 on the lower horizontal to the right up, then beam 2 to the left down and flat beam 3 to the right up. In this case, clutch A is in the neutral position (H), clutch B is in the left (L), and clutch C is in the right (P) position (see Fig. 1). The torque from the input shaft 2 by the clutch B is transmitted to the first row of gears (gears 7-10), through the block of the secondary shaft to the second row of gears (gears 11-8), which in this case works in an accelerating mode (gear ratio is less than one), on the input shaft block to the third row of gears (gears 9-12), then on the coupling C to the tubular output shaft 6 and the ring gear 19. The gear ratio of this transmission is U _kp1 = 1.68 × 1 / 1.32 × 3.16 = 4.02; lq 4.02 = 0.605. Excluding summing gears 1, 2, 5, and 8, this gearbox of the gearbox after the 1st and 2nd PM is used in 8 gears: 3, 7, 11, 13, 15, 22, 27, 30 gears of the gearbox ( see the top row of the table of Fig. 2)

The second gear in the gearbox is realized only by the third pair of gears. Clutch B is switched to the right position (P). The torque from the input shaft 2 through the clutch B enters the gear block 8, 9, then through a pair of gears 9-12 and through the clutch C to the tubular shaft 6 and the _ring gear 19. U _kp2 = 3.16, lq 3.16 = 0 ,5. At the output of the gearbox it is 4, 10, 12, 16, 18, 25, 28, 32nd gears.

The third gear in the gearbox is provided by the first pair of gears, clutches B and C in the left position. U _cp3 = 1.68; lq 1.68 = 0.225. At the output of the gearbox it is 6, 14, 19, 21, 23, 29, 33, 35th gear.

The fourth gear in the gearbox is realized by the second pair of gears, the clutch B is switched to the right position. U _kn4 = 1.32: lq 1.32 = 0.12. At the output of the gearbox is 9, 17, 20, 24, 26, 31, 34, 36th gear.

1 gear reduction

Clutches A, C and D are in the right (P) position, couplings B, E and G are in the left (L) position, and clutch F is in position I (see the table above Fig. 2 on the right).

From the drive motor (electric motor, ICE - internal combustion engine) through the input shaft 2 (see Fig. 1), along the gear ring 15 and the coupling 16 (B), the torque is supplied to the pair of gears 1 (7-10), through the coupling 14 (A), gear ring 13 and the secondary shaft 3 on the sun gear 21 of the 1st PM. Drove 25 receives a drive through three pairs of gears 1, 2 and 3 through clutch 18 (C) to the gear ring 17 of the tubular output shaft 6, to the gear ring 19 of the gearbox output, by the two-position clutch 20 (D), the ring gear 27 and the tubular input shaft 26 with a rotation speed lower than the sun gear 21. On the satellites 24, power flows from the sun gear 21 and the carrier 25 are added up and removed from the epicyclic wheel 30 along the casing of this wheel 31, the tubular output shaft 32 to the ring gear 33, then along the three-position output clutch 1st PM 37 (F) for a clip of 36 s five-position m gear, then on the on-off coupling of the input of the 2nd PM 38 (G) to the gear gear 40, the shaft 4 of the sun gear drive 39 of the 2nd PM, the sun gear 39 rotates the satellites 41, which, rolling around the fixed epicyclic wheel 45, rotate drove 42 and the output shaft 5 of the gearbox with a low speed.

; lq 6=0,78 к т. 1 на верхней горизонтали.On the beam diagram (see Fig. 2) this transmission belongs to: 1st stream - from t. 0 beam 1 to the right upwards, then the dotted line of the hollow right to upwards U _pm1Σ = 17.7; lq 17.7 = 1.25; 2nd stream - from t. 0 three consecutive rays: 1, 2 and 3, then a dashed line that converges with the previous dashed line at a point on the third horizontal from below, then a gentle ray $$U_{ah}^b=\mathrm{TO}+\mathrm{one}=6$$

; lq 6 = 0.78 to t. 1 on the upper horizontal.

Gear ratio 1st gear

U ₁ = U _cp3 U _pm1 U _pm2m = 1.68 × 17.7 × 6.0 = 178.4; lq 178.4 = 2.25.

2nd gear

We switch clutch B to the right (P) position - instead of a pair of gears 1 (7-10), we include a pair of gears 2 (8-11), the gear ratio of which is slightly lower than that of the first pair.

From the input shaft 2 through the gear ring 15 and the clutch 16 (B), the torque is supplied to a pair of gears 2 (8-11), then to the clutch 14 (A), the gear ring 13, the secondary shaft 3 and the sun gear 21, the second flow of torque moment is transmitted only by a pair of gears 3 (9-12), then - as in first gear.

On the ray diagram this transmission belongs to rays 2 and 3, then dashed lines and a gentle beam to t. 2.

Gear ratio 2nd gear

U ₂ = U _kn4 U _pm1 U _pm2m = 1.32 × 17.7 × 6.0 = 140.2; lq 140.2 = 2.15.

3rd gear

Compared to 1st gear, we switch clutch A to the neutral position, clutch D to the left, clutch E to the right, and clutch F to position II. In this case, the 1st PM passes from the summing mode to the K + 1 mode. The housing 31 of the epicyclic wheel 30 is stopped by the tubular shaft 32, the ring gear 33, the coupling 35 (E) on the ring gear 34 of the wall of the gear housing 1.

To the gear ring 19 of the output tubular shaft 6, the torque is supplied, as in the first gearbox. Then, via the on-off clutch 20 (D) of the gearbox output to the gear ring 22, the secondary shaft 3 and the sun gear 21, which rotates the satellites 24 relative to the stopped epicyclic wheel 30. The satellites 24 rotate the carrier 25 more slowly than the sun gear, the torque is transmitted to the tubular shaft 28 ring gear 29, along the three-position clutch 37 (F) of the PM1 outlet in position II, then - as in previous gears.

к т. 3 на верхней горизонтали.On the beam diagram, this transmission is represented by rays 1, 2 and 3, then two gentle beams of the 1st and 2nd PM in the mode

to t. 3 on the upper horizontal.

Gear ratio 3rd gear

U ₃ = U _{KP1 pm2m} mU U _PM1 = 4,02 × 2,62 × 6,0 = 63,19 ; lq 63.19 = 1.8.

4th gear

Switch clutch B to the right position. Instead of three pairs of gear wheels, only a pair of gears 3 works.

к т. 4 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 3, then two gentle beams of the 1st and 2nd PM in the mode

to t. 4 on the upper horizontal.

Gear ratio 4th gear

U ₄ = U _kn2 U _pm1m U _pm2m = 3.16 × 2.62 × 6.0 = 49.68; lq 49.68 = 1.7.

5 gear

в режим прямой передачи с U_пм2п=1,0.Compared with the 1st gear, we switch the clutch G from the left to the right position, while the 2nd PM goes from mode

direct transmission mode with U _pm2p = 1.0.

Until the 2nd PM, the torque arrives as in the 1st (summing) gear. From the on-off coupling 38 (G) of the PM2 input, the torque is supplied to the ring gear 44 of the tubular shaft 43, then along the carrier 42 to the output shaft 5 of the gearbox.

The following diagrams belong to this transmission diagram: 1st stream - from t. 0 beam 1 to the right upwards, then the dashed line of the hollow right to upwards u _pm1Σ = 17.7; lq 17.7 = 1.25; 2nd stream - from t. 0 three consecutive rays: 1, 2 and 3, then a dashed line that converges with the previous dashed line at a point on the third horizontal from below, then a vertical ray U = 1 to t. 5 on the upper horizontal.

5th gear ratio

U ₅ = u _kp3 u _pm1Σ u _pm2p = 1.68 × 17.7 × 1.0 = 29.74; lq 29.74 = 1.47.

6th gear

Compared with the 3rd gear, we switch the clutch C from the right to the left position - in the two-shaft gearbox, instead of three pairs of gears, only the 1st pair works - instead of the 1st gear we get the 3rd gear of the gearbox.

к т. 6 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 1 and gentle beams of the 1st and 2nd PM

to t. 6 on the upper horizontal.

6th gear ratio

U ₆ = U _cp3 U _pm1m U _pm2m = 1.68 × 2.62 × 6.0 = 26.41; lq 26.41 = 1.42.

7th gear

We switch couplings C and D to the right position, and clutch E to the left. KP in 1st gear, there are three pairs of gears, 1st PM in direct gear.

к т. 7 на верхней горизонтали.In the beam diagram, this transmission is represented by beams 1, 2, and 3, then the vertical beam of the 1st PM and the gentle 2nd PM

to t. 7 on the upper horizontal.

7th gear ratio

U = U ₇ U _{KP1 pm1m pm2m} U = 4,02 × 1,0 × 6,0 = 24,12 ; lq 24.12 = 1.38.

8 gear

Compared to the 5th gear, we switch the clutch B from the left to the right position - the gearbox and the 1st PM works as in the 2nd (summing) gear, and the 2nd PM - in the direct one.

On the ray diagram, this transmission belongs to rays 2 and 3, then dashed lines and a vertical ray to t. 8 on the upper horizontal.

8th gear ratio

U ₈ = U _kn4 U _pm1 U _pm2p = 1.32 × 17.7 × 1.0 = 23.36; lq 23.36 = 1.37.

9 gear

Compared to the 6th gear, we switch clutch B from the left to the right position - instead of the 1st pair, the 2nd pair of gears works.

к т. 9 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 2 and gentle beams of the 1st and 2nd PM

to t. 9 on the upper horizontal.

9th gear ratio

U ₉ = U _kn4 U _pm1m U _pm2m = 1.32 × 2.62 × 6.0 = 20.75; lq 20.75 = 1.32.

10 gear

Compared to 4th gear, we switch clutch D from left to right, and clutch E from right to left — 1st PM works in direct gear.

к т. 10 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 3, then the vertical beam of the 1st PM and the flat beam of the 2nd PM in the mode

to t. 10 on the upper horizontal.

10th gear ratio

U ₁₀ = U _kn2 U _pm1p U _pm2m = 3.16 × 1.0 × 6.0 = 18.96; lq 18.96 = 1.28.

11 gear

; lq 2,52=0,42 переведен в режим 2. $$U_{hb}^a=К/\left(К+1\right)=\mathrm{1,62}/\mathrm{2,62}=\mathrm{0,62}$$

; lq 0,62=-0,21, при этом солнечная шестерня 21 с вторичным валом 3 зубчатым венцом 13 остановлена муфтой 14 (A) относительно корпуса 1. Крутящий момент от КП поступает на зубчатый венец 27 трубчатого вала 26 входа водила 25 и снимается с эпициклического колеса 30 по корпусу 31, трубчатому валу 32 и зубчатому венцу 33 на трехпозиционную муфту 37 (F) и далее - как на предыдущих передачах. На лучевой диаграмме эта передача представлена лучами 1, 2 и 3, далее луч вверх налево 1-го ПМ, затем пологий луч вверх направо 2-го ПМ в режиме

к т. 11 на верхней горизонтали.Compared to 3rd gear, we switch clutch A from neutral to the left position, clutch D from left to right, clutch F from position II to position I. In the 2nd gear, the 3rd gear pair works, 1 th PM from mode 4. $$U_{ah}^b=\mathrm{TO}+\mathrm{one}=2.62$$

; lq 2.52 = 0.42 is set to mode 2. $$U_{hb}^a=\mathrm{TO}/\left(\mathrm{TO}+\mathrm{one}\right)=\mathrm{1,62}/2.62=0.62$$

; lq 0.62 = -0.21, while the sun gear 21 with the secondary shaft 3 of the ring gear 13 is stopped by the clutch 14 (A) relative to the housing 1. Torque from the gearbox arrives at the ring gear 27 of the tubular shaft 26 of the carrier 25 input and is removed from epicyclic wheels 30 along the housing 31, the tubular shaft 32 and the ring gear 33 to the three-position clutch 37 (F) and then - as in previous gears. In the beam diagram, this transmission is represented by beams 1, 2, and 3, then the beam goes up to the left of the 1st PM, then the gentle beam goes up to the right of the 2nd PM in the mode

to t. 11 on the upper horizontal.

11th gear ratio

lq 14,95=1,175.

lq 14.95 = 1.175.

12 gear

Compared to the previous transmission, we switch clutch B from the left to the right position - instead of three pairs of gears, only the third pair works.

к т. 12 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 3, then the beam goes up to the left of the 1st PM, then the flat beam goes up to the right of the 2nd PM in the

to t. 12 on the upper horizontal.

12th gear ratio

lq 11,76=1,07.

lq 11.76 = 1.07.

13 gear

работает 1-й ПМ.Compared to the 7th gear, we switch the clutch D from the right to the left position, the clutches E and G from the left to the right position instead of the 2nd PM in the mode

The 1st PM works.

, затем вертикальный луч вверх к т. 13 на верхней горизонтали.In the beam diagram, this transmission is represented by beams 1, 2 and 3, then the beam goes up to the right of the 1st PM in the mode

, then the vertical ray up to t. 13 on the upper horizontal.

13th gear ratio

U = U ₁₃ U _{KP1 pm1m pm2p} U = 4,02 × 2,62 × 1,0 = 10,53 ; lq 10.53 = 1.02.

14 gear

Compared to the 10th gear, we switch clutches B and C from the right to the left position. Instead of the 3rd pair of gears of the gearbox, the 1st pair of gears works.

к т. 14 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 1, then the vertical beam of the 1st PM, then the flat beam of the 2nd PM in the mode

to t. 14 on the upper horizontal.

14th gear ratio

U ₁₄ = U _cp3 U _pm1p U _pm2m = 1.68 × 1.0 × 6.0 = 10.08; lq 10.08 = 1.003.

15 gear

lq 0,38=-0,42.Compared to the 7th gear, we switch clutch E from left to right, and clutch F - from position II to position III. 1st PM works in mode 1.

lq 0.38 = -0.42.

In the 1st PM, the epicyclic wheel 30, its body 31, the tubular shaft 32 and the ring gear 33 are stopped relative to the ring gear 34 of the wall of the gearbox housing 1 with the coupling 35 (E) in the right position, the torque after the gearbox arrives at the ring gear 27 of the tubular shaft 26 drove 25 and removed from the sun gear 21, the secondary shaft 3, the ring gear 23, the three-position clutch 37 (F) in position III on the yoke 36 (see Fig. 1), then - as in the previous gear.

, затем пологий луч 2-го ПМ в режиме $$U_{ah}^b$$

к т. 15 на верхней горизонтали.In the beam diagram, this transmission is represented by beams 1, 2, and 3, then from left to top the gentle beam of the 1st PM in the mode $$U_{ha}^b$$

, then the flat beam of the 2nd PM in the mode $$U_{ah}^b$$

to t. 15 on the upper horizontal.

15th gear ratio

lq 9,17=0,96.

lq 9.17 = 0.96.

16 gear

Compared with the 13th gear, we switch clutch B from the left to the right position - instead of three pairs of gears, only the third pair works.

, затем вертикальный луч 2-го ПМ к т. 16 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 3, then the beam goes up to the right of the 1st PM in the mode $$U_{ah}^b$$

, then the vertical beam of the 2nd PM to t. 16 on the upper horizontal.

16th gear ratio

U ₁₆ = U _kn2 U _pm1m U _pm2n = 3.16 × 2.62 × 1.0 = 8.28; lq 8.28 = 0.92.

17 gear

Compared to the 14th gear, we switch clutch B from the left to the right position - instead of the 1st pair of gears, the 2nd pair is working.

к т. 17 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 2, then the vertical beam of the 1st PM, then the flat beam of the 2nd PM in the mode

to t. 17 on the upper horizontal.

17th gear ratio

U ₁₇ = U _kn4 U _pm1p U _pm2m = 1.32 × 1.0 × 6.0 = 7.92; lq 7.92 = 0.9.

18 gear

Compared to the 15th gear, we switch clutch B from the left position to the right, and clutch D from the right position to the left - instead of 3 pairs of gears, the 3rd pair works.

, затем пологий луч 2-го ПМ в режиме $$U_{ah}^b$$

к т. 18 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 3, then from left to top the flat beam of the 1st PM in the mode $$U_{ha}^b$$

, then the flat beam of the 2nd PM in the mode $$U_{ah}^b$$

to t. 18 on the upper horizontal.

Gear ratio 18th gear

lq 7,2=0,86.

lq 7.2 = 0.86.

19 gear

Compared to the 12th gear, we switch clutches B and C from the right to the left position. Instead of the 3rd pair of gears of the gearbox, the 1st pair of gears works.

, затем пологий луч 2-го ПМ в режиме

к т. 19 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 1, then the beam of the 1st PM in the mode $$U_{hb}^a$$

, then the flat beam of the 2nd PM in the mode

to t. 19 on the upper horizontal.

19th gear ratio

lq 6,25=0,8.

lq 6.25 = 0.8.

20 gear

Compared to the previous transmission, we switch clutch B from the left to the right position - instead of the 1st pair of gears, the 2nd pair is working.

, затем пологий луч 2-го ПМ в режиме

к т. 20 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 2, then the beam of the 1st PM in the mode $$U_{hb}^a$$

, then the flat beam of the 2nd PM in the mode

to t. 20 on the upper horizontal.

Gear ratio of the 20th gear

lq 4,91=0,69.

lq 4.91 = 0.69.

21 gears

Compared to 16th gear, we switch clutches B and C from right to left. Instead of the 3rd pair of gears of the gearbox, the 1st pair of gears works.

, далее вертикальный луч 2-го ПМ к т. 21 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 1, then the flat beam of the 1st PM in the mode

, then the vertical beam of the 2nd PM to t. 21 on the upper horizontal.

Gear ratio 21st gear

U ₂₁ = U _cp3 Upm ₁ U _pm2 = 1.68 × 2.62 × 1.0 = 4.4; lq 4.4 = 0.64.

22 gear

Compared to the previous transmission, we switch clutches C and D from the left to the right position, and the clutch E from the right to the left position - instead of the first pair of gears, all three pairs work, and both PM transmit direct torque to the carrier in direct transmission.

On the beam diagram, this transmission is represented by rays 1, 2 and 3, then two vertical rays to t.22 on the upper horizontal.

Gear ratio 22nd gear

U = U ₂₂ U _{KP1 pm1p pm2p} U = 4.02 × 1.0 × 1.0 = 4.02; lq 4.02 = 0.605.

23 gear

Compared to the 18th gear, we switch the clutches B and C from the right to the left position, and the clutch D from the left to the right position - instead of the 3rd gear pair, the 1st pair works.

, затем пологий луч 2-го ПМ в режиме $$U_{ah}^b$$

к т. 23 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 1, then from left to top the flat beam of the 1st PM in the mode $$U_{ha}^b$$

, then the flat beam of the 2nd PM in the mode $$U_{ah}^b$$

to t. 23 on the upper horizontal.

23rd gear ratio

lq 3,83=0,58.

lq 3.83 = 0.58.

24 gear

Compared to the 21st gear, we switch clutch B from the left to the right position - instead of the 1st pair of gears, the 2nd pair is working.

, далее вертикальный луч 2-го ПМ к т. 24 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 2, then the flat beam of the 1st PM in the mode

, then the vertical beam of the 2nd PM to t. 24 on the upper horizontal.

24th gear ratio

U ₂₄ = U _kn4 U _pm1m U _pm2p = 1.32 × 2.62 × 1.0 = 3.46; lq 3.46 = 0.54.

25 gear

Compared to the 22nd gear, we switch the clutch B from the left to the right position - instead of 3 pairs of gears, the 3rd pair works.

In the beam diagram, this transmission is represented by beam 3, then two vertical rays to t. 25 on the upper horizontal.

Gear ratio 25th gear

U ₂₂ = U _kn2 U _pm1p U _pm2p = 3.16 × 1.0 × 1.0 = 3.16; lq 3.16 = 0.5.

26 gear

Compared to the 23rd gear, we switch clutch B from the left to the right position - instead of the 1st pair of gears, the 2nd pair is working.

, затем пологий луч 2-го ПМ в режиме $$U_{ah}^b$$

к т. 23 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 2, then from left to top the flat beam of the 1st PM in the mode $$U_{ha}^b$$

, then the flat beam of the 2nd PM in the mode $$U_{ah}^b$$

to t. 23 on the upper horizontal.

23rd gear ratio

lq 3,01=0,48.

lq 3.01 = 0.48.

27 gear

Compared with the 11th gear, we switch the clutch G from the left to the right position - the 2nd PM in direct gear.

In the beam diagram, this transmission is represented by rays 1, 2, and 3, then the ray up to the left of the 1st PM, then the vertical beam of the 2nd PM to t. 27 on the upper horizontal.

Gear ratio 27th gear

lq 2,49=0,4.

lq 2.49 = 0.4.

28 gear

Compared to the previous transmission, we switch clutch B from the left to the right position - instead of 3 pairs of gears, the 3rd pair works.

In the beam diagram, this transmission is represented by beam 3, then the ray up to the left of the 1st PM, then the vertical beam of the 2nd PM to t. 28 on the upper horizontal.

Gear ratio 28th gear

lq 1,96=0,29.

lq 1.96 = 0.29.

29 gear

Compared to the 25th gear, we switch the clutches B and C from the right to the left position - instead of the 3rd pair of gears, the 1st pair works.

In the beam diagram, this transmission is represented by beam 1 and two vertical PM rays to t. 29 on the upper horizontal.

Gear ratio 29th gear

U ₂₉ = U _cp3 U _pm1p U _pm2p = 1.68 × 1.0 × 1.0 = 1.68; lq 1.68 = 0.225.

30 gear

Compared to the 15th gear, we switch the clutch G from the left to the right position - the 2nd PM in direct gear.

, затем вертикальный луч 2-го ПМ к т. 30 на верхней горизонтали.In the beam diagram, this transmission is represented by beams 1, 2, and 3, then from left to top the gentle beam of the 1st PM in the mode $$U_{ha}^b$$

, then the vertical beam of the 2nd PM to t. 30 on the upper horizontal.

30th gear ratio

lq 1,53=0,185.

lq 1.53 = 0.185.

31 gear

Compared to the 29th gear, we switch clutch B from the left to the right position - instead of the 1st pair of gears, the 2nd pair is working.

In the beam diagram, this transmission is represented by beam 2 and two vertical PM beams to t. 31 on the upper horizontal.

Gear ratio 31st gear

U ₃₁ = U _kn4 U _pm1p U _pm2p = 1.32 × 1.0 × 1.0 = 1.32; lq 1.32 = 0.12.

32 gear

Compared to the 30th gear, we switch clutch B from the left to the right position - instead of 3 pairs of gears, the 3rd pair works.

, затем вертикальный луч 2-го ПМ к т. 32 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 3, then from left to top the flat beam of the 1st PM in the mode $$U_{ha}^b$$

, then the vertical beam of the 2nd PM to t. 32 on the upper horizontal.

32nd gear ratio

lq 1,2=0,08.

lq 1.2 = 0.08.

33 gear

Compared to the 28th gear, we switch the clutches B and C from the right to the left position - instead of the 3rd pair of gears, the 1st pair works.

In the beam diagram, this transmission is represented by beam 1, then the ray up to the left of the 1st PM, then the vertical beam of the 2nd PM to t. 33 on the upper horizontal.

Gear ratio 33rd gearbox

lq 1,04=0,02.

lq 1.04 = 0.02.

34 gear

Compared to the previous transmission, we switch clutch B from the left to the right position - instead of the 1st pair of gears, the 2nd pair is working.

In the beam diagram, this transmission is represented by beam 2, then the beam goes up to the left of the 1st PM, then the vertical beam of the 2nd PM to point 34 on the upper horizontal.

34th gear ratio

lq 0,82=-0,09.

lq 0.82 = -0.09.

35 gear

Compared to the 32nd gear, we switch the clutches B and C from the right to the left position - instead of the 3rd pair of gears, the 1st pair is working.

, затем вертикальный луч 2-го ПМ к т. 35 на верхней горизонтали.In the beam diagram, this transmission is represented by beam 1, then from left to top the flat beam of the 1st PM in the mode $$U_{ha}^b$$

, then the vertical beam of the 2nd PM to t. 35 on the upper horizontal.

35th gear ratio

lq 0,64=-0,19.

lq 0.64 = -0.19.

36 gear

Compared to the previous transmission, we switch clutch B from the left to the right position - instead of the 1st pair of gears, the 2nd pair is working.

In the beam diagram, this transmission is represented by beam 2, then the beam goes up to the left of the 1st PM, then the vertical beam of the 2nd PM to t. 36 on the upper horizontal.

36th gear ratio

lq 0,5=-0,3.

lq 0.5 = -0.3.

If, for example, you install a drive motor with a speed of n ₁ = 1500 rpm, then in the end we get a number of gear ratios from n ₁ = 1500 / U ₁ = 1500 / 178.4 = 8.4 rpm to n ₃₆ = 1500 / U ₃₆ = 1500 / 0.5 = 3000 rpm. The rotational speed of the output shaft of the gearbox of less than 10 rpm will provide a reliable conclusion from the idle state of large mass rotors, and a number of gear ratios in a wide range allows you to choose the necessary algorithm for accelerating the gas turbine before starting it, bypassing the resonant frequencies of low orders. The proposed technical solution can be used for dynamic balancing of gas turbines. It is advisable to perform it on a moving platform, dividing the gearbox into two units. 1st unit: twin-shaft misaligned gearbox and first PM, 2nd unit - separately the second PM.

Changing the gear ratios of pairs of gears and internal PM parameters will change the number of gear ratios and the range of the gearbox. Particular attention should be paid to the interval between the gear ratios of the 3rd and 2nd gear pairs. The previously considered series of gear ratios were obtained for the interval lq U ₃ -lq U ₂ = lq 3.16-lq 1.32 = 0.5-0.12 = 0.38, which provided the total mode of the 1st PM U _pm1 = 17.7. A slight increase in this interval to 0.39 leads to a significant increase in the gear ratio of the 1st PM to U _pm1 = 22.5.

Designations:

1 - gear housing

2 - input shaft of an off-axis twin-shaft gearbox and gearbox,

3 - the secondary shaft of the gearbox and the shaft of the drive of the sun gear of the first PM,

4 - the drive shaft of the sun gear of the second PM,

5 - output shaft of the gearbox,

6 - tubular output shaft KP,

7 - gear input shaft 2 KP,

8 and 9 - gears of the input shaft 2 of the gearbox,

10 and 11 - gears of a block of a secondary shaft 3 KP,

12 - gear of the tubular output shaft 6 KP,

13 - the gear ring of the front end of the secondary shaft 3 KP,

14 (A) - three-position clutch switching the secondary shaft 3 KP,

15 - the gear rim of the input shaft 2 KP,

16 (V) - three-position clutch for switching input shaft 2 of the gearbox,

17 - the gear rim of the three-position coupling of the tubular output shaft 6 of the gearbox,

18 - three-position clutch switching tubular output shaft 6 KP,

19 - two-position gear ring output KP,

20 (D) - two-position clutch output gearbox,

21 - the sun gear of the first PM,

22 - the gear rim of the entrance of the sun gear 21 on the shaft 3,

23 - the gear crown of the output of the sun gear 21 on the shaft 3,

24 - satellites of the first PM,

25 - drove the first PM,

26 - tubular input shaft drove 25 of the first PM,

27 - the gear rim of the tubular input shaft 26,

28 - a tubular output shaft drove 25 of the first PM,

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

30 - epicyclic wheel of the first PM,

31 - casing of the epicyclic wheel of the first PM,

32 - tubular shaft of the housing 31,

33 - the gear rim of the tubular shaft 32 of the body of the epicyclic wheel,

34 - gear ring of the wall of the housing 1,

35 (E) - on-off clutch stop epicyclic wheel,

36 - clip with a five-position gear ring,

37 (F) - three-position output coupling of the 1st PM,

38 (G) - on-off coupling of the input of the 2nd PM,

39 - the sun gear of the second PM,

40 - the gear crown of the shaft 4 of the drive of the sun gear of the second PM,

41 - satellites of the second PM,

42 - drove the second PM,

43 - a tubular drive shaft carrier 42 of the second PM,

44 - the gear rim of the tubular shaft 43,

45 - epicyclic wheel of the second PM.

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 comprising a gearbox with three pairs of interlocked gears and a simple three-link planetary mechanism, two gears are freely mounted on the input shaft of the gearbox, a gear ring is fixed between them with a three-position switching clutch, a gear ring with a three-position switching clutch of a tubular output shaft is fixed to the front end located I’m waiting for the second and third rows of gears, a double two-position clutch is installed on the second gear rim of this shaft, next to it are the 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 gear, and with an 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 wall gearbox housing next to the gear rim of the tubular shaft of the epicyclic wheel, characterized in that the output is equipped with a second three-link planetary mechanism, the gearbox is misaligned, a secondary shaft with a freely installed block of two gears and a tubular output shaft with a gear located freely on it is located parallel to the input shaft , with three gear rims fixed to the secondary shaft, the first ring gear with a three-position switching clutch is fixed at the end between the housing and the gear block, W a swirl gear is fixed between the gear rims of the tubular output shaft of the gearbox and the tubular input shaft of the carrier of the first planetary gear, the third gear rim is located between the gear rims of the tubular output shaft of the first planetary gear and the tubular input shaft of the carrier of the second planetary gear, a clip with a five-position gear rim is freely installed at the output of the secondary shaft and the input of the drive shaft of the sun gear of the second planetary mechanism, the output shaft of the gearbox is fixed and the carrier of the second planetary gear.

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