An integrated transmission device for barring and starting a gas turbine generator set

Abstract

An integrated transmission device for turning and starting a gas turbine generator set. The present invention solves the problems of the existing starting clutch and turning clutch of a gas turbine generator set being dispersedly arranged, resulting in a complex main gearbox shafting, difficult machining, large floor area and high cost. In the present invention, the starting clutch and the turning clutch are concentrically arranged, the turning clutch is located outside the starting clutch, both the starting clutch and the turning clutch are of a synchronous automatic clutch structure and share the same output flange. The starting input shaft and the turning reversing transmission assembly are supported on the housing through bearings, the turning clutch is supported on the turning reversing transmission assembly, the axis of the starting clutch is perpendicular to the axis of the turning clutch. The input shaft of the turning reversing transmission assembly is connected to the turning motor, the starting input shaft of the starting clutch is connected to the starting motor, and the output flange is rigidly connected to the main gearbox gear. The present invention is used for power transmission in the process of turning and starting a gas turbine generator set.

Description

Technical Field

[0001] The invention relates to a transmission device for cranking and ignition starting process of a gas turbine generator set, in particular to an integrated transmission device capable of integrating a cranking clutch and a starting clutch of a gas turbine generator set which are dispersedly arranged. Background Art

[0002] At present, gas turbine generator sets used for industrial power generation generally require auxiliary power to perform low-speed cranking and high-speed rotation compression before the engine is ignited. Low-speed cranking is also required after the engine is shut down to prevent the rotor from bending due to uneven cooling. Since low-speed cranking and high-speed compression have different power and speed requirements for auxiliary power, gas turbine generator sets are usually equipped with electric cranking machines and electric starters, which are connected to the main transmission gearbox through their own clutches, resulting in complex shafting of the main transmission gearbox, difficult processing, large floor space and high cost.

[0003] In summary, the existing gas turbine generator sets are dispersedly equipped with a cranking clutch and a starting clutch, which has the problems of complex main drive gearbox shaft system, difficult processing, large floor space and high cost. Summary of the invention

[0004] The purpose of the present invention is to solve the problems of the existing gas turbine generator set, which has a complex main transmission gearbox shaft system, difficult processing, large floor space and high cost due to the dispersed configuration of the cranking clutch and the starting clutch. Further, an integrated transmission device for cranking and starting of the gas turbine generator set is provided.

[0005] The technical solution of the present invention is: an integrated transmission device for cranking and starting a gas turbine generator set is composed of a starting clutch, a cranking clutch, a cranking reversing transmission assembly, a housing, a starting input shaft bearing, a small bevel gear bearing and a large bevel gear bearing. The starting clutch and the cranking clutch are arranged concentrically, the cranking clutch is located outside the starting clutch and supported on the cranking reversing transmission assembly, the starting clutch and the cranking clutch are both synchronous automatic clutch structures, and the starting clutch and the cranking clutch share the same output flange, the starting input shaft of the starting clutch is supported on the housing through the starting input shaft bearing, the cranking reversing transmission assembly is also supported on the housing through the starting input shaft bearing and the small bevel gear bearing, the starting motor axis of the starting clutch is perpendicular to the cranking motor axis of the cranking clutch, the input shaft of the cranking reversing transmission assembly is connected to the cranking motor, the starting input shaft of the starting clutch is connected to the starting motor, and the output flange is rigidly connected to the gear of the main gearbox of the unit.

[0006] Further, the barring gear reversing drive assembly includes a small bevel gear, a large bevel gear, a small bevel gear bearing and a large bevel gear bearing. The small bevel gear is rotatably mounted on the housing through the small bevel gear bearing, and the large bevel gear is rotatably mounted on the housing through the large bevel gear bearing. The large bevel gear meshes with the small bevel gear and their axes are perpendicular to each other. The small bevel gear is connected to the barring motor, and the large bevel gear is provided with an internal spline of the barring clutch.

[0007] Further, the housing is provided with a barring motor mounting flange and a main mounting flange connected to the main gearbox. The barring motor mounting flange and the main mounting flange are perpendicular to each other. The housing is divided into an upper housing and a lower housing, and the middle of the upper housing and the lower housing is a split surface. The small bevel gear and the barring motor mounting flange are both mounted on the upper housing.

[0008] Further, the starting clutch includes a starting input shaft, a starting input shaft bearing, an input gear ring, a starting clutch sliding member, an internal spline of the starting clutch, an external spline of the starting clutch and an external driving tooth of the starting clutch. The starting input shaft is rotatably mounted on the housing through the starting input shaft bearing. The input gear ring is sleeved on the starting input shaft. The external spline of the starting clutch is mounted on the input gear ring. The internal spline of the starting clutch is mounted on the starting clutch sliding member. The starting clutch sliding member is mounted on the input gear ring, and the internal spline of the starting clutch is connected to the external spline of the starting clutch. The starting clutch sliding member is provided with an external driving tooth of the starting clutch.

[0009] Further, the output flange includes a flange body, an internal driving tooth of the starting clutch, an external driving tooth of the barring clutch, a low-speed pawl mechanism of the barring clutch, a low-speed pawl mechanism of the starting clutch and a high-speed ratchet of the starting clutch. The internal driving tooth of the starting clutch and the external driving tooth of the barring clutch are respectively arranged on the inner side wall and the outer side wall of the flange body. After the starting clutch sliding member slides, the internal driving tooth of the starting clutch meshes with the external driving tooth of the starting clutch. The low-speed pawl mechanism of the barring clutch, the low-speed pawl mechanism of the starting clutch and the high-speed ratchet of the starting clutch are sequentially mounted on the flange body from left to right.

[0010] Furthermore, the barring clutch low-speed pawl mechanism includes a barring clutch pawl stop pin, a barring clutch pawl spring, a barring clutch low-speed pawl, a barring clutch pawl pin, and an internal ratchet of the barring clutch sliding member; the barring clutch pawl pin is installed on the flange body, the barring clutch low-speed pawl is installed on the barring clutch pawl pin through the barring clutch pawl spring, the barring clutch pawl stop pin is installed on the flange body on the left side of the barring clutch pawl pin, an internal ratchet of the barring clutch sliding member is provided on the inner side of the barring clutch sliding member, the barring clutch sliding member and the large bevel gear are meshed and connected through an external spiral spline and an internal spiral spline of the barring clutch, and an internal driving tooth of the barring clutch is provided on the inner side wall of the barring clutch sliding member. When the barring clutch low-speed pawl meshes with the internal ratchet of the barring clutch sliding member, the barring clutch sliding member slides, the internal driving tooth of the barring clutch meshes with the external driving tooth of the barring clutch, and the torque of the barring motor is transmitted. When the output flange speed is greater than the barring speed, the barring clutch sliding member slides reversely, the internal driving tooth of the barring clutch and the external driving tooth of the barring clutch disengage from each other, and the transmission of the barring torque stops.

[0011] Furthermore, the starting clutch low-speed pawl mechanism includes an external ratchet of the starting clutch sliding member, a starting clutch low-speed pawl stop pin, a starting clutch low-speed pawl pin, a starting clutch low-speed pawl, and a starting clutch low-speed pawl spring. The starting clutch low-speed pawl pin is installed on the flange body, an external ratchet of the starting clutch sliding member is provided on the starting clutch sliding member, the starting clutch low-speed pawl is rotatably installed on the starting clutch pawl pin through the starting clutch pawl spring, the starting clutch pawl stop pin is installed on the flange body on the left side of the starting clutch pawl pin, and when the starting clutch low-speed pawl meshes with the external ratchet of the starting clutch sliding member, the starting clutch sliding member slides, so that the internal driving tooth of the starting clutch meshes with the external driving tooth of the starting clutch, and the torque of the starting motor is transmitted. When the output flange speed is greater than the starting motor speed, the starting clutch sliding member slides reversely, the internal driving tooth of the starting clutch and the external driving tooth of the starting clutch disengage from each other, and the transmission of the starting motor torque stops.

[0012] Furthermore, the high-speed ratchet of the starting clutch includes an inner ratchet of the output flange, a high-speed pawl of the starting clutch, a high-speed pawl pin of the starting clutch, and a high-speed pawl retaining pin of the starting clutch. An inner ratchet of the output flange is provided on the inner side wall of the output flange body. The high-speed pawl pin of the starting clutch is installed on the starting clutch sliding member. The high-speed pawl of the starting clutch is rotatably installed on the high-speed pawl pin of the starting clutch. The high-speed pawl retaining pin of the starting clutch is installed on the starting clutch sliding member on the right side of the starting clutch pawl pin. When the high-speed pawl of the starting clutch meshes with the inner ratchet of the output flange, the starting clutch sliding member slides, so that the inner driving teeth of the starting clutch mesh with the outer driving teeth of the starting clutch, and the torque of the starting motor is transmitted. When the rotational speed of the output flange is greater than the rotational speed of the starting motor, the starting clutch sliding member slides in the reverse direction, and the inner driving teeth of the starting clutch and the outer driving teeth of the starting clutch disengage from each other, and the transmission of the torque of the starting motor stops.

[0013] The present invention has the following effects compared with the prior art:

[0014] 1. In the present invention, the barring clutch 700 and the starting clutch 600 are integrated into the same transmission device, reducing the number of drive shafts, gears, and bearings in the main transmission gearbox, and reducing the processing difficulty and cost of the main transmission gearbox. Due to the reduction in the number of drive shafts, the floor area of the main transmission gearbox is also greatly reduced.

[0015] 2. The present invention uses a synchronous automatic clutch as the basic structure of the barring clutch 700 and the starting clutch 600. The starting clutch 600 and the barring clutch 700 are concentrically arranged, with the starting clutch 600 located inside and the barring clutch 700 located outside. The starting clutch 600 and the barring clutch 700 share a single part as the output part to connect to the main gearbox, rather than setting two output parts to connect to the main gearbox separately. The input ends of the starting clutch 600 and the barring clutch 700 are supported by the housing 900 of the present invention through their respective bearings, and the output part is supported by the gear bearings of the main gearbox. The housing 900 of the present invention is connected to the main gearbox through the main mounting flange, and the main gearbox provides positioning and support for the whole of the present invention. Since the power of the barring motor is relatively small, it is supported on the housing 900 of the present invention through the barring motor mounting flange.

[0016] 3. The barring motor of the present invention is connected to the input end of the barring clutch 700 by using well-known transmission forms such as bevel gears and worm gears. Since the power of the starting motor is relatively large, it is independently supported by a base and connected to the input end of the starting clutch 600 through a coupling.

[0017] 4. The present invention integrates the barring clutch 700, the starting clutch 600, the barring motor mounting flange, and the main mounting flange into one transmission device, simplifying the shafting of the main transmission gearbox, reducing the floor area, and reducing the processing difficulty and cost. Brief Description of the Drawings

[0018] Figure 1 is the layout schematic diagram of an existing gas turbine generator set.

[0019] Figure 2 is the power flow diagram when the existing gas turbine generator set is turning the engine over.

[0020] Figure 3 is the power flow diagram when the existing gas turbine generator set is starting up.

[0021] Figure 4 is the layout schematic diagram of the gas turbine generator set adopting the present invention.

[0022] Figure 5 is the power flow diagram when the gas turbine generator set adopting the present invention is turning the engine over.

[0023] Figure 6 is the power flow diagram when the gas turbine generator set adopting the present invention is starting up.

[0024] Figure 7 is the connection relationship diagram of the present invention with the turning-over motor, starting motor and main gearbox

[0025] Figure 8 is the simplified layout principle diagram of the present invention.

[0026] Figure 9 is the simplified mechanism principle diagram of the present invention.

[0027] Figure 10 is the state and power flow diagram of the internal clutch when the gas turbine is operating normally in the present invention.

[0028] Figure 11 is the state and power flow diagram of the internal clutch when turning the engine over in the present invention.

[0029] Figure 12 is the state and power flow diagram of the internal clutch when starting up in the present invention.

[0030] Figure 13 is the sectional view of a specific embodiment of the present invention.

[0031] Figure 14 is Figure 13 the axial view of

[0032] Figure 15 is Figure 13 the state and power flow diagram of the internal clutch when the gas turbine is operating normally.

[0033] Figure 16 is Figure 13 the state and power flow diagram of the internal clutch when turning the engine over.

[0034] Figure 17 is Figure 13 The state of the internal clutch and the power flow diagram during startup.

[0035] Figure 18 is Figure 13 The state where the low-speed pawl of the barring clutch extends.

[0036] Figure 19 is Figure 13 The state where the low-speed pawl of the barring clutch retracts.

[0037] Figure 20 is Figure 13 The state where the low-speed pawl of the starting clutch extends.

[0038] Figure 21 is Figure 13 The state where the low-speed pawl of the starting clutch retracts.

[0039] Figure 22 is Figure 13 The state where the high-speed pawl of the starting clutch 600 extends.

[0040] Figure 23 is Figure 13 The state where the high-speed pawl of the starting clutch 600 retracts.

[0041] In the figure, 10 is a gas turbine, 20 is a generator, 30 is a starting motor, 40 is a barring motor, 42 is a barring motor coupling, 60 is a barring clutch 700 in the prior art, 70 is a starting clutch 600 in the prior art, 82 is a coupling, 84 is a coupling, 86 is a coupling. 100 is a main transmission gearbox, 110 is an improved main transmission gearbox, 120 is a low-speed main transmission gear z1, 110 is a high-speed main transmission gear z2, 130 is an accessory gear z3, 140 is an accessory gear z4, 142 is the oil supply for the main gearbox, 150 is an accessory gear z5, 160 is an accessory gear z6, 170 is an accessory gear z7. 201 is the gas turbine power generation power flow, 202 is the barring power flow, 203 is the starting power flow, 210 is the gas turbine power generation power flow of this patent, 220 is the barring power flow of this patent, 230 is the starting power flow of this patent, 500 is the overall of this invention patent, 505 is a barring reversing transmission component, 510 is a small bevel gear, 520 is a large bevel gear, 530 is a large bevel gear bearing. 600 is a starting clutch, the starting input shaft 610 is a starting input shaft, 612 is the left positioning of the starting clutch, 614 is the right positioning of the starting clutch, 620 is the internal spiral spline of the starting clutch, 622 is the input gear ring of the starting clutch, 630 is the external spiral spline of the starting clutch, 631 is the high-speed pawl stop pin of the starting clutch, 632 is the high-speed pawl pin of the starting clutch, 633 is the high-speed pawl of the starting clutch, 634 is the internal ratchet of the output flange, 635 is the sliding part of the starting clutch, 636 is the external ratchet of the sliding part of the starting clutch, 650 is the internal driving tooth of the starting clutch, 640 is the external driving tooth of the starting clutch, 660 is the external driving tooth of the barring clutch, 670 is the output flange, 671 is the barring clutch pawl stop pin, 672 is the barring clutch pawl spring, 673 is the low-speed pawl of the barring clutch, 674 is the barring clutch pawl pin, 675 is the low-speed pawl stop pin of the starting clutch, 676 is the low-speed pawl pin of the starting clutch, 677 is the low-speed pawl of the starting clutch, 678 is the low-speed pawl spring of the starting clutch, 682 is the internal ratchet of the sliding part of the barring clutch. 700 is a barring clutch, 712 is the left positioning of the starting clutch, 714 is the right positioning of the starting clutch, 720 is the external spiral spline of the barring clutch, 730 is the internal spiral spline of the barring clutch, 740 is the sliding part of the barring clutch, 760 is the internal driving tooth of the barring clutch, 900 is the housing 900, 904 is the split surface of the housing 900, 906 is the upper housing 900, 908 is the lower housing 900, 910 is the starting input shaft bearing, 920 is the small bevel gear bearing, 930 is the main mounting flange, 935 is the positioning stop, 940 is the barring motor mounting flange. Detailed implementation mode

[0042] Detailed implementation mode 1: In combination with Figures 4 to 23To describe this embodiment, an integrated transmission device for turning gear and starting of a gas turbine generator set is composed of a starting clutch 600, a turning gear clutch 700, a turning gear reversing transmission component 505, a housing 900, a starting input shaft bearing 910, a small bevel gear bearing 920 and a large bevel gear bearing 530. Its characteristics are as follows: The starting clutch 600 and the turning gear clutch 700 are concentrically arranged. The turning gear clutch 700 is located outside the starting clutch 600 and is supported on the turning gear reversing transmission component 505. Both the starting clutch 600 and the turning gear clutch 700 are of synchronous automatic clutch structure, and the starting clutch 600 and the turning gear clutch 700 share the same output flange 670. The starting input shaft 610 of the starting clutch 600 is supported on the housing 900 through the starting input shaft bearing 910. The turning gear reversing transmission component 505 is also supported on the housing 900 through the starting input shaft bearing 910 and the small bevel gear bearing 920. The axis of the starting motor of the starting clutch 600 is perpendicular to the axis of the turning gear motor of the turning gear clutch 700. The input shaft of the turning gear reversing transmission component 505 is connected to the turning gear motor, the starting input shaft 610 of the starting clutch 600 is connected to the starting motor, and the output flange 670 is rigidly connected to the gear of the main gearbox of the unit.

[0043] Specific Embodiment 2: In combination with Figures 13 to 17 To describe this embodiment, the turning gear reversing transmission component 505 of this embodiment includes a small bevel gear 510, a large bevel gear 520, a small bevel gear bearing 920 and a large bevel gear bearing 530. The small bevel gear 510 is rotatably installed on the housing 900 through the small bevel gear bearing 920. The large bevel gear 520 is rotatably installed on the housing 900 through the large bevel gear bearing 530, and the large bevel gear 520 meshes with the small bevel gear 510 and their axes are perpendicular to each other. The small bevel gear 510 is connected to the turning gear motor, and the large bevel gear 520 is provided with an internal spline 730 of the turning gear clutch. Such a setting facilitates the transmission of power. Other compositions and connection relationships are the same as those in Specific Embodiment 1.

[0044] Specific Embodiment 3: In combination with Figures 13 to 17 To describe this embodiment, the housing 900 of this embodiment is provided with a turning gear motor mounting flange 940 and a main mounting flange 930 connected to the main gearbox. The turning gear motor mounting flange 940 and the main mounting flange 930 are perpendicular to each other. The housing 900 is divided into an upper housing 906 and a lower housing 908. The middle of the upper housing 906 and the lower housing 908 is a split surface 904. The small bevel gear 510 and the turning gear motor mounting flange 940 are both installed on the upper housing 906. Such a setting facilitates the installation of the entire transmission system and is also convenient for production, processing and manufacturing. Other compositions and connection relationships are the same as those in Specific Embodiment 1 or 2.

[0045] Specific Embodiment 4: In combination with Figures 13 to 17Referring to this embodiment, the starting clutch 600 of this embodiment includes a starting input shaft 610, a starting input shaft bearing 910, an input gear ring 622, a starting clutch sliding member 635, an internal helical spline 620 of the starting clutch, an external helical spline 630 of the starting clutch, and an external drive tooth 640 of the starting clutch; the starting input shaft 610 is rotatably mounted on the housing 900 through the starting input shaft bearing 910, the input gear ring 622 is sleeved on the starting input shaft 610, the external helical spline 630 of the starting clutch is mounted on the input gear ring 622, the internal helical spline 620 of the starting clutch is mounted on the starting clutch sliding member 635, the starting clutch sliding member 635 is mounted on the input gear ring 622, and the internal helical spline 620 of the starting clutch is connected to the external helical spline 630 of the starting clutch. The external drive tooth 640 of the starting clutch is formed on the starting clutch sliding member 635. Other components and connection relationships are the same as those in the first, second, or third specific embodiments.

[0046] Specific Embodiment Five: In combination with Figures 13 to 17 Referring to this embodiment, the output flange 670 of this embodiment includes a flange body, an internal drive tooth 650 of the starting clutch, an external drive tooth 660 of the barring clutch, a barring clutch low-speed pawl mechanism, a starting clutch low-speed pawl mechanism, and a starting clutch high-speed ratchet. The internal drive tooth 650 of the starting clutch and the external drive tooth 660 of the barring clutch are respectively formed on the inner and outer side walls of the flange body. After the starting clutch sliding member 635 slides, the internal drive tooth 650 of the starting clutch meshes with the external drive tooth 640 of the starting clutch. The barring clutch low-speed pawl mechanism, the starting clutch low-speed pawl mechanism, and the starting clutch high-speed ratchet are sequentially mounted on the flange body from left to right. Other components and connection relationships are the same as those in the first, second, third, or fourth specific embodiments.

[0047] Specific Embodiment Six: In combination with Figures 18 to 19Description of this embodiment. The low-speed pawl mechanism of the turning gear clutch in this embodiment includes: a turning gear clutch pawl stop pin 671, a turning gear clutch pawl spring 672, an inner ratchet wheel 682 of the turning gear clutch sliding member, a low-speed pawl 673 of the turning gear clutch, and a turning gear clutch pawl pin 674. The turning gear clutch pawl pin 674 is installed on the flange body. The low-speed pawl 673 of the turning gear clutch is rotatably installed on the turning gear clutch pawl pin 674 through the turning gear clutch pawl spring 672. The turning gear clutch pawl stop pin 671 is installed on the flange body on the left side of the turning gear clutch pawl pin 674. An inner ratchet wheel 682 of the turning gear clutch is provided on the inner side of the turning gear clutch sliding member 740. The turning gear clutch sliding member 740 and the large bevel gear 520 are meshed and connected through an external spiral spline 720 of the turning gear clutch and an internal spiral spline 730 of the turning gear clutch. An internal driving tooth 760 of the turning gear clutch is provided on the inner side wall of the turning gear clutch sliding member 740. When the low-speed pawl 673 of the turning gear clutch meshes with the inner ratchet wheel 682 of the turning gear clutch sliding member, the turning gear clutch sliding member 740 slides. The internal driving tooth 760 of the turning gear clutch meshes with the external driving tooth 660 of the turning gear clutch to transmit the torque of the turning gear motor. When the rotational speed of the output flange 670 is greater than the turning gear speed, the turning gear clutch sliding member 740 slides in the reverse direction, and the internal driving tooth 760 of the turning gear clutch disengages from the external driving tooth 660 of the turning gear clutch, stopping the transmission of the turning gear torque. Other components and connection relationships are the same as those in the first, second, third, fourth, or fifth specific embodiments.

[0048] Specific Embodiment Seven: In combination with Figures 20 to 21 Description of this embodiment. The low-speed pawl mechanism of the starting clutch in this embodiment includes an external ratchet wheel 636 of the starting clutch sliding member, a low-speed pawl stop pin 675 of the starting clutch, a low-speed pawl pin 676 of the starting clutch, a low-speed pawl 677 of the starting clutch, and a low-speed pawl spring 678 of the starting clutch. The low-speed pawl pin 676 of the starting clutch is installed on the flange body. An external ratchet wheel 636 of the starting clutch is provided on the starting clutch sliding member 635. The low-speed pawl 677 of the starting clutch is rotatably installed on the low-speed pawl pin 676 of the starting clutch through the low-speed pawl spring 678 of the starting clutch. The low-speed pawl stop pin 675 of the starting clutch is installed on the flange body on the left side of the low-speed pawl pin 676 of the starting clutch. When the low-speed pawl 677 of the starting clutch meshes with the external ratchet wheel 636 of the starting clutch sliding member, the starting clutch sliding member 635 slides, causing the internal driving tooth 650 of the starting clutch to mesh with the external driving tooth 640 of the starting clutch and transmitting the torque of the starting motor. When the rotational speed of the output flange 670 is greater than the rotational speed of the starting motor, the starting clutch sliding member 635 slides in the reverse direction, and the internal driving tooth 650 of the starting clutch disengages from the external driving tooth 640 of the starting clutch, stopping the transmission of the torque of the starting motor. Other components and connection relationships are the same as those in the first, second, third, fourth, fifth, or sixth specific embodiments.

[0049] Embodiment VIII: In combination with Figures 22 to 23 This embodiment will be described. The high-speed ratchet of the starting clutch in this embodiment includes an inner ratchet 634 of the output flange, a high-speed pawl 633 of the starting clutch, a high-speed pawl pin 632 of the starting clutch, and a high-speed pawl retaining pin 631 of the starting clutch. An inner ratchet 634 of the output flange is provided on the inner side wall of the output flange 670 body. The high-speed pawl pin 632 of the starting clutch is installed on the starting clutch sliding member 635. The high-speed pawl 633 of the starting clutch is rotatably installed on the high-speed pawl pin 632 of the starting clutch. The high-speed pawl retaining pin 631 of the starting clutch is installed on the starting clutch sliding member 635 on the right side of the high-speed pawl pin 632 of the starting clutch. When the high-speed pawl 633 of the starting clutch meshes with the inner ratchet 634 of the output flange, the starting clutch sliding member 635 slides, so that the inner drive tooth 650 of the starting clutch meshes with the outer drive tooth 640 of the starting clutch, and the torque of the starting motor is transmitted. When the rotational speed of the output flange 670 is greater than the rotational speed of the starting motor, the starting clutch sliding member 635 slides reversely, and the inner drive tooth 650 of the starting clutch disengages from the outer drive tooth 640 of the starting clutch, and the transmission of the torque of the starting motor is stopped. Other compositions and connection relationships are the same as any one of Embodiments I to VII.

[0050] Regarding the transmission of the turning clutch low-speed ratchet and pawl mechanism, the starting clutch low-speed ratchet and pawl mechanism, and the starting clutch high-speed ratchet and pawl mechanism are as follows:

[0051] The outer spline on the turning clutch sliding member is connected to the inner spline of the large bevel gear of the turning clutch reversing transmission assembly 505, and the inner drive tooth on the turning clutch sliding member can be axially meshed with the outer drive tooth of the output flange.

[0052] The inner spline on the starting clutch sliding member is connected to the outer spline of the starting clutch, and the outer drive tooth on the starting clutch sliding member can be axially meshed with the inner drive tooth of the output flange.

[0053] The turning clutch 700 is provided with a set of low-speed pawls with pawl springs, and the starting clutch 600 is provided with 1 set of low-speed pawls with pawl springs and 1 set of high-speed pawls without pawl springs.

[0054] The low-speed pawl of the turning clutch is provided on the output flange and can extend outwards under the action of the pawl spring. When the rotational speed of the output flange is higher than a certain value, the pawl automatically retracts under the action of centrifugal force.

[0055] The low-speed pawl of the starting clutch is provided on the output flange and can extend inwards under the action of the pawl spring. When the rotational speed of the output flange is higher than a certain value, the pawl automatically retracts under the action of centrifugal force.

[0056] The high-speed pawl of the starting clutch 600 is set on the sliding part of the starting clutch. When the rotational speed of the sliding part is higher than a certain value, the pawl automatically lifts under the action of centrifugal force.

[0057] After the low-speed pawl of the barring clutch on the output flange meshes with the internal ratchet of the barring clutch sliding part, it can drive the barring clutch sliding part to move axially, and make the internal and external driving teeth of the barring clutch 700 enter into engagement and transmit torque.

[0058] After the low-speed pawl of the starting clutch on the output flange meshes with the external ratchet on the starting clutch sliding part, it can drive the starting clutch sliding part to move axially, and make the internal and external driving teeth of the starting clutch 600 enter into engagement and transmit torque.

[0059] After the high-speed pawl on the starting clutch sliding part meshes with the internal ratchet on the output flange, it can drive the starting clutch sliding part to move axially, and make the internal and external driving teeth of the starting clutch 600 enter into engagement and transmit torque.

[0060] After the internal and external driving teeth of the barring clutch 700 enter into engagement and transmit torque, when the rotational speed of the output flange is higher than that of the barring clutch sliding part, the barring clutch sliding part moves axially, and makes the internal and external driving teeth of the barring clutch 700 disengage.

[0061] After the internal and external driving teeth of the starting clutch 600 enter into engagement and transmit torque, when the rotational speed of the output flange is higher than that of the starting clutch sliding part, the starting clutch sliding part moves axially, and makes the internal and external driving teeth of the starting clutch 600 disengage.

[0062] Combined Figures 1 to 23 Describe the working principle of the present invention:

[0063] In Figure 1 the gas turbine 10, the main transmission gearbox 100, the generator 20, the starting motor 30, the existing barring clutch 60, and the existing starting clutch 70 form a gas turbine generator set. Seven groups of parallel shaft gears 110 to 170 are arranged inside the main transmission gearbox 100 to match the movement relationships such as the steering and rotational speed of the unit.

[0064] The gas turbine 10 is connected to the gear 110 through the first coupling 82, the generator 20 is connected to the gear 120 through the second coupling 84, and the starting motor 30 is connected to the gear 170 through the third coupling 86.

[0065] The barring motor 40 is connected to the gear 150 through the coupling 42 and the barring reversing transmission assembly 505 through the barring clutch 60, and the gear 150 is also connected to the gear 140 through the starting clutch 70.

[0066] The low-speed main drive gear z1120 meshes with the improved main drive main gearbox 110. The improved main drive main gearbox 110 meshes with the accessory gear z3130. The accessory gear z3130 meshes with the accessory gear z4140. The accessory gear z5150 meshes with the accessory gear z6160. The accessory gear z6160 meshes with the accessory gear z7170.

[0067] When the gas turbine generates electricity, the power flow transmission route is: gas turbine 10 → first coupling 82 → improved main drive main gearbox 110 → low-speed main drive gear z1120 → generator 20 and improved main drive main gearbox 110 → accessory gear z3130 → accessory gear z4140 → starting clutch 70. When the gas turbine generates electricity, the starting clutch 70 is in the disengaged state. The accessory gears z5150, z6160, and z7170 are in a stationary state.

[0068] The barring clutch 60 and the starting clutch 70 are both of the synchronous automatic clutch structure. The characteristics of the barring clutch 60 and the starting clutch 70 are that the clutch automatically engages when the input end speed is higher than the output end speed, and the clutch automatically disengages when the output end speed is higher than the input end speed. The output end of the starting clutch 70 is connected to the accessory gear z4140. When the gas turbine generates electricity, the output end speed of the starting clutch 70 is higher than the input end speed, so the starting clutch 70 is in the disengaged state.

[0069] The input end of the barring clutch 60 is connected to the barring motor 40 through the small bevel gear 510 and the large bevel gear 520. The output end of the barring clutch 60 is connected to the accessory gear z5150. After the gas turbine stops generating electricity and barring is required, the barring motor 40 starts. When the input end speed of the barring clutch 60 is greater than the output end speed, the barring clutch 60 automatically engages. At the same time, the starting clutch 70 also meets the engagement condition that the input end speed is greater than the output end speed. Then the barring motor 40 drives the 7 groups of parallel shaft gears arranged inside the main drive gearbox 100 to start the barring movement. The power flow 202 transmission route is: barring motor 40 → barring clutch 60 → accessory gear z5150 → starting clutch 70 → accessory gear z4140 → accessory gear z3130 → improved main drive main gearbox 110 → low-speed main drive gear z1120 → second coupling 84 → generator 20, improved main drive main gearbox 110 → first coupling 82 → gas turbine 10 and accessory gear z5150 → accessory gear z6160 → accessory gear z7170 → third coupling 86 → starting motor 30.

[0070] When the turning gear operation is completed and the gas turbine needs to be started again, the starting motor 30 starts to increase its speed. When the speed of the starting motor is greater than the turning gear speed, the turning gear clutch 60 automatically disengages, but the starting clutch 70 always remains engaged. The power flow 203 transmission route is: starting motor 30 → third coupling 86 → accessory gear z7 170 → accessory gear z6 160 → accessory gear z5 150 → starting clutch 70 → accessory gear z4 140 → accessory gear z3 130 → improved main drive main gearbox 110 → low-speed main drive gear z1 120 → second coupling 84 → generator 20, improved main drive main gearbox 110 → first coupling 82 → gas turbine 10. The starting motor 30 drives the gas turbine to increase its speed through the starting clutch 70 and the gear set. The compressor of the gas turbine starts to compress air. After the gas turbine reaches a certain speed (2000 r / min - 3000 r / min), the gas turbine ignites and continues to increase its speed to enter the normal working state. After the gas turbine ignites successfully, the starting clutch 70 automatically disengages, and the starting motor 30 can reduce its speed and stop.

[0071] Figure 1 For the gas turbine generator set with a turning gear and a starting motor arranged, the gearbox 100 has a total of six shafts and 5 pairs of meshing gears. The gearbox is difficult to machine, occupies a large area, and has a high cost.

[0072] To solve Figure 1 the problem, the turning gear clutch 60 and the starting clutch 70 are integrated together, sharing a single output part and a support housing 900 to form the integrated transmission device 500 of this invention patent, achieving the purpose of simplifying the main gearbox shafting. As Figure 4 shown, the improved main gearbox 110 has only 4 shafts, 4 gears, and 3 meshing points. The machining difficulty of the main gearbox is greatly reduced, and the floor area is also greatly reduced.

[0073] Figure 5 During turning gear operation, the power flow 220 transmission route is: turning gear motor 40 → turning gear clutch 700 → accessory gear z4 140 → accessory gear z3 130 → high-speed main drive gear z2 110 → low-speed main drive gear z1 120 → second coupling 84 → generator 20, high-speed main drive gear z2 110 → first coupling 82 → gas turbine 10; Figure 6 During starting, the power flow 230 transmission route is: starting motor 30 → third coupling 86 → starting clutch 600 → accessory gear z4 140 → accessory gear z3 130 → improved main drive main gearbox 110 → low-speed main drive gear z1 120 → second coupling 84 → generator 20, improved main drive main gearbox 110 → first coupling 82 → gas turbine 10. Since 2 gear meshing points and 5 bearings are reduced, the loss of the starting power flow route is smaller and the efficiency is higher.

[0074] Figure 7 In it, the integrated transmission device 500 of the present invention is supplied with oil through the main gearbox, and the oil supply route is 142. The integrated transmission device 500 is connected to the starting motor 30 through the third coupling 86, the integrated transmission device 500 is connected to the barring motor 40 through the coupling 42, the integrated transmission device 500 is connected to the main gearbox gear 140 through the output flange 670, and the integrated transmission device 500 is supported on the main gearbox housing through the main mounting flange 930.

[0075] Figure 8 In it, the integrated transmission device 500 of the present invention mainly consists of a starting barring clutch 600, a barring starting clutch 700, a barring reversing transmission assembly 505, and a housing 900. Both the starting barring clutch 600 and the barring starting clutch 700 are of synchronous automatic clutch structure.

[0076] Figure 9 In it, the starting barring clutch 600 consists of a starting input shaft 610, a starting clutch sliding member 635, an output flange 670, a ratchet and pawl ( Figure 9 not marked), etc. The starting input shaft 610 is supported on the housing 900 through a bearing 910. The starting clutch sliding member 635 is supported on the starting input shaft 610. An internal helical spline 620 of the starting clutch is machined on the starting input shaft 610, and an external helical spline 630 is machined on the starting clutch sliding member 635. The internal helical spline 620 of the starting clutch is connected to the external helical spline 630 of the starting clutch. An external driving tooth 640 of the starting clutch is also machined on the starting clutch sliding member 635, and an internal driving tooth 650 is machined on the output flange 670. Based on the well-known synchronous automatic clutch principle, when the rotational speed of the starting input shaft 610 exceeds the rotational speed of the output flange 670, the starting clutch sliding member 635 moves leftward under the action of the ratchet and pawl. When the external driving tooth 640 of the starting clutch meshes with the internal driving tooth 650 of the starting clutch, the torque can be transmitted from the starting input shaft 610 to the output flange 670, and the starting barring clutch 600 is in the engaged state. When the rotational speed of the output flange 670 increases, the starting clutch sliding member 635 moves rightward. When the external driving tooth 640 of the starting clutch disengages from the internal driving tooth 650 of the starting clutch, the starting barring clutch 600 is in the disengaged state.

[0077] Figure 9 In it, the barring starting clutch 700 consists of a large bevel gear 520, a sliding member 740, and the output flange 670 shared with the starting clutch 600, a ratchet and pawl ( Figure 9It consists of components such as (not marked). The large bevel gear 520 is supported on the housing 900 through bearings 530. An internal helical spline 720 is made on the large bevel gear 520, and an external helical spline 730 is made on the turning clutch sliding member 740. The external helical spline 720 of the turning clutch is connected to the internal helical spline 730 of the turning clutch. An internal driving tooth 760 of the turning clutch is also made on the turning clutch sliding member 740, and an external driving tooth 660 is made on the output flange 670. Based on the well-known principle of synchronous automatic clutch, when the rotational speed of the large bevel gear 520 exceeds the rotational speed of the output flange 670, the turning clutch sliding member 740 moves leftward under the action of the ratchet and pawl. When the external driving tooth 660 of the turning clutch meshes with the internal driving tooth 760 of the turning clutch, torque can be transmitted from the large bevel gear 520 to the output flange 670, and the turning start clutch 700 is in the engaged state. When the rotational speed of the output flange 670 increases, the turning clutch sliding member 740 moves rightward. When the external driving tooth 660 of the turning clutch disengages from the internal driving tooth 760 of the turning clutch, the turning start clutch 700 is in the disengaged state.

[0078] The turning clutch sliding member 635 is axially positioned through the left positioning 612 of the turning clutch and the right positioning 614 of the turning clutch on the positioning surface; the turning clutch sliding member 740 is axially positioned through the left positioning 712 of the turning clutch and the right positioning 714 of the turning clutch on the positioning surface. The output flange 670 is rigidly connected to the gear 140 of the main gearbox 110, and the accessory gear z4 140 provides support and positioning for the output flange 670.

[0079] The turning reversing transmission assembly 505 consists of a small bevel gear 510 and a large bevel gear 520. The small bevel gear 510 is supported on the housing 900 through a bearing 920, and the small bevel gear 510 meshes with the large bevel gear 520.

[0080] The housing 900 is provided with a turning motor mounting flange 940 and a main mounting flange 930. The turning motor mounting flange 940 is concentric with the small bevel gear bearing 920, and the main mounting flange 930 is concentric with the starting input shaft bearing 910.

[0081] Figure 10 In the figure, the gas turbine generates electricity normally, the power flow is 210, the turning clutch sliding member 635 is positioned at 614, the sliding member 740 is positioned at 714, the starting clutch 600 and the turning clutch 700 are both in the disengaged state, and the output flange 670 idles together with the accessory gear z4 140.

[0082] Figure 11In this case, the unit is in the turning gear state, the power flow is 220, the starting clutch sliding member 635 is still positioned at 614, the sliding member 740 is positioned at the left positioning 712 of the starting clutch, the turning gear clutch 700 is in the engaged state, the starting clutch 600 is in the disengaged state, and the torque is transmitted from the small bevel gear 510 to the output flange 670.

[0083] Figure 12 In this case, the unit is in the starting and accelerating state, the power flow is 230, the starting clutch sliding member 635 is positioned at 612, the sliding member 740 is positioned at the right positioning 714 of the starting clutch, the starting clutch 600 is in the engaged state, the turning gear clutch 700 is in the disengaged state, and the torque is transmitted from the starting input shaft 610 to the output flange 670.

[0084] Figure 13 、 Figure 14 This is a specific embodiment of the present invention. The starting input shaft bearing 910 and the small bevel gear bearing 920 adopt rolling bearings, the large bevel gear bearing 530 adopts a sliding bearing, the housing 900 has a split surface and is divided into an upper housing 906 and a lower housing 908. The starting clutch input gear ring 622 is provided with an external spline, and the starting clutch input gear ring 622 is rigidly connected to the starting input shaft 610.

[0085] Figure 15 、 Figure 16 、 Figure 17 is a specific embodiment of the present invention as Figure 13 expressed, showing the positioning states of the clutch sliding members and the power flow conditions under three working conditions: disengagement, turning gear, and starting.

[0086] Figures 18 - 23 This is the arrangement of the ratchet and pawl in the starting turning gear clutch 600 and the turning gear starting clutch 700 of the present invention.

[0087] Figure 18 、 Figure 19 In this case, the turning gear clutch low-speed pawl 673 of the turning gear starting clutch 700 is arranged on the output flange 670. The turning gear clutch low-speed pawl 673 can swing around the turning gear clutch pawl pin 674, and the pawl spring 672 raises the head of the turning gear clutch low-speed pawl 673. During turning gear, the output flange 670 is stationary, the ratchet 682 rotates clockwise, the ratchet 682 meshes with the pawl 673, forcing the sliding member 740 to move, and realizing the engagement of the turning gear starting clutch 700. After the turning gear is completed, when the rotational speed of the output flange 670 exceeds the rotational speed of the ratchet 682, the center of gravity of the turning gear clutch low-speed pawl 673 is located at the tail. Under the action of centrifugal force, the tail of the turning gear clutch low-speed pawl 673 is raised, and the head can be pressed down against the stop pin 671 and no longer moves, avoiding wear between the turning gear clutch low-speed pawl 673 and the internal ratchet 682 of the turning gear clutch sliding member.

[0088] Figure 20 、 Figure 21 In it, the starting clutch low-speed pawl 677 of the starting disk clutch 600 is arranged on the output flange 670. The starting clutch low-speed pawl 677 can swing around the starting clutch pawl pin 676, and the starting clutch pawl spring 678 presses down the head of the starting clutch low-speed pawl 677. When starting, the output flange 670 is still rotating slowly driven by the barring motor. The external ratchet wheel 636 of the starting clutch sliding part rotates clockwise and accelerates. When the rotational speed of the external ratchet wheel 636 of the starting clutch sliding part exceeds the rotational speed of the output flange 670, the external ratchet wheel 636 of the starting clutch sliding part meshes with the starting clutch low-speed pawl 677, forcing the starting clutch sliding part 635 to move, realizing the engagement of the starting clutch 700 at a low rotational speed.

[0089] After the start is completed, when the rotational speed of the output flange 670 exceeds the rotational speed of the external ratchet wheel 636 of the starting clutch sliding part, the center of gravity of the starting clutch low-speed pawl 677 is located at the head. Under the action of centrifugal force, the head of the starting clutch low-speed pawl 677 is lifted, and the head can be lifted and leaned against the starting clutch pawl stop pin 675 and no longer moves, avoiding wear between the starting clutch low-speed pawl 677 and the external ratchet wheel 636 of the starting clutch sliding part.

[0090] Figure 22 、 Figure 23 In it, the starting clutch low-speed pawl 633 of the starting disk clutch 600 is arranged on the starting clutch sliding part 635. The starting clutch low-speed pawl 633 can swing around the starting clutch pawl pin 632, and the center of gravity of the starting clutch low-speed pawl 633 is located at the head. When the rotational speed of the starting clutch sliding part 635 increases, the head of the starting clutch low-speed pawl 633 will be lifted under the action of centrifugal force. After the first start, although the barring clutch 600 has been disengaged and the rotational speed of the output flange 670 is greater than the rotational speed of the starting clutch sliding part 635. However, the starting motor 30 does not stop, and the starting motor 30 always keeps the rotational speed of the starting clutch sliding part 635 at a relatively high level. When the first start of the gas turbine fails, the rotational speed of the output flange 670 begins to decrease. When the rotational speed of the output flange 670 is lower than the rotational speed of the starting clutch sliding part 635 instantaneously, the internal ratchet wheel 634 of the output flange meshes with the starting clutch low-speed pawl 633, forcing the starting clutch sliding part 635 to move, realizing the re-engagement of the starting clutch 700 at a high rotational speed.

[0091] After the start-up process ends, the starting motor 30 stops running, and the rotational speed of the starting clutch sliding member 635 gradually decreases to 0. The centrifugal force acting on the starting clutch low-speed pawl 633 also gradually decreases. Since the rotational speed of the output flange 670 is much higher than that of the starting clutch sliding member 635, the oil ring (caused by the high-speed rotation of the output flange 670) between the output flange 670 and the starting clutch sliding member 635 forces the starting clutch low-speed pawl 633 to press against the starting clutch pawl stop pin 631, thus avoiding wear between the starting clutch low-speed pawl 633 and the internal ratchet wheel 634 of the output flange.

Claims

1. An integrated transmission device for the barring and starting of a gas turbine generator set, which is connected by a starting clutch (600), a barring clutch (700), a barring reversing transmission assembly (505), a housing (900), a starting input shaft bearing (910), a small bevel gear bearing (920) and a large bevel gear bearing (530), and is characterized in that: The starting clutch (600) and the barring clutch (700) are concentrically arranged. The barring clutch (700) is located outside the starting clutch (600) and is supported on the barring reversing transmission assembly (505). Both the starting clutch (600) and the barring clutch (700) are of synchronous automatic clutch structure, and the starting clutch (600) and the barring clutch (700) share the same output flange (670). The starting input shaft (610) of the starting clutch (600) is supported on the housing (900) through the starting input shaft bearing (910). The barring reversing transmission assembly (505) is also supported on the housing (900) through the starting input shaft bearing (910) and the pinion bearing (920). The axis of the starting motor of the starting clutch (600) is perpendicular to the axis of the barring motor of the barring clutch (700). The input shaft of the barring reversing transmission assembly (505) is connected to the barring motor, the starting input shaft (610) of the starting clutch (600) is connected to the starting motor, and the output flange (670) is rigidly connected to the gear of the main gearbox of the unit. The barring reversing transmission assembly (505) includes a pinion (510), a large bevel gear (520), a pinion bearing (920) and a large bevel gear bearing (530). The pinion (510) is rotatably mounted on the housing (900) through the pinion bearing (920). The large bevel gear (520) is rotatably mounted on the housing (900) through the large bevel gear bearing (530). The large bevel gear (520) meshes with the pinion (510) and their axes are perpendicular to each other. The pinion (510) is connected to the barring motor, and the large bevel gear (520) is provided with an internal spline of the barring clutch (730). The starting clutch (600) includes a starting input shaft (610), a starting input shaft bearing (910), an input gear ring (622), a starting clutch sliding member (635), an internal spline of the starting clutch (620), an external spline of the starting clutch (630) and an external driving tooth of the starting clutch (640). The starting input shaft (610) is rotatably mounted on the housing (900) through the starting input shaft bearing (910). The input gear ring (622) is sleeved on the starting input shaft (610). The external spline of the starting clutch (630) is mounted on the input gear ring (622). The internal spline of the starting clutch (620) is mounted on the starting clutch sliding member (635). The starting clutch sliding member (635) is mounted on the input gear ring (622), and the internal spline of the starting clutch (620) is connected to the external spline of the starting clutch (630). The starting clutch sliding member (635) is provided with an external driving tooth of the starting clutch (640).

2. The integrated transmission device for turning gear and starting of a gas turbine generator set according to claim 1, characterized in that: The housing (900) is provided with a barring motor mounting flange (940) and a main mounting flange (930) connected to the main gearbox. The barring motor mounting flange (940) and the main mounting flange (930) are perpendicular to each other. The housing (900) is divided into an upper housing (906) and a lower housing (908). The middle of the upper housing (906) and the lower housing (908) is a split surface (904). The small bevel gear (510) and the barring motor mounting flange (940) are both mounted on the upper housing (906).

3. The integrated transmission device for turning gear and starting of a gas turbine generator set according to claim 2, characterized in that: The output flange (670) includes a flange body, an inner driving tooth (650) of the starting clutch, an outer driving tooth (660) of the barring clutch, a low-speed pawl mechanism of the barring clutch, a low-speed pawl mechanism of the starting clutch, and a high-speed ratchet of the starting clutch. The inner side wall and the outer side wall of the flange body are respectively provided with the inner driving tooth (650) of the starting clutch and the outer driving tooth (660) of the barring clutch. After the starting clutch sliding member (635) slides, the inner driving tooth (650) of the starting clutch meshes with the outer driving tooth (640) of the starting clutch. The low-speed pawl mechanism of the barring clutch, the low-speed pawl mechanism of the starting clutch, and the high-speed ratchet of the starting clutch are sequentially mounted on the flange body from left to right.

4. An integrated transmission device for turning gear and starting of a gas turbine generator set according to claim 3, characterized in that: The low-speed pawl mechanism of the barring clutch includes a barring clutch pawl stop pin (671), a barring clutch pawl spring (672), a low-speed pawl (673) of the barring clutch, and a barring clutch pawl pin (674), and an inner ratchet (682) of the barring clutch sliding member; the barring clutch pawl pin (674) is mounted on the flange body, the low-speed pawl (673) of the barring clutch is mounted on the barring clutch pawl pin (674) through the barring clutch pawl spring (672), the barring clutch pawl stop pin (671) is mounted on the flange body on the left side of the barring clutch pawl pin (674), the inner side of the barring clutch sliding member (740) is provided with the inner ratchet (682) of the barring clutch sliding member. The barring clutch sliding member (740) and the large bevel gear (520) are meshed and connected through an outer spline (720) of the barring clutch and an inner spline (730) of the barring clutch. The inner side wall of the barring clutch sliding member (740) is provided with an inner driving tooth (760) of the barring clutch. When the low-speed pawl (673) of the barring clutch meshes with the inner ratchet (682) of the barring clutch sliding member, the barring clutch sliding member (740) slides, and the inner driving tooth (760) of the barring clutch meshes with the outer driving tooth (660) of the barring clutch to transmit the torque of the barring motor. When the rotational speed of the output flange (670) is greater than the barring rotational speed, the barring clutch sliding member (740) slides reversely, and the inner driving tooth (760) of the barring clutch disengages from the outer driving tooth (660) of the barring clutch, and the transmission of the barring torque stops.

5. An integrated transmission device for turning gear and starting of a gas turbine generator set according to claim 4, characterized in that: The starting clutch low-speed ratchet mechanism includes the outer ratchet wheel (636) of the starting clutch sliding member, the starting clutch low-speed ratchet stop pin (675), the starting clutch low-speed ratchet pin (676), the starting clutch low-speed ratchet (677), and the starting clutch low-speed ratchet spring (678). The starting clutch low-speed ratchet pin (676) is installed on the flange body. The outer ratchet wheel (636) of the starting clutch sliding member is provided on the starting clutch sliding member (635). The starting clutch low-speed ratchet (677) is rotatably installed on the starting clutch ratchet pin (676) through the starting clutch ratchet spring (678). The starting clutch ratchet stop pin (675) is installed on the flange body on the left side of the starting clutch ratchet pin (676). When the starting clutch low-speed ratchet (677) meshes with the outer ratchet wheel (636) of the starting clutch sliding member, the starting clutch sliding member (635) slides, so that the inner drive tooth (650) of the starting clutch meshes with the outer drive tooth (640) of the starting clutch and transmits the torque of the starting motor. When the rotational speed of the output flange (670) is greater than the rotational speed of the starting motor, the starting clutch sliding member (635) slides in the reverse direction, the inner drive tooth (650) of the starting clutch disengages from the outer drive tooth (640) of the starting clutch, and the transmission of the torque of the starting motor stops.

6. The integrated transmission device for turning gear and starting of a gas turbine generator set according to claim 5, characterized in that: The starting clutch high-speed ratchet includes the inner ratchet wheel (634) of the output flange, the starting clutch high-speed ratchet (633), the starting clutch high-speed ratchet pin (632), and the starting clutch high-speed ratchet stop pin (631). The inner ratchet wheel (634) of the output flange is provided on the inner side wall of the output flange (670) body. The starting clutch high-speed ratchet pin (632) is installed on the starting clutch sliding member (635). The starting clutch high-speed ratchet (633) is rotatably installed on the starting clutch high-speed ratchet pin (632). The starting clutch high-speed ratchet stop pin (631) is installed on the starting clutch sliding member (635) on the right side of the starting clutch ratchet pin (632). When the starting clutch high-speed ratchet (633) meshes with the inner ratchet wheel (634) of the output flange, the starting clutch sliding member (635) slides, so that the inner drive tooth (650) of the starting clutch meshes with the outer drive tooth (640) of the starting clutch and transmits the torque of the starting motor. When the rotational speed of the output flange (670) is greater than the rotational speed of the starting motor, the starting clutch sliding member (635) slides in the reverse direction, the inner drive tooth (650) of the starting clutch disengages from the outer drive tooth (640) of the starting clutch, and the transmission of the torque of the starting motor stops.

Images