CN211288517U - Integrated transmission device for turning and starting of gas turbine generator set - Google Patents

Abstract

An integrated transmission device for turning and starting a gas turbine generator set. The utility model provides a current gas turbine generating set start-up clutch and barring clutch disperse to be arranged, lead to the problem that master gearbox shafting is complicated, processing difficulty, area is big and the cost is high. The utility model discloses well start-up clutch arranges with the barring clutch is concentric, the barring clutch is located the start-up clutch outside, start-up clutch and barring clutch are synchronous automatic clutch structure sharing same output flange, start input shaft and barring reverse drive subassembly pass through the bearing support on the casing, the barring clutch supports on barring reverse drive subassembly, start-up clutch axis and barring clutch line mutually perpendicular, the input shaft and the barring motor of barring reverse drive subassembly are connected, the start-up input shaft and the starting motor of start-up clutch are connected, output flange and master gear box gear rigid connection. The utility model is used for the power transmission of gas turbine generating set barring and start-up process.

Description

Integrated transmission device for turning and starting of gas turbine generator set

Technical Field

The utility model relates to a transmission of gas turbine generating set barring and ignition start-up process, especially can be with the integrated form transmission that barring clutch and starting clutch integrated together that gas turbine generating set dispersion was arranged.

Background

At present, a gas turbine generator set for industrial power generation generally needs to perform a low-speed turning and high-speed rotating air compression process by means of auxiliary power before ignition of a combustion engine. The low-speed jigger is also needed after the combustion engine is stopped, and the rotor is prevented from being bent due to uneven cooling. Because the power and rotating speed requirements of low-speed jiggering and high-speed air compression on auxiliary power are different, an electric jigger and an electric starter are respectively arranged on a gas turbine generator set, and the electric jigger and the electric starter are connected with a main transmission gear box through respective clutches, so that the main transmission gear box is complex in shafting, difficult to machine, large in occupied area and high in manufacturing cost.

In conclusion, the existing gas turbine generator set is provided with the turning clutch and the starting clutch in a dispersed manner, and the problems of complex shafting of the main transmission gear box, difficult processing, large occupied area and high manufacturing cost exist.

SUMMERY OF THE UTILITY MODEL

The utility model aims at solving the problem that the main transmission gear box shafting that leads to is complicated, the processing difficulty, area are big and the cost is high because dispersion configuration barring clutch and starting clutch of current gas turbine generating set. Further provides an integrated transmission device for turning and starting of the gas turbine generator set.

The technical scheme of the utility model is that: an integrated transmission device for turning and starting a gas turbine generator set is formed by connecting a starting clutch, a turning reversing transmission assembly, a shell, a starting input shaft bearing, a small bevel gear bearing and a large bevel gear bearing, wherein the starting clutch and the turning clutch are concentrically arranged, the turning clutch is positioned outside the starting clutch and supported on the turning reversing transmission assembly, the starting clutch and the turning clutch are both synchronous automatic clutch structures, the starting clutch and the turning clutch share the same output flange, the starting input shaft of the starting clutch is supported on the shell through the starting input shaft bearing, the turning reversing transmission assembly is also supported on the shell through the starting input shaft bearing and the small bevel gear bearing, the axis of a starting motor of the starting clutch is mutually vertical to the axis of a turning motor of the turning clutch, and the input shaft of the turning reversing transmission assembly is connected with a turning motor, the starting input shaft of the starting clutch is connected with a starting motor, and the output flange is rigidly connected with a main gearbox gear of the unit.

Further, the jigger reversing transmission assembly comprises 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 installed on the shell through the small bevel gear bearing, the large bevel gear is rotatably installed on the shell through the large bevel gear bearing, the large bevel gear and the small bevel gear are meshed with each other, the axes of the large bevel gear and the small bevel gear are mutually vertical, the small bevel gear is connected with the jigger motor, and the large bevel gear is provided with a jigger clutch inner spiral spline.

Furthermore, a turning motor mounting flange and a main mounting flange connected with a main gear box are manufactured on the shell, the turning motor mounting flange and the main mounting flange are perpendicular to each other, the shell is divided into an upper shell and a lower shell, a middle split surface is arranged between the upper shell and the lower shell, and the small bevel gear and the turning motor mounting flange are both mounted on the upper shell.

Furthermore, the starting clutch comprises a starting input shaft, a starting input shaft bearing, an input gear ring, a starting clutch sliding piece, a starting clutch internal helical spline, a starting clutch external helical spline and a starting clutch external driving gear; the starting input shaft is rotatably installed on the shell through a starting input shaft bearing, the input gear ring is sleeved on the starting input shaft, the input gear ring is provided with a starting clutch external spiral spline, the starting clutch sliding piece is provided with a starting clutch internal spiral spline, the starting clutch sliding piece is installed on the input gear ring, the starting clutch internal spiral spline is connected with the starting clutch external spiral spline, and the starting clutch sliding piece is provided with a starting clutch external driving tooth.

Further, the output flange comprises a flange body, a starting clutch inner driving tooth, a barring clutch outer driving tooth, a barring clutch low-speed pawl mechanism, a starting clutch low-speed pawl mechanism and a starting clutch high-speed ratchet wheel, the starting clutch inner driving tooth and the barring clutch outer driving tooth are respectively arranged on the inner side wall and the outer side wall of the flange body, after a starting clutch sliding piece slides, the starting clutch inner driving tooth is meshed with the starting clutch outer driving tooth, and the barring clutch low-speed pawl mechanism, the starting clutch low-speed pawl mechanism and the starting clutch high-speed ratchet wheel are sequentially installed on the flange body from left to right.

Furthermore, the barring clutch low-speed pawl mechanism comprises a barring clutch pawl stop pin, a barring clutch pawl spring, a barring clutch low-speed pawl, a barring clutch pawl pin and a barring clutch sliding piece inner ratchet wheel; the turning gear clutch pawl pin is arranged on the flange body, the turning gear clutch low-speed pawl is arranged on the turning gear clutch pawl pin through a turning gear clutch pawl spring, the turning gear clutch pawl stop pin is arranged on the flange body on the left side of the turning gear clutch pawl pin, the inner side of the turning gear clutch sliding piece is provided with an inner ratchet wheel of the turning gear clutch sliding piece, the turning gear clutch sliding piece and the large bevel gear are meshed and connected through an outer helical spline of the turning gear clutch and an inner helical spline of the turning gear clutch, the inner side wall of the turning gear clutch sliding piece is provided with inner driving teeth of the turning gear clutch, when the turning gear clutch low-speed pawl is meshed with the inner ratchet wheel of the turning gear clutch sliding piece, the turning gear clutch sliding piece slides, the inner driving teeth of the turning gear clutch are meshed with the outer driving teeth of the turning gear clutch, the turning gear motor torque is transmitted, and when the rotating speed of the output flange is greater than the rotating speed of the turning gear, the turning gear clutch sliding piece reversely slides, the inner driving gear of the barring clutch is meshed with the outer driving gear of the barring clutch in a withdrawing mode, and the barring torque is stopped being transmitted.

Furthermore, the starting clutch low-speed pawl mechanism comprises a starting clutch sliding piece outer ratchet wheel, a starting clutch low-speed pawl stop pin, a starting clutch low-speed pawl and a starting clutch low-speed pawl spring, wherein the starting clutch low-speed pawl pin is arranged on the flange body, the starting clutch sliding piece outer ratchet wheel is arranged on the starting clutch sliding piece, the starting clutch low-speed pawl is rotatably arranged on the starting clutch pawl pin through the starting clutch pawl spring, the starting clutch low-speed pawl stop pin is arranged on the flange body on the left side of the starting clutch pawl pin, the starting clutch sliding piece slides when the starting clutch low-speed pawl is meshed with the starting clutch sliding piece outer ratchet wheel, so that the starting clutch inner driving teeth are meshed with the starting clutch outer driving teeth, the starting motor torque is transmitted, and when the rotating speed of the output flange is greater than the rotating speed of the starting motor, the starting clutch sliding piece slides reversely, the starting clutch inner driving teeth and the starting clutch outer driving teeth are meshed with each other in a retreating mode, and the transmission of the starting motor torque is stopped.

Further, the starting clutch high-speed ratchet wheel comprises an output flange inner ratchet wheel, a starting clutch high-speed pawl pin and a starting clutch high-speed pawl stop pin, the output flange inner ratchet wheel is arranged on the inner side wall of the output flange body, the starting clutch high-speed pawl pin is arranged on the starting clutch sliding piece, the starting clutch high-speed pawl is rotatably arranged on the starting clutch high-speed pawl pin, the starting clutch high-speed pawl stop pin is arranged on the starting clutch sliding piece on the right side of the starting clutch pawl pin, when the starting clutch high-speed pawl is meshed with the output flange inner ratchet wheel, the starting clutch sliding piece slides to enable the starting clutch inner driving teeth to be meshed with the starting clutch outer driving teeth and transmit the starting motor torque, when the output flange rotating speed is greater than the starting motor rotating speed, the, and the starting clutch inner driving teeth and the starting clutch outer driving teeth are meshed in a withdrawing way, and the transmission of the starting motor torque is stopped.

Compared with the prior art, the utility model has the following effect:

1. the utility model discloses with barring clutch 700 and start-up clutch 600 integration in same transmission, reduced the quantity of final drive gear case transmission shaft, gear, bearing, reduced the processing degree of difficulty and the cost of final drive gear case. The occupied area of the main transmission gear box is greatly reduced due to the reduction of the number of the transmission shafts.

2. The utility model discloses a synchronous automatic clutch is as barring clutch 700 and starting clutch 600's basic structure, and starting clutch 600 arranges with barring clutch 700 is concentric, and starting clutch 600 is located inside, and barring clutch 700 is located the outside, and starting clutch 600 couples with a part of barring clutch 700 sharing as output part and master gearbox, rather than setting up two output parts and coupling respectively with the master gearbox. The input of the start clutch 600 and the turning gear clutch 700 and the housing 900 of the present invention are supported by their bearings, and the output parts are supported by the gear bearings of the main gearbox. The utility model discloses a casing 900 is through main mounting flange and the hookup of master gear box, and the master gear box does the utility model discloses wholly provide location and support. The barring motor supports through barring motor mounting flange because power is less the utility model discloses on the casing 900.

3. The utility model discloses a barring motor adopts publicly known transmission forms such as bevel gear, worm gear and worm to articulate with barring clutch 700 input. The starting motor is independently supported by a base due to high power and is connected with the input end of the starting clutch 600 through a coupler.

4. The utility model discloses a with integrated barring clutch 700, start-up clutch 600, barring motor mounting flange, main mounting flange in a transmission, simplified the shafting of main drive gear box, reduced area, reduced the processing degree of difficulty and cost.

Drawings

Fig. 1 is a schematic diagram of an arrangement of a conventional gas turbine power plant.

FIG. 2 is a power flow diagram of a conventional gas turbine genset during barring.

FIG. 3 is a power flow diagram of a prior art gas turbine power plant at start-up.

Fig. 4 is a schematic layout of a gas turbine power generator set according to the present invention.

Fig. 5 is a power flow diagram when the gas turbine generator set is turned on.

Fig. 6 is a power flow diagram when the gas turbine generator set of the present invention is started.

FIG. 7 is a drawing showing the connection relationship between the present invention and the barring motor, the starting motor and the main gearbox

Fig. 8 is a schematic diagram of the arrangement principle of the present invention.

Fig. 9 is a schematic diagram of the mechanism of the present invention.

Fig. 10 is a diagram showing the state and power flow of the internal clutch in the normal operation of the internal combustion engine according to the present invention.

Fig. 11 is a diagram showing the state and power flow of the internal clutch during turning of the vehicle according to the present invention.

Fig. 12 is a diagram showing the state and power flow of the internal clutch at the time of starting the present invention.

Fig. 13 is a cross-sectional view of an embodiment of the invention.

Fig. 14 is an axial view of fig. 13.

Fig. 15 is a state and power flow diagram of the internal clutch during normal operation of the engine of fig. 13.

Fig. 16 is a diagram showing the state and power flow of the internal clutch during turning of fig. 13.

FIG. 17 is a chart showing the state and power flow of the internal clutches during the launch of FIG. 13.

Fig. 18 is the condition of fig. 13 with the low-speed pawl extended.

Fig. 19 is a state of the low-speed pawl of the barring clutch of fig. 13 retracted.

FIG. 20 is the condition of FIG. 13 with the launch clutch low-speed pawls extended.

FIG. 21 is the condition of FIG. 13 with the launch clutch low-speed pawls retracted.

Fig. 22 is a state in which the high speed pawls of the starting clutch 600 of fig. 13 are extended.

Fig. 23 is a state in which the high speed pawls of the starting clutch 600 of fig. 13 are retracted.

In the figure, 10, gas turbine, 20, generator, 30, starter motor, 40, barring motor, 42, barring motor coupling, 60, prior art barring clutches 700, 70, prior art starter clutches 600, 82, coupling, 84, coupling, 86, coupling. 100. Main transmission gearbox, 110, modified main transmission gearbox, 120, low speed main transmission gears z1, 110, high speed main transmission gears z2, 130, accessory gears z3, 140, accessory gears z4, 142, main transmission gearbox oil supply, 150, accessory gears z5, 160, accessory gears z6, 170, accessory gear z 7. 201 combustion engine power generation power flows, 202 barring power flows, 203 starting power flows, 210, this patent combustion engine power generation power flows, 220, this patent barring power flows, 230, this patent starting power flows, 500 the utility model discloses a wholly, 505, barring switching-over transmission subassembly, 510, little bevel gear, 520, big bevel gear, 530, big bevel gear bearing. 600. A start clutch, a start input shaft 610, a start input shaft 612, a start clutch left location, 614, a start clutch right location, 620, a start clutch internal helical spline, 622, a start clutch input ring gear, 630, a start clutch external helical spline, 631, a start clutch high speed pawl catch pin, 632, a start clutch high speed pawl pin, 633, a start clutch high speed pawl, 634, an output flange internal ratchet, 635, a start clutch slip, 636, a start clutch slip external ratchet, 650, a start clutch internal drive tooth, 640, a start clutch external drive tooth, 660, a barring clutch external drive tooth, 670, an output flange, 671, a barring clutch pawl catch pin, 672, a barring clutch pawl spring, 673, a barring clutch low speed pawl, 674, a barring clutch pawl pin, 675, a start clutch low speed pawl pin, 676. a starting clutch low speed pawl pin 677, a starting clutch low speed pawl 678, a starting clutch low speed pawl spring 682, and a ratchet wheel in the barring clutch glide. 700. The turning clutch comprises a turning clutch body 712, a starting clutch left positioning body 714, a starting clutch right positioning body 720, a turning clutch outer spiral spline, 730, a turning clutch inner spiral spline, 740, a turning clutch sliding piece 760, a turning clutch inner driving tooth 900, a shell 900, 904, a shell 900 middle split surface, 906, an upper shell 900, 908, a lower shell 900, 910, a starting input shaft bearing, 920, a small bevel gear bearing, 930, a main mounting flange, 935, a positioning spigot, 940 and a turning motor mounting flange.

Detailed Description

The first embodiment is as follows: the present embodiment is described with reference to fig. 4 to 23, and the integrated transmission device for turning and starting a gas turbine generator set in the present embodiment is formed by connecting a starting clutch 600, a turning clutch 700, a turning 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 is concentrically arranged with the barring clutch 700, the barring clutch 700 is located outside the starting clutch 600 and supported on the barring reversing gear assembly 505, both the starting clutch 600 and the barring clutch 700 are synchronous automatic clutch structures, 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 bevel 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 with the barring motor, the starting input shaft 610 of the starting clutch 600 is connected with the starting motor, and the output flange 670 is rigidly connected with a main gearbox gear of the unit.

The second embodiment is as follows: referring to fig. 13 to 17, the turning gear reversing transmission assembly 505 of the present 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 mounted on the housing 900 through the small bevel gear 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 and the small bevel gear 510 are engaged with each other and have perpendicular axes, the small bevel gear 510 is connected with a turning motor, and the large bevel gear 520 is provided with a turning clutch internal helical spline 730. So set up, be convenient for transmit power. Other components and connections are the same as in the first embodiment.

The third concrete implementation mode: referring to fig. 13 to 17, the present embodiment is described, a housing 900 of the present embodiment is provided with a mounting flange 940 of a barring motor and a main mounting flange 930 connected to a main gearbox, the mounting flange 940 of the barring motor 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, a middle section 904 is arranged between the upper housing 906 and the lower housing 908, and the bevel pinion 510 and the mounting flange 940 of the barring motor are both mounted on the upper housing 906. So set up, be convenient for install whole transmission system, it is convenient to produce manufacturing simultaneously. Other compositions and connections are the same as in the first or second embodiments.

The fourth concrete implementation mode: describing the present embodiment with reference to fig. 13 to 17, the starting clutch 600 of the present embodiment includes a starting input shaft 610, a starting input shaft bearing 910, an input ring gear 622, a starting clutch slip 635, a starting clutch female helical spline 620, a starting clutch male helical spline 630, and a starting clutch male drive tooth 640; the starting input shaft 610 is rotatably installed on the shell 900 through a starting input shaft bearing 910, an input gear ring 622 is sleeved on the starting input shaft 610, a starting clutch external helical spline 630 is installed on the input gear ring 622, a starting clutch internal helical spline 620 is installed on a starting clutch sliding piece 635, the starting clutch sliding piece 635 is installed on the input gear ring 622, the starting clutch internal helical spline 620 is connected with the starting clutch external helical spline 630, and a starting clutch external driving gear 640 is manufactured on the starting clutch sliding piece 635. Other compositions and connection relationships are the same as in the first, second or third embodiment.

The fifth concrete implementation mode: the present embodiment is described with reference to fig. 13 to 17, an output flange 670 of the present embodiment includes a flange body, a start clutch inner driving tooth 650, a barring clutch outer driving tooth 660, a barring clutch low-speed pawl mechanism, a start clutch low-speed pawl mechanism and a start clutch high-speed ratchet wheel, the start clutch inner driving tooth 650 and the barring clutch outer driving tooth 660 are respectively disposed on the inner side wall and the outer side wall of the flange body, after a start clutch sliding member 635 slides, the start clutch inner driving tooth 650 is engaged with the start clutch outer driving tooth 640, and the barring clutch low-speed pawl mechanism, the start clutch low-speed pawl mechanism and the start clutch high-speed ratchet wheel are sequentially mounted on the flange body from left to right. Other compositions and connection relationships are the same as those in the first, second, third or fourth embodiment.

The sixth specific implementation mode: the present embodiment will be described with reference to fig. 18 to 19, and the barring clutch low speed pawl mechanism of the present embodiment includes: a barring clutch pawl catch pin 671, a barring clutch pawl spring 672, a barring clutch glide inner ratchet gear 682, a barring clutch low speed pawl 673 and a barring clutch pawl pin 674, wherein the barring clutch pawl pin 674 is mounted on the flange body, the barring clutch low speed pawl 673 is rotatably mounted on the barring clutch pawl pin 674 through the barring clutch pawl spring 672, the barring clutch pawl catch 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 glide 740 is provided with a barring clutch glide inner ratchet gear 682, the barring clutch glide 740 and the large bevel gear 520 are in meshing connection through a barring clutch outer helical spline 720 and a barring clutch spline 730, the inner side wall of the barring clutch glide 740 is provided with a barring clutch inner drive gear 760, and the barring clutch low speed pawl 673 is meshed with the barring clutch inner ratchet gear 682, the barring clutch glide 740 glides, the barring clutch inner drive teeth 760 mesh with the barring clutch outer drive teeth 660, transferring the barring motor torque, when the rotational speed of the output flange 670 is greater than the barring rotational speed, the barring clutch glide 740 glides in reverse direction, the barring clutch inner drive teeth 760 mesh with the barring clutch outer drive teeth 660, and stopping transferring the barring torque. Other compositions and connection relationships are the same as in the first, second, third, fourth or fifth embodiment.

The seventh embodiment: describing the present embodiment with reference to fig. 20 to 21, the start clutch low-speed pawl mechanism of the present embodiment includes a start clutch slider outer ratchet wheel 636, a start clutch low-speed pawl catch pin 675, a start clutch low-speed pawl pin 676, a start clutch low-speed pawl 677 and a start clutch low-speed pawl spring 678, the start clutch low-speed pawl pin 676 is installed on the flange body, the start clutch slider 635 is provided with a start clutch slider outer ratchet wheel 636, the start clutch low-speed pawl 677 is rotatably installed on the start clutch pawl pin 676 by the start clutch low-speed pawl spring 678, the start clutch low-speed pawl catch pin 675 is installed on the flange body on the left side of the start clutch pawl pin 676, and the start clutch slider 635 slides when the start clutch low-speed pawl 677 is engaged with the start clutch slider outer ratchet wheel 636, so that the start clutch inner drive teeth 650 are engaged with the start clutch outer drive teeth 640, and transmits the starting motor torque, when the rotating speed of the output flange 670 is greater than that of the starting motor, the starting clutch sliding member 635 slides reversely, the starting clutch inner driving teeth 650 and the starting clutch outer driving teeth 640 are disengaged, and the transmission of the starting motor torque is stopped. Other compositions and connection relationships are the same as in the first, second, third, fourth, fifth or sixth embodiment.

The specific implementation mode is eight: referring to fig. 22 to 23, the start clutch high speed ratchet according to this embodiment includes an output flange inner ratchet 634, a start clutch high speed pawl 633, a start clutch high speed pawl pin 632, and a start clutch high speed pawl stop pin 631, the output flange inner ratchet 634 is disposed on an inner sidewall of a body of the output flange 670, the start clutch high speed pawl pin 632 is mounted on a start clutch sliding member 635, the start clutch high speed pawl 633 is rotatably mounted on the start clutch high speed pawl pin 632, the start clutch high speed pawl stop pin 631 is mounted on the start clutch sliding member 635 at a right side of the start clutch high speed pawl pin 632, when the start clutch high speed pawl 633 is engaged with the output flange inner ratchet 634, the start clutch sliding member 635 slides to engage the start clutch inner drive teeth 650 with the start clutch outer drive teeth 640 and transmit a start motor torque, when the rotational speed of the output flange 670 is greater than the rotational speed of the starter motor, the start clutch slider 635 slides in the reverse direction, the start clutch inner drive teeth 650 and the start clutch outer drive teeth 640 are disengaged, and the transmission of the torque of the starter motor is stopped. Other constitutions and connection relations are the same as those of any one of the first to seventh embodiments.

The transmission conditions of the low-speed ratchet-pawl mechanism of the turning gear clutch, the low-speed ratchet-pawl mechanism of the starting clutch and the high-speed ratchet-pawl mechanism of the starting clutch are as follows:

the external helical spline on the sliding part of the turning gear clutch is connected with the internal helical spline of the big bevel gear 505 of the turning gear reversing transmission component, and the internal driving tooth on the sliding part of the turning gear clutch and the external driving tooth of the output flange can be axially meshed.

The internal helical spline on the starting clutch sliding piece is connected with the external helical spline of the starting clutch, and the external driving tooth on the starting clutch sliding piece and the internal driving tooth of the output flange can be axially meshed.

The barring 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.

The low-speed pawl of the turning clutch is arranged on the output flange and can extend outwards under the action of a pawl spring. When the rotating speed of the output flange is higher than a certain value, the pawl is automatically retracted under the action of centrifugal force.

The low-speed pawl of the starting clutch is arranged on the output flange and can extend inwards under the action of a pawl spring. When the rotating speed of the output flange is higher than a certain value, the pawl is automatically retracted under the action of centrifugal force.

The high-speed pawl of the starting clutch 600 is arranged on the starting clutch sliding member, and when the rotating speed of the sliding member is higher than a certain value, the pawl is automatically lifted under the action of centrifugal force.

After the low-speed pawl of the turning clutch on the output flange is meshed with the ratchet wheel in the sliding piece of the turning clutch, the sliding piece of the turning clutch can be driven to axially move, the inner driving teeth and the outer driving teeth of the turning clutch 700 are meshed, and torque is transmitted.

After the low-speed pawl of the starting clutch on the output flange is meshed with the outer ratchet wheel on the sliding piece of the starting clutch, the sliding piece of the starting clutch can be driven to axially move, the inner driving teeth and the outer driving teeth of the starting clutch 600 are meshed, and torque is transmitted.

After a high-speed pawl on the starting clutch sliding piece is meshed with an inner ratchet wheel on the output flange, the starting clutch sliding piece can be driven to move axially, the inner driving teeth and the outer driving teeth of the starting clutch 600 are meshed, and torque is transmitted.

After the inner and outer driving teeth of the barring clutch 700 are engaged and transmit torque, when the rotating speed of the output flange is higher than that of the barring clutch sliding piece, the barring clutch sliding piece moves axially, and the inner and outer driving teeth of the barring clutch 700 are disengaged.

After the internal and external driving teeth of the starting clutch 600 are engaged and transmit torque, when the rotating speed of the output flange is higher than that of the starting clutch sliding piece, the starting clutch sliding piece moves axially, and the internal and external driving teeth of the starting clutch 600 are disengaged.

The working principle of the present invention is explained with reference to fig. 1 to 23:

in fig. 1, a gas turbine 10, a main transmission gearbox 100, a generator 20, a starter motor 30, an existing turning gear clutch 60, and an existing starter clutch 70 constitute a gas turbine generator set. 7 groups of parallel shaft gears 110 to 170 are arranged inside the main transmission gear box 100 and are used for matching the motion relations of steering, rotating speed and the like of the unit.

The gas turbine 10 is connected to the gear 110 by a first coupling 82, the generator 20 is connected to the gear 120 by a second coupling 84, and the starter motor 30 is connected to the gear 170 by a third coupling 86.

The barring motor 40 is connected with the gear 150 through the shaft coupling 42 and the barring reversing transmission assembly 505 through the barring clutch 60, and the gear 150 is connected with the gear 140 through the starting clutch 70.

The low-speed main drive gear z1120 meshes with the modified main drive gear box 110, the modified main drive gear box 110 meshes with the accessory gear z3130, the accessory gear z3130 meshes with the accessory gear z 4140, the accessory gear z 5150 meshes with the accessory gear z 6160, and the accessory gear z 6160 meshes with the accessory gear z 7170.

When the combustion engine generates power, the power flow transmission route is that the gas turbine 10 → the first coupler 82 → the modified main transmission gearbox 110 → the low-speed main transmission gear z1120 → the generator 20 and the modified main transmission gearbox 110 → the accessory gear z3130 → the accessory gear z 4140 → the starting clutch 70, and when the combustion engine generates power, the starting clutch 70 is in a disengaged state. The accessory gear z 5150, the accessory gear z 6160, and the accessory gear z 7170 are in a stationary state.

The turning clutch 60 and the starting clutch 70 are both synchronous automatic clutch structures, and the turning clutch 60 and the starting clutch 70 have the characteristics that: the clutch is automatically engaged when the input end rotating speed is higher than the output end rotating speed, and the clutch is automatically disengaged when the output end rotating speed is higher than the input end rotating speed. The output end of the starting clutch 70 is connected with the accessory gear z 4140, and when the internal combustion engine generates power, the speed of the output end of the starting clutch 70 is higher than that of the input end, so that the starting clutch 70 is in a disengaged state.

The input end of the turning clutch 60 is connected with the turning motor 40 through the small bevel gear 510 and the large bevel gear 520, the output end of the turning clutch 60 is connected with the accessory gear z 5150, after the power generation of the combustion engine is finished, when the turning is needed, the turning motor 40 is started, when the rotating speed of the input end of the turning clutch 60 is greater than the rotating speed of the output end, the turning clutch 60 is automatically combined, meanwhile, the starting clutch 70 also meets the joint condition that the rotating speed of the input end is greater than the rotating speed of the output end, and then the turning motor 40 drives 7 groups of parallel shaft gears arranged in the main transmission gear box 100 to start turning motion. The power flow 202 is routed by the barring electric motor 40 → the barring clutch 60 → the accessory gear z 5150 → the starting clutch 70 → the accessory gear z 4140 → the accessory gear z3130 → the modified main transmission gearbox 110 → the low speed main transmission gear z1120 → the second coupling 84 → the generator 20, the modified main transmission gearbox 110 → the first coupling 82 → the gas turbine 10 and the accessory gear z 5150 → the accessory gear z 6160 → the accessory gear z 7170 → the third shaft coupler 86 → the starting electric motor 30.

When the barring is finished and the combustion engine needs to be started again, the starting motor 30 starts to increase the speed, and when the rotating speed of the starting motor is greater than that of the barring, the barring clutch 60 is automatically disengaged, but the starting clutch 70 is always in an engaged state. The transmission route of the power flow 203 is that the starting motor 30 → the third coupler 86 → the accessory gear z 7170 → the accessory gear z 6160 → the accessory gear z 5150 → the starting clutch 70 → the accessory gear z 4140 → the accessory gear z3130 → the modified main transmission main gear box 110 → the low-speed main transmission gear z1120 → the second coupler 84 → the generator 20, the modified main transmission main gear box 110 → the first coupler 82 → the gas turbine 10, the starting motor 30 drives the combustion engine to accelerate through the starting clutch 70 and the gear set, the compressor of the combustion engine starts to compress air, the combustion engine ignites after the combustion engine is accelerated to a certain rotation speed (2000r/min-3000r/min), the combustion engine continues to be accelerated to a normal working state, the starting clutch 70 is automatically disengaged after the combustion engine is ignited, and the starting motor 30 can be stopped at a reduced speed.

In the gas turbine generator set shown in fig. 1, in order to arrange the jigger and the starting motor, the gear box 100 has six shafts, 5 pairs of meshing gears, and the gear box has the disadvantages of high processing difficulty, large occupied area and high manufacturing cost.

To solve the problem of fig. 1, the turning clutch 60 and the starting clutch 70 are integrated together, and share an output part and a supporting housing 900, thereby forming the integrated transmission 500 of the present invention, and achieving the purpose of simplifying the main gearbox shafting. As shown in FIG. 4, the improved main gearbox 110 has only 4 shafts, 4 gears and 3 meshing points, the difficulty of processing the main gearbox is greatly reduced, and the floor area is also greatly reduced.

The power flow 220 during turning in fig. 5 is routed from the turning motor 40 → the turning clutch 700 → the accessory gear z 4140 → the accessory gear z3130 → the high speed final drive gear z 2110 → the low speed final drive gear z1120 → the second coupling 84 → the generator 20, the high speed final drive gear z 2110 → the first coupling 82 → the gas turbine 10; in fig. 6, the power flow 230 at the time of starting is transmitted by the starter motor 30 → the third coupling 86 → the starter clutch 600 → the accessory gear z 4140 → the accessory gear z3130 → the modified main transmission gearbox 110 → the low speed main transmission gear z1120 → the second coupling 84 → the generator 20, the modified main transmission gearbox 110 → the first coupling 82 → the gas turbine 10, and since 2 gear mesh points and 5 bearings are reduced, the starting power flow path is less lost and more efficient.

In fig. 7, the integrated transmission 500 of the present invention supplies oil through the main gearbox, the oil supply route is 142, the integrated transmission 500 is connected to the starter motor 30 through the third coupling 86, the integrated transmission 500 is connected to the barring motor 40 through the coupling 42, the integrated transmission 500 is connected to the main gearbox gear 140 through the output flange 670, and the integrated transmission 500 is supported on the main gearbox casing through the main mounting flange 930.

In fig. 8, the integrated transmission 500 of the present invention mainly comprises a starting barring clutch 600, a barring starting clutch 700, a barring reversing transmission assembly 505, and a housing 900. The starting barring clutch 600 and the barring starting clutch 700 are both synchronous automatic clutch structures.

In fig. 9, the starting turning clutch 600 includes an input shaft starting input shaft 610, a starting clutch slider 635, an output flange 670, a ratchet pawl (not shown in fig. 9), and the like, where the starting input shaft 610 is supported on a housing 900 through a bearing 910, the starting clutch slider 635 is supported on the input shaft starting input shaft 610, a female spiral spline starting clutch female spiral spline 620 is formed on the starting input shaft 610, a male spiral spline 630 is formed on the starting clutch slider 635, and the starting clutch female spiral spline 620 is connected with the starting clutch male spiral spline 630. The start clutch slip 635 is further provided with start clutch outer drive teeth 640, the output flange 670 is provided with inner drive teeth 650, and based on the well-known synchronous automatic clutch principle, when the rotation speed of the start input shaft 610 exceeds the rotation speed of the output flange 670, the start clutch slip 635 moves to the left under the action of a ratchet pawl, and when the start clutch outer drive teeth 640 are meshed with the start clutch inner drive teeth 650, torque can be transmitted from the start input shaft 610 to the output flange 670, and the start barring clutch 600 is in an engaged state. When output flange 670 increases in speed, launch clutch slide 635 moves to the right, and launch barring clutch 600 is in a disengaged state when launch clutch outer drive teeth 640 are disengaged from launch clutch inner drive teeth 650.

In fig. 9, a turning gear starting clutch 700 is composed of a large bevel gear 520, a sliding member 740, an output flange 670 shared with the starting clutch 600, a ratchet pawl (not shown in fig. 9) and the like, the large bevel gear 520 is supported on a housing 900 through a bearing 530, an internal helical spline 720 is formed on the large bevel gear 520, an external helical spline 730 is formed on the turning gear sliding member 740, the external helical spline 720 of the turning gear is connected with the internal helical spline 730 of the turning gear, inner driving teeth 760 of the turning gear is formed on the turning gear sliding member 740, and outer driving teeth 660 are formed on the output flange 670. Based on well-known synchronous automatic clutch principles, when the large bevel gear 520 rotates faster than the output flange 670, the barring clutch glide 740 moves to the left under the ratchet and pawl action, and when the barring clutch outer drive teeth 660 engage with the barring clutch inner drive teeth 760, torque can be transferred from the large bevel gear 520 to the output flange 670 and the barring initiation clutch 700 is in an engaged state. As output flange 670 increases in speed, barring clutch glide 740 moves to the right and barring initiation clutch 700 is in a disengaged state when barring clutch outer drive teeth 660 disengage from barring clutch inner drive teeth 760.

The starting clutch slide 635 is axially positioned by a positioning surface starting clutch left positioning 612 and a starting clutch right positioning 614; the barring clutch glide 740 is axially located by the locating surface launch clutch left location 712 and launch clutch right location 714. The output flange 670 is rigidly connected to the gear 140 of the main gearbox 110 and the accessory gear z 4140 provides support and positioning for the output flange 670.

The turning gear reversing assembly 505 is composed of a small bevel gear 510 and a large bevel gear 520, the small bevel gear 510 is supported on the shell 900 through a bearing 920, and the small bevel gear 510 is meshed with the large bevel gear 520.

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 bevel pinion bearing 920, and the main mounting flange 930 is concentric with the start input shaft bearing 910.

In FIG. 10, the gas turbine is generating power normally, power flow is 210, start clutch slip 635 is positioned at 614, slip 740 is positioned at 714, start clutch 600, and barring clutch 700 are both disengaged, and output flange 670 idles with accessory gear z 4140.

In fig. 11, the unit is in a turning gear state with power flow 220, start clutch slip 635 is still positioned at 614, slip 740 is positioned at start clutch left position 712, turning gear clutch 700 is in a engaged state, start clutch 600 is in a disengaged state, and torque is transferred from bevel pinion 510 to output flange 670.

In fig. 12, the unit is in a start-up ramp-up condition with power flow 230, start-up clutch slip 635 is positioned at 612, slip 740 is positioned at start-up clutch right location 714, start-up clutch 600 is engaged, turning clutch 700 is disengaged, and torque is transferred from start-up input shaft 610 to output flange 670.

Fig. 13 and 14 show a specific embodiment of the present invention, wherein the start input shaft bearing 910 and the bevel pinion bearing 920 are rolling bearings, the bevel pinion bearing 530 is a sliding bearing, the housing 900 has a middle split surface and is divided into an upper housing 906 and a lower housing 908, the start clutch input ring 622 is provided with a male helical spline, and the start clutch input ring 622 is rigidly connected to the start input shaft 610.

Fig. 15, 16 and 17 show the positioning state and power flow condition of the clutch sliding part under three working conditions of disengagement, turning and starting according to the embodiment of the invention as shown in fig. 13.

Fig. 18-23 illustrate the arrangement of the ratchet and pawl in the starting barring clutch 600, 700 of the present invention.

In fig. 18 and 19, the barring clutch low speed pawls 673 of the barring launch clutch 700 are arranged on the output flange 670, the barring clutch low speed pawls 673 can swing about the barring clutch pawl pins 674, and the pawl springs 672 lift the heads of the barring clutch low speed pawls 673. When the barring gear is engaged, the output flange 670 is stationary, the ratchet gear 682 rotates clockwise, and the ratchet gear 682 engages the pawl 673, forcing the slide 740 to move, and effecting engagement of the barring initiation clutch 700. After the turning is finished, when the rotating speed of the output flange 670 exceeds the rotating speed of the ratchet wheel 682, the gravity center of the low-speed pawl 673 of the turning clutch is positioned at the tail part, under the action of centrifugal force, the tail part of the low-speed pawl 673 of the turning clutch is lifted, and the head part of the low-speed pawl 673 of the turning clutch can be pressed down to lean against the stop pin 671 and not move any more, so that the low-speed pawl 673 of the turning clutch and the ratchet wheel 682 in a sliding part of the turning clutch are prevented from being.

In fig. 20, 21, the starting clutch low-speed pawl 677 of the starting barring 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 low-speed pawl spring 678 presses down the head of the starting clutch low-speed pawl 677. When the starting clutch is started, the output flange 670 is still driven by the turning gear motor to rotate at a low speed, the starting clutch sliding piece outer ratchet wheel 636 rotates clockwise in an accelerated manner, and when the starting clutch sliding piece outer ratchet wheel 636 exceeds the rotating speed of the output flange 670, the starting clutch sliding piece outer ratchet wheel 636 is meshed with the starting clutch low-speed pawl 677 to force the starting clutch sliding piece 635 to move, so that the starting clutch 700 is combined and jointed at the low rotating speed.

After starting, when the rotating speed of the output flange 670 exceeds the rotating speed of the outer ratchet wheel 636 of the sliding piece of the starting clutch, the gravity center of the low-speed pawl 677 of the starting clutch is positioned at the head, the head of the low-speed pawl 677 of the starting clutch is lifted under the action of centrifugal force, and the head can be lifted to lean against the stop pin 675 of the low-speed pawl of the starting clutch to stop moving, so that the low-speed pawl 677 of the starting clutch and the outer ratchet wheel 636 of the sliding piece of the starting clutch are prevented from being abraded.

In fig. 22 and 23, the start clutch low-speed pawl 633 of the starting barring clutch 600 is arranged on the start clutch slider 635, the start clutch low-speed pawl 633 can swing around the start clutch pawl pin 632, the center of gravity of the start clutch low-speed pawl 633 is located at the head, when the rotation speed of the start clutch slider 635 is increased, the head of the start clutch low-speed pawl 633 can be lifted up under the centrifugal force, and after the first start, although the barring clutch 600 is already disengaged, the rotation speed of the output flange 635 is greater than that of the start clutch slider 635. But starter motor 30 is not stopped, starter motor 30 maintains the rotational speed of starter clutch slip 635 at a higher rotational speed at all times. When the first start of the internal combustion engine fails, the rotation speed of the output flange 670 begins to drop, and when the rotation speed of the output flange 670 is lower than that of the start clutch sliding piece 635, the output flange inner ratchet wheel 634 is meshed with the start clutch low-speed pawl 633 to force the start clutch sliding piece 635 to move, so that the start clutch 700 is re-engaged at a high rotation speed.

After the starting process is finished, the starting motor 30 is stopped, the rotating speed of the starting clutch sliding member 635 is gradually reduced to 0, the centrifugal force applied to the starting clutch low-speed pawl 633 is also gradually reduced, and because the rotating speed of the output flange 670 is far greater than that of the starting clutch sliding member 635, an 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, so that the abrasion of the starting clutch low-speed pawl 633 and the ratchet 634 in the output flange is avoided.

Claims (8)

1. The utility model provides an integrated form transmission for combustion engine generating set barring and start-up, is formed by starting clutch (600), barring clutch (700), barring switching-over drive assembly (505), casing (900), start input shaft bearing (910), little bevel gear bearing (920) and big bevel gear bearing (530) are connected, characterized by: the starting clutch (600) and the barring clutch (700) are concentrically arranged, the barring clutch (700) is positioned outside the starting clutch (600) and supported on the barring reversing transmission assembly (505), the starting clutch (600) and the barring clutch (700) are both in a synchronous automatic clutch structure, the starting clutch (600) and the barring clutch (700) share the same output flange (670), a starting input shaft (610) of the starting clutch (600) is supported on the shell (900) through a starting input shaft bearing (910), the barring reversing transmission assembly (505) is also supported on the shell (900) through a starting input shaft bearing (910) and a small bevel gear bearing (920), the axis of a starting motor of the starting clutch (600) is perpendicular to the axis of the barring motor of the barring clutch (700), and the input shaft of the barring reversing transmission assembly (505) is connected with a barring motor, a starting input shaft (610) of the starting clutch (600) is connected with a starting motor, and an output flange (670) is rigidly connected with a main gearbox gear of the unit.

2. The integrated transmission device for turning and starting a gas turbine generator set according to claim 1, wherein: jigger reversing transmission assembly (505) comprises a small bevel gear (510), a large bevel gear (520), a small bevel gear bearing (920) and a large bevel gear bearing (530), wherein the small bevel gear (510) is rotatably installed on a shell (900) through the small bevel gear bearing (920), the large bevel gear (520) is rotatably installed on the shell (900) through the large bevel gear bearing (530), the large bevel gear (520) is meshed with the small bevel gear (510) and the axis of the large bevel gear is mutually vertical, the small bevel gear (510) is connected with a jigger motor, and the large bevel gear (520) is provided with a jigger clutch internal spiral spline (730).

3. An integrated transmission for turning and starting a gas turbine generator set according to claim 1 or 2, wherein: a turning motor mounting flange (940) and a main mounting flange (930) connected with a main gear box are arranged on a shell (900), the turning motor mounting flange (940) and the main mounting flange (930) are perpendicular to each other, the shell (900) is divided into an upper shell (906) and a lower shell (908), a middle split surface (904) is arranged between the upper shell (906) and the lower shell (908), and both the bevel pinion (510) and the turning motor mounting flange (940) are arranged on the upper shell (906).

4. The integrated transmission device for turning and starting of a gas turbine generator set according to claim 3, wherein: the starting clutch (600) comprises a starting input shaft (610), a starting input shaft bearing (910), an input gear ring (622), a starting clutch sliding piece (635), a starting clutch internal helical spline (620), a starting clutch external helical spline (630) and a starting clutch external driving tooth (640); the starting input shaft (610) is rotatably installed on the shell (900) through a starting input shaft bearing (910), an input gear ring (622) is sleeved on the starting input shaft (610), a starting clutch external helical spline (630) is installed on the input gear ring (622), a starting clutch internal helical spline (620) is installed on a starting clutch sliding piece (635), the starting clutch sliding piece (635) is installed on the input gear ring (622), the starting clutch internal helical spline (620) is connected with the starting clutch external helical spline (630), and starting clutch external driving teeth (640) are manufactured on the starting clutch sliding piece (635).

5. The integrated transmission device for turning and starting of a gas turbine generator set according to claim 4, wherein: the output flange (670) comprises a flange body, a starting clutch inner driving tooth (650), a barring clutch outer driving tooth (660), a barring clutch low-speed pawl mechanism, a starting clutch low-speed pawl mechanism and a starting clutch high-speed ratchet wheel, wherein the starting clutch inner driving tooth (650) and the barring clutch outer driving tooth (660) are respectively arranged on the inner side wall and the outer side wall of the flange body, after a starting clutch sliding piece (635) slides, the starting clutch inner driving tooth (650) is meshed with the starting clutch outer driving tooth (640), and the barring clutch low-speed pawl mechanism, the starting clutch low-speed pawl mechanism and the starting clutch high-speed ratchet wheel are sequentially arranged on the flange body from left to right.

6. The integrated transmission for turning gear and starting of a gas turbine generator set according to claim 5, characterized in that: the barring clutch low-speed pawl mechanism comprises a barring clutch pawl catch pin (671), a barring clutch pawl spring (672), a barring clutch low-speed pawl (673) and a barring clutch pawl pin (674), and a barring clutch sliding piece inner ratchet wheel (682);

a barring clutch pawl pin (674) is arranged on a flange body, a barring clutch low-speed pawl (673) is arranged on the barring clutch pawl pin (674) through a barring clutch pawl spring (672), the barring clutch pawl stop pin (671) is arranged on the flange body on the left side of the barring clutch pawl pin (674), an inner ratchet wheel (682) of the barring clutch sliding piece (740) is arranged on the inner side of the barring clutch sliding piece, the barring clutch sliding piece (740) is in meshing connection with a large bevel gear (520) through a barring clutch outer spiral spline (720) and a barring clutch inner spiral spline (730), a barring clutch inner driving tooth (760) is arranged on the inner side wall of the barring clutch sliding piece (740), and when the barring clutch low-speed pawl (673) is meshed with the inner ratchet wheel (682), the barring clutch sliding piece (740) slides, the inner driving gear (760) of the barring clutch is meshed with the outer driving gear (660) of the barring clutch to transmit the torque of the barring motor, when the rotating speed of the output flange (670) is larger than that of the barring, the slipping piece (740) of the barring clutch slips in the reverse direction, the inner driving gear (760) of the barring clutch is meshed with the outer driving gear (660) of the barring clutch in a withdrawing mode, and the barring torque is stopped being transmitted.

7. The integrated transmission for turning gear and starting of a gas turbine generator set according to claim 6, characterized in that: the starting clutch low-speed pawl mechanism comprises a starting clutch sliding piece outer ratchet wheel (636), a starting clutch low-speed pawl stop pin (675), a starting clutch low-speed pawl pin (676), a starting clutch low-speed pawl (677) and a starting clutch low-speed pawl spring (678), wherein the starting clutch low-speed pawl pin (676) is installed on the flange body, the starting clutch sliding piece (635) is provided with the starting clutch sliding piece outer ratchet wheel (636), the starting clutch low-speed pawl (677) is rotatably installed on the starting clutch low-speed pawl pin (676) through the starting clutch low-speed pawl spring (678), the starting clutch low-speed pawl stop pin (675) is installed on the flange body on the left side of the starting clutch low-speed pawl pin (676), and the starting clutch sliding piece (635) slides when the starting clutch low-speed pawl (677) is meshed with the starting clutch sliding piece outer ratchet wheel (636), and the starting clutch inner driving teeth (650) are meshed with the starting clutch outer driving teeth (640) and transmit the torque of the starting motor, when the rotating speed of the output flange (670) is greater than that of the starting motor, the starting clutch sliding piece (635) slides reversely, the starting clutch inner driving teeth (650) are meshed with the starting clutch outer driving teeth (640) in a withdrawing way, and the transmission of the torque of the starting motor is stopped.

8. The integrated transmission for turning gear and starting of a gas turbine generator set according to claim 7, characterized in that: the starting clutch high-speed ratchet wheel comprises an output flange inner ratchet wheel (634), a starting clutch high-speed pawl (633), a starting clutch high-speed pawl pin (632) and a starting clutch high-speed pawl stop pin (631), wherein the output flange inner ratchet wheel (634) is arranged on the inner side wall of the output flange (670), the starting clutch high-speed pawl pin (632) is arranged on a starting clutch sliding piece (635), the starting clutch high-speed pawl (633) is rotatably arranged on the starting clutch high-speed pawl pin (632), the starting clutch high-speed pawl stop pin (631) is arranged on the starting clutch sliding piece (635) on the right side of the starting clutch high-speed pawl pin (632), and when the starting clutch high-speed pawl (633) is meshed with the output flange inner ratchet wheel (634), the starting clutch sliding piece (635) slides to enable the starting clutch inner driving teeth (650) to be meshed with the starting clutch outer driving teeth (640), and transmitting the torque of the starting motor, when the rotating speed of the output flange (670) is greater than that of the starting motor, the starting clutch sliding piece (635) slides reversely, the driving teeth (650) in the starting clutch and the driving teeth (640) outside the starting clutch are disengaged, and the transmission of the torque of the starting motor is stopped.

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