CN114198428A - High-power synchronous automatic clutch of combustion-evaporation combined cycle generator set - Google Patents
High-power synchronous automatic clutch of combustion-evaporation combined cycle generator set Download PDFInfo
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- CN114198428A CN114198428A CN202111500596.8A CN202111500596A CN114198428A CN 114198428 A CN114198428 A CN 114198428A CN 202111500596 A CN202111500596 A CN 202111500596A CN 114198428 A CN114198428 A CN 114198428A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D43/00—Automatic clutches
- F16D43/02—Automatic clutches actuated entirely mechanically
- F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
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Abstract
The invention belongs to the technical field of clutches, and particularly relates to a high-power synchronous automatic clutch of a combustion-steam combined cycle generator set. The invention adds a set of secondary slip components on the basis of the input component, the slip component and the output component of the traditional low-power synchronous automatic clutch to form four parts of the input component, the main slip component, the secondary slip component and the output component, so that the jointing process of the high-power synchronous automatic clutch is carried out in two steps, the main slip component in the second step slips to be driven by the sleeve gear, the size and the weight of the main slip component are not limited, and the clutch can increase the structural size of a torque transmission component as required. The length of a torque transmission structure and a synchronizing mechanism in the clutch is lengthened to adapt to the thermal expansion of a shaft system of the combustion-steam combined cycle generator set. The invention can meet the requirement of transmitting larger power by the clutch of the combustion-evaporation combined cycle generator set, can absorb the thermal expansion amount of a set shafting, and improves the operation flexibility of the combustion-evaporation combined cycle generator set.
Description
Technical Field
The invention belongs to the technical field of clutches, and particularly relates to a high-power synchronous automatic clutch of a combustion-steam combined cycle generator set.
Background
The gas turbine power generation using clean natural gas as fuel has the advantages of small pollution, quick start, small limitation by geographical conditions, short construction period, stable construction cost and the like, and the centralized gas turbine power generation is usually in a gas-steam combined cycle form. The gas-steam combined cycle unit is classified according to the shafting arrangement mode, and mainly comprises a single-shaft arrangement: the gas turbine and the steam turbine simultaneously drive a generator which is provided with a shaft system; multi-axis arrangement: the gas turbine and the steam turbine respectively drive a generator which is provided with two shafting. The single-shaft combustion-steam combined cycle generator set is mostly used for peak shaving of a power grid, and the generator set runs in two shifts. The shaft system connecting structure of the type of the unit is a gas turbine-steam turbine-generator, the unit is in rigid connection, and the steam turbine provides power by recovering heat exhausted by the gas turbine through a waste heat boiler. When the gas turbine operates to drive the generator to generate electricity, the waste heat boiler recovers the flue gas waste heat exhausted by the gas turbine to provide power for the steam turbine, the gas turbine and the steam turbine are in parallel operation to drive the generator to generate electricity together, the effect of waste heat recovery is achieved, and the unit efficiency is improved.
Single-shaft combined cycle gas-steam power plants suffer from several problems. Firstly: because the gas turbine, the steam turbine and the generator are rigidly connected, in the starting process of the unit, the gas turbine needs to be dragged to idle, so that the gas turbine is difficult to start, an auxiliary boiler needs to be configured for this purpose, when the unit is started, the steam turbine is driven by steam of the auxiliary boiler to start together with the gas turbine, and the auxiliary boiler increases equipment investment. Secondly, the method comprises the following steps: when a steam system or a steam turbine breaks down, the steam turbine cannot be separated from the unit, the gas turbine still needs to be dragged to idle, energy waste is caused, and the steam turbine cannot be stopped for maintenance.
The synchronous automatic clutch is a high-power-density and high-reliability tooth clutch which can be automatically engaged and disengaged by means of the change of the rotating speed of an input end and an output end, and is widely applied to the transmission fields of ships, metallurgy, chemical industry, power generation and the like. The synchronous automatic clutch can realize the on-line input and exit of the power device, and particularly can improve the operation flexibility of the unit in a double-power system. A synchronous automatic clutch can be arranged between a steam turbine and a generator in the combustion-evaporation combined cycle generator set, the steam turbine can be independently started and stopped, the on-line 'input' or 'exit' of the steam turbine is realized, and the unit is started more quickly and runs more flexibly. However, the maximum power of the domestic synchronous automatic clutch product is only 25MW at present, and the use requirement that the clutch of the combustion-steam combined cycle generator set transmits power of more than 150MW cannot be met.
Disclosure of Invention
The invention aims to provide a high-power synchronous automatic clutch of a combustion-steam combined cycle generator set, which can realize the independent start and stop of a steam turbine when the gas turbine operates and improve the flexibility of the operation of the combustion-steam single-shaft combined cycle generator set.
A high-power synchronous automatic clutch of a combustion-steaming combined cycle generator set comprises an input assembly, a sliding assembly and an output assembly; the output assembly is provided with a ratchet wheel and main inner driving teeth; the sliding component is provided with a main external driving tooth and a pawl;
the sliding component comprises a main sliding component and a secondary sliding component; the main sliding component is sleeved with the input component through a main spiral spline pair; the secondary sliding component is sleeved with the main sliding component through a secondary spiral spline pair; the bottom of the main sliding component is provided with a secondary sliding component joint positioning groove, and the secondary sliding component joint positioning groove is positioned behind the tail end of the secondary spiral spline pair; the pawl is positioned at the front end of the secondary sliding component, and the tail end of the secondary sliding component is provided with a secondary external driving tooth; the main external driving gear is positioned on the main sliding component; the lower part of the output assembly is provided with an axial lengthened part which extends to the front of the joint positioning groove of the secondary sliding assembly, and the tail end of the axial lengthened part is provided with a secondary inner driving tooth;
when the clutch is in a disengaged state, the output assembly is at a certain rotating speed point, and the rotating speeds of the secondary sliding assembly, the primary sliding assembly and the input assembly are the same and are at a certain rotating speed point lower than the rotating speed of the output assembly;
when the rotating speed of the input assembly tends to exceed that of the output assembly, a ratchet wheel on the output assembly is engaged with a pawl ratchet on the secondary sliding assembly, and the secondary sliding assembly axially moves under the action of the secondary spiral spline pair; when the secondary sliding component axially moves to the position where the end faces of the secondary outer driving teeth and the secondary inner driving teeth are overlapped, the ratchet wheel and the pawl are still engaged; when the secondary sliding component axially moves to the position where the ratchet wheel is axially separated from the pawl, the secondary outer driving teeth are attached to the tooth surface on one side of the secondary inner driving teeth; when the secondary sliding component moves axially to the tail end of the positioning groove jointed with the secondary sliding component, the secondary sliding component and the main sliding component move axially together under the action of the main spiral spline pair; when the main sliding component and the secondary sliding component axially move together to the position where the end faces of the main outer driving tooth and the main inner driving tooth are overlapped, the secondary outer driving tooth is still attached to the tooth surface on one side of the secondary inner driving tooth; when the main sliding component and the secondary sliding component axially move together to the position where the secondary outer driving teeth and the secondary inner driving teeth are axially separated, the tooth surfaces of one side of the main outer driving teeth and one side of the main inner driving teeth are attached; when the main sliding component and the secondary sliding component axially move together to be in contact with the input component, the main sliding component and the secondary sliding component stop moving, the main outer driving tooth is still attached to the tooth surface on one side of the main inner driving tooth, and the clutch finishes engaging action;
when the input assembly rotation speed is lower than the output assembly rotation speed, the clutch starts to perform a disengagement action, and the movement process of the disengagement action is opposite to that of the engagement action.
Further, when the secondary sliding assembly axially moves to the position where the end faces of the secondary outer driving tooth and the secondary inner driving tooth are overlapped under the action of the secondary spiral spline pair, the tooth side gaps on two sides of the secondary outer driving tooth and the secondary inner driving tooth are consistent to be a; when the secondary sliding component continues to axially move to enable the secondary external driving tooth to be attached to one side tooth face of the secondary internal driving tooth, the tooth side gap between the secondary external driving tooth and the other side of the secondary internal driving tooth is 2 a.
Further, when the main sliding component and the secondary sliding component axially move together to the position where the end faces of the main outer driving tooth and the main inner driving tooth are overlapped, the tooth side gaps on the two sides of the main outer driving tooth and the main inner driving tooth are consistent and are a; when the main sliding component and the secondary sliding component continue to axially move together until the tooth surfaces of one sides of the main outer driving tooth and the main inner driving tooth are jointed, the tooth side gap of the other sides of the main outer driving tooth and the main inner driving tooth is 2 a.
Further, the axial width of the ratchet wheel design is greater than the rotor thermal expansion; when the shafting rotor produces the axial expansion volume, the thermal expansion volume of clutch both ends rotor is all absorbed by the clutch, and when the clutch was in the off-going state, because the axial width of ratchet design is greater than the rotor thermal expansion volume, after the clutch absorbed the rotor thermal expansion volume, still do not influence ratchet, the ratchet function of pawl.
Furthermore, when the clutch is in an engaged state, after the clutch absorbs the heat expansion of the rotor, the main inner driving teeth and the main outer driving teeth still have a certain meshing width, and the torque transmission capacity of the main inner driving teeth and the main outer driving teeth is not influenced.
The invention has the beneficial effects that:
the invention adds a set of secondary slip components on the basis of the input component, the slip component and the output component of the traditional low-power synchronous automatic clutch to form four parts of the input component, the main slip component, the secondary slip component and the output component, so that the jointing process of the high-power synchronous automatic clutch is carried out in two steps, the main slip component in the second step slips to be driven by the sleeve gear, the size and the weight of the main slip component are not limited, and the clutch can increase the structural size of a torque transmission component as required. The length of a torque transmission structure and a synchronizing mechanism in the clutch is lengthened to adapt to the thermal expansion of a shaft system of the combustion-steam combined cycle generator set. The invention can meet the requirement of transmitting larger power by the clutch of the combustion-evaporation combined cycle generator set, can absorb the thermal expansion amount of a set shafting, and improves the operation flexibility of the combustion-evaporation combined cycle generator set.
Drawings
FIG. 1 is a schematic diagram of a combined cycle gas-steam turbine generator set layout with a steam turbine rigidly coupled to a generator.
FIG. 2 is a schematic diagram of a combined cycle gas-steam turbine generator set arrangement with a steam turbine coupled to a generator by a clutch.
Fig. 3 is a schematic diagram of a conventional low-power synchronous automatic clutch structure.
Fig. 4 is a schematic cross-sectional view of the clutch of the present invention in a disengaged state.
Fig. 5 is a simplified schematic diagram illustrating key structures in fig. 4.
Figure 6 is a schematic cross-sectional view of the present invention when the secondary outer drive teeth are in end-face registration with the secondary inner drive teeth.
Fig. 7 is a simplified schematic diagram illustrating key structures of fig. 6.
FIG. 8 is a cross-sectional view of the present invention when the ratchet and pawl are in an axially disengaged position.
Fig. 9 is a simplified schematic diagram illustrating key structures in fig. 8.
FIG. 10 is a schematic cross-sectional view of the present invention when the secondary slide assembly is in the secondary slide assembly engagement detent.
Fig. 11 is a simplified schematic diagram illustrating key structures of fig. 10.
Figure 12 is a cross-sectional schematic view of the present invention when the main outer drive teeth are in end-face coincidence with the main inner drive teeth.
Fig. 13 is a simplified schematic diagram illustrating key structures of fig. 12.
Figure 14 is a cross-sectional schematic view of the present invention when the secondary outer drive teeth are axially separated from the secondary inner drive teeth.
Fig. 15 is a simplified schematic diagram illustrating key structures of fig. 14.
Fig. 16 is a schematic sectional view showing the clutch in the engaged state according to the present invention.
Fig. 17 is a simplified schematic diagram illustrating key structures in fig. 16.
FIG. 18 is a schematic cross-sectional view of the clutch in the disengaged state after absorbing the thermal expansion of the shafting of the unit.
FIG. 19 is a schematic cross-sectional view of the clutch in the engaged state after absorbing the thermal expansion of the shafting of the unit.
In the figure: 100. the waste heat boiler comprises a waste heat boiler, 200 gas turbines, 500 steam turbines, 300 generators, 600 auxiliary steam, 400 synchronous automatic clutches, 410 input assemblies, 411 main spiral spline pairs, 420 main sliding assemblies, 423 main external driving teeth, 430 secondary sliding assemblies, 431 secondary spiral spline pairs, 432 secondary external driving teeth, 433 pawls, 440 output assemblies, 441 main internal driving teeth, 442 secondary internal driving teeth, 443 ratchet wheels, 450 main sliding assembly engagement positioning surfaces, 460 secondary sliding assembly engagement positioning surfaces, 470 main sliding assembly disengagement positioning surfaces, 480 secondary sliding assembly disengagement positioning surfaces and 490 sliding assemblies.
Detailed Description
The invention is further described below with reference to the accompanying drawings.
As shown in fig. 1, the gas turbine 200, the generator 300, and the steam turbine 500 are rigidly connected to form a gas-steam single-shaft combined cycle unit, and since the gas turbine 200, the generator 300, and the steam turbine 500 are rigidly connected to drag the steam turbine 500 to idle when the gas turbine 200 is started, the gas turbine 200 is difficult to start, and the auxiliary steam 600 is required to drive the steam turbine 500 to start together with the gas turbine 200; when the steam system or the steam turbine 500 has a fault, the gas turbine 200 still drags the steam turbine 500 to idle, on one hand, the steam turbine 500 cannot be stopped for maintenance, on the other hand, the blades of the steam turbine 500 are blown to generate heat, and auxiliary steam 600 is also required to be arranged and introduced into the cylinder for cooling.
In order to improve the starting flexibility of the combustion-evaporation single-shaft combined cycle unit and reduce auxiliary devices, the combustion-evaporation single-shaft combined cycle unit can be arranged as shown in fig. 2, and the generator 300 is connected with the steam turbine 500 through the synchronous automatic clutch 400. In the process that the gas turbine 200 is started to the full rotating speed, the synchronous automatic clutch 400 is in a disengaged state, the steam turbine 500 does not participate in the starting process, when the exhaust parameters of the gas turbine 200 and the steam parameters of the waste heat boiler 100 meet the requirements, the steam turbine 500 can be independently started, the steam turbine 500 is increased to the full rotating speed to be synchronous with the rotating speed of the generator 300, the synchronous automatic clutch 400 is connected, and the gas turbine 200 and the steam turbine 500 drive the generator 300 together. When a steam system or turbine 500 fails, turbine 500 may be shut down alone, synchronous automatic clutch 400 is disengaged, and gas turbine 200 continues to operate in the simple cycle mode.
Fig. 3 shows a common structure of a low-power synchronous automatic clutch, which is mainly divided into an input assembly 410, a slip assembly 490 and an output assembly 440. When the rotation speed of the input assembly 410 and the sliding assembly 490 exceeds the rotation speed of the output assembly 440, the pawl 433 engages with the ratchet 443, and the sliding assembly 490 starts to slide axially under the action of the primary helical spline pair 411 and the ratchet 443, the pawl 433 and the ratchet 443 at the moment of engagement will generate a certain impact force therebetween, and the magnitude of the impact force is related to the difference in rotation speed of the output assembly 440 of the input assembly 410 at the moment of engagement and the magnitude of the mass moment of inertia of the sliding assembly 490. When the power required to be transmitted by the synchronous automatic clutch is large, the radial dimensions and weights of the input assembly 410, the sliding assembly 490 and the output assembly 440, which are mainly used for transmitting torque, are inevitably increased, and at the moment of engagement of the synchronous automatic clutch, the impact force of the ratchet 443 and the pawl 433 is greatly increased, so that the reliability of the ratchet 443 and the pawl 433 cannot be ensured by continuously using the basic structure shown in fig. 3.
In order to realize a more flexible operation mode of the combustion-steam combined cycle generator set, the invention provides the high-power synchronous automatic clutch 400 of the combustion-steam combined cycle generator set, the high-power synchronous automatic clutch is arranged between a steam turbine and a generator, and the independent starting and stopping of the steam turbine can be realized when the gas turbine operates by means of the automatic engaging and disengaging functions of the high-power synchronous automatic clutch according to the rotating speeds of an input end and an output end, so that the operation flexibility of the combustion-steam single-shaft combined cycle generator set is improved.
The invention adds a set of secondary slip components on the basis of the input component, the slip component and the output component of the traditional low-power synchronous automatic clutch to form four parts of the input component, the main slip component, the secondary slip component and the output component, so that the jointing process of the high-power synchronous automatic clutch is carried out in two steps, the main slip component in the second step slips to be driven by the sleeve gear, the size and the weight of the main slip component are not limited, and the clutch can increase the structural size of a torque transmission component as required. The length of a torque transmission structure and a synchronizing mechanism in the clutch is lengthened to adapt to the thermal expansion of a shaft system of the combustion-steam combined cycle generator set.
Example 1:
the invention provides a technical scheme of a high-power synchronous automatic clutch, and as shown in fig. 4, a slip assembly 490 in the synchronous automatic clutch is divided into two parts, namely a main slip assembly 420 and a secondary slip assembly 430. The main sliding component 420 and the input component 410 are sleeved through a main spiral spline pair 411, and the secondary sliding component 430 and the main sliding component 420 are sleeved through a secondary spiral spline pair 431. The secondary slide assembly 430 is formed with a pawl 433 and secondary outer drive teeth 432. The output member 440 is formed with a ratchet 443, a sub inner drive tooth 442, and a main inner drive tooth 441. Primary outer drive teeth 423 are located on primary glide assembly 420. Fig. 5 is a simplified wire-frame diagram of the key structure.
When the high-power synchronous automatic clutch is in a disengaged state, the output assembly 440 is at a certain rotation speed point, and the rotation speeds of the secondary slip assembly 430, the primary slip assembly 420 and the input assembly 410 are the same and are at a certain rotation speed point lower than the rotation speed of the output assembly 440. When the rotation speed of the input assembly 410 tends to exceed that of the output assembly 440, the ratchet wheel 443 and the pawl 433 ratchet, under the action of the secondary helical spline pair 431, only the secondary sliding assembly 430 with small mass needs to be pushed to move axially, as shown in fig. 6. When the secondary outer drive teeth 432 are in end-face coincidence with the secondary inner drive teeth 442, the backlash on both sides of the secondary outer drive teeth 432 is ensured to be uniform, as shown in fig. 7.
The secondary sliding assembly 430 continues to axially move under the action of the ratchet wheel 443, the pawl 433 and the secondary helical spline pair 431 until the ratchet wheel 443, the pawl 433 and the pawl 433 axially separate, as shown in fig. 8, and at the moment the ratchet wheel 443, the pawl 433 and the secondary outer driving tooth 432 and the secondary inner driving tooth 442 are axially separated, as shown in fig. 9, the secondary outer driving tooth 432 and the secondary inner driving tooth 442 are engaged.
The secondary glide assembly 430 continues to move axially under the action of the secondary outer drive teeth 432, the secondary inner drive teeth 442 and the secondary helical spline pair 431 until the secondary glide assembly engagement locating surfaces 460 engage, as shown in fig. 10 and 11. At this time, under the action of the secondary external drive teeth 432, the secondary internal drive teeth 442 and the primary helical spline pair 411, the secondary sliding assembly 430 and the primary sliding assembly 420 axially move together until the primary external drive teeth 423 and the primary internal drive teeth 441 are overlapped in end face, as shown in fig. 12; the flank clearance on both sides of the main outer drive teeth 423 is guaranteed to be uniform as shown in fig. 13.
The secondary sliding assembly 430 and the primary sliding assembly 420 continue to axially move under the action of the secondary outer driving teeth 432, the secondary inner driving teeth 442 and the primary helical spline pair 411 until the secondary outer driving teeth 432 and the secondary inner driving teeth 442 are axially separated, as shown in fig. 14; the main outer drive teeth 423 are in tooth surface abutment with the main inner drive teeth 441 side as shown in figure 15. At this time, the main slipping assembly 420 continues to axially move under the action of the main outer driving teeth 423, the main inner driving teeth 441 and the main helical spline pair 411 until the main slipping assembly engagement positioning surfaces 450 are attached, and as shown in fig. 16 and 17, the high-power synchronous automatic clutch 400 completes the engagement action.
When the input assembly 410 rotates at a speed lower than the output assembly 440, the automatic disengagement process of the high power synchronous automatic clutch 400 is reversed from the engagement motion process.
Example 2:
further, when the secondary sliding assembly 430 axially moves to the position where the end faces of the secondary outer drive teeth 432 and the secondary inner drive teeth 442 are overlapped under the action of the secondary helical spline pair 431, the tooth side gaps on the two sides of the secondary outer drive teeth 432 and the secondary inner drive teeth 442 are consistent to be a; when the secondary glide assembly 430 continues to move axially so that the secondary outer drive teeth 432 flank the secondary inner drive teeth 442, the flank clearance between the secondary outer drive teeth 432 and the secondary inner drive teeth 442 is 2 a.
Example 3:
further, when the main sliding assembly 420 and the sub sliding assembly 430 axially move together to the position where the end faces of the main outer driving teeth 423 and the main inner driving teeth 441 are overlapped, the tooth side gaps on the two sides of the main outer driving teeth 423 and the main inner driving teeth 441 are consistent to be a; when main sliding assembly 420 and sub sliding assembly 430 continue to move axially together until main outer drive tooth 423 is engaged with one side of main inner drive tooth 441, the tooth side clearance between main outer drive tooth 423 and the other side of main inner drive tooth 441 is 2 a.
Example 4:
further, the axial width of the ratchet 443 design is greater than the rotor thermal expansion. As shown in fig. 19, when the axial expansion of the shafting rotors occurs, the thermal expansion of the rotors at both ends of the high-power synchronous automatic clutch 400 needs to be absorbed by the clutch. When the high-power synchronous automatic clutch 400 is in a disengaged state, the ratchet 443 is designed to have an axial width larger than the rotor thermal expansion, and the engagement function of the ratchet 443 and the pawl 433 is not affected after the clutch absorbs the rotor thermal expansion.
Example 5:
further, as shown in fig. 19, when the high power synchronous automatic clutch 400 is in the engaged state, because the axial width of the main inner driving teeth 441 is designed to be larger, after the clutch absorbs the rotor thermal expansion, the main inner driving teeth 441 and the main outer driving teeth 423 still have a certain meshing width, and the torque transmission capability is not affected.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (5)
1. A high-power synchronous automatic clutch of a combustion-steam combined cycle generator set comprises an input assembly (410), a sliding assembly (490) and an output assembly (440); the output component (440) is provided with a ratchet wheel (443) and a main inner driving tooth (441); the sliding component (490) is provided with a main external driving tooth (423) and a pawl (433); the method is characterized in that:
the sliding component (490) comprises a primary sliding component (420) and a secondary sliding component (430); the main sliding component (420) is sleeved with the input component (410) through a main spiral spline pair (411); the secondary sliding component (430) is sleeved with the main sliding component (420) through a secondary spiral spline pair (431); the bottom of the main sliding component (420) is provided with a secondary sliding component joint positioning groove (460), and the secondary sliding component joint positioning groove (460) is positioned behind the tail end of the secondary spiral spline pair (431); the pawl (433) is positioned at the front end of the secondary sliding component (430), and the tail end of the secondary sliding component (430) is provided with a secondary external driving tooth (432); the main outer driving teeth (423) are positioned on the main sliding component (420); the lower part of the output assembly (440) is provided with an axial lengthening part, the axial lengthening part extends to the front of the joint positioning groove (460) of the secondary sliding assembly, and the tail end of the axial lengthening part is provided with a secondary inner driving tooth (442);
when the clutch is in a disengaged state, the output assembly (440) is at a certain rotating speed point, and the rotating speeds of the secondary slip assembly (430), the primary slip assembly (420) and the input assembly (410) are the same and at a certain rotating speed point lower than the rotating speed of the output assembly (440);
when the rotating speed of the input assembly (410) tends to exceed that of the output assembly (440), a ratchet wheel (443) on the output assembly (440) is meshed with a pawl (433) on the secondary sliding assembly (430), and the secondary sliding assembly (430) axially moves under the action of the secondary helical spline pair (431); when the secondary sliding component (430) axially moves to the position where the end surfaces of the secondary outer driving tooth (432) and the secondary inner driving tooth (442) are overlapped, the ratchet wheel (443) and the pawl (433) are still engaged; when the secondary sliding component (430) axially moves to the position where the ratchet wheel (443) is axially separated from the pawl (433), the secondary outer driving tooth (432) is attached to one side tooth surface of the secondary inner driving tooth (442); when the secondary sliding component (430) axially moves to the end of the secondary sliding component joint positioning groove (460), the secondary sliding component (430) and the main sliding component (420) axially move together under the action of the main spiral spline pair (411); when the main sliding component (420) and the secondary sliding component (430) axially move together to the position where the end faces of the main outer driving tooth (423) and the main inner driving tooth (441) are overlapped, the secondary outer driving tooth (432) is still attached to the tooth surface on one side of the secondary inner driving tooth (442); when the main sliding component (420) and the secondary sliding component (430) axially move together to the position where the secondary outer driving tooth (432) is axially separated from the secondary inner driving tooth (442), the main outer driving tooth (423) is attached to the tooth surface on one side of the main inner driving tooth (441); when the main sliding component (420) and the secondary sliding component (430) axially move together to be in contact with the input component (410), the main sliding component (420) and the secondary sliding component (430) stop moving, at the moment, the main outer driving tooth (423) is still attached to the tooth surface on one side of the main inner driving tooth (441), and the clutch finishes engaging action;
when the rotation speed of the input assembly (410) is lower than that of the output assembly (440), the clutch starts to perform a disengagement action, and the movement process of the disengagement action is opposite to that of the engagement action.
2. The high-power synchronous automatic clutch of the combustion-steam combined cycle generator set according to claim 1, characterized in that: when the secondary sliding assembly (430) axially moves to a position where the end faces of the secondary outer driving teeth (432) and the secondary inner driving teeth (442) are overlapped under the action of the secondary spiral spline pair (431), the tooth side gaps on the two sides of the secondary outer driving teeth (432) and the secondary inner driving teeth (442) are consistent to a; when the secondary sliding component (430) continues to axially move to enable the secondary outer driving tooth (432) to be in tooth surface engagement with one side of the secondary inner driving tooth (442), the tooth side clearance between the secondary outer driving tooth (432) and the other side of the secondary inner driving tooth (442) is 2 a.
3. The high-power synchronous automatic clutch of the combustion-steam combined cycle generator set according to claim 1, characterized in that: when the main sliding component (420) and the sub sliding component (430) axially move together to the position where the end faces of the main outer driving tooth (423) and the main inner driving tooth (441) are overlapped, the tooth side gaps on the two sides of the main outer driving tooth (423) and the main inner driving tooth (441) are consistent to be a; when the main sliding component (420) and the secondary sliding component (430) continue to axially move together until the main outer driving tooth (423) is in tooth surface fit with one side of the main inner driving tooth (441), the tooth side clearance between the main outer driving tooth (423) and the other side of the main inner driving tooth (441) is 2 a.
4. The high-power synchronous automatic clutch of the combustion-steam combined cycle generator set according to claim 1, characterized in that: the axial width of the ratchet (443) design is greater than the rotor thermal expansion; when the shafting rotor generates axial expansion, the thermal expansion of the rotors at two ends of the clutch is absorbed by the clutch, and when the clutch is in a disengaged state, the ratchet (443) is designed to have an axial width larger than the thermal expansion of the rotors, so that the ratchet engagement functions of the ratchet (443) and the pawl (433) are not affected after the clutch absorbs the thermal expansion of the rotors.
5. The high-power synchronous automatic clutch of the combustion-steam combined cycle generator set according to claim 1, characterized in that: when the clutch is in an engaged state, after the clutch absorbs the heat expansion of the rotor, the main inner driving teeth (441) and the main outer driving teeth (423) still have a certain meshing width, and the torque transmission capacity of the clutch is not influenced.
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| CN202111500596.8A CN114198428A (en) | 2021-12-09 | 2021-12-09 | High-power synchronous automatic clutch of combustion-evaporation combined cycle generator set |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114992256A (en) * | 2022-05-22 | 2022-09-02 | 中国船舶重工集团公司第七0三研究所 | Synchronous automatic clutch engagement locking tooth structure |
| CN116907403A (en) * | 2023-09-13 | 2023-10-20 | 哈尔滨船舶锅炉涡轮机研究所(中国船舶集团有限公司第七0三研究所) | Continuous displacement measuring device for large-stroke sliding assembly of synchronous automatic clutch |
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| CN201651116U (en) * | 2010-05-26 | 2010-11-24 | 中国船舶重工集团公司第七○三研究所 | Automatic synchronizing clutch of steam turbine turning gear |
| CN201696526U (en) * | 2010-06-30 | 2011-01-05 | 沈阳申克动力机械有限公司 | Synchronous overrunning clutch |
| CN102454727A (en) * | 2010-10-26 | 2012-05-16 | 茅菁 | Synchronizing clutch of gas and steam combined cycle unit |
| CN104295630A (en) * | 2014-10-29 | 2015-01-21 | 中国船舶重工集团公司第七�三研究所 | Mechanism for synchronizing radial disengaging of ratchet wheel and pawl in automatic clutch |
| CN104315040A (en) * | 2014-10-29 | 2015-01-28 | 中国船舶重工集团公司第七�三研究所 | Synchronous automatic clutch with high-speed pawl mechanism and low-speed pawl mechanism |
| CN104329389A (en) * | 2014-10-29 | 2015-02-04 | 中国船舶重工集团公司第七�三研究所 | Large-torque synchronous automatic clutch with relay type structure |
| CN106704399A (en) * | 2015-11-12 | 2017-05-24 | 通用汽车环球科技运作有限责任公司 | Pawl grounding clutch with synchronizer |
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| GB422002A (en) * | 1933-09-26 | 1935-01-03 | William Thomas Carling | Improvements in or relating to positive bi-directional clutches |
| GB1281519A (en) * | 1968-08-02 | 1972-07-12 | Fluidrive Eng Co Ltd | Synchronous self-shifting clutch |
| GB1296374A (en) * | 1969-03-03 | 1972-11-15 | ||
| US3715019A (en) * | 1970-03-11 | 1973-02-06 | Sss Patents Ltd | Synchronous self-shifting clutches |
| GB1384532A (en) * | 1971-01-27 | 1975-02-19 | Fluidrive Eng Co Ltd | Synchronous self-shifting clutches |
| GB1469409A (en) * | 1974-11-18 | 1977-04-06 | Sss Patents Ltd | Synchronous self-shifting toothed clutch |
| CN201651116U (en) * | 2010-05-26 | 2010-11-24 | 中国船舶重工集团公司第七○三研究所 | Automatic synchronizing clutch of steam turbine turning gear |
| CN201696526U (en) * | 2010-06-30 | 2011-01-05 | 沈阳申克动力机械有限公司 | Synchronous overrunning clutch |
| CN102454727A (en) * | 2010-10-26 | 2012-05-16 | 茅菁 | Synchronizing clutch of gas and steam combined cycle unit |
| CN104295630A (en) * | 2014-10-29 | 2015-01-21 | 中国船舶重工集团公司第七�三研究所 | Mechanism for synchronizing radial disengaging of ratchet wheel and pawl in automatic clutch |
| CN104315040A (en) * | 2014-10-29 | 2015-01-28 | 中国船舶重工集团公司第七�三研究所 | Synchronous automatic clutch with high-speed pawl mechanism and low-speed pawl mechanism |
| CN104329389A (en) * | 2014-10-29 | 2015-02-04 | 中国船舶重工集团公司第七�三研究所 | Large-torque synchronous automatic clutch with relay type structure |
| CN106704399A (en) * | 2015-11-12 | 2017-05-24 | 通用汽车环球科技运作有限责任公司 | Pawl grounding clutch with synchronizer |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114992256A (en) * | 2022-05-22 | 2022-09-02 | 中国船舶重工集团公司第七0三研究所 | Synchronous automatic clutch engagement locking tooth structure |
| CN114992256B (en) * | 2022-05-22 | 2024-04-05 | 中国船舶重工集团公司第七0三研究所 | Synchronous automatic clutch joint locking tooth structure |
| CN116907403A (en) * | 2023-09-13 | 2023-10-20 | 哈尔滨船舶锅炉涡轮机研究所(中国船舶集团有限公司第七0三研究所) | Continuous displacement measuring device for large-stroke sliding assembly of synchronous automatic clutch |
| CN116907403B (en) * | 2023-09-13 | 2024-03-01 | 哈尔滨船舶锅炉涡轮机研究所(中国船舶集团有限公司第七0三研究所) | Continuous displacement measuring device for large-stroke sliding assembly of synchronous automatic clutch |
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