Clutch mechanism of low-speed hydraulic power-assisted jigger used in power generation gas turbine accidents

Abstract

The invention discloses a clutch mechanism of a low-speed hydraulic power-assisted jigger used in power generation gas turbine accidents, and relates to the technical field of steam turbine operation and maintenance. The clutch mechanism of the low-speed hydraulic power-assisted jigger used in the power generation gas turbine accident comprises a gas turbine center shaft, and further comprises two sets of semicircular hoops, semicircular gear rings arranged on the outer rings of the semicircular hoops in a sliding mode, a driving gear arranged on one side of the rotating track of the driving gear ring after the two sets of semicircular hoops are hooped, and a clutch arranged on the other side of the rotating track of the driving gear. And the clutch driving assembly is arranged on one side of the driving gear. New clutch drive can be formed on the central shaft of the gas turbine, an original shaft system structure does not need to be transformed, even if an original barring clutch fails, stable meshing and separation with the central shaft of the gas turbine can still be achieved, continuous low-speed barring is guaranteed, thermal deformation and locking of a rotor are effectively prevented, a pure mechanical forward and reverse rotation clutch mechanism is combined, manual operation intervention is avoided, and the working efficiency is improved. And damage to equipment and personnel caused by misoperation of the clutch is completely eradicated.

Description

Technical Field

[0001] This invention relates to the field of gas turbine operation and maintenance technology, specifically a clutch mechanism for a low-speed hydraulically assisted turning gear in the event of a gas turbine accident. Background Technology

[0002] With the widespread application of gas turbines in power generation, industry, and other fields, their operational reliability is of paramount importance. During the sequential start-up and shutdown of gas turbines and in emergency turning gear operation, the reliability of the turning gear system plays a crucial role. After a gas turbine shutdown due to an accident, timely, safe, and effective turning gear operation is essential to prevent problems such as thermal deformation and bending of the rotor due to prolonged static placement.

[0003] For example, Chinese patent CN107227979B discloses a combined cycle steam turbine rapid start-up warm-up system and method. In use, this type of system increases the speed of the steam turbine by turning gear, so that the speed of the steam turbine exceeds that of the gas turbine. The main helical sliding component of the clutch can be pried by a manual lever to align the phase of the driving teeth and driven teeth, so as to achieve clutch engagement. Warming steam is introduced into the steam turbine, and the steam turbine drives the gas turbine to rotate, thus starting the warm-up. The warm-up ends when the temperature of the intermediate pressure rotor of the steam turbine reaches the preset temperature or the warm-up time reaches the preset time.

[0004] However, most of the existing gas turbine turning gear systems use hydraulic motor gear transmission, and their clutch mechanisms are prone to problems such as engagement failure and response lag. This results in the turning gear not being able to operate normally after an accident shutdown. Furthermore, traditional manual turning gears rely on manual operation, which is not only inefficient, but also prone to safety accidents due to mechanical interference during clutch switching, such as collisions between the manual crank handle and the suddenly started electric turning gear. Summary of the Invention

[0005] To address the shortcomings of existing technologies, this invention provides a clutch mechanism for a low-speed hydraulically assisted turning gear in the event of a gas turbine accident, thus solving the problems mentioned in the background art.

[0006] To achieve the above objectives, the present invention provides the following technical solution: a clutch mechanism for a low-speed hydraulically assisted turning gear in a gas turbine accident, comprising a gas turbine central shaft, and further comprising: two sets of semi-circular clamps, which are capable of being clamped onto the gas turbine central shaft by high-strength bolts; two sets of semi-circular gear rings, which are slidably disposed on the outer ring of the semi-circular clamps, and together with the two sets of semi-circular clamps, form a drive gear ring, which drives the gas turbine central shaft to rotate in the same direction, and is also capable of rotating in the opposite direction of the gas turbine central shaft under no-load conditions; a drive gear, disposed on one side of the rotation trajectory of the drive gear ring, and capable of intermittently meshing with the drive gear ring; and a clutch drive assembly, disposed on one side of the drive gear, for selectively engaging the drive gear with the drive gear ring, so that when the drive gear engages with the drive gear ring, a driving force is generated to drive the gas turbine central shaft to rotate, and when the drive gear disengages from the drive gear ring, the drive force acting on the gas turbine central shaft is stopped.

[0007] Furthermore, the clutch drive assembly includes: a drive shaft, located on the central shaft of the drive gear, and having a splined section in its axial direction, wherein a splined bushing is slidably mounted on the splined section in the axial direction, and the splined bushing is fixedly connected to the drive gear; a cam, located at one end of the splined bushing, and having a rotating arm on one side therein, wherein a slider is provided on one side of the rotation path of the rotating arm, and the slider can rotate into contact with the convex surface of the cam to generate a driving force that pushes the drive gear to move and mesh with the drive gear ring.

[0008] Furthermore, the clutch drive assembly further includes: a stop block, located at the convex top of the cam, which generates a driving force to rotate the drive gear when the slider rotates to engage with the stop block; a second track groove, formed on one side of the stop block and extending along the convex surface of the cam to its convex bottom; and a second slide rail, located at one end of the slider and capable of sliding along the second track groove, which causes the drive gear to separate from the drive gear ring when the slider rotates in the opposite direction to the convex bottom of the cam.

[0009] Furthermore, it also includes a first compensating gear rotatably mounted on one side of the drive gear and a second compensating gear rotatably mounted on the other side of the drive gear. In addition, a backlash compensation structure is provided along the axial direction of the splined bushing to drive the first compensating gear and the second compensating gear to deflect relative to each other, so that when the drive gear moves to engage with the drive gear ring, the first compensating gear and the second compensating gear deflect relative to each other to compensate for the backlash between the drive gear and the drive gear ring.

[0010] Furthermore, the backlash compensation structure includes: a yaw cavity, which is formed on the drive gear and has two sets; and a yaw slide, which has two sets and is slidably disposed in the two sets of yaw cavities respectively. One set of yaw slides is fixedly connected to the first compensation gear, and the other set of yaw slides is fixedly connected to the second compensation gear. A first abutment is provided on one set of yaw slides, and a second abutment is provided on the other set of yaw slides, forming a situation where the center of the distance between the first abutment and the second abutment is subjected to force, pushing the first compensation gear and the second compensation gear to deflect in opposite directions.

[0011] Furthermore, the backlash compensation structure further includes: a support arm, which is fixed to the axial direction of the spline bushing and has a slot formed on it; a telescopic platform, which is slidably disposed within the support arm, wherein: a cavity is formed above the telescopic platform, a second pivot pin is provided inside the cavity, a boss is rotatably mounted above the second pivot pin, and the boss extends to the center of the distance between the first and second abutments, so that when the boss moves upward, it applies a thrust in a self-oscillating state to the first and second abutments; a wedge block is formed below the telescopic platform and is aligned with the slot; and an impact block, which is disposed in the axial direction of the drive shaft and is aligned with the slot, so that when the drive gear moves toward the drive gear ring, it contacts the wedge block and generates a driving force that pushes the boss upward.

[0012] Furthermore, it also includes: a first track groove, which is formed on the outer ring of the semicircular clamp, and after the two sets of semicircular clamps are engaged, it forms an annular track that provides a drive gear ring for rotational sliding, wherein the annular track has at least one set of ratchet grooves along its circumference; and a first slide rail, which is set on the inner ring of the semicircular gear ring, and after the two sets of semicircular gear rings form a drive gear ring, it forms an annular guide rail, which allows it to rotate and slide along the annular track, and is offset from the mating ends of the two sets of semicircular clamps, providing a limiting pre-tightening after the semicircular clamps are engaged, wherein the annular guide rail has at least one set of ratchet structures along its circumference.

[0013] Furthermore, the ratchet structure includes: an inner shell disposed within the inner ring of the annular guide rail; and a swing arm disposed inside the inner shell and rotatably mounted to the inner shell via a first pivot pin. One side of the swing arm is provided with a compression spring to provide its swing-back reset, and the other side of the swing arm is provided with ratchet teeth, enabling the ratchet teeth to be limited to abutting against the ratchet groove or to engage in relative sliding engagement with the ratchet groove.

[0014] Furthermore, one side of the ratchet teeth has an arc surface structure, which allows the ratchet teeth to slide and engage along the ratchet groove, and the arc surface is set opposite to the rotation direction of the gas turbine central shaft, converting the rotational thrust of the drive gear ring into sliding thrust, which rotates relative to the gas turbine central shaft.

[0015] Furthermore, the other side of the ratchet tooth has a straight surface structure, which allows the ratchet tooth to be positioned and abutted along the ratchet groove, transmitting the rotational thrust of the drive gear ring to the gas turbine central shaft.

[0016] The present invention has the following beneficial effects:

[0017] (1) The clutch mechanism of the low-speed hydraulically assisted turning gear used in the accident of the gas turbine for power generation is held in the central shaft of the gas turbine by two sets of semi-circular clamps, and a drive gear ring is provided on the clamps. The clutch drive component acts on the intermittent meshing drive of the drive gear and the drive gear ring to form a new clutch drive on the central shaft of the gas turbine. There is no need to modify the original shaft system structure. Even if the original turning gear clutch fails, it can still achieve stable meshing and separation with the central shaft of the gas turbine, ensuring the continuous operation of the low-speed turning gear, effectively preventing rotor thermal deformation and seizure, and also has a pure mechanical forward and reverse clutch mechanism to avoid human operation intervention and eliminate equipment and personnel injury caused by clutch misoperation.

[0018] (2) The clutch mechanism of the low-speed hydraulic power steering wheel used in the accident of the gas turbine generator has a purely mechanical clutch drive state through the forward and reverse rotation of the clutch drive component. It does not require additional power drive, which reduces the risk of human operation and has more reliable engagement and disengagement characteristics, ensuring the continuity of the low-speed steering wheel.

[0019] (3) The clutch mechanism of the low-speed hydraulic power steering wheel used in the gas turbine accident can also act on the two sets of compensation gears through the tooth backlash compensation structure when the clutch drive assembly pushes the drive gear to move and mesh with the drive gear ring. This causes the two sets of compensation gears to wobble in opposite directions, compensate for the meshing clearance between the drive gear and the drive gear ring, prevent tooth surface loosening, and ensure that the large torque acting on the gas turbine central shaft is transmitted without slippage. In addition, during the process of the clutch drive assembly pushing the drive gear and the drive gear ring to disengage, the meshing resistance when the drive gear and the drive gear ring disengage can be converted into the meshing state under the "slippage" no-load rotation, and is not transmitted to the gas turbine central shaft, thus avoiding impact damage.

[0020] (4) The clutch mechanism of the low-speed hydraulic power steering wheel used in the gas turbine accident, after the two sets of semi-circular clamps are engaged on the central shaft, the outer ring of the ring track can provide the space required for the drive gear ring to rotate and slide. On the one hand, it can make the engagement ends of the drive gear ring and the two sets of semi-circular clamps staggered, providing the limit pre-tightening after the semi-circular clamps are engaged, and strengthening the installation tightness. On the other hand, with the matching of ratchet structure and ratchet groove, it can make the drive gear ring rotate with the gas turbine central shaft, driving the gas turbine central shaft to rotate continuously at low speed. At the same time, it can also make the drive gear ring rotate relative to the gas turbine central shaft, so that the meshing resistance during the engagement does not act on the gas turbine central shaft, making the engagement and disengagement more reliable.

[0021] (5) The clutch mechanism of the low-speed hydraulic power steering wheel used in the accident of the gas turbine has good modular disassembly and assembly characteristics. The integrated assembly with the gas turbine central shaft is simple and convenient, and can be quickly disassembled and assembled. The installation and maintenance process is faster and more efficient, and the modification cost is lower.

[0022] Of course, any product implementing this invention does not necessarily need to achieve all of the advantages described above at the same time. Attached Figure Description

[0023] Figure 1 This is a schematic diagram of the structure of the present invention;

[0024] Figure 2 This is a first sectional view of the present invention;

[0025] Figure 3 This is a second sectional view of the present invention;

[0026] Figure 4 This is a schematic diagram of the assembly of the semi-circular clamp and the semi-circular gear ring in this invention;

[0027] Figure 5 This is a schematic diagram of the assembly of the semi-circular clamp in this invention;

[0028] Figure 6 This is a schematic diagram of the assembly of the semi-circular gear ring in this invention;

[0029] Figure 7 This is a schematic diagram of the ratchet structure in this invention;

[0030] Figure 8 This is a schematic diagram of the first structure of the sliding assembly of the semicircular toothed ring relative to the semicircular clamp in this invention;

[0031] Figure 9 This is a schematic diagram of the second structure of the sliding assembly of the semicircular toothed ring relative to the semicircular clamp in this invention;

[0032] Figure 10 This is a schematic diagram of the first structure of the clutch drive assembly in this invention;

[0033] Figure 11 This is a schematic diagram of the second structure of the clutch drive assembly in this invention;

[0034] Figure 12 This is a schematic diagram of the assembly of the cam and the slider in this invention;

[0035] Figure 13 This is a schematic diagram of the first drive shaft in this invention;

[0036] Figure 14 This is a schematic diagram of the second drive shaft in this invention;

[0037] Figure 15This is a schematic diagram of the first drive mechanism of the backlash compensation structure in this invention;

[0038] Figure 16 This is a schematic diagram of the second drive mechanism of the backlash compensation structure in this invention;

[0039] Figure 17 This is a schematic diagram of the third drive mechanism of the backlash compensation structure in this invention;

[0040] Figure 18 This is a schematic diagram of the first assembly of the two sets of compensating gears in this invention;

[0041] Figure 19 This is a second assembly diagram of the two sets of compensating gears in this invention;

[0042] Figure 20 This is a schematic diagram of the force driving of the two sets of compensating gears in this invention.

[0043] In the diagram, 1. Engine housing; 2. Semicircular clamp; 201. Positioning pin; 3. Gas turbine central shaft; 301. Pre-drilled hole; 4. Hydraulic drive motor; 5. Semicircular gear ring; 6. Drive shaft; 7. Drive gear; 71. First compensating gear; 72. Second compensating gear; 8. Cam; 9. First track groove; 10. Rattle groove; 11. First slide rail; 12. Rattle structure; 121. Inner shell; 122. Compression spring; 123. First pivot pin; 124. Swing arm; 12 5. Ratchet; 13. Spline section; 14. Spline bushing; 15. First abutment; 16. Second abutment; 17. Boss; 18. Impact block; 19. Rotating arm; 20. Slider; 21. Second slide rail; 22. Second track groove; 23. Stop block; 24. Support arm; 25. Slot; 26. Telescopic table; 27. Second pivot pin; 28. Wedge block; 29. ​​Swing cavity; 30. Swing slide; 31. Relief cavity; 32. Swing guide rod; 33. Return spring. Detailed Implementation

[0044] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0045] In the description of this invention, it should be understood that the terms "opening", "upper", "lower", "thickness", "top", "middle", "length", "inner", "around", etc., which indicate orientation or positional relationship, are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the components or elements referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as limiting this invention.

[0046] The following is based on Figures 1-20 This invention describes a clutch mechanism for a low-speed hydraulically assisted turning gear in a power generation gas turbine accident, provided by an embodiment of the present invention.

[0047] like Figures 1-3 As shown, a clutch mechanism for low-speed hydraulically assisted turning gear in a gas turbine accident includes a gas turbine central shaft 3 and two sets of semi-circular clamps 2. The two sets of semi-circular clamps 2 can be clamped onto the gas turbine central shaft 3 by high-strength bolts. A semi-circular gear ring 5 is provided on the outer ring of the semi-circular clamps 2, so that the two sets of semi-circular clamps 2 form a drive gear ring after clamping, which drives the gas turbine central shaft 3 to rotate. It can also rotate in the opposite direction to the gas turbine central shaft 3 under no-load conditions. The rotation of the drive gear ring can drive the gas turbine central shaft 3 to continuously turn gear at low speed, and its reverse rotation can also rotate relative to the gas turbine central shaft 3 under no-load conditions, so as to avoid impact damage caused by different rotational force directions.

[0048] Furthermore, a drive gear 7 is provided on one side of the rotation trajectory of the drive gear ring, and can engage with the drive gear ring intermittently. Simultaneously, a clutch drive assembly is provided on one side of the drive gear 7. This clutch drive assembly can selectively engage the drive gear 7 with the drive gear ring using a purely mechanical clutch drive method. When the drive gear 7 engages with the drive gear ring, it generates a driving force that rotates the gas turbine central shaft 3. When it disengages from the drive gear ring, the drive force acting on the gas turbine central shaft 3 stops. (In response to the aforementioned action of the drive gear ring driving the gas turbine central shaft 3, if the clutch drive assembly rotates forward, it pushes the drive gear 7 towards the drive gear ring for engagement, and after engagement, a gear pair drive is formed, continuously driving the gas turbine central shaft 3 at low speed.) The clutch drive assembly reverses after the original clutch system is running normally, separating the drive gear 7 from the drive gear ring and releasing the continuous drive state. Since there is a time difference between the engagement and disengagement of the drive gear 7 and the drive gear ring, the drive gear ring continues to rotate due to the rotation of the gas turbine central shaft 3. The engagement and disengagement of the drive gear ring and the drive gear 7 creates meshing resistance on the gas turbine central shaft 3. Therefore, by utilizing the characteristic that the drive gear ring can slide in the opposite direction of the rotation of the gas turbine central shaft 3, when the drive gear 7 and the drive gear ring are not fully engaged, the drive gear ring can convert the meshing resistance into rotational force in an unloaded state, thereby eliminating the resistance acting on the gas turbine central shaft 3 during the engagement and disengagement process and avoiding impact damage.

[0049] like Figures 10-14As shown, to achieve a purely mechanical clutch drive for the gas turbine central shaft 3, the clutch drive assembly includes a drive shaft 6 located on the central shaft of the drive gear 7, with a splined section 13 on its axial portion. A splined sleeve 14 is slidably mounted on the splined section 13, and the splined sleeve 14 is fixedly connected to the drive gear 7. Meanwhile, a cam 8 is provided at one end of the splined sleeve 14, and a rotating arm 19 is provided on one side of it. A slider 20 is provided on one side of the rotation path of the rotating arm 19. The slider 20 can rotate and contact the convex surface of the cam 8, generating a driving force to push the drive gear 7 to move and mesh with the drive gear ring. A hydraulic drive motor 4 is provided at the rotation center of the rotating arm 19 to drive the rotating arm 19 to rotate. During the rotation of the rotating arm 19, the slider 20 is driven to rotate along the convex surface of the cam 8, converting the rotational force into a linear thrust, pushing the cam 8 to move. Then, during the movement, the cam 8 pushes the splined sleeve 14 to slide along the splined section 13, moving the drive gear 7 to move and mesh with the drive gear ring.

[0050] As a further embodiment of this solution, the clutch drive assembly also includes a stop block 23 located at the convex top of the cam 8. When the slider 20 rotates to the convex top of the cam 8, it contacts and limits the movement of the stop block 23. At this time, the linear thrust acting on the cam 8 returns to the rotational force, pushing the cam 8 to rotate. Then, under the spline meshing of the spline sleeve 14 and the spline segment 13, a driving force is generated to push the drive shaft 6. The driving force is applied to the drive gear 7, so that after the drive gear 7 meshes with the drive gear ring, a gear pair drive state is formed, driving the gas turbine center shaft 3 to continuously rotate at low speed to compensate for the continuous operation of the gas turbine when the original rotating system fails.

[0051] Furthermore, the clutch drive assembly also includes a second track groove 22 opened on one side of the stop block 23, extending along the convex surface of the cam 8 to its convex bottom position, and a second slide rail 21 provided at one end of the slider 20, allowing the second slide rail 21 to slide along the second track groove 22. The combination of the second slide rail 21 and the second track groove 22 can preferably be set as a "T" shaped structure, which serves as a guide for the slider 20 when sliding along the convex surface of the cam 8, and as a connection and limiting function, so that the slider 20 and the cam 8 are always connected. After the original turning gear system is running normally, the hydraulic drive motor 4 is controlled to rotate in the opposite direction, causing the slider 20 to rotate in the opposite direction and separate from the stop block 23, and return to the bottom of the cam 8. At this time, its reverse rotation and reset action causes the cam 8 to reset and move, separating the drive gear 7 from the drive gear ring, disengaging the meshing drive state, and using the forward and reverse rotation of the hydraulic drive motor 4 to realize its pure mechanical clutch drive.

[0052] like Figures 15-20As shown, to improve the transmission efficiency when the drive gear 7 meshes with the drive gear ring, a first compensating gear 71 is rotatably mounted on one side of the drive gear 7 and a second compensating gear 72 is rotatably mounted on the other side of the drive gear 7. Furthermore, a backlash compensation structure is provided along the axial direction of the splined bushing 14 to drive the first compensating gear 71 and the second compensating gear 72 to deflect relative to each other. This ensures that when the drive gear 7 moves towards the drive gear ring to mesh, the first compensating gear 71 and the second compensating gear 72 deflect relative to each other, compensating for the backlash between the drive gear 7 and the drive gear ring. Specifically:

[0053] The backlash compensation structure includes two sets of yaw chambers 29 formed on the drive gear 7. Two sets of yaw slides 30 are slidably disposed within each of the two sets of yaw chambers 29. A combination of a yaw guide rod 32 and a return spring 33 is provided within each of the two sets of yaw chambers 29 to guide the sliding of the two sets of yaw slides 30 and facilitate subsequent reset. One set of yaw slides 30 is fixedly connected to the first compensation gear 71, and the other set of yaw slides 30 is fixedly connected to the second compensation gear 72. Furthermore, a first... One set of deflectors 15, and another set of deflecting slides 30 is provided with a second set of deflectors 16 (the first compensating gear 71 is provided with a relief cavity 31 to provide the deflection and sliding of the deflecting slides 30 close to the second set of deflectors 16), forming a center force between the first set of deflectors 15 and the second set of deflectors 16, pushing the first compensating gear 71 and the second compensating gear 72 to deflect in opposite directions. The opposing deflection of the first compensating gear 71 and the second compensating gear 72 is used to drive and compensate for the gap that may exist on both sides when the drive gear 7 meshes with the drive gear ring.

[0054] As a further embodiment, the backlash compensation structure also includes a support arm 24 fixed to the axial direction of the splined bushing 14, and a slot 25 is formed on the support arm 24. A telescopic platform 26 is slidably provided within the support arm 24, and a wedge-shaped block 28 is formed below the telescopic platform 26, aligning the wedge-shaped block 28 with the slot 25. An impact block 18, synchronously aligned with the slot 25, is provided axially on the drive shaft 6. When the clutch drive assembly pushes the drive gear 7 to move and engage with the drive gear ring, the splined bushing 14 moves synchronously, causing the support arm 24 to move towards the impact block 18, making relative contact between the wedge-shaped block 28 and the impact block 18. This converts the horizontal thrust into a lifting thrust, pushing the telescopic platform 26 to extend. Furthermore, a square... A concave cavity is formed, and a second pivot pin 27 is provided inside the cavity. A boss 17 is rotatably mounted on the top of the second pivot pin 27, and the boss 17 extends to the center of the distance between the first abutment 15 and the second abutment 16. During the extension of the telescopic platform 26, the boss 17 is pushed upward to apply a thrust to the first abutment 15 and the second abutment 16, generating a thrust that acts on the first compensating gear 71 and the second compensating gear 72 to deflect in opposite directions, so as to compensate for the meshing clearance difference between the drive gear 7 and the drive gear ring (when the drive gear 7 separates from the drive gear ring later, the wedge block 28 and the impact block 18 separate synchronously. At this time, the first abutment 15 and the second abutment 16 are reset by the elastic force of the reset spring 33, and a downward pressure is applied to the boss 17, so that the telescopic platform 26 retracts and resets).

[0055] It should be noted that since the meshing clearance between the drive gear 7 and the drive gear ring is fixed, but their meshing orientation is not fixed, during the upward abutment of the boss 17, the boss 17 is supported by the rotation of the second pivot pin 27 and can rotate in the cavity. While it is in contact with the first abutment 15 and the second abutment 16, it has a self-swaying ability under reverse force. After the compensation gear corresponding to one set of abutments contacts the drive gear ring, it can still sway towards the other set of abutments, continuously generating an upward thrust acting on the other set until the two sets of compensation gears mesh with the drive gear ring, eliminating the gap during the meshing process, preventing the tooth surface from loosening, and enabling it to have the self-compensation ability of tooth gap, so as to achieve its meshing drive more accurately.

[0056] Furthermore, the relative movement of the wedge block 28 and the impact block 18 can provide a movement limit for the spline bushing 14, so that after the combination of the drive gear 7, the first compensating gear 71, and the second compensating gear 72 meshes with the drive gear ring, the spline bushing 14 stops moving along the spline section 13, ensuring the accuracy of its tooth surface meshing.

[0057] like Figures 4-9As shown, to achieve the smoothness of the purely mechanical clutch mechanism, a first track groove 9 is provided on the outer ring of the semicircular clamp 2. After the two sets of semicircular clamps 2 are engaged, an annular track is formed to provide rotational sliding for the drive gear ring. The annular track has at least one set of ratchet grooves 10 along its circumference. At the same time, a first slide rail 11 is provided on the inner ring of the semicircular gear ring 5. After the two sets of semicircular gear rings 5 ​​form the drive gear ring, an annular guide rail is formed, allowing it to rotate and slide along the annular track. The annular guide rail has at least one set of ratchet structures 12 along its circumference. After the two sets of semicircular clamps 2 are engaged on the gas turbine central shaft 3, the annular track formed on its outer ring matches the annular guide rail formed on the inner ring of the drive gear ring. By preferably setting the cross-section of the annular track and the annular guide rail to a "T" shape, the drive gear ring can rotate and slide along the semicircular clamp. The clamp 2 is limited by rotational sliding and is offset from the mating ends of the two sets of semicircular clamps 2, providing a pre-tightening limit after the semicircular clamps 2 are engaged (while the two sets of semicircular clamps 2 are engaged, the corresponding semicircular toothed ring 5 is slid into the other set, such as rotating and sliding the semicircular toothed ring 5 into the other set by 90° to form a cross-interlocking method, realizing the pre-tightening when assembling the semicircular clamps 2 and the semicircular toothed ring 5, and also providing a limit for the continuous engagement of the two sets of semicircular clamps 2, improving the engagement firmness). Furthermore, by utilizing the unidirectional meshing and sliding of the ratchet structure 12 and the ratchet groove 10, the drive toothed ring can both drive the gas turbine central shaft 3 to continuously rotate at low speed and rotate relative to the gas turbine central shaft 3 under no-load conditions, so that it always maintains the driving force acting on the gas turbine central shaft 3 to rotate in the same direction, avoiding impact damage caused by relative rotation.

[0058] As a further embodiment, the ratchet structure 12 includes an inner shell 121 disposed on the inner ring of the annular guide rail, and a swing arm 124 disposed inside the inner shell 121. The swing arm 124 is rotatably mounted to the inner shell 121 via a first pivot pin 123. One side of the swing arm 124 is provided with a compression spring 122 to provide its swing reset, and the other side of the swing arm 124 is provided with a ratchet 125, so that the ratchet 125 can be limited to abutting against the ratchet groove 10 or to slide relative to the ratchet groove 10. By utilizing the elastic support of the compression spring 122 acting on the swing arm 124, the ratchet 125 can slide along the ratchet groove 10, providing the ability to drive the gear ring to rotate and slide relative to the gas turbine central shaft. At the same time, the one-way sliding engagement between the ratchet 125 and the ratchet groove 10 means that when subjected to reverse force, the ratchet 125 can abut and be limited to the ratchet groove 10, providing the ability to drive the gear ring to drive the gas turbine central shaft 3 to continuously rotate at low speed.

[0059] It should be noted that one side of the ratchet 125 has an arc surface structure, which enables the ratchet 125 to slide and mesh along the ratchet groove 10. The arc surface is set opposite to the rotation direction of the gas turbine central shaft 3, so that during the engagement or disengagement of the drive gear 7 and the drive gear ring, the meshing resistance during engagement or disengagement is converted into rotational sliding force, allowing the drive gear ring to rotate relative to the gas turbine central shaft 3 under no-load conditions, avoiding relative impact damage. At the same time, the other side of the ratchet 125 has a straight surface structure, which enables the ratchet 125 to limit and abut along the ratchet groove 10, so that when the drive gear ring rotates, it can transmit the rotational force to the gas turbine central shaft 3, driving the gas turbine central shaft 3 to continuously rotate at low speed.

[0060] In addition to the above, this design also features convenient and quick assembly and disassembly. During assembly, a positioning pin 201 is set in the circumferential direction of the inner ring of the semi-circular clamp 2, which matches the pre-drilled hole 201 on the original shaft system of the gas turbine central shaft 3. This enables modular assembly of the two sets of semi-circular clamps 2 with the gas turbine central shaft 3 when they are engaged (and provides a deep-hole contact node to stably transmit the subsequent clutch driving force to the gas turbine central shaft 3, avoiding relative slippage after installation). After the two sets of semi-circular clamps 2 are engaged, the semi-circular gear ring 5 is pushed. With the mating ends offset to provide pre-tightening limits, high-strength bolts are installed on the mating ends of the two sets of semi-circular clamps 2, thus achieving the integrated assembly of the semi-circular clamps 2 and the gas turbine central shaft 3. Then, the matching housing 1 is placed over the semi-circular clamps 2, and the drive gear 7 is aligned with the drive gear ring side. Subsequently, the corresponding power control is connected to complete the assembly process. Using the forward and reverse clutch drive of the clutch drive assembly, the gas turbine central shaft 3 is continuously driven at low speed in a purely mechanical clutch manner after the original turning gear system fails.

[0061] During use (operation), the two sets of semi-circular clamps 2 are engaged on the gas turbine central shaft 3 of the gas turbine, so that the two sets of semi-circular gear rings 5 ​​on its outer ring form a drive gear ring, which can apply continuous low-speed turning drive to the gas turbine central shaft 3. When the original turning system of the gas turbine fails, the drive gear 7 can be pushed to the drive gear ring for meshing in a purely mechanical way based on the drive of the clutch drive component, and a gear pair drive is formed after meshing, driving the gas turbine central shaft 3 to continuously turn at low speed.

[0062] During the meshing process between the drive gear 7 and the drive gear ring, its thrust can also act on the two sets of compensating gears, causing the two sets of compensating gears to deflect in opposite directions, compensating for the meshing clearance between the drive gear 7 and the drive gear ring, and forming an efficient meshing transmission state.

[0063] When the original turning gear system returns to normal, the clutch drive assembly can be controlled to rotate in the reverse direction to separate the drive gear 7 from the drive gear ring. Furthermore, during the forward and reverse clutch engagement and disengagement process of the clutch drive assembly, the engagement and disengagement state of the drive gear 7 and the drive gear ring can be affected by the unidirectional meshing and sliding of the ratchet structure 12 and the ratchet groove 10. This allows the drive gear ring to both drive the gas turbine central shaft 3 to continuously turn at low speed and to rotate relative to the gas turbine central shaft 3 under no-load conditions, eliminating meshing resistance during the clutch engagement process and preventing impact damage caused by relative rotation.

[0064] It should be noted that, in this document, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such process, method, article, or apparatus.

[0065] The preferred embodiments of the present invention disclosed above are merely illustrative of the invention. These preferred embodiments do not exhaustively describe all details, nor do they limit the invention to the specific implementations described. Clearly, many modifications and variations can be made based on the content of this specification. This specification selects and specifically describes these embodiments to better explain the principles and practical applications of the invention, thereby enabling those skilled in the art to better understand and utilize the invention. The invention is limited only by the claims and their full scope and equivalents.

Claims

1. A clutch mechanism for a low-speed hydraulically assisted turning gear in a gas turbine accident, comprising a gas turbine central shaft (3), characterized in that, Also includes: The semi-circular clamp (2) is provided in two sets and can be clamped to the central shaft (3) of the gas turbine by high-strength bolts; The semicircular gear ring (5) is provided in two sets, which are respectively slidably disposed on the outer ring of the semicircular clamp (2). After the two sets of semicircular clamps (2) are engaged, they form a drive gear ring, which drives the gas turbine central shaft (3) to rotate in the same direction, and can rotate in the opposite direction of the gas turbine central shaft (3) under no-load conditions. The drive gear (7) is located on one side of the rotation trajectory of the drive gear ring and can mesh with the drive gear ring intermittently. The clutch drive assembly is located on one side of the drive gear (7) and is used to push the drive gear (7) to selectively mesh with the drive gear ring. When the drive gear (7) meshes with the drive gear ring, it generates a driving force to drive the rotation of the gas turbine central shaft (3). When it separates from the drive gear ring, it stops the drive acting on the gas turbine central shaft (3).

2. The clutch mechanism for a low-speed hydraulically assisted turning gear in a gas turbine generator accident as described in claim 1, characterized in that, The clutch drive assembly includes: The drive shaft (6) is located on the central shaft of the drive gear (7) and has a spline section (13) in its axial part. The spline section (13) is axially slidably provided with a spline bushing (14) and the spline bushing (14) is fixedly connected to the drive gear (7). A cam (8) is located at one end of a splined bushing (14) and a rotating arm (19) is provided on one side of it. A slider (20) is provided on one side of the rotation path of the rotating arm (19). The slider (20) can rotate and contact the convex surface of the cam (8) to generate a driving force that pushes the drive gear (7) to move and mesh with the drive gear ring.

3. The clutch mechanism for a low-speed hydraulically assisted turning gear in a gas turbine generator accident as described in claim 2, characterized in that, The clutch drive assembly further includes: The stop block (23) is located on the convex top of the cam (8). When the slider (20) rotates to fit with the stop block (23), it generates a driving force to push the drive gear (7) to rotate. The second track groove (22) is opened on one side of the stop block (23) and extends along the convex surface of the cam (8) to its convex bottom position; The second slide rail (21) is located at one end of the slider (20) and can slide along the second track groove (22) so that when the slider (20) rotates in the opposite direction to the bottom of the cam (8), it drives the drive gear (7) to separate from the drive gear ring.

4. A clutch mechanism for a low-speed hydraulically assisted turning gear in a gas turbine generator accident, as described in any one of claims 2-3, characterized in that, It also includes a first compensating gear (71) rotatably mounted on one side of the drive gear (7) and a second compensating gear (72) rotatably mounted on the other side of the drive gear (7). Furthermore, along the axial direction of the spline bushing (14), a backlash compensation structure is provided to drive the first compensating gear (71) and the second compensating gear (72) to deflect relative to each other. When the drive gear (7) moves to engage with the drive gear ring, the first compensating gear (71) and the second compensating gear (72) deflect relative to each other to compensate for the backlash between the drive gear (7) and the drive gear ring.

5. The clutch mechanism for a low-speed hydraulically assisted turning gear in a gas turbine generator accident as described in claim 4, characterized in that, The backlash compensation structure includes: The swaying cavity (29) is located on the drive gear (7) and has two sets; The oscillating slide (30) is provided in two sets, which are respectively slidably disposed in two sets of oscillating cavities (29); One set of sway slides (30) is fixedly connected to the first compensating gear (71), and the other set of sway slides (30) is fixedly connected to the second compensating gear (72). Furthermore, a first abutment (15) is provided on one set of sway slides (30), and a second abutment (16) is provided on the other set of sway slides (30), forming a situation where the first abutment (15) and the second abutment (16) are subjected to force at the center of the distance between them, which pushes the first compensating gear (71) and the second compensating gear (72) to deflect in opposite directions.

6. The clutch mechanism for a low-speed hydraulically assisted turning gear in a gas turbine generator accident as described in claim 4, characterized in that, The backlash compensation structure further includes: Support arm (24), which is fixed to the axial direction of spline bushing (14) and has a slot (25) formed on the support arm (24). Telescopic platform (26), wherein the telescopic platform (26) is slidably disposed within the support arm (24); A concave cavity is formed above the telescopic platform (26), and a second pivot pin (27) is provided inside the concave cavity. A boss (17) is rotatably installed above the second pivot pin (27), and the boss (17) extends to the center of the distance between the first abutment (15) and the second abutment (16), so that when the boss (17) moves upward, it applies a thrust in a self-swaying state to the first abutment (15) and the second abutment (16). A wedge-shaped block (28) is formed below the telescopic platform (26), and the wedge-shaped block (28) is aligned with the slot (25); Impact block (18), which is located in the axial direction of the drive shaft (6) and is aligned with the slot (25), so that when the drive gear (7) moves toward the drive gear ring, it contacts the wedge block (28) and generates a driving force to push the boss (17) upward.

7. The clutch mechanism for a low-speed hydraulically assisted turning gear in a gas turbine generator accident as described in claim 6, characterized in that, Also includes: The first track groove (9) is opened on the outer ring of the semicircular clamp (2), and after the two sets of semicircular clamps (2) are engaged, an annular track is formed to provide a drive gear ring to rotate and slide. The annular track is provided with at least one set of ratchet grooves (10) along its circumference. The first slide rail (11) is located on the inner ring of the semi-circular toothed ring (5). After the two sets of semi-circular toothed rings (5) form a drive toothed ring, an annular guide rail is formed, which enables it to rotate and slide along the annular track. It is offset from the mating ends of the two sets of semi-circular clamps (2) to provide a limiting pre-tightening after the semi-circular clamps (2) are engaged. The annular guide rail is provided with at least one set of ratchet structures (12) along its circumference.

8. The clutch mechanism for a low-speed hydraulically assisted turning gear in a gas turbine generator accident as described in claim 7, characterized in that, The ratchet structure (12) includes: Inner shell (121), the inner shell (121) is disposed on the inner ring of the annular guide rail; A swing arm (124) is located inside the inner shell (121) and is rotatably mounted to the inner shell (121) via a first pivot pin (123). One side of the swing arm (124) is provided with a compression spring (122) to provide its swing reset, and the other side of the swing arm (124) is provided with a ratchet (125) so that the ratchet (125) can be limited to abut against the ratchet groove (10) or to slide relative to the ratchet groove (10).

9. The clutch mechanism for a low-speed hydraulically assisted turning gear in a gas turbine generator accident as described in claim 7, characterized in that, The ratchet (125) has an arc-shaped structure on one side, which allows the ratchet (125) to slide and engage along the ratchet groove (10), and its arc surface is set opposite to the rotation direction of the gas turbine central shaft (3), so that the rotational thrust of the drive gear ring is converted into sliding thrust and rotates relative to the gas turbine central shaft (3).

10. The clutch mechanism for a low-speed hydraulically assisted turning gear in a gas turbine generator accident according to claim 7, characterized in that, The other side of the ratchet (125) is a straight structure, which allows the ratchet (125) to be limited and abutted along the ratchet groove (10), and transmit the rotational thrust of the drive gear ring to the gas turbine central shaft (3).

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