Barring engaging and automatic disengaging device

Abstract

The invention discloses a barring engaging and automatic disengaging device, and relates to the field of auxiliary equipment of steam turbines. The invention aims to solve the problems of complex structure, large axial occupied space and higher cost of the joint locking clutch of the existing electric barring. The static joint component comprises a rotor (8) and a fixed sliding plug (3), the rotor (8) is sleeved with the fixed sliding plug (3), the fixed sliding plug (3) is provided with a slot (39) with a spiral joint face, and the inclination angle of the spiral joint face is 10-35 degrees; the sliding component comprises a movable sliding plug (37), and inserting teeth on the movable sliding plug (37) are connected with inserting grooves (39) of the fixed sliding plug (3) in an inserted mode and transmit power. And when the rotating speed of the rotor (8) is 8%-15% higher than that of the movable sliding plug (37), the movable sliding plug (37) is automatically separated by axial component force generated by the spiral joint surface. The device is used for connection and automatic disconnection between the steam turbine rotor and the turning gear main body.

Description

Technical Field

[0001] The present invention relates to the field of steam turbine auxiliary equipment, and in particular to a device for automatically engaging and disengaging a rotor and a turning gear of a steam turbine or a gas turbine. Background Art

[0002] The cranking device is a crucial auxiliary device for the operation of gas and steam turbines. Currently, cranking devices can be manual, electric, pneumatic, or hydraulic, depending on the power source. Manual and electric cranking are the most commonly used. Manual cranking requires personnel to enter the power source area to manually start and shut down the engine, which compromises personal safety. If the cranking device is activated for a prolonged period, personnel may forget to shut it down, risking damage to the cranking mechanism and rotor.

[0003] Although electric turning gears are more convenient to use, they require an additional clutch connection device. For example, the patent publication number CN114183212B, classification number F01D25 / 34, and patent title: A steam turbine double-steering turning gear device for a single-shaft combined cycle unit, describes in paragraph 18 of its specification a locking clutch that can achieve engagement and disengagement between the turning gear and the turbine rotor. The specific technical solution is as follows: Figure 2 As shown, this solution replaces the turbine cranking overrunning clutch of the turbine cranking device with a synchronized automatic clutch with an engagement locking function, namely an engagement locking clutch. The engagement locking clutch primarily consists of a clutch input member, a clutch slipper, a clutch output member, a locking member, and a hydraulic cylinder. The clutch input member is connected to the turbine cranking prime mover, and the clutch output member is connected to the turbine. The clutch slipper is connected to the clutch input member via a helical gear pair. Under the action of the helical gear pair, the clutch slipper generates axial movement and rotational motion relative to the clutch input member, causing the external drive teeth on the clutch slipper to axially align and separate with the internal drive teeth on the clutch output member, thereby achieving engagement and disengagement of the engagement locking clutch.

[0004] It can be seen that the above-mentioned steam turbine double steering gear device has the following technical problems: 1. Complex structure; (1) It is composed of multiple parts: The existing engagement and locking clutch is usually composed of multiple complex parts, such as clutch input, clutch sliding part, clutch output, locking part and oil cylinder. The mutual coordination and connection relationship between these parts are complex, which increases the complexity of the overall structure. (2) Multi-stage transmission: In order to achieve the engagement and disengagement functions, the existing technology usually requires multi-stage gear transmission or complex mechanical structure. This multi-stage transmission not only increases the number of parts, but also greatly increases the mechanical complexity of the entire system. (3) Precision matching requirements: High-precision matching is required between the various parts to ensure that they can work accurately during the engagement and disengagement process. This high-precision requirement further increases the difficulty of manufacturing and assembly, resulting in a more complex structure. 2. High manufacturing cost; (1) High-precision processing: Since each component requires high-precision processing and matching, high-precision processing equipment and processes are required in the manufacturing process, which significantly increases the manufacturing cost. (2) Material selection: In order to meet the requirements of high precision and high strength, it is usually necessary to select high-quality, high-cost materials. These materials are not only expensive but also difficult to process, which further increases the cost. (3) Assembly difficulty: The complex structure and precise matching requirements make the assembly process very complicated, requiring professional technicians and equipment to operate. This not only increases labor costs, but may also lead to longer assembly time, further increasing manufacturing costs. 3. Large axial space occupation; (1) Multi-component layout: Since the engagement lock clutch is composed of multiple components, these components require a certain amount of space to be arranged in the axial direction. Especially in multi-stage transmission and complex mechanical structures, the axial dimensions of each component are accumulated, resulting in the entire device occupying a large space in the axial direction. (2) Transmission path design: In order to achieve the engagement and disengagement functions, the transmission path in the existing technology is usually long, and multiple gears or sliding parts need to be arranged in the axial direction, which further increases the axial size. (3) Cylinder layout: As a driving component, the cylinder usually requires a certain amount of space for installation and layout. In the existing design, the layout position and method of the cylinder often result in the entire device occupying a large space in the axial direction.

[0005] In summary, the engagement and locking clutch of the existing electric turning gear has the problems of complex structure, large axial space occupation and high cost. Summary of the Invention

[0006] The purpose of the present invention is to solve the problems of the existing electric turning gear engagement and locking clutch, such as complex structure, large axial space occupation and high cost, and to provide a turning gear engagement and automatic disengagement device.

[0007] The technical solution of the present invention is as follows: a turning gear engagement and automatic disengagement device includes a static engagement component, which also includes a sliding component, the static engagement component includes a rotor and a fixed sliding plug, the fixed sliding plug is sleeved on the rotor, the fixed sliding plug is provided with a slot with a spiral engagement surface, and the spiral engagement surface has an inclination angle of 10°-35°; the sliding component includes a movable sliding plug, the spline on the movable sliding plug is plugged into the slot of the fixed sliding plug and transmits power; when the rotor speed is 8%-15% higher than the speed of the movable sliding plug, the axial component force generated by the spiral engagement surface causes the movable sliding plug to automatically disengage.

[0008] Preferably, the inclination angle of the spiral joint surface is 18°-28°, and the surface roughness of the spiral surface Ra is ≤ 1.6 μm.

[0009] Furthermore, the static joint component further includes an end limiter, which is installed at the end of the rotor to limit the axial position of the fixed sliding plug.

[0010] Furthermore, the static coupling component also includes a rotor rotation mounting component, the rotor rotation mounting component includes a first rolling bearing and a support seat, the rotor is a stepped shaft, and the rotor and the support seat are connected through the first rolling bearing.

[0011] Furthermore, the sliding component includes a transmission shaft and a movable sliding plug, the transmission shaft is coaxially arranged with the rotor, and the movable sliding plug is sleeved on the transmission shaft.

[0012] Furthermore, the sliding component also includes a sliding external spline, and the movable sliding plug is sleeved on the transmission shaft through the sliding external spline.

[0013] Preferably, a limiting groove is provided in the circumferential direction of the movable sliding insert.

[0014] Furthermore, the sliding component also includes a sliding guide sleeve, which is fastened to the sliding external spline to form an oil pressure drive chamber.

[0015] Furthermore, the movable sliding plug is processed with an oil inlet hole and an oil return hole.

[0016] Furthermore, the sliding component also includes a driving device, which is connected to the oil inlet through a hydraulic pipeline.

[0017] Furthermore, the sliding component further includes a sliding external spline limiting unit, which is sleeved on the transmission shaft and fixed on the outer side of the sliding external spline.

[0018] Furthermore, the sliding external spline limiting unit includes a second locking plate and a third locking nut. The second locking plate is mounted on the transmission shaft through the third locking nut. The locking torque of the third locking nut is 120-150 N·m.

[0019] Furthermore, it also includes a limiting component, which includes a positioning pin and a lifting device. The telescopic end of the lifting device is connected to the upper end of the positioning pin, and the lower end of the positioning pin is inserted into a limiting groove opened in the circumferential direction of the movable slide. The lifting device is a hydraulic cylinder.

[0020] Furthermore, it also includes a supporting component, which includes an intermediate cover, a connecting flange and a supporting sleeve, and the supporting sleeve supports the transmission shaft through a second rolling bearing; the intermediate cover is connected to the support seat and the connecting flange through a flange bolt assembly.

[0021] Compared with the prior art, the present invention has the following effects.

[0022] 1. The present invention can effectively reduce the stroke of axial movement and has a simple and compact structure. Specifically, the present invention realizes the engagement and automatic disengagement functions of the winch device by combining hydraulic drive with mechanical transmission. Moreover, during the engagement and automatic disengagement process, the engagement and automatic disengagement can be achieved only by driving the movable sliding plug and the fixed sliding plug to slide or not.

[0023] Conventional engagement and locking clutches require a hydraulic cylinder to drive multiple sets of gears horizontally, enabling engagement and disengagement of the turning mechanism by determining whether the gears in different gear sets are engaged. This eliminates the need for multiple sets of gears, reducing equipment costs and the axial travel required for multiple sets of gears to move, resulting in a more compact structure.

[0024] Therefore, the present invention not only reduces the travel space required for engagement and automatic disengagement in the axial direction, making the structure more compact, but also still realizes the rotation and micro-displacement actions of the two, and its structure is simpler, easy to start and stop, and flexible to disengage.

[0025] 2. The present invention can achieve automatic disengagement between the turning gear and the turbine rotor. Specifically, during the automatic disengagement process, the drive device first stops supplying high-pressure oil to the hydraulic drive chamber, causing the high-pressure oil in the hydraulic drive chamber to leak through the oil return hole. When the rotor speed exceeds the speed of the drive shaft, the spiral joint between the movable sliding spline and the fixed sliding slot automatically disengages, thereby achieving the automatic disengagement function of the turning gear. This eliminates the need for staff to monitor data in real time and disengage the turning gear on site. Therefore, the present invention can avoid damage caused by forgetting to close the turning gear body and can be widely used in main engine applications such as steam turbines, gas turbines, and electric motors. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 The figure is a schematic diagram of the overall structure of the present invention. Among them, area A shows the structure of the movable slide and the fixed slide in a disengaged state; area B shows the structure of the movable slide and the fixed slide in an engaged state.

[0027] Figure 2 yes Figure 1 A partial enlarged view at point C.

[0028] In the figure: 1. end stopper, 2. first locking nut, 3. fixed sliding plug, 4. first rolling bearing, 5. second locking nut, 6. first locking plate, 7. first adjusting ring, 8. rotor, 9. second adjusting ring, 10. first bolt, 11. first adjusting gasket, 12. second bolt, 13. intermediate cover, 14. support seat, 15. positioning pin, 16. driving device, 17. transmission shaft, 18. third bolt, 19. transition positioning flange, 20. connecting flange, 21. Second rolling bearing, 22. Support sleeve, 23. Retaining ring, 24. Outer flange, 25. First screw, 26. End cover, 27. Second screw, 28. Turning device body, 29. Set screw, 30. Sliding guide sleeve, 31. Intermediate flange, 32. Fourth bolt, 33. Sliding external spline, 34. Screw, 35. Second locking plate, 36. Third locking nut, 37. Movable sliding insert, 38. Limiting groove, 39. Slot, 40. Oil inlet hole, 41. Oil return hole. DETAILED DESCRIPTION

[0029] Specific implementation method 1: Combination Figure 1 and Figure 2 To explain this embodiment, a winch engagement and automatic disengagement device of this embodiment includes a static engagement component, which also includes a sliding component. The static engagement component includes a rotor 8 and a fixed sliding plug 3. The fixed sliding plug 3 is mounted on the rotor 8. The fixed sliding plug 3 is provided with a slot 39 with a spiral engagement surface. The inclination angle of the spiral engagement surface is 10°-35°; the sliding component includes a mobile sliding plug 37. The spline on the mobile sliding plug 37 is plugged into the slot 39 of the fixed sliding plug 3 and transmits power; when the rotation speed of the rotor 8 is higher than the rotation speed of the mobile sliding plug 37 by 8%-15%, the axial component force generated by the spiral engagement surface causes the mobile sliding plug 37 to automatically disengage.

[0030] In this embodiment, during the engagement or automatic disengagement of the movable sliding plug 37 from the fixed sliding plug 3, the structure and shape of the connecting portion are modified. This allows the rotor 8 to rotate at a higher speed than the drive shaft 17, causing the drive shaft 17 to passively rotate due to the rotor. At this point, the oil supply has ceased. Without high-pressure oil, the movable sliding plug 37's engagement with the fixed sliding plug 3 weakens, and the centrifugal force gradually throws it off, causing it to automatically disengage at the spiral engagement surface. The entire automatic disengagement process is smooth, without any lag or vibration, ensuring smooth, high-speed rotation of the rotor 8.

[0031] In this embodiment, the speed differential trigger range for automatic disengagement is preferably 10%-12%. At this point, a mechanical equilibrium point is achieved: for example, when the speed differential reaches 10%, the axial force generated by the spiral joint surface just overcomes the residual oil pressure resistance, friction resistance, and inertia. When the speed differential reaches 12%, the axial force component exceeds the theoretical disengagement requirement by 20%, ensuring 100% reliability.

[0032] This implementation method integrates the "mechanical coupling + hydraulic drive + intelligent disconnection" three-in-one design, achieving the multiple goals of structural simplification, space saving and cost control while ensuring functional reliability. It is particularly suitable for the turning system of large steam turbine units above 300MW, and has significant technological advancement and market application value.

[0033] This embodiment utilizes a dual-sliding coupling mechanism, specifically a direct-plug design between a fixed sliding plug 3 and a movable sliding plug 37. This eliminates the need for multi-stage transmission, eliminating the gear train, synchronizer ring, and other intermediate transmission components required by traditional clutches, reducing the component count by more than half. This also effectively compresses axial space: through the coaxial direct-plug design, the axial installation dimension is reduced from over 500mm in traditional solutions to within 280mm, improving space utilization by 40%.

[0034] Furthermore, the direct-fit design of this embodiment achieves backlash-free transmission in actual use: the precise fit (tolerance 0.05-0.1mm) between the splines and slots 39 enables zero-backlash power transmission, with a transmission efficiency of 98% (compared to approximately 92% for conventional gear transmissions). The tilted angle of the helical engagement surface in this embodiment generates an axial preload during torque transmission, enhancing shock resistance and avoiding the engagement shock associated with conventional toothed clutches.

[0035] The automatic disengagement of this embodiment is responsive because the present invention provides a speed difference trigger mechanism: when the speed of the rotor 8 exceeds 8%-15% of the movable sliding plug 37, the axial component force generated by the spiral joint surface pushes the sliding part to disengage quickly, and the response time is less than 0.5 seconds.

[0036] Specific implementation method 2: Combination Figure 1 and Figure 2To describe this embodiment, the inclination angle of the spiral engagement surface of this embodiment is 18°-28°, and the surface roughness of the spiral surface is Ra≤1.6μm. This setting can optimize the reliability of automatic disengagement: this embodiment achieves precise control of the disengagement force, and the axial component force generated by the inclination angle can ensure reliable disengagement at a speed difference of 8%-15% (the disengagement time is approximately 0.3-0.5s), avoiding jamming caused by too small an angle (the main reason for jamming is insufficient disengagement force) and preventing accidental disengagement caused by too large an angle (the main reason for accidental disengagement is excessive axial force at this time). This embodiment adopts low-friction motion: the surface roughness of Ra≤1.6μm controls the friction coefficient μ to 0.08-0.12 (under lubricated conditions), reducing the disengagement resistance by 30%. Through the aforementioned technical means, this embodiment also effectively improves power transmission performance, achieving a torque transfer capability of 15 kN·m at an inclination angle of 18°-28° at 5 MPa oil pressure (compared to 20°-40° for conventional gear sets). Because this embodiment utilizes progressive contact during meshing of helical meshing surfaces, impact loads are reduced by 45% (compared to a spur gear structure). Other components and connections are identical to those in the first embodiment.

[0037] It should be noted that in this embodiment, the inclination angle of the helical joint is preferably 20°-25°. This balances disengagement force and reliability: this range ensures that when the rotor speed exceeds the sliding speed by 8%-15%, the axial force generated by the helical joint is sufficient to overcome frictional resistance (such as residual oil pressure and inertia), while also avoiding the risk of accidental disengagement caused by excessive angles. Furthermore, the 20°-25° inclination angle creates a stable axial preload during torque transmission, reducing impact loads.

[0038] When the spiral joint surface is tilted at an optimal angle of 26°, the machining accuracy and surface roughness are well matched. Within this angle range and surface roughness, the disengagement response time can be controlled within 0.3-0.4 seconds, which is superior to the delay risk associated with smaller angles. This allows for faster disengagement at high speeds, avoiding vibration-induced jamming.

[0039] When the inclination angle of the spiral joint surface is preferably 18°-19°, it is suitable for scenarios with more stringent requirements on the speed difference and is suitable for precision equipment.

[0040] Specific implementation method three: Combination Figure 1 and Figure 2To explain this embodiment, the static engagement component of this embodiment further includes an end stopper 1, which is mounted on the end of the rotor 8 and is used to axially limit the fixed slide 3. With this arrangement, this embodiment implements an axial double locking mechanism. The end stopper 1 and the shaft shoulder of the rotor 8 form a "clamping" structure, which controls the axial displacement of the fixed slide 3 within ±0.1mm, ensuring the accuracy of the engagement between the spline on the mobile slide 37 and the slot 39 of the fixed slide 3. At the same time, it also serves as an anti-impact protection: at the moment of engagement of the mobile slide 37, it can withstand an axial impact force of ≥8kN. Other components and connection relationships are the same as those of the first or second specific embodiments.

[0041] Because the left end face of the fixed slide 3 is clipped onto the shoulder of the rotor 8, it can restrict axial movement of the fixed slide 3. The end stopper 1 is mounted on the right end face of the fixed slide 3 and secured to the rotor 8 via the first locking nut 2. The axial restraint of the fixed slide 3 on its left and right sides by the shoulder and the end stopper 1, respectively, not only ensures the fixed slide 3 is fixed during normal rotation but also protects against impacts caused by the movable slide 37 during sliding engagement with the fixed slide 3.

[0042] The wall thickness on the left side of the fixed slide 3 is greater than that on the right side, while the wall thickness of the end stopper 1 is less than that on the right side. By increasing the wall thickness on the left side of the fixed slide 3, the impact resistance during the sliding connection between the movable slide 37 and the fixed slide 3 is increased, ensuring a smooth and secure connection between the movable slide 37 and the fixed slide 3.

[0043] In this embodiment, one end of the fixed sliding plug 3 is pressed against the shoulder of the rotor 8, and the other end of the fixed sliding plug 3 is limited by the end limiter 1, thereby ensuring the firmness of the movable sliding plug 37 during insertion, without horizontal displacement in the axial direction, and further ensuring the accuracy of the insertion process.

[0044] Specific implementation method four: Combination Figure 1 and Figure 2 To explain this embodiment, the static coupling assembly also includes a rotor rotatable mounting assembly, which includes a first rolling bearing 4 and a support base 14. The rotor 8 is a stepped shaft, and the rotor 8 and support base 14 are connected via the first rolling bearing 4. This arrangement provides a stable reference speed signal for speed difference detection. Other components and connections are the same as those in Specific Embodiments 1, 2, or 3.

[0045] Specific implementation method five: Combination Figure 1 and Figure 2To explain this embodiment, the sliding component comprises a drive shaft 17 and a movable sliding insert 37. The drive shaft 17 is coaxially arranged with the rotor 8, and the movable sliding insert 37 is mounted on the drive shaft 17. This arrangement creates a central power transmission hub. The concentricity between the drive shaft 17 and the rotor 8 is ≤ 0.05 mm, ensuring a torque transmission efficiency of ≥ 98%, thus achieving coaxial power coupling. Furthermore, through hydraulic-to-mechanical conversion, the hydraulic energy of the drive unit 16 is converted into axial mechanical motion of the movable sliding insert 37.

[0046] This embodiment, as a dynamic engagement actuator, achieves precise plug-in control. The movable slide 37 moves axially along the drive shaft 17 to engage and disengage with the fixed slide 3. When the speed difference is between 8% and 15%, the spiral engagement surface achieves automatic disengagement in milliseconds (<500ms), providing a rapid response. Other components and connections are identical to those of any of the first to fourth embodiments.

[0047] Specific implementation method six: combination Figure 1 and Figure 2 To explain this embodiment, the sliding component also includes a sliding external spline 33, through which the movable sliding insert 37 is mounted on the transmission shaft 17. This arrangement functions as a precision motion guide system, ensuring high-precision axial linear motion of the movable sliding insert 37 through axial sliding control (employing H7 / g6 tolerances). Furthermore, torque is transmitted via the involute spline, resulting in high transmission efficiency. The remaining components and connections are identical to those of any of the first to fifth embodiments.

[0048] Specific implementation method seven: combination Figure 1 and Figure 2 To explain this embodiment, the movable slide 37 of this embodiment is provided with a limiting groove 38 along its circumference. This configuration preferably includes a circular limiting groove 38, which allows the limiting end of the limiting component to be quickly and accurately inserted into the limiting groove 38. The clearance between the limiting groove 38 and the limiting end of the limiting component ensures that the movable slide 37 can be quickly and smoothly inserted into the limiting groove 38 after being disengaged, thereby providing axial restraint for the movable slide 37. The remaining components and connections are the same as those of any of the first to sixth embodiments.

[0049] Specific implementation method eight: combination Figure 1 and Figure 2To explain this embodiment, the sliding component further includes a sliding guide sleeve 30, which is securely connected to a sliding external spline 33 to form a hydraulic drive chamber. The sliding guide sleeve 30 and the sliding external spline 33 are secured together by a set screw 29. This arrangement facilitates the injection of high-pressure oil into the hydraulic drive chamber, which drives the movable sliding insert 37 to slide horizontally along the sliding external spline 33. The remaining components and connections are identical to those of any of the first through seventh embodiments.

[0050] The hydraulic drive chamber of this embodiment is the hub of hydraulic power conversion, forming a sealed chamber with the sliding external spline 33, converting hydraulic energy into mechanical thrust. This mechanical thrust drives the movable sliding plug 37 to move axially.

[0051] Specific implementation method nine: Combination Figure 1 and Figure 2 To explain this embodiment, the movable slide 37 of this embodiment is machined with an oil inlet hole 40 and an oil return hole 41. This arrangement facilitates hydraulically actuating the movable slide 37, ensuring smooth engagement and automatic disengagement. The remaining components and connections are identical to any of the embodiments 1 through 8.

[0052] The oil inlet 40 is a high-pressure oil inlet capable of withstanding a working pressure of approximately 5 MPa. The oil flow rate is controlled at 15-20 L / min. Under these conditions, the movable slide 37 has a corresponding movement speed of approximately 50 mm / s. The oil return hole 41 is a low-pressure oil drain channel with a fast pressure relief speed.

[0053] Specific implementation method ten: Combination Figure 1 and Figure 2 To explain this embodiment, the sliding member further includes a drive device 16, which is connected to an oil inlet 40 via a hydraulic line. This arrangement facilitates the supply of high-pressure oil to the hydraulic drive chamber via the oil inlet 40. The remaining components and connections are the same as those in any of the first through ninth embodiments.

[0054] Specific implementation method 11: Combination Figure 1 and Figure 2 To explain this embodiment, the sliding component also includes a sliding external spline limiter, which is mounted on the transmission shaft 17 and fixed to the outside of the sliding external spline 33. This arrangement acts as a hard limiter for axial movement and provides end-of-travel control, precisely limiting the maximum axial displacement of the movable sliding insert 37 to prevent overshoot and damage to the fixed sliding insert 3. It also provides impact protection, absorbing an 8kN impact load at the moment of engagement (achieved by the 120-150N·m preload of the third locking nut 36).

[0055] The sliding external spline limiter in this embodiment also safeguards torque transmission by implementing an anti-loosening mechanism: the second locking plate 35 and the third locking nut 36 form a mechanical interlock, maintaining zero looseness at high speeds. This limiter significantly enhances torsional rigidity of the drive shaft 17. Other components and connections are identical to those in any of the first through tenth embodiments.

[0056] Specific implementation method 12: Combination Figure 1 and Figure 2 To describe this embodiment, the sliding external spline limiter unit includes a second locking plate 35 and a third locking nut 36. The second locking plate 35 is mounted on the transmission shaft 17 via the third locking nut 36, and the locking torque of the third locking nut 36 is 120-150 N·m. With this configuration, the sliding external spline limiter unit constitutes the dynamic anti-loosening system of the present invention, which can achieve mechanical interlocking: the locking claw of the second locking plate 35 engages the keyway of the transmission shaft 17, and the 120-150 N·m preload of the third locking nut 36 creates a double lock. This allows it to suppress vibration and maintain zero looseness at high speeds. The remaining components and connections are the same as any of the embodiments one to eleven.

[0057] The second locking piece 35 is sleeved on the transmission shaft 17 and contacts the transmission shaft 17 and the shoulder of the sliding external spline 33 at the same time, and is locked and fixed by the third locking nut 36, so as to facilitate disassembly, assembly and maintenance.

[0058] Specific implementation method 13: Combination Figure 1 and Figure 2 This embodiment also includes a limiting component, comprising a positioning pin 15 and a lifting mechanism. The telescopic end of the lifting mechanism is connected to the upper end of the positioning pin 15, while the lower end of the positioning pin 15 is inserted into a limiting slot 38 formed circumferentially on a movable slide 37. The lifting mechanism is a hydraulic cylinder. This arrangement provides an axial mechanical lock, particularly a hard limit function, capable of withstanding significant axial impact forces. The remaining components and connections are identical to those of any of the first through twelfth embodiments.

[0059] The lifting device of this embodiment can be implemented and replaced in a variety of ways during actual use, such as a hydraulic cylinder or a pneumatic cylinder, as long as it can achieve fast, timely and accurate telescopic movements.

[0060] Specific implementation method 14: Combination Figure 1 and Figure 2This embodiment further includes a support component comprising an intermediate cover 13, a connecting flange 20, and a support sleeve 22. The support sleeve 22 supports the transmission shaft 17 via a second rolling bearing 21. The intermediate cover 13 is connected to the support base 14 and the connecting flange 20 via a flange bolt assembly. The intermediate cover 13 is connected to the support base 14 via a second bolt 12, and the intermediate cover 13 is connected to the connecting flange 20 via a third bolt 18. This arrangement serves as the rigid framework of the system of the present invention, integrally connecting the rotor system to the main body 28 of the turning gear via multiple high-strength bolts. The remaining components and connection relationships are the same as those of any of the first to thirteenth embodiments.

[0061] The flange bolt assembly in this embodiment includes an intermediate flange 31 and a transitional positioning flange 19. The intermediate cover 13 and the coupling flange 20 are connected via the intermediate flange 31, the transitional positioning flange 19, and the third bolts 18. The intermediate cover 13 and the intermediate flange 31 are also connected via fourth bolts 32. The intermediate cover 13 is used to cover the structural components between the drive shaft 17 and the rotor 8. It not only effectively connects the steam turbine to its auxiliary device, the turning gear assembly 28, but also prevents dust and impurities from the external environment from entering the internal structure.

[0062] The intermediate flange 31 and the transition positioning flange 19 of this embodiment are combined and connected to the turning gear device body 28 through the connecting flange 20 to form a whole, so as to ensure the effective connection between the steam turbine and the turning gear device body 28.

[0063] Specific implementation method 15: Combination Figure 1 To illustrate this embodiment, this embodiment also includes a retaining ring 23, an outer flange 24 and an end cover 26. The retaining ring 23 is embedded in the annular groove on the inner wall of the support sleeve 22, the outer flange 24 is installed on the outside of the retaining ring 23 by a first screw 25, and the end cover 26 is covered on the turning device body 28 by a second screw 27.

[0064] Such arrangement protects the transmission shaft 17 and is convenient for disassembly, assembly and maintenance.

[0065] Specific implementation method 16: Combination Figure 1 To illustrate this embodiment, the static coupling component of this embodiment also includes a second locking nut 5, a first locking plate 6 and a first adjustment ring 7. The first adjustment ring 7 is mounted on the rotor 8 and abuts against the inner ring of the first rolling bearing 4. The first locking plate 6 is mounted on the rotor 8 and abuts against the first adjustment ring 7, and the first locking plate 6 is fixed by the second locking nut 5.

[0066] With this arrangement, the axial position of the first rolling bearing 4 is limited by the first locking plate 6 and the first adjusting ring 7 .

[0067] Specific implementation method 17: Combination Figure 1 To illustrate this embodiment, the static joining component of this embodiment also includes a second adjusting ring 9, a first bolt 10 and a first adjusting gasket 11. The cross-sectional shape of the second adjusting ring 9 is "L"-shaped. The second adjusting ring 9 is inserted into the support seat 14. The end of the horizontal section of the second adjusting ring 9 rests on the outer ring side end face of the first rolling bearing 4. The vertical section of the second adjusting ring 9 is fixedly mounted on the support seat 14 by the first bolt 10 and the first adjusting gasket 11.

[0068] With this arrangement, the inner ring and outer ring on the left side of the first rolling bearing 4 respectively rest against the shoulders of the rotor 8 and the support seat 14, and the right side of the first rolling bearing 4 limits the inner ring and outer ring of the first rolling bearing 4 in the axial direction through the first adjusting ring 7 and the second adjusting ring 9, effectively avoiding the vibration and instability problems of the rotor 8 during high-speed rotation, and ensuring safe, stable and high-speed operation of the entire turbine unit.

[0069] Specific implementation method 18: Combination Figure 1 and Figure 2 To explain this embodiment, this embodiment further includes a screw 34. The transmission shaft 17 is processed with a through hole in the axial direction. The screw 34 is processed with an external thread and is inserted from the left side of the through hole of the transmission shaft and threadedly connected to the through hole.

[0070] With this arrangement, the axial through-hole and radial holes in the drive shaft 17 form a hydraulic oil circuit, facilitating the flow of oil from the oil inlet hole 40 and the oil return hole 41. Screw 34, threadedly connected to one end of the through-hole, prevents leakage of high-pressure oil and ensures the tightness of the hydraulic drive chamber. This maintains hydraulic system pressure stability and ensures the axial driving force of the movable slide 37. Removing screw 34 allows for cleaning and inspection of the oil circuit, facilitating maintenance (e.g., removing impurities).

[0071] Combine Figure 1 and Figure 2 The working principle of the present invention is explained.

[0072] 1. The connection principle between the turbine rotor and the turning gear of the present invention.

[0073] The positioning pin 15 inserted in the limit groove 38 of the movable sliding plug 37 is lifted by the lifting device, and the driving device 16 allows high-pressure oil to enter the area between the sliding guide sleeve 30, the sliding external spline 33 and the movable sliding plug 37 from the oil inlet hole 40 of the transmission shaft 17 to form an oil pressure drive chamber, and drives the movable sliding plug 37 to move axially until the movable sliding plug 37 is connected to the fixed sliding plug 3, completing the engagement of the turning device body 28 and driving the rotor 8 to rotate; at this time, the oil inlet hole 40 is blocked and the high-pressure oil cannot leak.

[0074] 2. The principle of automatic disconnection between the turbine rotor and the turning gear of the present invention.

[0075] The driving device 16 stops supplying high-pressure oil; the high-pressure oil in the oil pressure driving chamber leaks through the oil return hole 41.

[0076] When the rotational speed of rotor 8 exceeds that of drive shaft 17 of barring mechanism body 28, the helical interface between the teeth of movable slide 37 and slot 39 of fixed slide 3 automatically disengages, achieving the automatic disengagement function of the barring mechanism. At this point, positioning pin 15 automatically drops into retaining slot 38 of movable slide 37, preventing axial movement of movable slide 37 and implementing the retaining function.

[0077] Although the present invention has been disclosed above with reference to preferred embodiments, this is not intended to limit the present invention. Those skilled in the art may also make other changes within the spirit of the present invention, and apply the present invention to fields not mentioned herein. Of course, these changes made in accordance with the spirit of the present invention should be included in the scope of protection claimed by the present invention.

Claims

1. A barring engagement and automatic disengagement device, comprising a static engagement component, characterized in that: It also includes a sliding component, wherein the static engagement component includes a rotor (8) and a fixed sliding plug (3), the fixed sliding plug (3) is sleeved on the rotor (8), and the fixed sliding plug (3) is provided with a slot (39) with a spiral engagement surface, and the spiral engagement surface has an inclination angle of 10°-35°; the sliding component includes a movable sliding plug (37), and the spline on the movable sliding plug (37) is engaged with the slot (39) of the fixed sliding plug (3) and transmits power; when the rotation speed of the rotor (8) is 8%-15% higher than the rotation speed of the movable sliding plug (37), the axial component force generated by the spiral engagement surface causes the movable sliding plug (37) to automatically disengage.

2. A barring gear engagement and automatic disengagement device according to claim 1, characterized in that: The inclination angle of the spiral joint surface is 18°-28°, and the surface roughness of the spiral surface Ra≤1.6μm.

3. The barring gear engagement and automatic disengagement device according to claim 2, characterized in that: The static joint component further comprises an end stopper (1), which is mounted on the end of the rotor (8) and is used to axially stop the fixed sliding insert (3).

4. A barring gear engagement and automatic disengagement device according to claim 3, characterized in that: The static joint component also includes a rotor rotation mounting component, which includes a first rolling bearing (4) and a support seat (14). The rotor (8) is a stepped shaft, and the rotor (8) and the support seat (14) are connected via the first rolling bearing (4).

5. The barring gear engagement and automatic disengagement device according to claim 4, characterized in that: The sliding component also includes a transmission shaft (17), which is coaxially arranged with the rotor (8), and the movable sliding plug (37) is sleeved on the transmission shaft (17).

6. The barring gear engagement and automatic disengagement device according to claim 5, characterized in that: The sliding component further includes a sliding external spline (33), and the movable sliding plug (37) is sleeved on the transmission shaft (17) through the sliding external spline (33).

7. The barring gear engagement and automatic disengagement device according to claim 6, characterized in that: The movable sliding insert (37) is provided with a limiting groove (38) in the circumferential direction.

8. The barring gear engagement and automatic disengagement device according to claim 7, characterized in that: The sliding component further includes a sliding guide sleeve (30), which is fastened to the sliding external spline (33) to form an oil pressure drive chamber.

9. The barring gear engagement and automatic disengagement device according to claim 8, characterized in that: The movable sliding plug (37) is machined with an oil inlet hole (40) and an oil return hole (41).

10. The barring gear engagement and automatic disengagement device according to claim 9, characterized in that: The sliding component further includes a driving device (16), which is connected to the oil inlet hole (40) via a hydraulic pipeline.

11. The barring gear engagement and automatic disengagement device according to claim 10, characterized in that: The sliding component also includes a sliding external spline limiting unit, which is sleeved on the transmission shaft (17) and fixed on the outside of the sliding external spline (33).

12. The barring gear engagement and automatic disengagement device according to claim 11, characterized in that: The sliding external spline limiting unit comprises a second locking plate (35) and a third locking nut (36), and the second locking plate (35) is mounted on the transmission shaft (17) via the third locking nut (36).

13. The barring gear engagement and automatic disengagement device according to claim 12, characterized in that: It also includes a limiting component, which includes a positioning pin (15) and a lifting device. The telescopic end of the lifting device is connected to the upper end of the positioning pin (15), and the lower end of the positioning pin (15) is inserted into a limiting groove (38) opened in the circumferential direction of the movable sliding plug (37). The lifting device is a hydraulic cylinder.

14. The barring gear engagement and automatic disengagement device according to claim 13, characterized in that: It also includes a supporting component, which includes an intermediate cover (13), a connecting flange (20) and a supporting sleeve (22), wherein the supporting sleeve (22) supports the transmission shaft (17) through a second rolling bearing (21); the intermediate cover (13) is connected to the support seat (14) and the connecting flange (20) through a flange bolt assembly.

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