A turning gear engagement and automatic disengagement device

Abstract

The application relates to a disc engaging and automatic disengaging device, and relates to the field of steam turbine auxiliary equipment. In order to solve the problems of complex structure, large axial space occupation and high cost of the existing electric disc engaging and automatic disengaging device, the static engaging part of the application comprises a rotor (8) and a fixed sliding plug (3), the fixed sliding plug (3) is sleeved on the rotor (8), the fixed sliding plug (3) is provided with a plug groove (39) with a spiral engaging surface, and the inclination angle of the spiral engaging surface is 10-35 degrees; the sliding part comprises a movable sliding plug (37), the plug teeth on the movable sliding plug (37) are inserted into the plug groove (39) of the fixed sliding plug (3) and power is transmitted; when the rotating speed of the rotor (8) is higher than that of the movable sliding plug (37) by 8-15%, the axial component force generated by the spiral engaging surface makes the movable sliding plug (37) automatically disengage. The application is used for the engagement and automatic disengagement between a steam turbine rotor and a disc engaging device main body.

Description

TECHNICAL FIELD

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

[0002] The turning gear is one of the important auxiliary equipment for the operation of the gas turbine and the steam turbine. At present, the turning gear can be manual, electric, pneumatic and hydraulic according to different power sources, among which, the manual and electric turning gears are the most commonly used. The manual turning gear needs the staff to enter the area where the power source is located to start and stop manually, and the safety of the staff is poor during the process of starting and stopping manually. If the turning gear is started for a long time, the staff may forget to stop, which may cause damage to the turning gear mechanism and the rotor.

[0003] Although the electric turning gear is more convenient to use, it needs to add a set of clutch connecting device. For example, the patent with the publication number CN114183212B, the classification number F01D25 / 34 and the patent name A steam turbine double turning gear device of a single-shaft combined cycle unit discloses a kind of engaging and disengaging locking clutch that can realize the engagement and disengagement between the turning gear and the rotor of the steam turbine. Figure 2 As shown in the patent, the steam turbine turning gear overrunning clutch of the steam turbine turning gear device is replaced by a synchronous automatic clutch with engagement and locking function, i.e., the engaging and locking clutch. The engaging and locking clutch mainly consists of a clutch input, a clutch sliding part, a clutch output, a locking part and an oil cylinder. The clutch input is connected with the original power source of the steam turbine turning gear, and the clutch output is connected with the steam turbine. The clutch sliding part is connected with the clutch input through a helical tooth pair. Under the action of the helical tooth pair, the clutch sliding part will produce axial movement and relative rotation with the clutch input, so that the driving teeth on the clutch sliding part and the driven teeth on the clutch output will axially coincide and separate, thereby realizing the engagement and disengagement of the engaging and locking clutch.

[0004] Therefore, the above-mentioned steam turbine double steering disc car device has the following technical problems: 1. Complex structure: (1) It is composed of multiple components: the existing engagement locking clutch is usually composed of multiple complex components, such as clutch input, clutch slip, clutch output, locking piece and oil cylinder, etc. The complex interworking and connection relationship between these components increases the complexity of the overall structure. (2) Multi-stage transmission: In order to realize the engagement and disengagement function, multi-stage gear transmission or complex mechanical structure is usually required in the prior art. This multi-stage transmission not only increases the number of components, but also greatly increases the mechanical complexity of the whole system. (3) High precision requirement: High precision is required between components to ensure accurate work during engagement and disengagement. This high precision requirement further increases the difficulty of manufacturing and assembly, resulting in more complex structure. 2. High manufacturing cost: (1) High precision machining: Due to the high precision machining and cooperation of each component, high precision machining equipment and process 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, high quality and high cost materials are usually selected. These materials are not only expensive, but also difficult to process, further increasing the cost. (3) Assembly difficulty: The complex structure and precise cooperation requirement makes the assembly process very complex, which requires professional technicians and equipment for operation, which not only increases the labor cost, but also may cause the assembly time to be prolonged, further increasing the manufacturing cost. 3. Large axial space occupation: (1) Multiple component arrangement: Since the engagement locking clutch is composed of multiple components, these components need to be arranged in a certain space in the axial direction. Especially in multi-stage transmission and complex mechanical structure, the axial dimensions of each component are added, resulting in a large axial space occupation of the whole device. (2) Transmission path design: In order to realize the engagement and disengagement function, the transmission path in the prior art is usually long, and multiple gears or slip members need to be arranged in the axial direction, which further increases the axial size. (3) Oil cylinder arrangement: As a driving component, the oil cylinder usually needs a certain space for installation and arrangement. In the existing design, the arrangement position and method of the oil cylinder often leads to a large axial space occupation of the whole device.

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

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

[0007] The technical scheme of the present application is: a disc engaging and automatic disengaging device comprises a static engaging part, and further comprises a sliding part, the static engaging part comprises a rotor and a fixed slide plug, the fixed slide plug is sleeved on the rotor, the fixed slide plug is provided with a plug slot with a spiral engaging surface, the spiral engaging surface has an inclination angle of 10-35 degrees; the sliding part comprises a movable slide plug, the plug teeth on the movable slide plug are inserted into the plug slot of the fixed slide plug and transmit power; when the rotor speed is higher than the movable slide plug speed by 8-15%, the axial component force generated by the spiral engaging surface makes the movable slide plug automatically disengage.

[0008] Preferably, the inclination angle of the spiral engaging surface is 18-28 degrees, and the surface roughness Ra of the spiral surface is less than or equal to 1.6 microns.

[0009] Further, the static engaging part further comprises an end limiting part, the end limiting part is installed at the end of the rotor for axially limiting the fixed slide plug.

[0010] Further, the static engaging part further comprises a rotor rotating installation part, the rotor rotating installation part comprises a first rolling bearing and a support seat, the rotor is a stepped shaft, and the rotor is connected with the support seat through the first rolling bearing.

[0011] Further, the sliding part comprises a transmission shaft and a movable slide plug, the transmission shaft is coaxially arranged with the rotor, and the movable slide plug is sleeved on the transmission shaft.

[0012] Further, the sliding part further comprises a sliding outer spline, and the movable slide plug is sleeved on the transmission shaft through the sliding outer spline.

[0013] Preferably, the movable slide plug is provided with a limiting groove in the circumferential direction.

[0014] Further, the sliding part further comprises a sliding guide sleeve, the sliding guide sleeve is tightly connected with the sliding outer spline, and forms an oil pressure driving chamber.

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

[0016] Further, the sliding part further comprises a driving device, and the driving device is connected with the oil inlet hole through a hydraulic pipeline.

[0017] Further, the sliding part further comprises a sliding outer spline limiting unit, the sliding outer spline limiting unit is sleeved on the transmission shaft and fixed on the outside of the sliding outer spline.

[0018] Further, the sliding outer spline limiting unit comprises a second locking plate and a third locking nut, the second locking plate is installed on the transmission shaft through the third locking nut, and the locking torque of the third locking nut is 120-150 N·m.

[0019] Further, it further comprises a limiting component, the limiting component comprises a positioning bolt and a lifting device, the telescopic end of the lifting device is connected with the upper end of the positioning bolt, the lower end of the positioning bolt is inserted into the limiting slot which is opened in the circumferential direction of the movable sliding plug, and the lifting device is a hydraulic oil cylinder.

[0020] Further, it further comprises a supporting component, the supporting component comprises an intermediate cover, a connecting flange and a supporting shaft sleeve, the supporting shaft sleeve supports the transmission shaft through the second rolling bearing; the intermediate cover is connected between the supporting seat and the connecting flange through a flange bolt assembly.

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

[0022] 1. The present application can effectively reduce the axial movement stroke, and the structure is simple and compact, which is embodied in that: the present application realizes the functions of engagement and automatic disengagement of the turning gear device by combining hydraulic drive and mechanical transmission, and in the process of engagement and automatic disengagement, the sliding plug connection of the movable sliding plug and the fixed sliding plug is realized only by driving the driving device.

[0023] The conventional engagement and locking clutch needs to drive multiple sets of gears horizontally by an oil cylinder to realize the engagement and driving disengagement of the turning gear device by whether the gears in different gear sets are engaged. By omitting multiple sets of gears, the equipment cost is reduced, and the axial stroke occupied by multiple sets of gears in the movement process is reduced, and the structure is more compact.

[0024] Therefore, the present application not only reduces the required stroke space in the axial direction of engagement and automatic disengagement, makes the structure more compact, still realizes the rotation and micro movement of the two, and the structure is more simple, convenient to start and stop, and flexible to disengage.

[0025] 2. The present application can realize the automatic disengagement between the turning gear device and the steam turbine rotor, which is embodied in that: in the automatic disengagement process, first, the driving device stops supplying high-pressure oil into the oil pressure driving chamber, the high-pressure oil in the oil pressure driving chamber leaks through the oil return hole, and when the rotational speed of the rotor is greater than that of the transmission shaft, the spiral engagement surface between the pin teeth of the movable sliding plug and the plug groove of the fixed sliding plug is automatically disengaged, thereby realizing the automatic disengagement function of the turning. It is not necessary for the staff to detect data and disengage the turning in real time, therefore, the present application can avoid damage caused by forgetting to close the turning gear device main body, and can be widely applied in the main machine field of steam turbines, gas turbines, motors and the like. BRIEF DESCRIPTION OF DRAWINGS

[0026] Figure 1 is the overall structure schematic diagram of the present application. Among them, the A area represents the structure schematic diagram of the movable sliding plug and the fixed sliding plug in the disengaged state; the B area represents the structure schematic diagram of the movable sliding plug and the fixed sliding plug in the engaged state.

[0027] Figure 2 is Figure 1 Local enlarged view at C.

[0028] In the figure: 1, end position limiting member, 2, first locking nut, 3, fixed slide, 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 washer, 12, second bolt, 13, middle cover, 14, support seat, 15, positioning bolt, 16, driving device, 17, transmission shaft, 18, third bolt, 19, transition positioning flange, 20, coupling 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 gear device body, 29, set screw, 30, sliding guide sleeve, 31, middle flange, 32, fourth bolt, 33, sliding outer spline, 34, screw rod, 35, second locking plate, 36, third locking nut, 37, movable slide, 38, limiting groove, 39, slot, 40, oil inlet hole, 41, oil return hole. DETAILED DESCRIPTION

[0029] Specific implementation one: combined Figure 1 and Figure 2 This embodiment is a turning gear engagement and automatic disengagement device, which comprises a static engagement component and a sliding component. The static engagement component comprises a rotor 8 and a fixed slide 3, and the fixed slide 3 is sleeved on the rotor 8. The fixed slide 3 is provided with a slot 39 with a spiral engagement surface, and the inclination angle of the spiral engagement surface is 10°-35°. The sliding component comprises a movable slide 37, and the teeth on the movable slide 37 are inserted into the slot 39 of the fixed slide 3 and transmit power. When the rotor 8 rotates at a speed higher than that of the movable slide 37 by 8%-15%, the axial component force generated by the spiral engagement surface causes the movable slide 37 to automatically disengage.

[0030] In the engagement or automatic disengagement process of the movable slide 37 and the fixed slide 3, by changing the structure and shape of the insertion part, when the rotor 8 rotates at a speed higher than that of the transmission shaft 17, the transmission shaft 17 is passively rotated by the rotor, and at this time, the oil supply has been stopped. Under the premise of no high-pressure oil, the engagement between the movable slide 37 and the fixed slide 3 is weak, and gradually separated by centrifugal force, and naturally and automatically disengaged at the spiral engagement surface. The whole automatic disengagement process is smooth, without jamming and vibration, ensuring smooth high-speed rotation of the rotor 8.

[0031] The rotational speed difference trigger range of the embodiment is preferably 10%-12% when automatically disengaging. At this time, the mechanical equilibrium point can be reached: for example, when the rotational speed difference reaches 10%, the axial component force generated by the helical engagement surface just overcomes the residual oil pressure resistance, frictional resistance and inertial force. When the rotational speed difference reaches 12%, the axial component force is 20% higher than the theoretical disengagement requirement, ensuring 100% reliability.

[0032] The embodiment integrates "mechanical coupling + hydraulic drive + intelligent disengagement" in a trinity design, which not only ensures functional reliability, but also achieves multiple goals of structural simplification, space saving and cost control. It is particularly suitable for the turning gear system of large steam turbine units above 300 MW, and has significant technical advancement and market application value.

[0033] The embodiment adopts a double sliding insertion coupling mechanism, specifically: a fixed sliding insertion 3 and a movable sliding insertion 37 are designed in a straight insertion type, and multiple stages of transmission are cancelled: the intermediate transmission components such as gear sets and synchronization rings required by traditional clutches are omitted, and the number of components is reduced by more than half. The axial space is effectively compressed: through coaxial straight insertion design, the axial installation size is reduced from more than 500mm of the traditional scheme to within 280mm, and the space utilization rate is increased by 40%.

[0034] In addition, the "straight insertion type design" of the embodiment can realize gapless transmission in actual use: the precise fit (tolerance 0.05-0.1mm) of the pin teeth and the insertion slot 39 realizes zero backlash power transmission, and the transmission efficiency reaches 98% (traditional gear transmission is about 92%). Since the helical engagement surface of the embodiment generates an axial pre-tightening force when transmitting torque, the impact resistance is enhanced, and the meshing impact of traditional tooth type clutches is avoided.

[0035] The automatic disengagement response of the embodiment is sensitive, because the invention sets up a rotational speed difference trigger mechanism: when the rotational speed of the rotor 8 exceeds 8%-15% of the movable sliding insertion 37, the axial component force generated by the helical engagement surface pushes the sliding component to disengage quickly, and the response time is <0.5 seconds.

[0036] Specific implementation method two: combination Figure 1 and Figure 2In the embodiment, the helical engagement surface has an inclination angle of 18°-28°, and the helical surface roughness Ra≤1.6 μm. In this way, the automatic disengagement reliability is optimized: the embodiment realizes accurate control of the disengagement force, the axial force generated by the inclination angle ensures reliable disengagement at a speed difference of 8%-15% (disengagement time is about 0.3-0.5 s), avoids the jamming caused by too small angle (the main reason for jamming is insufficient disengagement force), and prevents accidental disengagement caused by too large angle (the main reason for accidental disengagement is that the axial force is too large at this time). The embodiment uses low friction movement: the surface roughness Ra≤1.6 μm controls the friction coefficient μ to be 0.08-0.12 (under lubrication), which reduces the disengagement resistance by 30%. Through the above technical means, the power transmission performance of the embodiment can also be effectively improved, and the torque transmission capacity enables the 18°-28° inclination angle to realize 15 kN·m torque transmission under 5 MPa oil pressure (the traditional gear set requires 20°-40°). Since the embodiment uses a helical engagement surface to form a progressive contact when engaged, the impact load is reduced by 45% (compared with a straight tooth structure). The other components and connection relationships are the same as those in the first embodiment.

[0037] It should be noted that in the embodiment, the inclination angle of the helical engagement surface is preferably 20°-25°, at which the disengagement force and reliability are balanced: this range ensures that when the rotor speed exceeds the mobile sliding insertion by 8%-15%, the axial force generated by the helical engagement surface is sufficient to overcome the friction resistance (such as oil pressure residual force, inertial force), while avoiding the risk of accidental disengagement caused by too large angle. In addition, the 20°-25° inclination angle can form a stable axial pre-tightening force when transmitting torque, reducing the impact load.

[0038] When the inclination angle of the helical engagement surface is preferably 26°, the machining precision and surface roughness are matched: when the angle range and surface roughness are matched, the disengagement response time can be controlled to be 0.3-0.4 seconds, which is better than the delay risk of smaller angles. It can be disengaged more quickly under high-speed working conditions, avoiding jamming caused by vibration.

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

[0040] Specific embodiment three: combination Figure 1 and Figure 2To illustrate the embodiment, the static joint component of the embodiment further comprises an end position limiting member 1 installed at the end of the rotor 8 for axially limiting the fixed slide insert 3. In this way, the embodiment realizes an axial double locking mechanism, the end position limiting member 1 and the shoulder of the rotor 8 form a "clamping type" structure, the axial displacement of the fixed slide insert 3 is controlled within ±0.1mm, which ensures the precision when the pin teeth on the movable slide insert 37 are inserted into the slot 39 of the fixed slide insert 3. At the same time, it also plays a role in impact protection: at the moment of engagement of the movable slide insert 37, it can withstand an axial impact force of ≥8kN. The other components and connection relationships are the same as those in embodiment one or two.

[0041] Since the left end face of the fixed slide insert 3 is clamped on the shoulder of the rotor 8, the movement of the fixed slide insert 3 in the axial direction is limited, and the end position limiting member 1 is sleeved on the right end face of the fixed slide insert 3 and is fixed on the rotor 8 by the first locking nut 2. The axial limiting of the left and right sides of the fixed slide insert 3 by the shoulder and the end position limiting member 1 not only ensures the fixed effect of the fixed slide insert 3 in the normal rotation process, but also plays a role in resisting the impact on the fixed slide insert 3 during the sliding connection of the movable slide insert 37 and the fixed slide insert 3.

[0042] The wall thickness of the left side of the fixed slide insert 3 is greater than that of the right side of the fixed slide insert 3, and the wall thickness of the end position limiting member 1 is less than that of the right side of the fixed slide insert 3. By increasing the wall thickness of the left side of the fixed slide insert 3, the impact degree during the sliding connection of the movable slide insert 37 and the fixed slide insert 3 is increased, which ensures the smooth and safe connection of the movable slide insert 37 and the fixed slide insert 3.

[0043] By abutting one end of the fixed slide insert 3 against the shoulder of the rotor 8 and limiting the other end of the fixed slide insert 3 by the end position limiting member 1, the embodiment also ensures the firmness during the insertion of the movable slide insert 37, there is no horizontal displacement in the axial direction, and further ensures the accuracy of the insertion process.

[0044] Embodiment four: combination Figure 1 and Figure 2 To illustrate the embodiment, the static joint component of the embodiment further comprises a rotor rotating installation component, which comprises a first rolling bearing 4 and a support seat 14, the rotor 8 is a stepped shaft, and the rotor 8 is connected with the support seat 14 through the first rolling bearing 4. In this way, a stable reference speed signal is provided for the rotating speed difference detection. The other components and connection relationships are the same as those in embodiment one, two or three.

[0045] Embodiment five: combination Figure 1 and Figure 2The embodiment is described as follows. The slip component of the embodiment comprises a transmission shaft 17 coaxially arranged with the rotor 8 and a movable slip joint 37 sleeved on the transmission shaft 17. In this way, the embodiment realizes a power transmission hub, the coaxiality of the transmission shaft 17 and the rotor 8 is ≤0.05 mm, the torque transmission efficiency is ensured to be ≥98%, and the coaxial power coupling is realized. In addition, the hydraulic energy of the driving device 16 is converted into the axial mechanical movement of the movable slip joint 37 through hydraulic-mechanical conversion.

[0046] The embodiment is described as follows. The slip component of the embodiment comprises a transmission shaft 17 coaxially arranged with the rotor 8 and a movable slip joint 37 sleeved on the transmission shaft 17. In this way, the embodiment realizes a power transmission hub, the coaxiality of the transmission shaft 17 and the rotor 8 is ≤0.05 mm, the torque transmission efficiency is ensured to be ≥98%, and the coaxial power coupling is realized. In addition, the hydraulic energy of the driving device 16 is converted into the axial mechanical movement of the movable slip joint 37 through hydraulic-mechanical conversion.

[0047] Specific embodiment six: combination Figure 1 and Figure 2 The embodiment is described as follows. The slip component of the embodiment further comprises a slip outer spline 33, and the movable slip joint 37 is sleeved on the transmission shaft 17 through the slip outer spline 33. In this way, the function of a precision motion guide system is realized, and the high-precision axial movement straightness of the movable slip joint 37 is ensured through axial sliding control (H7 / g6 level matching tolerance is adopted). In addition, the torque is transmitted through the involute spline, and the transmission efficiency is high. Other components and connection relationships are the same as any one of the first to fifth specific embodiments.

[0048] Specific embodiment seven: combination Figure 1 and Figure 2 The embodiment is described as follows. The movable slip joint 37 of the embodiment is provided with a limiting groove 38 in the circumferential direction. In this way, the limiting groove 38 is preferably a circular limiting groove, so that the limiting end of the limiting component can be quickly and accurately inserted into the limiting groove 38, and the gap between the limiting groove 38 and the limiting end of the limiting component facilitates the quick and smooth insertion of the movable slip joint 37 into the limiting groove 38 after the movable slip joint 37 is disengaged, thereby realizing the axial limiting function of the movable slip joint 37. Other components and connection relationships are the same as any one of the first to sixth specific embodiments.

[0049] Specific embodiment eight: combination Figure 1 and Figure 2The sliding part of the embodiment further comprises a sliding guide sleeve 30, which is fastened with the sliding outer spline 33 to form an oil pressure driving chamber. The sliding guide sleeve 30 and the sliding outer spline 33 are fastened by a clamping screw 29. In this way, high-pressure oil can be injected into the oil pressure driving chamber, and the movable sliding insert 37 is driven by the high-pressure oil to slide horizontally along the sliding outer spline 33. The other components and connection relationships are the same as any one of embodiments 1 to 7.

[0050] The oil pressure driving chamber of the embodiment is the core of hydraulic power conversion, and forms a sealed chamber with the sliding outer spline 33 to convert hydraulic energy into mechanical thrust. The mechanical thrust drives the movable sliding insert 37 to move axially.

[0051] Embodiment 9: Combination Figure 1 and Figure 2 The movable sliding insert 37 of the embodiment is provided with an oil inlet hole 40 and an oil return hole 41. In this way, the sliding drive of the movable sliding insert 37 is realized by hydraulic drive, and the smooth engagement and automatic disengagement are ensured. The other components and connection relationships are the same as any one of embodiments 1 to 8.

[0052] The oil inlet hole 40 is a high-pressure oil inlet, which can withstand a working pressure of about 5 MPa, and the oil inlet flow is controlled at 15-20 L / min. Under this condition, the corresponding moving speed of the movable sliding insert 37 is about 50 mm / s. The oil return hole 41 is a low-pressure oil discharge channel, which has a fast pressure relief speed.

[0053] Embodiment 10: Combination Figure 1 and Figure 2 The sliding part of the embodiment further comprises a driving device 16, which is connected to the oil inlet hole 40 through a hydraulic pipeline. In this way, the driving device 16 can supply high-pressure oil to the oil pressure driving chamber through the oil inlet hole 40. The other components and connection relationships are the same as any one of embodiments 1 to 9.

[0054] Embodiment 11: Combination Figure 1 and Figure 2 The sliding part of the embodiment further comprises a sliding outer spline limiting unit, which is sleeved on the transmission shaft 17 and fixed outside the sliding outer spline 33. In this way, the axial movement is hard-limited, the stroke end control is provided, the maximum axial displacement of the movable sliding insert 37 is accurately limited, and the damage of the fixed sliding insert 3 caused by overshoot is prevented. The impact protection is also provided, and an impact load of 8 kN can be absorbed at the moment of engagement (by the pre-tightening force of 120-150 N·m of the third locking nut 36).

[0055] The slip outer spline limiting unit of the embodiment also plays a role in guaranteeing torque transmission, and can realize a loosening prevention mechanism: the second locking plate 35 and the third locking nut 36 form mechanical interlocking, and zero loosening is maintained at a high rotational speed. The torsional stiffness is enhanced, and the limiting unit greatly improves the torsional stiffness of the transmission shaft 17. The other components and connection relationships are the same as any one of embodiments one to ten.

[0056] Embodiment twelve: Figure 1 and Figure 2 This embodiment is described. The slip outer spline limiting unit of the embodiment includes a second locking plate 35 and a third locking nut 36, the second locking plate 35 is installed on the transmission shaft 17 through the third locking nut 36, and the locking torque of the third locking nut 36 is 120-150 N·m. In this way, the slip outer spline limiting unit is a dynamic loosening prevention system of the application, which can realize mechanical interlocking: the stopper of the second locking plate 35 is embedded in the key groove of the transmission shaft 17, and the 120-150 N·m pre-tightening force of the third locking nut 36 forms double locking. It can suppress vibration and maintain zero loosening at high speed. The other components and connection relationships are the same as any one of embodiments one to eleven.

[0057] The second locking plate 35 is sleeved on the transmission shaft 17 and simultaneously contacts the shoulder of the transmission shaft 17 and the slip outer spline 33, and is locked and fixed by the third locking nut 36, which is convenient for disassembly, assembly and maintenance.

[0058] Embodiment thirteen: Figure 1 and Figure 2 This embodiment is described. The embodiment also includes a limiting component, the limiting component includes a positioning bolt 15 and a lifting device, the extension end of the lifting device is connected with the upper end of the positioning bolt 15, and the lower end of the positioning bolt 15 is inserted into a limiting groove 38 opened in the circumferential direction of the movable slide 37, and the lifting device is a hydraulic oil cylinder. In this way, the function of axial mechanical locking is realized, especially the hard limiting function, which can withstand a large axial impact force. The other components and connection relationships are the same as any one of embodiments one to twelve.

[0059] The lifting device of the embodiment can have various implementation and replacement modes in actual use, such as a hydraulic oil cylinder or an air cylinder, which can realize quick, timely and accurate extension and retraction actions.

[0060] Embodiment fourteen: Figure 1 and Figure 1The embodiment is described, and the embodiment further comprises a support component, which comprises an intermediate cover 13, a coupling flange 20, and a support sleeve 22 supporting the transmission shaft 17 through a second rolling bearing 21; the intermediate cover 13 is connected with the support base 14 and the coupling flange 20 through a flange bolt assembly, wherein the intermediate cover 13 is connected with the support base 14 through a second bolt 12, and the intermediate cover 13 is connected with the coupling flange 20 through a third bolt 18. In this way, as a rigid framework of the system of the application, the rotor system and the turning gear main body 28 are connected as a whole through a plurality of high-strength bolts. The other components and connection relationships are the same as those in any one of the first to thirteenth embodiments.

[0061] The flange bolt assembly in the embodiment comprises an intermediate flange 31 and a transition positioning flange 19, and the intermediate cover 13 is connected with the coupling flange 20 through the intermediate flange 31, the transition positioning flange 19, and the third bolt 18, and the intermediate cover 13 is further connected with the intermediate flange 31 through a fourth bolt 32. The intermediate cover 13 is used to cover the structural members between the transmission shaft 17 and the rotor 8, and not only effectively connects the steam turbine and the turning gear main body 28, but also prevents dust and impurities in the external environment from entering the internal structure.

[0062] The intermediate flange 31 and the transition positioning flange 19 in the embodiment are combined and connected with the turning gear main body 28 through the coupling flange 20, thereby facilitating the effective connection between the steam turbine and the turning gear main body 28.

[0063] Embodiment Fifteen: Combination Figure 1 The embodiment is described, and the embodiment further comprises a retainer 23, an outer flange 24, and an end cover 26, the retainer 23 is embedded on the annular groove of the inner side wall of the support sleeve 22, the outer flange 24 is installed on the outer side of the retainer 23 through a first screw 25, and the end cover 26 is covered on the turning gear main body 28 through a second screw 27.

[0064] In this way, the transmission shaft 17 is protected, and the disassembly and maintenance are convenient.

[0065] Embodiment Sixteen: Combination Figure 1 The embodiment is described, and the static joint component of the embodiment further comprises a second locking nut 5, a first locking plate 6, and a first adjusting ring 7, the first adjusting ring 7 is sleeved on the rotor 8 and abuts against the inner ring of the first rolling bearing 4, the first locking plate 6 is sleeved on the rotor 8 and abuts against the first adjusting ring 7, and the first locking plate 6 is fixed through the second locking nut 5.

[0066] In this way, the first locking plate 6 and the first adjusting ring 7 limit the axial position of the first rolling bearing 4.

[0067] Specific embodiment seventeen: combination Figure 2 In this embodiment, the static joint part further comprises a second adjusting ring 9, a first bolt 10 and a first adjusting washer 11. The second adjusting ring 9 has a cross-sectional shape of "L", and is inserted into the support seat 14. The horizontal section of the second adjusting ring 9 abuts against the outer ring side end face of the first rolling bearing 4, and the vertical section of the second adjusting ring 9 is fixedly installed on the support seat 14 through the first bolt 10 and the first adjusting washer 11.

[0068] In this way, the inner ring and the outer ring on the left side of the first rolling bearing 4 abut against the rotor 8 and the shoulder of the support seat 14, respectively. The right side of the first rolling bearing 4 is limited in the axial direction by the first adjusting ring 7 and the second adjusting ring 9. The vibration and instability problems of the rotor 8 during high-speed rotation are effectively avoided, and the safe and stable high-speed operation of the entire steam turbine unit is ensured.

[0069] Specific embodiment eighteen: combination Figure 1 and Figure 2 In this embodiment, a screw rod 34 is further included. The transmission shaft 17 is processed with a through hole in the axial direction, and the screw rod 34 is processed with external threads and is inserted from the left side of the through hole of the transmission shaft and is threadedly connected with the through hole.

[0070] In this way, the through hole in the axial direction of the transmission shaft 17 and the radial hole constitute a hydraulic oil circuit for the oil flow of the oil inlet hole 40 and the oil return hole 41. The screw rod 34 threadedly connects and closes one end of the through hole, preventing high-pressure oil leakage and ensuring the sealing of the oil pressure driving chamber. The stability of the hydraulic system pressure is maintained, and the axial driving force of the movable sliding insert 37 is ensured. After the screw rod 34 is removed, the oil circuit can be cleaned or repaired, facilitating maintenance (such as removing impurities in the oil circuit).

[0071] Combination ​ and ​ The working principle of the present application is described.

[0072] I. The engagement principle between the steam turbine rotor and the turning gear of the present application.

[0073] The positioning pin 15 inserted into the limiting groove 38 of the movable sliding insert 37 is lifted by the lifting device, the driving device 16 drives the high-pressure oil from the oil inlet hole 40 of the transmission shaft 17 into the area enclosed by the sliding guide sleeve 30, the sliding outer spline 33 and the movable sliding insert 37 to form an oil pressure driving chamber, and drives the movable sliding insert 37 to move axially, until the movable sliding insert 37 is connected with the fixed sliding insert 3, the engagement of the turning gear main body 28 is completed, and the rotor 8 is driven to rotate; at this time, the oil inlet hole 40 is blocked, and the high-pressure oil cannot leak.

[0074] II. The automatic disengagement principle between the steam turbine rotor and the turning gear of the present application.

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

[0076] When the rotating speed of the rotor 8 is greater than the rotating speed of the transmission shaft 17 of the body 28 of the turning gear, the spiral engagement surface between the movable sliding insert 37 and the fixed sliding insert 3 is automatically decoupled, realizing the automatic decoupling function of the turning gear. At this time, the positioning pin 15 automatically falls into the limiting groove 38 of the movable sliding insert 37, preventing the axial movement of the movable sliding insert 37 and realizing the limiting function.

[0077] Although the present application has been disclosed in the above preferred embodiments, it is not intended to limit the present application, and those skilled in the art can make other changes within the spirit of the present application and apply the present application to fields not mentioned in the present application. Of course, these changes made according to the spirit of the present application should be included in the scope of protection required by the present application.

Claims

1. A barring engagement and automatic disengagement device, comprising a static engagement component, characterized in that: It also includes a sliding component and a limiting component, 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), a sliding external spline (33) and a sliding guide sleeve (30), the movable sliding plug (37) is sleeved on the transmission shaft (17) through the sliding external spline (33), and the sliding guide sleeve (30) is fastened to the sliding external spline (33) to form an oil pressure drive chamber; the spline on the movable 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 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; The movable sliding insert (37) is provided with a limiting groove (38) in the circumferential direction; the movable sliding insert (37) is processed with an oil inlet hole (40) and an oil return hole (41); The sliding component further includes a driving device (16), and the driving device (16) is connected to the oil inlet hole (40) through a hydraulic pipeline; The limiting component 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), 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), and the lifting device is a hydraulic cylinder.

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≤1.6 μm.

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 comprises a transmission shaft (17) and a movable sliding insert (37). The transmission shaft (17) is coaxially arranged with the rotor (8), and the movable sliding insert (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 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).

7. The barring gear engagement and automatic disengagement device according to claim 6, 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).

8. The barring gear engagement and automatic disengagement device according to claim 7, 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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