A turbine turning gear

Abstract

The application discloses a turbine turning gear, which comprises a turning gear assembly, a putting-in assembly and a rotor gear. The turning gear assembly comprises a first bevel gear and a second bevel gear. The second bevel gear is provided with a first cylindrical gear on a rotating shaft. The first cylindrical gear is engaged with a second cylindrical gear. The shaft end of the first bevel gear is provided with a manual turning gear and / or an automatic turning gear. The putting-in assembly comprises a rocker arm provided on the rotating shaft. The rocker arm rotates around the central shaft of the rotating shaft. The second cylindrical gear is rotatably arranged on the rocker arm. The two ends of the rocker arm are respectively provided with a manual putting-in device and / or an automatic putting-in device. The manual putting-in device and the automatic putting-in device are used to control the second cylindrical gear to engage with the rotor gear or to disengage the second cylindrical gear from the rotor gear. The manual turning gear and the automatic turning gear are used to adjust the gap between the gear teeth of the second cylindrical gear and the gear teeth of the rotor gear and drive the rotor gear to rotate. The application can greatly improve the putting-in success rate, reduce the possibility of gear wear and prolong the service life.

Description

Technical Field

[0001] This application relates to the field of steam turbine technology, and in particular to a steam turbine turning gear. Background Technology

[0002] Steam turbines are power machines that use steam as the working fluid to convert the thermal energy of steam into the mechanical energy of a rotating rotor. They are widely used in industries such as power, petrochemicals, and metallurgy.

[0003] Before the turbine starts, the turbine rotor is stationary. Since the heat flow of steam is upward, the upper part of the rotor is hotter and the lower part is colder. Due to the temperature difference, the rotor undergoes upward thermal deformation, causing it to bend. When the turbine starts, the moving and stationary parts rub and collide. After the turbine stops, the lower part of the turbine rotor cools down faster and is colder, while the upper part cools down slower and is colder. Due to the temperature difference, the rotor undergoes upward thermal deformation, causing it to bend. If the thermal bending of the rotor is large, the moving and stationary parts will rub and collide when the turbine starts.

[0004] To avoid the above situation, the turbine must be turned at low speed using a turning gear before startup and after shutdown to ensure uniform heating of the rotor. Existing turbine turning gears use worm gear reduction. Engagement is achieved by using a screw to engage the turning gear axially. During engagement, a pin holds a tooth on one side of the turning gear to prevent rotation. The motor is then started or the screw is manually rotated to move the turning gear axially until it meshes with the turbine rotor gear.

[0005] The aforementioned ejector pin is operated manually or hydraulically. An internal spring acts as a buffer. When the torque on the turning gear is too large, if the ejector pin force is insufficient, the turning gear will rotate. At this point, the turning gear cannot continue to move axially and engage. When the screw is rotated, causing the turning gear to move axially along the screw, two situations occur:

[0006] Case 1: If the teeth of the turning gear can be aligned with the gap between the teeth of the turbine rotor gear, then it can smoothly mesh with the turbine rotor gear.

[0007] Scenario 2: If the teeth of the turning gear are exactly aligned with the teeth of the turbine rotor gear, the turning gear will be blocked by the turbine rotor gear and cannot move axially. If the screw continues to rotate, the turning gear will be forced to rotate, compressing the spring inside the ejector pin. The turning gear will continue to rotate and will not mesh smoothly. It may even be pushed back to its initial disengaged position by the spring. In this case, the turbine rotor must be rotated by a certain angle, or the position of the ejector pin must be changed, so that when the teeth of the turning gear are blocked by the ejector pin, the angle of the turning gear relative to its previous position changes, causing the teeth of the turning gear to misalign with the teeth of the turbine rotor gear, satisfying Scenario 1, so that meshing can proceed smoothly.

[0008] The above-mentioned method of engaging the turning gear has a low probability of successful on-site engagement, requires multiple manual trials until it can be smoothly engaged, which is time-consuming and labor-intensive, and is not suitable for remote operation. The pin and turning gear experience significant wear and have a short lifespan.

[0009] Therefore, in view of the above-mentioned technical problems, how to improve the success rate of the commissioning of the turning gear is a technical problem that needs to be solved by those skilled in the art. Summary of the Invention

[0010] The purpose of this application is to provide a turbine turning gear device that has a high success rate of deployment, requires no manual intervention, has highly reliable remote operation capabilities, and a long service life.

[0011] To achieve the above objectives, this application provides a turbine turning gear, comprising:

[0012] The turning assembly includes a first bevel gear, a second bevel gear meshing with the first bevel gear, a first cylindrical gear coaxially rotating on the shaft of the second bevel gear, the first cylindrical gear meshing with the second cylindrical gear, and a manual turning component and / or an automatic turning component for controlling the rotation of the first bevel gear on the shaft end of the first bevel gear.

[0013] The input component includes a rocker arm disposed on the rotating shaft and rotatably disposed relative to the rotating shaft. The rocker arm rotates about the central axis of the rotating shaft. A second cylindrical gear is rotatably disposed on the rocker arm. Both ends of the rocker arm are respectively provided with a manual input component and / or an automatic input component for controlling the rocker arm to swing, so that the rocker arm drives the second cylindrical gear to revolve around the first cylindrical gear.

[0014] The manual engagement component and the automatic engagement component are used individually to control the revolution angle of the second cylindrical gear, so that the second cylindrical gear reaches the meshing position with the rotor gear of the steam turbine, or disengages the second cylindrical gear from the rotor gear.

[0015] Both the manual and automatic turning components are used individually to control the rotation of the second cylindrical gear, thereby adjusting the tooth clearance between the second cylindrical gear and the rotor gear, and driving the rotor gear to rotate after the second cylindrical gear meshes with the rotor gear.

[0016] Preferably, the turbine turning gear further includes a housing, in which the first bevel gear, the second bevel gear, the first cylindrical gear, the second cylindrical gear, and the rocker arm are located, and the shaft end of the first bevel gear passes through and is rotatably disposed on the upper wall of the housing, and the rotating shaft is rotatably disposed on the side wall of the housing.

[0017] Preferably, the automatic turning component is an electric motor, which is fixedly mounted on the upper wall of the housing via a circular flange, and the power end of the electric motor is coaxially connected to the shaft end of the first bevel gear.

[0018] Preferably, the manual turning component includes:

[0019] A ratchet is fitted around the outer circumference of the first bevel gear shaft end and located inside the circular flange, and the circular flange has a notch corresponding to the ratchet;

[0020] The first handle has a handle at the first end and a second end hinged to the upper wall of the box body;

[0021] The pawl has a first end hinged to the middle of the first handle, and a second end engaged with the ratchet through the notch. The pawl is provided with an elastic element for pressing the pawl onto the ratchet.

[0022] Preferably, the manual input component includes:

[0023] The mounting base is installed on the housing and corresponds to the first end of the rocker arm;

[0024] The second handle is hinged to the mounting base and has a handle at the first end;

[0025] The connecting rod has its first end hinged to the second end of the second handle, and its second end extends into the housing and is hinged to the first end of the rocker arm.

[0026] Specifically, pulling the second handle causes the connecting rod to lift upward or press downward on the first end of the rocker arm, so that the second cylindrical gear on the rocker arm meshes with or disengages from the rotor gear.

[0027] Preferably, a first spring is sleeved on the outer periphery of the connecting rod, and the two ends of the first spring abut against the rocker arm and the mounting base respectively, and have an initial compression amount;

[0028] When the second cylindrical gear is engaged with the rotor gear, the torque of the first spring on the rocker arm is less than the resultant torque of the first cylindrical gear and the rotor gear on the rocker arm.

[0029] When the second cylindrical gear is disengaged from the rotor gear, the torque of the first spring is greater than the torque of the first cylindrical gear on the rocker arm.

[0030] Preferably, the automatic dispensing component includes:

[0031] A hydraulic cylinder is mounted on the housing and corresponds to the second end of the rocker arm. The hydraulic cylinder has a piston inside, and a blind hole is provided on the piston along its direction of movement.

[0032] The push rod has a first end located inside the blind hole and a second end corresponding to the second end of the rocker arm, used to abut against the rocker arm to press down the second end of the rocker arm;

[0033] A second spring, located within the blind hole, abuts against the piston and the push rod respectively, and the second spring has an initial compression.

[0034] Preferably, a third spring is sleeved around the piston, with one end of the third spring disposed on the piston and the other end disposed on the side wall of the cylinder, for providing the piston with a spring force away from the rocker arm.

[0035] Preferably, the housing is provided with a positioning rod extending into the housing, the positioning rod is located on both sides of the second cylindrical gear, and an elongated hole corresponding to the shaft end of the second cylindrical gear is provided at the end of the positioning rod. The shaft end of the second cylindrical gear extends into the elongated hole and moves within the elongated hole. The elongated hole is used to limit the revolution angle of the second cylindrical gear.

[0036] Preferably, the rocker arm is mounted on the rotating shaft via a bearing, and the second cylindrical gear is mounted on the rocker arm via a bearing.

[0037] Compared to the aforementioned background technology, this application has functions such as automatic engagement, manual engagement, automatic gear turning, manual gear turning, and automatic disengagement. During gear turning, the rotation of the second cylindrical gear is controlled by a manual or automatic gear turning component. This allows for fine-tuning of the second cylindrical gear's rotation, making it easier for the second cylindrical gear and rotor gear to mesh. Furthermore, continuous manual or automatic gear turning is possible after engagement. During engagement, the swing of the rocker arm is controlled by manual or automatic engagement components at both ends, causing the second cylindrical gear to revolve around the first cylindrical gear. After a certain degree of revolution, it engages or disengages with the rotor gear. During automatic disengagement, when the linear velocity of the rotor gear's meshing point exceeds the linear velocity of the second cylindrical gear's meshing point, the rocker arm automatically swings in the disengagement direction under the force of the rotor gear, thus achieving the automatic disengagement function.

[0038] It should be noted that when the second cylindrical gear meshes with the rotor gear, if the teeth of the second cylindrical gear exactly correspond to the gap between the teeth of the rotor gear, the meshing of the second cylindrical gear and the rotor gear is directly controlled by manual or automatic engagement. If the teeth of the second cylindrical gear correspond to the teeth of the rotor gear, the rotation angle of the second cylindrical gear is finely adjusted by manual or automatic turning mechanisms to ensure that the teeth of the second cylindrical gear exactly correspond to the gap between the teeth of the rotor gear, thus completing the engagement operation. Therefore, the turning device configured in the above manner can significantly improve the engagement success rate, requires no manual intervention, and has a flexible and reliable automatic disengagement action, reducing the possibility of gear wear and extending service life. Attached Figure Description

[0039] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only embodiments of this application. For those skilled in the art, other drawings can be obtained based on the provided drawings without creative effort.

[0040] Figure 1 This is a cross-sectional view of the turbine turning gear provided in an embodiment of this application;

[0041] Figure 2 This is an internal assembly drawing of the housing provided in an embodiment of this application;

[0042] Figure 3 This is an exploded view of the internal assembly of the housing provided in an embodiment of this application;

[0043] Figure 4 This is an external view of the turbine turning gear provided in an embodiment of this application;

[0044] Figure 5 This is a schematic diagram of the disengaged state of the second cylindrical gear and the rotor gear provided in the embodiments of this application;

[0045] Figure 6 This is a schematic diagram illustrating the successful manual input status provided in an embodiment of this application;

[0046] Figure 7 A schematic diagram showing the top teeth of the second cylindrical gear and the rotor gear in the manually engaged state, as provided in an embodiment of this application.

[0047] Figure 8 This is a schematic diagram of the automatic deployment success status provided in an embodiment of this application;

[0048] Figure 9 A schematic diagram showing the top teeth of the second cylindrical gear and the rotor gear in the automatic engagement state provided in the embodiments of this application;

[0049] Figure 10 This is a schematic diagram of the normal turning state provided in the embodiments of this application.

[0050] In the diagram: 1. Electric motor; 2. Round flange; 3. Housing; 4. First bevel gear; 5. Second handle; 6. First handle; 7. Second bevel gear; 8. First cylindrical gear; 9. Second cylindrical gear; 10. Rocker arm; 11. Mounting base; 12. First spring; 13. Connecting rod; 14. Oil cylinder; 15. Oil inlet; 16. Piston; 17. Second spring; 18. Third spring; 19. Push rod; 20. Flange; 21. Positioning rod; 22. Pawl; 23. Ratchet; 24. Shaft; 25. Bearing; 26. Rotor gear. Detailed Implementation

[0051] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0052] It should be noted that in this embodiment, the orientation or positional relationship indicated by terms such as "upper," "lower," "front," and "rear" is based on the orientation or positional relationship shown in the accompanying drawings. It is used only for the convenience of describing this application and for simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation of this application. Furthermore, "first," "second," "third," and "fourth" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0053] To enable those skilled in the art to better understand the present application, the present application will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0054] like Figure 1 As shown, in this embodiment, a turbine turning gear device is provided. The device includes a turning gear assembly and an engagement assembly. Turning refers to the use of a power device to rotate the rotor at a low speed before the turbine starts up and after it stops. Engaging refers to the action of engaging the gears of the turning gear device with the gears on the turbine rotor, at which time the turning gear device can drive the rotor to rotate.

[0055] The aforementioned turning gear assembly includes a first bevel gear 4, a second bevel gear 7, a first cylindrical gear 8, and a second cylindrical gear 9. The first bevel gear 4 meshes with the second bevel gear 7, and the first cylindrical gear 8 meshes with the second cylindrical gear 9. Furthermore, the first cylindrical gear 8 and the second bevel gear 7 are coaxially rotatable. Please refer to... Figure 1In this case, when the first bevel gear 4 rotates, it drives the second bevel gear 7 to rotate, thereby relying on the coaxial transmission of the rotating shaft 24 to drive the first cylindrical gear 8 to rotate synchronously, thereby driving the second cylindrical gear 9 to move.

[0056] The first bevel gear 4 is provided with a manual turning component and / or an automatic turning component to control the rotation of the first bevel gear 4. That is to say, this application may provide only a manual turning component or an automatic turning component, or both at the same time. However, for manual and automatic turning, the first bevel gear 4 needs to be controlled separately to avoid the conflict caused by controlling both at the same time.

[0057] The input component includes a rocker arm 10 mounted on and rotatably mounted relative to the rotating shaft 24. The rocker arm 10 rotates about the central axis of the rotating shaft 24. A second cylindrical gear 9 is rotatably mounted on the rocker arm 10. Based on the above embodiment, it is known that the second cylindrical gear 9 meshes with the first cylindrical gear 8. Therefore, during the swinging process of the rocker arm 10, the second cylindrical gear 9 will inevitably revolve around the first cylindrical gear 8, thereby adjusting the position of the second cylindrical gear 9 to facilitate meshing or disengaging with the rotor gear 26.

[0058] Manual and / or automatic input components are respectively provided at both ends of the rocker arm 10 to control the rocker arm 10 to swing. Similarly, this application may provide only manual or automatic input components, or both at the same time, as long as the control of the rocker arm 10 swings by the two components does not conflict. This will not be described in detail here.

[0059] It should be noted that using manual or automatic turning components alone, or using manual or automatic input components alone, will not cause any conflict with the turning and input operations. Therefore, they will not be described in detail here. Instead, we will take the simultaneous use of manual and automatic turning components, as well as manual and automatic input components, as examples.

[0060] Both the manual and automatic engagement components are used individually to control the revolution angle of the second cylindrical gear 9, so that the second cylindrical gear 9 reaches the meshing position with the rotor gear 26 of the steam turbine, or disengages the second cylindrical gear 9 from the rotor gear 26.

[0061] Both the manual and automatic turning mechanisms are used individually to control the rotation of the second cylindrical gear 9, adjusting the gap between the teeth of the second cylindrical gear 9 and the teeth of the rotor gear 26. After the second cylindrical gear 9 meshes with the rotor gear 26, it drives the rotor gear 26 to rotate, thereby achieving the purpose of normal turning.

[0062] In summary, this application has functions such as automatic engagement, manual engagement, automatic gear turning, manual gear turning, and automatic disengagement. During gear turning, the rotation of the second cylindrical gear 9 is controlled by a manual or automatic gear turning component. This allows for fine-tuning of the rotation of the second cylindrical gear 9, making it easier for the second cylindrical gear 9 and the rotor gear 26 to mesh. Furthermore, continuous manual or automatic gear turning is possible after engagement. During engagement, the swing degree of the rocker arm 10 is controlled by the manual or automatic engagement components at both ends, thereby driving the second cylindrical gear 9 to revolve around the first cylindrical gear 8. After a certain degree of revolution, it engages or disengages with the rotor gear 26. During automatic disengagement, when the linear velocity of the rotor gear 26 at the meshing point exceeds the linear velocity of the second cylindrical gear 9 at the meshing point, the rocker arm 10 automatically swings in the disengagement direction under the force of the rotor gear 26, thus achieving the automatic disengagement function. It should be noted that when the second cylindrical gear 9 meshes with the rotor gear 26, if the teeth of the second cylindrical gear 9 correspond exactly to the gap between the teeth of the rotor gear 26, the meshing of the second cylindrical gear 9 and the rotor gear 26 is directly controlled by manual or automatic engagement. If the teeth of the second cylindrical gear 9 correspond to the teeth of the rotor gear 26, the rotation angle of the second cylindrical gear 9 is finely adjusted by manual or automatic turning mechanisms to ensure that the teeth of the second cylindrical gear 9 correspond exactly to the gap between the teeth of the rotor gear 26, thus completing the engagement operation. Therefore, the turning device configured in the above manner can significantly improve the engagement success rate, requires no manual intervention, and has a flexible and reliable automatic disengagement action, reducing the possibility of gear wear and extending service life.

[0063] Please refer to Figure 1 The turning device of this application also includes a housing 3, and the first bevel gear 4, the second bevel gear 7, the first cylindrical gear 8, the second cylindrical gear 9, and the rocker arm 10 are all located inside the housing 3. The shaft end of the first bevel gear 4 passes through and is rotatably mounted on the upper wall of the housing 3, and the rotating shaft 24 is rotatably mounted on the side wall of the housing 3. The rotatable connection between the shaft and the outer wall of the housing 3 can be achieved by bearings 25, which will not be described in detail here.

[0064] Similarly, please refer to Figure 3 The rocker arm 10 can also be rotatably mounted on the rotating shaft 24 via the bearing 25, and the second cylindrical gear 9 is mounted on the rocker arm 10 via the bearing 25. Therefore, the second cylindrical gear 9 can revolve around the first cylindrical gear 8 at a certain angle, thereby realizing the meshing and disengagement of the second cylindrical gear 9 with the rotor gear 26.

[0065] The aforementioned automatic turning component is an electric motor 1. The electric motor 1 is fixed to the upper wall of the housing 3 via a round flange 2, and the power end of the electric motor 1 is coaxially connected to the shaft end of the first bevel gear 4, thereby driving the first bevel gear 4 to rotate, thus realizing the automatic turning function.

[0066] In addition, the manual cranking components include ratchet 23, first handle 6 and 22, please refer to... Figure 2 and Figure 4 The ratchet 23 is sleeved on the outer circumference of the shaft end of the first bevel gear 4 and is located within the range corresponding to the circular flange 2, and a notch is provided on the circular flange 2; the first end of the first handle 6 has a handle, and the second end is hinged to the upper wall of the housing 3, thereby realizing the rotation setting of the first handle 6; the first end of the pawl 22 is hinged to the middle of the first handle 6, and the second end of the pawl 22 cooperates with the ratchet 23 through the above-mentioned notch. The pawl 22 is provided with an elastic element for pressing the pawl 22 onto the ratchet 23, and the elastic element can be a spring.

[0067] It should be noted that by pulling the first handle 6, the pawl 22 drives the ratchet 23 to rotate, thereby driving the first bevel gear 4 to rotate. During the process of the pawl 22 driving the ratchet 23, due to the presence of the elastic element, the pawl 22 can automatically return to the next ratchet tooth of the ratchet 23, thereby realizing continuous manual turning operation.

[0068] It is worth noting that the rotation direction of the ratchet 23 must be consistent with the driving direction of the motor 1, and since the ratchet 23 can only rotate in one direction, the driving direction of the motor 1 will not conflict with the pawl 22.

[0069] The aforementioned manual input components include mounting base 11, second handle 5, and connecting rod 13. Please refer to... Figures 1 to 3 The mounting base 11 is fixed on the housing 3 and corresponds to the first end of the rocker arm 10. The second handle 5 is hinged to the mounting base 11, and the first end has a handle for pulling the second handle 5. The first end of the connecting rod 13 is hinged to the second end of the second handle 5, and the second end of the connecting rod 13 extends into the housing 3 and is hinged to the first end of the rocker arm 10.

[0070] It should be noted that when the second handle 5 is pulled to rotate, it can drive the connecting rod 13 to lift up or press down the first end of the rocker arm 10, thereby causing the second cylindrical gear 9 on the rocker arm 10 to revolve, so as to realize the meshing or disengagement of the second cylindrical gear 9 with the rotor gear 26.

[0071] A first spring 12 is sleeved on the outer periphery of the connecting rod 13. The two ends of the first spring 12 abut against the rocker arm 10 and the mounting base 11 respectively, and have an initial compression.

[0072] When the second cylindrical gear 9 is engaged with the rotor gear 26, the torque of the first spring 12 on the rocker arm 10 is less than the combined torque of the first cylindrical gear 8 and the rotor gear 26 on the rocker arm 10. In other words, when engaged, the rotation of the shaft 24 will drive the first cylindrical gear 8 to rotate, thus converting the rotational motion of the shaft 24 into a portion of the torque of the rocker arm 10 through the bearing 25. During the process of the second cylindrical gear 9 driving the rotor gear 26 to rotate, there is also a certain torque between the two, which acts on the rocker arm 10, thereby forming a combined torque that overcomes the elastic force of the first spring 12, ensuring that the second cylindrical gear 9 and the rotor gear 26 are properly engaged.

[0073] When the rotor gear 26 relies on the power of the steam turbine, causing the linear velocity of the meshing point of the rotor gear 26 to exceed the linear velocity of the meshing point of the second cylindrical gear 9, the second cylindrical gear 9 cannot provide driving force. Therefore, there is no torque between it and the rotor gear 26. At this time, the torque of the first spring 12 on the rocker arm 10 is greater than the torque of the first cylindrical gear 8 on the rocker arm 10. Therefore, the rocker arm 10 automatically swings in the disengagement direction under the force of the rotor gear 26, and under the elastic force of the first spring 12, the rocker arm 10 drives the second cylindrical gear 9 to automatically move away from the rotor gear 26, keeping the second cylindrical gear 9 in the disengaged position.

[0074] Please refer to Figure 5 At this time, the second handle 5 drives the rocker arm 10 to swing at a certain angle through the connecting rod 13, so that the second cylindrical gear 9 meshes with the rotor gear 26. After meshing, as... Figure 6 As shown, the second cylindrical gear 9 then drives the rotor gear 26 to rotate, realizing normal turning operation, as follows. Figure 10 As shown.

[0075] Of course, there is another situation, please refer to... Figure 7 The teeth of the second cylindrical gear 9 correspond to the teeth of the rotor gear 26, but they cannot mesh at this point. It is necessary to fine-tune the rotation angle of the second cylindrical gear 9 using a manual or automatic turning mechanism to align the gap between the teeth of the second cylindrical gear 9 and the teeth of the rotor gear 26. Then, continue pulling the second handle 5 to fully engage the second cylindrical gear 9 and the rotor gear 26. After engagement, as shown... Figure 6 As shown, this enables normal turning operations.

[0076] The aforementioned automatic engagement components include hydraulic cylinder 14, push rod 19, and second spring 17. Please refer to [reference needed]. Figure 1The hydraulic cylinder 14 is mounted on the housing 3 and corresponds to the second end of the rocker arm 10. The hydraulic cylinder 14 has a piston 16 inside, and a blind hole is formed on the piston 16 along its direction of movement. The first end of the push rod 19 is located in the blind hole, and the second end of the push rod 19 corresponds to the second end of the rocker arm 10 and is used to hold the second end of the rocker arm 10. Thus, the extension action of the push rod 19 presses the second end of the rocker arm 10 downward to realize the automatic engagement function.

[0077] It should be noted that a third spring 18 is sleeved on the outer periphery of the piston 16. One end of the third spring 18 is set on the piston 16, and the other end is set on the side wall of the oil cylinder 14, which is used to provide the piston 16 with a spring force away from the rocker arm 10.

[0078] exist Figure 5 Based on this, pressurized oil enters the oil cylinder 14 through the oil inlet 15, pushing the piston 16 downward. Then, the piston 16 pushes the push rod 19 downward through the second spring 17. The push rod 19 pushes the rocker arm 10 to swing, causing the second cylindrical gear 9 to mesh with the rotor gear 26. After meshing, as... Figure 8 As shown, the second cylindrical gear 9 then drives the rotor gear 26 to rotate, realizing normal turning operation, as follows. Figure 10 As shown.

[0079] Of course, there is another situation with automatic turn signals; please refer to [the relevant documentation]. Figure 9 The teeth of the second cylindrical gear 9 correspond to the teeth of the rotor gear 26, but they cannot mesh at this time. The piston 16 continues to move downward under the action of oil pressure, while the push rod 19 cannot continue to move downward. Therefore, the second spring 17 will be continuously compressed. It is necessary to finely adjust the rotation angle of the second cylindrical gear 9 by manual or automatic turning mechanism so that the gap between the teeth of the second cylindrical gear 9 and the teeth of the rotor gear 26 corresponds. The second spring 17 immediately fixes the push rod 19 at the second end of the rocker arm 10 and continues to press the rocker arm 10 downward, so that the second cylindrical gear 9 and the rotor gear 26 quickly mesh into place.

[0080] When the second cylindrical gear 9 is correctly meshed with the rotor gear 26, and the motor 1 starts, the controller automatically cuts off the oil supply to the hydraulic device. The piston 16 automatically retracts under the action of the third spring 18. Under the combined force of the first cylindrical gear 8 and the rotor gear 26, the second cylindrical gear 9 overcomes the spring force of spring a and remains meshed with the rotor gear 26. This is the normal operating state of the turning gear. Please refer to... Figure 10 .

[0081] Furthermore, the housing 3 is equipped with positioning rods 21 extending into the housing 3. The positioning rods 21 are located on both sides of the second cylindrical gear 9, and elongated holes corresponding to the shaft ends of the second cylindrical gear 9 are formed at the ends of the positioning rods 21. The shaft ends of the second cylindrical gear 9 extend into the elongated holes and move within them, thereby limiting the revolution angle of the second cylindrical gear 9 and preventing excessive revolution. The positioning rods 21 directly adjust and position the shaft of the second cylindrical gear 9, providing good positioning rigidity and avoiding additional bending moments on the shaft of the second cylindrical gear 9. This reduces the load on each bearing 25 and improves the service life of the turning device.

[0082] Regarding the initial compression of the first spring 12 and the second spring 17, springs with different stiffnesses can be selected according to the different output torques of the rocker arm 10. However, during automatic engagement, the stiffness of the second spring 17 should ensure that the piston 16 can drive the entire rocker arm 10 to move. For different models, the lengths of the connecting rod 13 and the push rod 19 are adjustable to adapt to the meshing position of the first cylindrical gear 8 of different models. For models with significant differences in meshing positions, flanges 20 of different heights can be replaced. Flanges 20 can be adapted to various existing bearing housings without changing the existing bearing housing design, thus significantly reducing the cost of upgrades.

[0083] With all components remaining unchanged, the turning gear direction can be altered simply by changing the assembly direction of parts such as the input mechanism and the ratchet 23 and pawl 22 of the manual turning gear. This allows for adaptation to turbine models with different turning directions, thus reducing product variety and lowering design and manufacturing costs and errors. During the design phase, for models with sufficient space, the turning gear direction can also be changed by replacing the appropriate flange 20 and rotating the entire turning gear horizontally by 180° to adapt to units with different turning directions.

[0084] Furthermore, by changing the transmission gear ratios of the aforementioned gears or replacing the motor 1 or hydraulic cylinder 14 with different speeds and power, different output speeds and torques can be obtained for the turning gear. Therefore, the design speed range is wide, which can meet the turning speed requirements of different models. The manual and automatic input components are installed outside the housing 3, thus facilitating debugging, installation, and maintenance.

[0085] It should be noted that in this specification, relational terms such as first and second are used only to distinguish one entity from several other entities, and do not necessarily require or imply any such actual relationship or order between these entities.

[0086] This document uses specific examples to illustrate the principles and implementation methods of this application. The descriptions of the embodiments above are only for the purpose of helping to understand the method and core ideas of this application. It should be noted that those skilled in the art can make several improvements and modifications to this application without departing from the principles of this application, and these improvements and modifications also fall within the protection scope of the claims of this application.

Claims

1. A turbine turning gear device, characterized in that, include: The turning assembly includes a first bevel gear, a second bevel gear meshing with the first bevel gear, a first cylindrical gear coaxially rotating on the shaft of the second bevel gear, the first cylindrical gear meshing with the second cylindrical gear, and a manual turning component and / or an automatic turning component for controlling the rotation of the first bevel gear on the shaft end of the first bevel gear. The input component includes a rocker arm disposed on the rotating shaft and rotatably disposed relative to the rotating shaft. The rocker arm rotates about the central axis of the rotating shaft. A second cylindrical gear is rotatably disposed on the rocker arm. The two ends of the rocker arm are respectively provided with a manual input component and / or an automatic input component for controlling the rocker arm to swing, so that the rocker arm drives the second cylindrical gear to revolve around the first cylindrical gear. The manual engagement component and the automatic engagement component are used individually to control the revolution angle of the second cylindrical gear, so that the second cylindrical gear reaches the meshing position with the rotor gear of the steam turbine, or disengages the second cylindrical gear from the rotor gear. Both the manual and automatic turning components are used individually to control the rotation of the second cylindrical gear, thereby adjusting the tooth clearance between the second cylindrical gear and the rotor gear, and driving the rotor gear to rotate after the second cylindrical gear meshes with the rotor gear.

2. The turbine turning gear device according to claim 1, characterized in that, It also includes a housing, in which the first bevel gear, the second bevel gear, the first cylindrical gear, the second cylindrical gear, and the rocker arm are located. The shaft end of the first bevel gear passes through and is rotatably disposed on the upper wall of the housing, and the rotating shaft is rotatably disposed on the side wall of the housing.

3. The turbine turning gear device according to claim 2, characterized in that, The automatic turning component is an electric motor, which is fixedly mounted on the upper wall of the housing via a round flange. The power end of the electric motor is coaxially connected to the shaft end of the first bevel gear.

4. The turbine turning gear device according to claim 3, characterized in that, The manual turning mechanism includes: A ratchet is fitted around the outer circumference of the first bevel gear shaft end and located inside the circular flange, and the circular flange has a notch corresponding to the ratchet; The first handle has a handle at the first end and a second end hinged to the upper wall of the box body; The pawl has a first end hinged to the middle of the first handle, and a second end engaged with the ratchet through the notch. The pawl is provided with an elastic element for pressing the pawl onto the ratchet.

5. The turbine turning gear device according to claim 2, characterized in that, The manual input component includes: The mounting base is installed on the housing and corresponds to the first end of the rocker arm; The second handle is hinged to the mounting base and has a handle at the first end; The connecting rod has its first end hinged to the second end of the second handle, and its second end extends into the housing and is hinged to the first end of the rocker arm. Specifically, pulling the second handle causes the connecting rod to lift upward or press downward on the first end of the rocker arm, so that the second cylindrical gear on the rocker arm meshes with or disengages from the rotor gear.

6. The turbine turning gear device according to claim 5, characterized in that, A first spring is sleeved on the outer periphery of the connecting rod. The two ends of the first spring abut against the rocker arm and the mounting base respectively, and have an initial compression amount. When the second cylindrical gear is engaged with the rotor gear, the torque of the first spring on the rocker arm is less than the resultant torque of the first cylindrical gear and the rotor gear on the rocker arm. When the second cylindrical gear is disengaged from the rotor gear, the torque of the first spring is greater than the torque of the first cylindrical gear on the rocker arm.

7. The turbine turning gear device according to claim 6, characterized in that, The automatic dispensing component includes: A hydraulic cylinder is mounted on the housing and corresponds to the second end of the rocker arm. The hydraulic cylinder has a piston inside, and a blind hole is provided on the piston along its direction of movement. The push rod has a first end located inside the blind hole and a second end corresponding to the second end of the rocker arm, used to abut against the rocker arm to press down the second end of the rocker arm; A second spring, located within the blind hole, abuts against the piston and the push rod respectively, and the second spring has an initial compression.

8. The turbine turning gear according to claim 7, characterized in that, A third spring is fitted around the piston, with one end of the third spring on the piston and the other end on the side wall of the cylinder, to provide the piston with a spring force away from the rocker arm.

9. The turbine turning gear device according to claim 2, characterized in that, The housing is provided with a positioning rod extending into the housing. The positioning rod is located on both sides of the second cylindrical gear, and an elongated hole corresponding to the shaft end of the second cylindrical gear is opened at the end of the positioning rod. The shaft end of the second cylindrical gear extends into the elongated hole and moves within the elongated hole. The elongated hole is used to limit the revolution angle of the second cylindrical gear.

10. The turbine turning gear according to any one of claims 1-9, characterized in that, The rocker arm is mounted on the rotating shaft via bearings, and the second cylindrical gear is mounted on the rocker arm via bearings.

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