Variable rotational inertia flywheel

Abstract

The invention relates to the technical field of flywheels, and particularly discloses a variable rotational inertia flywheel which comprises a flywheel body, an inertia disc, a bayonet lock piece and an elastic driving assembly. The flywheel body is formed by matching a bottom disc body and a top disc body, the bottom disc body and the top disc body are enclosed to form a sealed mounting groove, the inertia disc rotates relative to the flywheel body through a bearing, the bayonet lock piece and the elastic driving assembly are arranged in the mounting groove, and a meshing part of the bayonet lock piece is matched with a matching part of the inertia disc for separation and reunion. High-speed and low-speed rotational inertia can be adjusted, and operation is stable.

Description

Technical Field

[0001] This invention relates to the field of flywheel technology, specifically a flywheel with variable moment of inertia. Background Technology

[0002] Currently, single-cylinder and multi-cylinder engines are prone to vibration and resonance when running at low speeds. The resonance speed characteristics are as follows: when the inertia increases, the engine can run stably at a lower speed; when the inertia decreases, the engine needs to run at a higher speed.

[0003] In existing technologies, inertia adjustment is a continuous change, which has limited effect on suppressing first- and second-order torsional vibrations at low speeds; and linear adjustment with a single spring is prone to causing jerking during inertia switching, making it impossible to balance low-speed smoothness and high-speed dynamics.

[0004] The purpose of this invention is to provide a variable moment of inertia flywheel to solve the problems mentioned in the background art. Summary of the Invention

[0005] To achieve the above objectives, the present invention provides a variable moment of inertia flywheel, comprising a flywheel body, an inertia disk, a locking pin, and an elastic drive assembly; The flywheel body includes a bottom disc and a top disc. The bottom of the top disc has an annular groove, which is connected and fixed to the outside of the bottom disc and the top of the annular plate. The bottom disc has multiple guide blocks, each with a mounting groove. The top surface of the bottom disc has an annular plate, which has a guide plate that matches each guide block. The guide plate of the annular plate seals the top surface of the mounting groove. The inertia disk is coaxially mounted inside the flywheel body. The inertia disk slides and fits against the guide plate on the inner wall of the top disk and the ring plate respectively. A bearing is provided at the center of the bottom disk. The inertia disk is fixedly sleeved on the outer wall of the bearing and can rotate relative to the flywheel body. The locking pin is slidably disposed in the mounting groove, with one end extending toward the inertia disk and the other end abutting against the elastic drive component. The elastic drive component is disposed in the mounting groove and is used to drive the locking pin to move toward the inertia disk. The end of the locking pin near the inertia disk is provided with an engagement part, and the outer circumferential surface of the inertia disk is provided with a mating part adapted to the engagement part. When the engagement part and the mating part are engaged, the inertia disk and the flywheel body form a rotating integrated structure. When the engagement part and the mating part are disengaged, the inertia disk and the flywheel body are released from rotational constraint and can rotate relative to each other. Through the split flywheel body and the sealed mounting groove structure, reliable disengagement and engagement switching between the inertia disk and the flywheel body is realized, ensuring that the high and low speed rotational inertia is adjustable and the operation is stable.

[0006] As a further improvement of the present invention, the locking pin and the mounting groove are in clearance fit. The locking pin is radially guided by the inner wall of the mounting groove. The clearance fit between the locking pin and the mounting groove and the inner wall constraint and guidance ensure the linear movement of the locking pin and improve the accuracy of engagement and disengagement.

[0007] As a further improvement of the present invention, each outer periphery of the locking pin is provided with an axially penetrating venting groove. The axially penetrating venting groove on the outer periphery of the locking pin eliminates air damping during movement, making the locking pin move more smoothly and respond faster.

[0008] As a further improvement of the present invention, the meshing part includes a rectangular protrusion, and the mating part includes a rectangular slot adapted to the rectangular protrusion. The rectangular protrusion and the rectangular slot engage and engage to achieve effective engagement and disengagement of the inertia disk and the flywheel body, thereby meeting the basic inertia switching requirements.

[0009] As a further improvement of the present invention, a sealing ring is provided between the bottom plate and the top plate, and multiple exhaust holes are also provided on the top plate. The exhaust holes are used to install one-way exhaust valves. The sealing ring between the bottom plate and the top plate enhances the sealing effect, prevents impurities from entering and internal lubricating oil from leaking, and improves the reliability of the internal structure. The one-way exhaust valve installed in the exhaust hole is used to balance the air pressure inside and outside the flywheel body.

[0010] As a further improvement of the present invention, the meshing part further includes a wedge-shaped meshing surface, and the mating part further includes a wedge-shaped groove adapted to the wedge-shaped meshing surface. The wedge-shaped meshing surface and the wedge-shaped groove engage and lock together, forming a centrifugal force self-locking engagement, ensuring that the locking pin and the inertia disk are firmly engaged during low-speed / medium-speed operation, and preventing loosening and slippage.

[0011] As a further improvement of the present invention, a guide slope is provided at the entrance of the wedge-shaped slot. The opening angle of the guide slope is greater than the inclination angle of the slot wall of the wedge-shaped slot. The guide slope at the entrance of the wedge-shaped slot facilitates the smooth entry of the locking pin into the slot, thereby improving the meshing power and reset accuracy.

[0012] As a further improvement of the present invention, the side of the locking pin is provided with a positioning boss, and the inner wall of the mounting groove is provided with a positioning groove adapted to the positioning boss. The positioning boss is slidably disposed in the positioning groove. The positioning boss and the positioning groove cooperate to further limit the deflection and shaking of the locking pin and ensure that the locking pin always moves along the correct trajectory.

[0013] As a further improvement of the present invention, the elastic drive assembly includes a graded spring assembly, which includes a main spring and a secondary spring coaxially sleeved together. The main spring is sleeved on the outside of the secondary spring. The two ends of the main spring and the secondary spring respectively abut against the bottom of the mounting groove and the tail of the locking pin. The elastic coefficient of the main spring is smaller than that of the secondary spring. By using a coaxially nested graded spring assembly, graded driving force at different speeds can be realized, making the locking pin action smoother and the switching smoother.

[0014] As a further improvement of the present invention, the mounting slots are evenly distributed along the circumference of the bottom disc, and the number of locking pins and elastic drive components corresponds one-to-one with the number of mounting slots. The even distribution of mounting slots and the corresponding number of components ensure that the flywheel is subjected to balanced force and rotates smoothly, thereby improving the overall operational reliability.

[0015] Compared with the prior art, the beneficial effects of the present invention are as follows: This invention, through the clutch adjustment of the inertia disk, can precisely match the inertia requirements of the rotating shaft system during engine testing. At low speeds, the inertia disk remains engaged with the flywheel body, using its large inertia characteristic to improve the smoothness of the engine's low-speed operation. At high speeds, the inertia disk is disengaged from the flywheel body, using its small inertia characteristic to improve the engine's power output responsiveness at high speeds. Through the flexible adjustment of the variable inertia disk, the rotating shaft system meets the requirements of large inertia at low speeds and small inertia at high speeds throughout the entire operating speed range, effectively ensuring the stable operation of the rotating shaft system throughout the engine testing process, balancing low-speed smoothness and high-speed power responsiveness, and adapting to the usage requirements of engine testing under all operating conditions. Attached Figure Description

[0016] Figure 1 This is a plan view of the overall flywheel structure of the present invention; Figure 2 For the present invention Figure 1 Middle HH sectional view; Figure 3 For the present invention Figure 2 3D diagram; Figure 4 Internal view of the flywheel of the present invention Figure 1 ; Figure 5 Internal view of the flywheel of the present invention Figure 2 ; Figure 6 This is a schematic diagram of the pin and elastic drive assembly structure according to Embodiment 1 of the present invention; Figure 7 The overall explosion of the present invention Figure 1 ; Figure 8 This is an internal view of the flywheel in Embodiment 2 of the present invention; Figure 9 The overall explosion of the present invention Figure 2 ; Figure 10 This is a second embodiment of the present invention, consisting of a flywheel locking pin and an elastic drive assembly.

[0017] In the diagram: 1. Flywheel body; 101. Top disc; 102. Bottom disc; 103. Annular plate; 104. Guide plate; 105. Mounting groove; 106. Annular groove; 107. Positioning slide; 108. Positioning boss; 109. Guide block; 110. Exhaust hole; 2. Inertia disc; 3. Pin; 31. Rectangular protrusion; 32. Rectangular groove; 33. Wedge-shaped meshing surface; 34. Wedge-shaped groove; 35. Exhaust groove; 4. Elastic drive assembly; 5. Main spring; 6. Secondary spring; 7. Sealing ring. Detailed Implementation

[0018] To facilitate understanding of the present invention, a more comprehensive description of the present invention will be given below with reference to the accompanying drawings, which illustrate several embodiments of the present invention. However, the present invention can be implemented in different forms and is not limited to the embodiments described in the text. Rather, these embodiments are provided to make the disclosure of the present invention more thorough and complete.

[0019] It should be noted that when an element is referred to as being "fixed to" another element, it can be directly on the other element or there may be an intervening element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "left," "right," and similar expressions used in this document are for illustrative purposes only.

[0020] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly associated with those skilled in the art to which this invention pertains. The terminology used herein in the description of the invention is for the purpose of describing particular embodiments only and is not intended to limit the invention. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0021] The present invention will be further described in detail below with reference to the accompanying drawings.

[0022] Example 1: Please see Figure 1-7This invention discloses a variable moment of inertia flywheel, comprising a flywheel body 1, an inertia disk 2, a locking pin 3, and an elastic drive assembly 4. The flywheel body 1 includes a bottom disk 102 and a top disk 101. The bottom of the top disk 101 is provided with an annular groove 106, which is connected and fixed to the outside of the bottom disk 102 and the top of an annular plate 103. The bottom disk 102 is provided with a plurality of guide blocks 109, each guide block 109 being provided with a mounting groove 105. The top surface of the bottom disk 102 is provided with an annular plate 103, which is provided with a guide plate 104 adapted to each guide block 109. The guide plate 104 of the annular plate 103 seals the top surface of the mounting groove 105. The inertia disk 2 is coaxially disposed inside the flywheel body 1, and the inertia disk 2 is connected to the top disk 102. The inner wall of the disc 101 and the guide plate 104 on the annular plate 103 are slidably attached. A bearing is provided at the center of the bottom disc 102. The inertia disc 2 is fixedly sleeved on the outer wall of the bearing and can be rotatably set relative to the flywheel body 1. The locking pin 3 is slidably set in the mounting groove 105. One end of the locking pin 3 extends toward the inertia disc 2 and the other end abuts against the elastic drive component 4. The elastic drive component 4 is set in the mounting groove 105 and is used to drive the locking pin 3 to move toward the inertia disc 2. The end of the locking pin 3 near the inertia disc 2 is provided with a meshing part. The outer circumferential surface of the inertia disc 2 is provided with a mating part adapted to the meshing part. When the meshing part and the mating part are engaged, the inertia disc 2 and the flywheel body 1 form a rotating integrated structure. When the meshing part and the mating part are disengaged, the inertia disc 2 and the flywheel body 1 are released from rotational constraint and can rotate relative to each other.

[0023] Based on the above scheme, the assembly process should follow these steps: Flywheel body 1 assembly: The bottom disc 102 and the top disc 101 adopt a split design. The top surface of the top disc 101 and the bottom disc 102 and the fixed annular plate 103 are provided with multiple threaded holes, which are connected and fixed by bolts. Multiple guide plates 104 are evenly distributed on the annular plate 103 along the circumference. The shape of the guide plate 104 is consistent with the shape of the guide block 109 of the bottom disc 102. Each guide block 109 of the bottom disc 102 is machined with a groove. The guide plate 104 of the annular plate 103 corresponds to the groove one by one, forming a sealing installation groove 105 (the groove size is adapted to the cross section of the locking pin 3).

[0024] Inertia disk 2 assembly: The bearing is installed at the center of the bottom disk 102 through an interference fit, and the center of the inertia disk 2 is connected to the outer ring of the bearing; the outer diameter of the inertia disk 2 is 0.1mm smaller than the inner diameter of the top disk 101 and 0.1mm smaller than the inner distance between the annular plate 103 and the guide plate 104, so as to achieve sliding contact with the inner wall of the top disk 101 and the guide plate 104, and the radial runout is controlled within 0.05mm.

[0025] Pin and elastic component assembly: A set of elastic drive components 4 are placed in each mounting slot 105, and then a set of pins 3 are installed. The inner end of the pin 3 abuts against the elastic component. The engagement part of the pin 3 is designed as a rectangular protrusion 31, and the outer peripheral surface of the inertia disk 2 is machined with a corresponding rectangular groove 32 to ensure that the two are fully engaged during engagement and that the torque is transmitted without slippage.

[0026] The locking pin 3 and the mounting groove 105 are in clearance fit, and the locking pin 3 is radially guided by the constraint of the inner wall of the mounting groove 105.

[0027] The engaging part includes a rectangular protrusion 31, and the mating part includes a rectangular slot 32 adapted to the rectangular protrusion 31. The rectangular protrusion 31 and the rectangular slot 32 engage and snap together.

[0028] During implementation, the cross-section of the locking pin 3 is rectangular, and the cross-section of the mounting groove 105 is a matching rectangle with a fitting clearance of 0.03mm. This ensures that the locking pin can extend and retract flexibly, while the inner wall of the mounting groove 105 restricts the circumferential deflection of the locking pin. The outer circumferential surface of the locking pin 3 is ground to ensure that there is no jamming when sliding and fitting.

[0029] The cross-section of the locking pin 3 is rectangular, and the mounting groove 105 is machined into a matching rectangular groove with a fitting clearance of 0.05mm. Through the full circumferential fit constraint of the rectangular surface, the circumferential rotation and radial tilt of the locking pin are restricted, ensuring that the locking pin extends and contracts linearly along the axial direction. The meshing part of the locking pin 3 is designed as a rectangular hollow protrusion, and the mating part of the inertia disk 2 is a corresponding rectangular groove 32. One end of the elastic drive component 4 is fixedly connected to the inside of the rectangular hollow protrusion of the locking pin 3, and the other end is fixedly connected to the inner wall of the mounting groove 105. The elastic drive component 4 provides preload force to make the rectangular protrusion 31 fit into the groove, realizing the synchronous rotation of the inertia disk 2 and the flywheel body 1. The meshing structure relies on the elastic preload force to maintain the fit, and can work stably under low speed and low torque conditions.

[0030] A sealing ring 7 is provided between the bottom plate 102 and the top plate 101. Multiple vent holes 110 are provided on the top plate 101. The vent holes 110 are used to install one-way vent valves. The one-way vent valves balance the air pressure inside and outside the flywheel body 1, so as to prevent the internal air pressure change from forming motion resistance when the locking pin 3 moves in and out of the mounting groove 105. At the same time, it prevents abnormal internal air pressure from squeezing the sealing ring 7 and affecting the sealing effect, thus ensuring the smooth clutch action of the locking pin 3 and the overall sealing performance of the flywheel.

[0031] During implementation, a sealing ring 7 groove is machined in the inner layer of the annular groove 106 of the top disc 101 and the outer layer of the bottom disc 102, and a fluororubber O-ring 7 is embedded therein. After assembly, the sealing ring 7 completely fills the gap between the bottom disc 102 and the top disc 101, preventing dust and moisture from entering the interior and preventing internal lubricant leakage.

[0032] The mounting slots 105 are evenly distributed around the bottom plate 102, and the number of the locking pins 3 and the elastic drive components 4 corresponds one-to-one with the number of mounting slots 105.

[0033] In practice, one mounting slot 105 is set every 90° along the circumference of the bottom plate 102, and each mounting slot 105 is equipped with a set of locking pins 3 and a set of graded spring assemblies.

[0034] Example 2: This embodiment differs from Embodiment 1 in that, see [link to Embodiment 1] Figure 8-10 The meshing part also includes a wedge-shaped meshing surface 33, and the mating part also includes a wedge-shaped groove 34 adapted to the wedge-shaped meshing surface 33, and the wedge-shaped meshing surface 33 and the wedge-shaped groove 34 engage and snap together.

[0035] In practice, the meshing part is machined into a 20° wedge-shaped surface and the surface is polished to reduce frictional resistance during meshing, ensuring that centrifugal force is converted into self-locking force at low speed and into disengagement driving force at high speed. A wedge-shaped groove 34 that matches the wedge meshing surface 33 is machined on the inertia disk 2, and the groove wall inclination angle is also 20° to ensure that the wedge-shaped surface fits. The bottom of the groove is provided with a rounded transition to avoid jamming during high-speed disengagement.

[0036] At low / medium speed (≤2000r / min), the locking pin is engaged by the elastic drive component 4. The centrifugal force generated by the rotation of the flywheel forms a normal pressure along the wedge surface, which is converted into a self-locking friction force to ensure a stable engagement without loosening. At high speed (>2000r / min), the centrifugal force on the locking pin increases quadratically with the increase of the rotation speed. At this time, the tangential component of the centrifugal force along the wedge surface is greater than the sum of the elastic preload and the self-locking friction force, which pushes the locking pin to retract quickly. The wedge surface automatically disengages from the slot, achieving a smooth high-speed disengagement.

[0037] The guide structure in Embodiment 1 ensures that the wedge-shaped meshing surface 33 is precisely aligned and smoothly fitted with the slot, while providing a linear motion trajectory for high-speed disengagement. In this embodiment, the wedge-shaped structure achieves a graded effect of low-speed / medium-speed self-locking stability and high-speed automatic disengagement through angle optimization. This not only solves the problem of low-speed meshing looseness in Embodiment 1, but also meets the requirement of automatic disengagement during high-speed operation, significantly improving the reliability of inertia switching and the adaptability to working conditions.

[0038] Example 3: Please see Figure 6 Each outer periphery of the locking pin 3 is provided with an exhaust groove 35 that runs through its axial direction.

[0039] In practice, an axially continuous venting groove 35 is machined on each of the four outer peripheral surfaces of the locking pin 3. The groove extends from the head to the tail of the locking pin without interruption. When the locking pin extends or retracts, the air in the mounting groove 105 flows quickly through the venting groove 35, eliminating air damping, shortening the locking pin response time, and avoiding jamming during low-speed engagement or high-speed disengagement.

[0040] Example 4: Please see Figure 5 , Figure 9 , Figure 10 The wedge-shaped groove 34 has a guide slope at its entrance, and the opening angle of the guide slope is greater than the inclination angle of the groove wall of the wedge-shaped groove 34.

[0041] During implementation, the inlet of the wedge-shaped slot 34 is machined with an inclined surface, which is larger than the opening of the slot wall; the guide inclined surface adopts a rounded transition, and when the locking pin is reset and engaged, it is guided into the slot through the inclined surface.

[0042] Preferably, the side of the locking pin 3 is provided with a positioning boss 108, and the inner wall of the mounting groove 105 is provided with a positioning slide groove 107 that is adapted to the positioning boss 108, and the positioning boss 108 is slidably disposed in the positioning slide groove 107.

[0043] In implementation, one or more positioning bosses 108 are machined on each side of the locking pin 3, and positioning grooves 107 are machined on the inner wall of the mounting groove 105 accordingly. The fit clearance between the bosses and the grooves is 0.02mm, which restricts the circumferential rotation of the locking pin and reduces the docking deviation between the wedge surface and the locking groove. In this embodiment, the positioning bosses 108 of the locking pin 3 are only integrally formed in the middle and tail areas away from the meshing part. The meshing section of the locking pin 3 that cooperates with the inertia disk 2 has a smooth outer peripheral structure without any protrusions. The positioning grooves 107 of the mounting groove 105 are only opened in the inner wall area that cooperates with the middle and tail areas of the locking pin 3, and the positioning grooves 107 extend axially along the mounting groove 105 to the groove opening. During assembly and extension, the bosses only slide in the groove to achieve positioning and guidance. Because the meshing section is smooth and has no protrusions, it can smoothly extend into / out of the meshing part of the inertia disk 2 without any structural interference, taking into account both guiding accuracy and smooth engagement / disengagement.

[0044] Example 5: This embodiment differs from Embodiment 1 in that, see [link to Embodiment 1] Figure 9-10 The elastic drive assembly 4 includes a graded spring assembly, which includes a main spring 5 and a secondary spring 6 coaxially sleeved. The main spring 5 is sleeved on the outside of the secondary spring 6. The two ends of the main spring 5 and the secondary spring 6 respectively abut the bottom of the mounting groove 105 and the tail of the locking pin 3. The elastic coefficient of the main spring 5 is less than that of the secondary spring 6.

[0045] During implementation, the main spring 5 is sleeved on the outside of the auxiliary spring 6, with its two ends abutting against the bottom of the mounting groove 105 and the inner spring seat at the tail of the locking pin, respectively, to achieve a graded driving effect of low-speed main spring 5 driving and high-speed main and auxiliary springs 6 being compressed together.

[0046] The specific workflow is as follows: In the low-speed stage (≤2000r / min): the driving force of the elastic component is greater than the centrifugal force of the locking pin, pushing the locking pin out, the meshing part (wedge-shaped surface) and the mating part (wedge-shaped groove 34) mesh, the inertia disk 2 and the flywheel body 1 rotate synchronously, the rotational inertia reaches 1.2kg・m², improving the low-speed smoothness of the engine.

[0047] High-speed stage (>2000r / min): The centrifugal force of the locking pin increases with the rotational speed. When the rotational speed reaches 2500r / min, the centrifugal force is greater than the elastic driving force. The locking pin compresses the main and auxiliary springs 6 and retracts. The meshing part and the mating part disengage. The inertia disk 2 rotates freely. The rotational inertia of the flywheel is reduced to 0.5kg・m², which improves the high-speed dynamic response.

[0048] This variable moment of inertia flywheel achieves precise adaptation across the entire speed range through a progressive design of a basic guiding structure and an advanced wedge-shaped self-locking structure. At low / medium speeds, the wedge-shaped self-locking structure ensures stable engagement and prevents loosening. At high speeds, centrifugal force guides the smooth disengagement of the locking pin without interference from the self-locking mechanism. This not only meets the core requirement of high inertia at low speeds and low inertia at high speeds in engine testing, but also ensures the reliability and smoothness of inertia switching through precise guidance. The structural design is adaptable to different operating conditions, has high durability, and effectively balances smooth operation at low speeds with responsive power output at high speeds.

[0049] The present invention has been described by way of example in conjunction with the accompanying drawings. Obviously, the specific implementation of the present invention is not limited to the above-described manner. Any non-substantial improvement made by adopting the inventive concept and technical solution of the present invention, or the direct application of the inventive concept and technical solution of the present invention to other occasions without modification, shall be within the protection scope of the present invention.

Claims

1. A flywheel with variable moment of inertia, characterized in that: It includes a flywheel body (1), an inertia disk (2), a locking pin (3), and a flexible drive assembly (4); The flywheel body (1) includes a bottom disc (102) and a top disc (101). The bottom of the top disc (101) is provided with an annular groove (106). The annular groove (106) is connected and fixed to the outside of the bottom disc (102) and the top of the annular plate (103). The bottom disc (102) is provided with multiple guide blocks (109). Each guide block (109) is provided with a mounting groove (105). The top surface of the bottom disc (102) is provided with an annular plate (103). The annular plate (103) is provided with a guide plate (104) that is compatible with each guide block (109). The guide plate (104) of the annular plate (103) seals the top surface of the mounting groove (105). The inertia disk (2) is coaxially disposed inside the flywheel body (1). The inertia disk (2) is slidably attached to the inner wall of the top disk (101) and the guide plate (104) on the annular plate (103). The bottom disk (102) is provided with a bearing at its center. The inertia disk (2) is fixedly sleeved on the outer wall of the bearing and can be rotated relative to the flywheel body (1). The locking pin (3) is slidably disposed in the mounting groove (105). One end of the locking pin (3) extends toward the inertia disk (2) and the other end abuts against the elastic drive component (4). The elastic drive component (4) is disposed in the mounting groove (105) and is used to drive the locking pin (3) to move toward the inertia disk (2). The locking pin (3) has a meshing part at one end near the inertia disk (2). The outer circumferential surface of the inertia disk (2) has a mating part that matches the meshing part. When the meshing part and the mating part mesh, the inertia disk (2) and the flywheel body (1) form a rotating integrated structure. When the meshing part and the mating part disengage, the inertia disk (2) and the flywheel body (1) are released from rotational constraints and can rotate relative to each other.

2. The variable moment of inertia flywheel according to claim 1, characterized in that: The locking pin (3) and the mounting groove (105) are in clearance fit, and the locking pin (3) is radially guided by the inner wall constraint of the mounting groove (105).

3. The variable moment of inertia flywheel according to claim 1, characterized in that: Each outer periphery of the locking pin (3) is provided with an exhaust groove (35) that runs through its axial direction.

4. The variable moment of inertia flywheel according to claim 1, characterized in that: The engaging part includes a rectangular protrusion (31), and the mating part includes a rectangular slot (32) that is adapted to the rectangular protrusion (31). The rectangular protrusion (31) and the rectangular slot (32) engage and snap together.

5. The variable moment of inertia flywheel according to claim 1, characterized in that: A sealing ring (7) is provided between the bottom plate (102) and the top plate (101). The top plate (101) is also provided with multiple exhaust holes (110), which are used to install one-way exhaust valves.

6. The variable moment of inertia flywheel according to claim 1, characterized in that: The meshing part also includes a wedge-shaped meshing surface (33), and the mating part also includes a wedge-shaped groove (34) adapted to the wedge-shaped meshing surface (33), and the wedge-shaped meshing surface (33) and the wedge-shaped groove (34) engage and snap together.

7. The variable moment of inertia flywheel according to claim 6, characterized in that: The entrance of the wedge-shaped slot (34) is provided with a guide slope, and the opening angle of the guide slope is greater than the inclination angle of the slot wall of the wedge-shaped slot (34).

8. The variable moment of inertia flywheel according to claim 1, characterized in that: The side of the locking pin (3) is provided with a positioning boss (108), and the inner wall of the mounting groove (105) is provided with a positioning slide groove (107) that is adapted to the positioning boss (108). The positioning boss (108) is slidably disposed in the positioning slide groove (107).

9. The variable moment of inertia flywheel according to claim 1, characterized in that: The elastic drive assembly (4) includes a graded spring assembly, which includes a main spring (5) and a secondary spring (6) coaxially sleeved. The main spring (5) is sleeved on the outside of the secondary spring (6). The two ends of the main spring (5) and the secondary spring (6) respectively abut the bottom of the mounting groove (105) and the tail of the locking pin (3). The elastic coefficient of the main spring (5) is smaller than that of the secondary spring (6).

10. The variable moment of inertia flywheel according to claim 1, characterized in that: The mounting slots (105) are evenly distributed around the bottom plate (102), and the number of the locking pins (3) and the elastic drive components (4) corresponds one-to-one with the number of mounting slots (105).

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