Gravity self-locking bearing

Abstract

The invention discloses a gravity self-locking bearing which comprises an outer ring, a retainer and an inner ring, a plurality of rolling bodies are arranged between the outer ring and the inner ring, and the rolling bodies are arranged in pockets of the retainer. An inner hole of the inner ring is in clearance fit with the friction sleeve and is provided with fracture grooves along the axial direction of the outer ring; the outer ring is longer, the inner hole is a taper hole, the large-aperture end is provided with a check ring, and the small-aperture end is provided with a retainer. An abutting plate is arranged between the check ring and the retainer, a first spring abuts between the check ring and the abutting plate, a second spring abuts between the abutting plate and the retainer, and the elastic coefficient of the first spring is larger. A positioning groove is formed in the inner hole of the outer ring corresponding to the abutting plate, and the abutting plate is arranged in the groove in a floating mode. The bearing is simple in structure, reliable in use, capable of being self-locked in time when being impacted or collided, and good in use safety.

Description

Technical Field

[0001] This invention relates to a gravity self-locking bearing. Background Technology

[0002] In modern mechanical engineering, bearings, as core components for supporting mechanical rotation, play a vital role, much like joints in the human body. They effectively reduce the coefficient of friction during mechanical operation while ensuring the rotational accuracy of the shaft, thus finding widespread application in all aspects of our lives and work. Because different mechanical devices face vastly different working environments—some requiring stable operation under high temperature and pressure, others needing to adapt to humid and dusty conditions, and still others demanding extremely high precision and speed—a wide variety of bearings have emerged, such as deep groove ball bearings, tapered rolling element bearings, and thrust bearings. Gravity self-locking bearings are a particularly distinctive and valuable type. For example, they play a crucial role in magnetic levitation protection bearing systems. While magnetic levitation bearings enable contactless operation, the rotor is highly susceptible to instability during startup, shutdown, or when a sudden malfunction causes the magnetic levitation force to fail. In such cases, gravity self-locking bearings respond rapidly, locking the rotor through their structural characteristics and gradually reducing its speed using the braking force generated by mechanical contact. This prevents the rotor from colliding with other components due to high-speed loss of control, ensuring the safety of the entire magnetic levitation system. In devices requiring emergency stops, such as certain large lifting equipment and high-speed transmission machinery, gravity self-locking bearings eliminate the need for complex external braking systems. They rely solely on gravity to drive an internal locking mechanism to quickly clamp rotating components, achieving instantaneous braking and providing crucial protection for equipment operation safety. Furthermore, in aerial work platforms, construction hoists, and other equipment requiring fall prevention, gravity self-locking bearings are a core safety component. If the equipment unexpectedly begins to slide downwards, its locking mechanism immediately triggers, firmly locking the transmission components and preventing the equipment from falling, maximizing the protection of operators' lives and the integrity of the equipment. Summary of the Invention

[0003] To address the shortcomings of existing technologies, this invention provides a gravity self-locking bearing, which has a simple structure, reliable use, and can self-lock promptly when subjected to impact or collision, thus exhibiting good safety in use.

[0004] To achieve the above objectives, the present invention provides a gravity self-locking bearing, comprising an outer ring, a cage, and an inner ring. A plurality of rolling elements are disposed between the outer ring and the inner ring, and the rolling elements are installed in pockets of the cage. A friction sleeve is fitted with the inner ring in a clearance fit. The friction sleeve and the inner ring are respectively provided with fracture grooves along the axial direction of the outer ring. The length of the outer ring is greater than that of the inner ring. The inner hole of the outer ring is tapered. A retaining ring is disposed at the end of the outer ring's inner hole with a larger diameter. The cage is disposed at the end of the outer ring's inner hole with a smaller diameter. An abutment plate is disposed between the retaining ring and the cage. A first spring abuts against the retaining ring and the abutment plate. A second spring abuts against the abutment plate and the cage. The elastic coefficient of the first spring is greater than that of the second spring. A positioning groove is disposed on the inner hole of the outer ring corresponding to the position of the abutment plate. The abutment plate is disposed in the positioning groove and is floatingly disposed in the positioning groove.

[0005] The advantages of this configuration are as follows: During installation, the end with the larger inner diameter of the outer ring is positioned at the top along the height, while the end with the smaller inner diameter is positioned downwards along the height. When the bearing is installed on the mating shaft, the outer ring, due to gravity, presses against the rolling elements, which in turn press against the inner ring. This causes the inner ring and friction sleeve to close together and hold tightly against the mating shaft. When the bearing needs to be moved to adjust its position, simply press the cage near the end with the smaller inner diameter of the outer ring. The cage moves inwards towards the outer ring, reducing the resistance force on the rolling elements. This loosens the friction sleeve and inner ring, preventing them from holding tightly against the shaft, thus allowing the bearing to move on the spindle. When the end with the larger inner diameter of the outer ring is subjected to gravity or external pressure, the entire outer ring moves downwards along the height. As the bearing moves downwards, the first spring actively releases its elastic force, acting directly on the contact plate. Due to the large elastic force of the first spring and the movement of the outer ring along the height direction, the contact plate, which is floating in the positioning groove (meaning it has space to slide along the length of the outer ring), moves towards the cage under the force of the first spring. This allows the force to be transferred to the second spring, resulting in better and more stable contact with the cage. This increases the contact force on the rolling elements from the outer ring, increases the pressure on the inner ring and friction sleeve, and increases the force of the friction sleeve pressing against the mating shaft. Thus, under the synergistic action of the first and second springs, the bearing can be instantly locked onto the spindle. This design allows for instantaneous and stable locking, effectively preventing accidental slippage caused by insufficient locking force in traditional bearings. It is particularly suitable for equipment installed vertically or in vibrating environments, offering excellent adaptability. Furthermore, when adjusting the position, simply press the end of the cage closest to the smaller diameter of the outer ring's inner bore to move the cage inward, reducing the resistance force on the rolling elements and allowing the inner ring and friction sleeve to loosen quickly. No complex tools are required; a single person can easily complete the position adjustment, significantly reducing operational difficulty and time costs. Additionally, the clearance fit design between the friction sleeve and the inner ring reduces wear between components during adjustment, extending the overall lifespan of the bearing.

[0006] As a further feature of the present invention, the inner ring end is provided with a skirt, and the friction sleeve abuts against the skirt.

[0007] The beneficial effects of this design are as follows: The contact design between the inner ring end skirt and the friction sleeve, besides precisely positioning and limiting the friction sleeve, also prevents axial movement of the friction sleeve during bearing operation or adjustment, preventing misalignment between the friction sleeve and the inner ring's groove. This ensures that both sleeves synchronously clamp the mating shaft when closed, guaranteeing uniform transmission of clamping force and preventing locking failure caused by uneven local force. Simultaneously, the skirt can absorb the axial force generated by the friction sleeve's clamping / loosening, reducing direct frictional loss between the friction sleeve and the inner ring bore wall, extending the friction sleeve's service life. Furthermore, it helps maintain the clearance fit accuracy between the inner ring and the friction sleeve, providing more reliable structural support for stable bearing locking and flexible adjustment.

[0008] As a further feature of the present invention, the cage is provided with a plurality of pockets, the rolling element is disposed in the pockets, and a retaining ring is engaged at the edge of the pocket, the edge of the retaining ring abutting against the rolling element.

[0009] The benefits of this design are as follows: By placing a retaining ring inside the cage pocket and having its edge abut against the roller, this design ensures the stability of the roller's position from multiple dimensions, providing crucial support for the reliable operation of the pneumatic lock. The retaining ring also reduces direct friction between the roller and the inner wall of the pocket, reducing component wear, extending the service life of the cage and roller, and ensuring that the structure maintains stable motion accuracy in both locked and unlocked states, making it suitable for long-term, high-frequency use scenarios.

[0010] As a further feature of the present invention, an abutting step is provided on the cage corresponding to the position of the second spring, and the other end of the second spring abuts against the abutting step.

[0011] The beneficial effects of this design are as follows: This design allows the abutment step to precisely limit the radial displacement of the spring on the cage side, preventing skewing due to uneven force during spring compression or reset, and ensuring that the spring force is accurately transmitted to the cage along the lock body axis. Simultaneously, the step provides a stable support point for the spring, reducing wear between the spring and the cage and preventing force attenuation due to spring displacement after prolonged use.

[0012] As a further feature of the present invention, a lubrication groove is spirally provided on the inner peripheral wall of the friction sleeve.

[0013] The beneficial effects of this design are as follows: The spiral lubrication groove design on the inner circumference of the friction sleeve primarily serves to efficiently store lubricating oil or grease, evenly distributing the lubricant across the contact surface to form a continuous and stable oil film. This significantly reduces dry friction between metals, lowers the wear rate of both the friction sleeve and the shaft, and extends their service life. Simultaneously, the lubrication grooves can accommodate tiny debris generated during friction, preventing scratches on the contact surface caused by debris accumulation, maintaining the precision of the inner wall of the friction sleeve, ensuring a stable fit clearance with the shaft, and not affecting the transmission of clamping force during locking. Furthermore, good lubrication reduces resistance during bearing adjustment, making the operation of moving the bearing by pressing the cage smoother, reducing component jamming problems caused by excessive frictional resistance, and improving overall reliability. Attached Figure Description

[0014] Figure 1 This is a schematic diagram of the structure of an embodiment of the present invention; Figure 2 This is a cross-sectional structural diagram of an embodiment of the present invention; Figure 3 This is a schematic diagram of the inner ring structure in an embodiment of the present invention; Figure 4This is a schematic diagram of the friction sleeve in an embodiment of the present invention; Figure 5 This is a schematic diagram of the cage structure in an embodiment of the present invention. Detailed Implementation

[0015] This invention provides an embodiment of a gravity self-locking bearing, such as... Figures 1 to 5As shown, the device includes an outer ring 1, a cage 4, and an inner ring 2. A plurality of rolling elements 41 are disposed between the outer ring 1 and the inner ring 2. The rolling elements 41 are installed in the pockets of the cage 4. A friction sleeve 3 is fitted with the inner hole of the inner ring 2 with clearance. Both the friction sleeve 3 and the inner ring 2 have axial grooves along the outer ring 1. The outer ring 1 is longer than the inner ring 2. The inner hole of the outer ring 1 is tapered. A retaining ring 11 is disposed at the end of the inner hole of the outer ring 1 with a larger diameter. The cage 4 is disposed at the end of the inner hole of the outer ring 1 with a smaller diameter. An abutment plate 13 is disposed between the retaining ring 11 and the cage 4. A first spring 5 abuts against the retaining ring 11 and the abutment plate 13. A second spring 6 abuts against the abutment plate 13. The elastic coefficient of the first spring 5 is greater than that of the second spring 6. A positioning groove is disposed on the inner hole of the outer ring 1 corresponding to the position of the abutment plate 13. The abutment plate 13 is disposed in the positioning groove and floats within the positioning groove. The beneficial effects of this configuration are as follows: During installation, the end with the larger inner diameter of the outer ring 1 is positioned at the top along the height, while the end with the smaller inner diameter is positioned downwards along the height. When the bearing is installed on the mating shaft, the outer ring 1, due to gravity, abuts against the rolling element 41, and the rolling element 41 presses against the inner ring 2, causing the inner ring 2 and friction sleeve 3 to close together and hold tightly on the mating shaft. When it is necessary to move the bearing to adjust its position, simply press the cage 4 near the end with the smaller inner diameter of the outer ring 1. The cage 4 moves inwards towards the outer ring 1, reducing the contact force between the rolling element 41 and the outer ring 1. This loosens the friction sleeve 3 and the inner ring 2, preventing them from holding tightly against the shaft, thus allowing the bearing to move on the spindle. When the end with the larger inner diameter of the outer ring 1 is subjected to gravity or external pressure, the entire outer ring 1 moves downwards along the height. As the bearing moves downward, the first spring 5 actively releases its elastic force, acting directly on the contact plate 13. Due to the large elastic force of the first spring 5 and the movement of the outer ring 1 along the height direction, the contact plate 13 is floatingly set in the positioning groove. Here, "floatingly set" means that the contact plate 13 can have space to slide along the length direction of the outer ring 1 in the positioning groove. The contact plate 13 moves towards the cage 4 under the elastic force of the first spring 5, thus transferring the force to the second spring 6, thereby better and more stably contacting the cage 4. This makes the rolling element 41 more susceptible to the contact force of the outer ring 1, and makes the inner ring 2 and friction sleeve 3 more susceptible to pressure. The friction sleeve 3 presses more force on the mating shaft. Thus, under the synergistic action of the first spring 5 and the second spring 6, the bearing can be instantly locked onto the spindle.This design allows for instantaneous and stable locking, effectively preventing accidental slippage caused by insufficient locking force in traditional bearings. It is particularly suitable for equipment installed vertically or in vibrating environments, offering excellent adaptability. Furthermore, when adjusting the position, simply pressing the end of the cage 4 closest to the smaller diameter of the inner hole of the outer ring 1 moves the cage 4 inward, reducing the resistance force on the rolling elements 41 and allowing the inner ring 2 and friction sleeve 3 to loosen quickly. No complex tools are required, and a single person can easily complete the position adjustment, significantly reducing operational difficulty and time costs. Additionally, the clearance fit design between the friction sleeve 3 and the inner ring 2 reduces wear between components during adjustment, extending the overall service life of the bearing.

[0016] As a further feature of this embodiment, a skirt 21 is provided at the end of the inner ring 2, and the friction sleeve 3 abuts against the skirt 21. The beneficial effects of this design are: This design, where the skirt 21 at the end of the inner ring 2 abuts against the friction sleeve 3, not only precisely positions and limits the friction sleeve 3, but also prevents axial movement of the friction sleeve 3 during bearing operation or adjustment, preventing misalignment between it and the groove of the inner ring 2, ensuring that both synchronously clamp the mating shaft when closed, guaranteeing uniform transmission of clamping force, and avoiding locking failure caused by uneven local force. Simultaneously, the skirt 21 can absorb the axial force generated by the clamping / loosening of the friction sleeve 3, reducing direct frictional loss between the friction sleeve 3 and the inner ring 2's bore wall, extending the service life of the friction sleeve 3; and it can also help maintain the clearance fit accuracy between the inner ring 2 and the friction sleeve 3, providing more reliable structural support for stable bearing locking and flexible adjustment.

[0017] As a further feature of this embodiment, the cage 4 is provided with a plurality of pockets, and the rolling element 41 is disposed in the pockets. A retaining ring 43 is engaged with the edge of the pocket, and the edge of the retaining ring 43 abuts against the rolling element 41. The beneficial effects of this configuration are: by placing the retaining ring 43 in the pocket of the cage 4 and having its edge abut against the roller, the stability of the roller position can be ensured from multiple dimensions, providing key support for the reliable operation of the pneumatic lock. The retaining ring 43 can also reduce the direct friction between the roller and the inner wall of the pocket, reduce component wear, extend the service life of the cage 4 and the roller, and ensure that the structure can maintain stable motion accuracy in both locked and unlocked states, making it suitable for long-term, high-frequency use scenarios.

[0018] As a further feature of this embodiment, an abutment step 42 is provided on the retainer 4 corresponding to the position of the second spring 6, and the other end of the second spring 6 abuts against the abutment step 42. The beneficial effects of this design are: the abutment step 42 precisely limits the radial displacement of the spring on the retainer 4 side, preventing skewing due to uneven force during spring compression or reset, and ensuring that the spring force is accurately transmitted to the retainer 4 along the lock body axis. Simultaneously, the step provides a stable force support point for the spring, reducing contact wear between the spring and the retainer 4, and preventing force attenuation due to spring displacement after long-term use.

[0019] As a further feature of this embodiment, a lubrication groove 31 is spirally provided on the inner peripheral wall of the friction sleeve 3. The beneficial effects of this design are as follows: the spiral lubrication groove 31 on the inner peripheral wall of the friction sleeve 3 primarily serves to efficiently store lubricating oil or grease, uniformly distributing the lubricant across the contact surface to form a continuous and stable oil film. This significantly reduces dry friction between metals, lowers the wear rate of the friction sleeve 3 and the shaft, and extends their service life. Simultaneously, the lubrication groove 31 can accommodate tiny debris generated by friction, preventing scratches on the contact surface caused by debris accumulation, maintaining the precision of the inner wall of the friction sleeve 3, ensuring a stable fit clearance with the shaft, and not affecting the transmission of clamping force during locking. Furthermore, good lubrication reduces resistance during bearing adjustment, making the operation of pressing the retainer 4 to move the bearing smoother, reducing component jamming problems caused by excessive frictional resistance, and improving overall reliability.

[0020] The above examples are merely one preferred embodiment of the present invention. Ordinary variations and substitutions made by those skilled in the art within the scope of the technical solution of the present invention are all included within the protection scope of the present invention.

Claims

1. A gravity self-locking bearing comprising an outer ring, a cage and an inner ring, a plurality of rolling elements being arranged between the outer ring and the inner ring, the rolling elements being mounted in pockets of the cage, characterized in that: The inner hole of the inner ring is matched with a friction sleeve, the friction sleeve and the inner ring are respectively provided with a fracture groove along the axial direction of the outer ring, the length of the outer ring is greater than that of the inner ring, the inner hole of the outer ring is a tapered hole, the end of the inner hole of the outer ring with a larger diameter is provided with a stop ring, the retainer is arranged at the end of the inner hole of the outer ring with a smaller diameter, a contact plate is arranged between the stop ring and the retainer, the stop ring and the contact plate are in contact with a first spring, the contact plate and the retainer are in contact with a second spring, the elastic coefficient of the first spring is greater than that of the second spring, the inner hole of the outer ring is provided with a positioning groove corresponding to the position of the contact plate, the contact plate is arranged in the positioning groove, and the contact plate is floatingly arranged in the positioning groove.

2. The gravity self-locking bearing of claim 1, wherein: The inner ring is provided with a skirt at the end, and the friction sleeve is in contact with the skirt.

3. The gravity self-locking bearing of claim 1, wherein: The retainer is provided with a plurality of pockets, the rolling body is arranged in the pocket, and a snap ring is arranged on the edge of the pocket.

4. The gravity self-locking bearing of claim 1, wherein: The retainer is provided with a contact step corresponding to the position of the second spring, and the other end of the second spring is in contact with the contact step.

5. The gravity self-locking bearing of claim 1, wherein: The inner wall of the friction sleeve is spirally provided with a lubricating groove.

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