Pneumatic lock

Abstract

The pneumatic lock comprises a lock body, positioning shaft sleeves are arranged at the two ends of the lock body respectively, core shafts are arranged in the positioning shaft sleeves in a sliding fit mode, pistons are further arranged on the peripheral walls of the positioning shaft sleeves in a sliding mode, the lock body is divided into an air cavity and a containing cavity through the pistons, a friction sleeve is arranged on the core shafts and located between the positioning shaft sleeves in a sleeving mode, and the friction sleeve is in clearance fit with the core shafts. A bearing is further matched between the friction sleeve and the lock body and comprises an inner ring, an outer ring and a retainer, the friction sleeve is sleeved with the inner ring, fracture grooves are formed in the friction sleeve and the inner ring, the retainer is arranged between the inner ring and the outer ring, a shaft clamp spring is arranged on the outer ring, a first spring abuts against the position between the shaft clamp spring and the lock body, and an inner hole of the outer ring is arranged in a taper hole shape. The end, with the large hole diameter, of the inner hole of the outer ring abuts against the piston, and a second spring is further arranged between the retainer and the outer ring in an abutting mode. The structure is simple, the production and processing are convenient, the use is reliable, and the use effect is good.

Description

Technical Field

[0001] This invention relates to a pneumatic lock. Background Technology

[0002] Pneumatic locks, with their stable characteristics and reliable locking performance due to air pressure control, play a crucial role in various scenarios. In the field of sports equipment parked for extended periods, their applications can be further refined: for electric vehicles parked daily, whether they are household electric vehicles near community charging stations or delivery vehicles parked in concentrated areas at food delivery stations, pneumatic locks can tightly engage the wheels or frame through a pneumatically driven locking tongue structure, effectively resisting theft such as prying and dragging, especially suitable for complex outdoor environments; for automobiles, in addition to the anti-theft needs of passenger cars parked in open-air parking lots for extended periods, pneumatic locks can be linked with the vehicle's braking system during periods of inactivity for heavy trucks in logistics parks and special-operation vehicles at construction sites, preventing property damage due to accidental slippage; in the field of construction machinery, such as excavators and loaders on construction sites, and tractors in agricultural production, which are susceptible to dust and rain corrosion during long-term parking, the sealed design of pneumatic locks can simultaneously ensure locking security and component protection. For mechanical devices exposed in public spaces, such as outdoor fitness equipment in community fitness areas, small amusement facilities in parks, and simple mechanical teaching aids in school laboratories, the installation of pneumatic locks can unlock them with a dedicated pneumatic key or password authorization, eliminating the risk of pinching or bumping caused by children's curious touching or unauthorized operation. In industrial production scenarios, for equipment such as stamping machines, cutting machines, and conveyor belts in factory workshops, pneumatic locks can be linked with the equipment's circuitry and pneumatic circuitry during shutdown maintenance or non-working periods. Even if the start button is accidentally pressed, the locking mechanism will prevent operation, creating a protective barrier for the safety of operators and equipment. However, existing pneumatic locks have relatively complex structures and high production and processing costs, which is not conducive to the promotion and use of the product. Summary of the Invention

[0003] To address the shortcomings of existing technologies, this invention provides a pneumatic lock that is simple in structure, easy to manufacture and process, reliable in use, and has good performance.

[0004] To achieve the above objectives, the present invention provides a pneumatic lock, comprising a lock body, with positioning sleeves respectively provided at both ends of the lock body. A spindle penetrating the lock body is slidably fitted in the positioning sleeve. A piston is also slidably disposed on the outer peripheral wall of the positioning sleeve, dividing the lock body into an air chamber and a receiving chamber. An air inlet and an air outlet are provided on the lock body corresponding to the positions of the air chambers. A friction sleeve is fitted on the spindle between the positioning sleeves, with a clearance fit between the friction sleeve and the spindle. The friction sleeve is disposed in the receiving chamber. A bearing is also fitted between the friction sleeve and the lock body. The lock body includes an inner ring, an outer ring, rollers, and a cage. The inner ring is fitted over the friction sleeve. Both the friction sleeve and the inner ring have break grooves along the length of the lock body. The cage is positioned between the inner and outer rings. The rollers are rotatably fitted onto the cage. A circlip is provided on the outer peripheral wall of the outer ring. A first spring abuts against the lock body, and the first spring is fitted onto the outer ring. The inner hole of the outer ring is tapered, and the larger end of the inner hole abuts against the piston. A second spring abuts against the cage and the outer ring.

[0005] The beneficial effects of this design are as follows: When the chamber is not filled with air and there is no air pressure, the first spring is under pressure, pushing the outer ring towards the piston. At this time, the second spring is not under force and is in a freely extended state. The rollers are under force, and the inner ring and friction sleeve receive pressure from the rollers, causing the grooves to close, thus locking the friction sleeve onto the mandrel. The entire device is in a locked state, with the mandrel held and locked by the friction sleeve. When air is added to the chamber, it pushes the piston towards the outer ring. The outer ring moves due to the piston's resistance. At this time, the second spring is still not under force, the steel ball is not under force, and the inner ring and friction sleeve are not under force. Because the inner ring and friction sleeve have grooves on their cylindrical surfaces, they freely unfold and do not contact the mandrel. This is the open state, allowing the mandrel to move axially and rotate circumferentially. If air continues to be added, the outer ring continues to move, and the second spring is under force, ensuring that the cage assembly does not detach from the outer ring raceway. The first spring transmits pressure via a circlip, pushing the outer ring to fit tightly against the piston, causing the outer ring's tapered hole to precisely compress the roller radially. The roller, under pressure, transmits this pressure to the inner ring and friction sleeve. Since both have grooves along the length of the lock body, these grooves quickly close under pressure, creating a tight, enveloping contact between the inner wall of the friction sleeve and the outer wall of the spindle. This force transmission path efficiently converts the elastic potential energy of the first spring into a locking force between the friction sleeve and the spindle, preventing axial movement or circumferential rotation of the spindle due to external forces. This is particularly suitable for scenarios requiring long-term parking, such as electric vehicles and construction machinery, effectively preventing equipment displacement or theft. Simultaneously, the clearance fit between the friction sleeve and the spindle transforms into an interference fit during locking. Combined with the wear-resistant material of the friction sleeve, this further enhances locking stability and extends the lock's lifespan. When the air chamber is filled with air, the air pressure pushes the piston to slide along the outer peripheral wall of the positioning sleeve through the air inlet. The piston contacts the outer ring and overcomes the pressure of the first spring, causing it to move in the opposite direction. The squeezing effect of the outer ring tapered hole on the roller disappears instantly. After the roller loses radial pressure, the inner ring and friction sleeve freely unfold due to the elastic recovery ability of the fracture groove and disengage from the mandrel. At this time, the mandrel can flexibly realize axial movement and circumferential rotation, meeting the component linkage requirements when the equipment is started. The entire switching process relies solely on pneumatic drive, eliminating the need for manual operation of mechanical parts. It boasts a fast response speed, and the piston's pushing force can be adjusted by controlling the intake air pressure, preventing damage to components due to excessive pressure. The air outlet allows for rapid release of air pressure from the air chamber, enabling the lock to quickly return to its locked state. This makes it suitable for high-frequency switching scenarios such as industrial equipment maintenance and temporary unlocking, improving operational efficiency. The positioning bushings at both ends of the lock body not only provide sliding guidance for the spindle but also prevent external dust and rainwater from entering the lock body. The receiving cavity isolates core components such as the friction sleeve and bearings from the outside, and combined with the piston's sealing effect on the air chamber, it effectively prevents components from jamming due to impurities.The bearing's inner ring, outer ring, rollers, and cage assembly structure reduces frictional resistance during spindle operation and prevents component wear. Especially under continuous inflation, the second spring abuts against the cage and outer ring, preventing excessive movement of the outer ring that could cause the cage assembly to disengage from the raceway, ensuring stable operation of the lock under high pressure conditions.

[0006] As a further feature of the present invention, a gap groove is provided between the friction sleeve and the positioning bushing, and a mating flange is provided on the outer peripheral wall of the inner ring, the mating flange being engaged in the gap groove.

[0007] The beneficial effects of this design are as follows: This design, combined with the engaging structure of the flange and the clearance groove, precisely limits the axial displacement of the inner ring along the lock body. This prevents the inner ring from shifting due to roller compression when not fully inflated, ensuring that the force centers of the outer ring's tapered hole, rollers, and inner ring are always aligned. This guarantees that the force transmission path remains consistent, allowing the break groove to close evenly and preventing loosening caused by uneven force distribution on the friction sleeve. This structure also improves the linkage stability between the inner ring and the friction sleeve. When the inner ring is under roller pressure, the flange can transmit the force to the friction sleeve through the clearance groove, causing both to deform synchronously. This ensures a more uniform clamping force of the friction sleeve on the spindle, further optimizing the transition from a clearance fit to an interference fit and reducing spindle wobble. Furthermore, during inflated unlocking, the flange limits excessive expansion of the inner ring, preventing it from detaching from the outer ring's raceway. This provides precise positioning for component repositioning during subsequent relocking, continuously ensuring the locking effect and lifespan of the lock.

[0008] As a further feature of the present invention, the friction sleeve is configured to have at least two sub-sleeves, which are sleeved on the mandrel and have a clearance fit with the mandrel.

[0009] The beneficial effects of this design are as follows: By dividing the friction sleeve into at least two sub-sleeves fitted onto the mandrel, the performance of the pneumatic lock is significantly optimized in terms of both locking uniformity and failure tolerance. Regarding the clamping effect, multiple sub-sleeves independently form a clearance fit with the mandrel. When not inflated, the pressure transmitted from the inner ring can be distributed to each sub-sleeve, ensuring that the grooves of each sub-sleeve close evenly. This avoids the problem of uneven localized fit caused by uneven deformation in a one-piece friction sleeve, resulting in more balanced force on the outer wall of the mandrel and significantly reducing the possibility of wobbling due to localized gaps, further enhancing locking stability. This design establishes a failure redundancy mechanism. When a sub-sleeve fails on one side due to wear, abnormal deformation, or other reasons, the remaining sub-sleeves can still normally accept the inner ring pressure and hold the spindle, ensuring that the lock will not lose its locking function due to the failure of a single component. This effectively improves the safety redundancy of the equipment under long-term use or complex working conditions, and is especially suitable for scenarios with extremely high requirements for lock reliability, such as automobiles and construction machinery, reducing safety accidents and property losses caused by sudden lock failures.

[0010] As a further feature of the present invention, the cage is provided with a plurality of pockets, the roller 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 roller.

[0011] The benefits of this design are as follows: By placing a retaining ring inside the cage pocket and ensuring its edge abuts 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, minimizing component wear, extending the service life of the cage and roller, and ensuring that the pneumatic lock maintains stable motion accuracy even during high-frequency switching between locking and unlocking states, making it suitable for long-term, high-frequency use scenarios.

[0012] As a further feature of the present invention, a retaining ring for a hole is fitted on the inner peripheral wall of the outer ring, and the second spring abuts against the retaining ring for the hole.

[0013] The beneficial effects of this design are: it provides a stable and precise positioning support for the second spring. When the pneumatic lock is continuously inflated and the outer ring is moved by the piston, the second spring needs to limit the displacement of the cage assembly through compression deformation; the retaining ring in the hole can firmly fix one end of the second spring, preventing the spring from shifting axially or radially due to force, ensuring that the spring force can act precisely on the cage, stably limiting the relative position of the cage and the outer ring raceway, and preventing the cage assembly from detaching.

[0014] 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.

[0015] 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, preventing force attenuation due to spring displacement after long-term use, further ensuring the limiting effect of the second spring on the cage assembly, and improving the structural stability and operational reliability of the pneumatic lock under high-frequency switching conditions. Attached Figure Description

[0016] Figure 1 This is a cross-sectional structural diagram of an embodiment of the present invention; Figure 2 This is a schematic diagram of the inner ring structure in an embodiment of the present invention; Figure 3 This is a schematic diagram of the structure of the sub-sleeve body in an embodiment of the present invention. Detailed Implementation

[0017] This invention provides an embodiment of a pneumatic lock, such as... Figures 1 to 3As shown, the lock includes a lock body 1, with positioning sleeves 21 at both ends. A spindle 2, penetrating the lock body 1, is slidably fitted within the positioning sleeves 21. A piston 11 is also slidably mounted on the outer peripheral wall of the positioning sleeves 21, dividing the lock body 1 into an air chamber 12 and a receiving chamber 13. An air inlet 121 and an air outlet 122 are provided on the lock body 1 corresponding to the positions of the air chambers 12. A friction sleeve 22 is fitted onto the spindle 2 between the positioning sleeves 21, with a clearance fit between the friction sleeve 22 and the spindle 2. The friction sleeve 22 is disposed in the receiving chamber 13, and a bearing is also fitted between the friction sleeve 22 and the lock body 1. The bearing includes an inner ring 3. The lock body 1 consists of an outer ring 5, a roller 41, and a retainer 4. The inner ring 3 is fitted over the friction sleeve 22. Both the friction sleeve 22 and the inner ring 3 have a break groove 31 along the length of the lock body 1. The retainer 4 is positioned between the inner ring 3 and the outer ring 5. The roller 41 is rotatably fitted onto the retainer 4. A shaft retainer 51 is provided on the outer peripheral wall of the outer ring 5. A first spring 53 abuts against the lock body 1 between the shaft retainer 51 and the lock body 1. The first spring 53 is fitted onto the outer ring 5. The inner hole of the outer ring 5 is tapered. The end of the inner hole with the larger diameter abuts against the piston 11. A second spring 43 is also abutting between the retainer 4 and the outer ring 5. The beneficial effects of this design are as follows: When the chamber is not filled with air and there is no air pressure, the first spring 53 is under pressure, pushing the outer ring 5 towards the piston 11. At this time, the second spring 43 is not under force and is in a freely extended state. The roller 41 is under force, and the inner ring 3 and friction sleeve 22 receive pressure from the roller 41, causing the break groove 31 to close, thus locking the friction sleeve 22 onto the spindle 2. At this time, the entire device is in a locked state, and the spindle 2 is tightly locked by the friction sleeve 22. When air is filled into the air chamber 12, the first spring 53 is under pressure, pushing the outer ring 5 towards the piston 11. The piston 11 moves towards the outer ring 5, and the outer ring 5 moves due to the contact of the piston 11. At this time, the second spring 43 is still not under force, the steel ball is not under force, and the inner ring 3 and friction sleeve 22 are not under force. Since the inner ring 3 and friction sleeve 22 have a break groove 31 on their cylindrical surfaces, the inner ring 3 and friction sleeve 22 can be freely unfolded and do not contact the spindle 2. At this time, it is in the open state, and the spindle 2 can move axially and rotate circumferentially. If inflation continues, the outer ring 5 continues to move, and the second spring 43 is under force, ensuring that the cage 4 assembly does not detach from the raceway of the outer ring 5. The first spring 53 transmits pressure through the shaft retaining ring 51, pushing the outer ring 5 to fit tightly against the piston 11, so that the tapered hole of the outer ring 5 produces precise radial compression against the roller 41; after the roller 41 is subjected to force, it transmits the pressure to the inner ring 3 and the friction sleeve 22. Since both are provided with a break groove 31 along the length of the lock body 1, the break groove 31 closes quickly under the action of pressure, and the inner wall of the friction sleeve 22 and the outer peripheral wall of the spindle 2 form a tight wrapping contact.This force transmission path efficiently converts the elastic potential energy of the first spring 53 into the locking force between the friction sleeve 22 and the spindle 2, preventing the spindle 2 from axially moving or rotating due to external forces. This is especially suitable for scenarios where electric vehicles, construction machinery, and other equipment need to be parked for extended periods, effectively preventing equipment displacement or theft. Simultaneously, the clearance fit between the friction sleeve 22 and the spindle 2 transforms into an interference fit during locking. Combined with the wear-resistant material properties of the friction sleeve 22 itself, this further enhances locking stability and extends the lock's service life. When air is introduced into the air chamber 12, the air pressure pushes the piston 11 along the outer circumferential wall of the positioning sleeve 21 through the air inlet 121. The piston 11 abuts against the outer ring 5 and overcomes the pressure of the first spring 53, causing it to move in the opposite direction. The squeezing effect of the tapered hole of the outer ring 5 on the roller 41 disappears instantly. After the roller 41 loses radial pressure, the inner ring 3 and the friction sleeve 22 freely unfold due to the elastic recovery capability of the fracture groove 31, disengaging from the spindle 2. At this time, the spindle 2 can flexibly achieve axial movement and circumferential rotation, meeting the component linkage requirements during equipment startup. The entire switching process relies solely on pneumatic drive, eliminating the need for manual operation of mechanical components. It boasts a fast response speed, and the piston 11's pushing force can be adjusted by controlling the intake air pressure, preventing damage to components due to excessive pressure. The air outlet 122 allows for rapid release of air pressure from the air chamber 12, enabling the lock to quickly return to its locked state. This adapts to high-frequency switching scenarios such as industrial equipment maintenance and temporary unlocking, improving operational efficiency. The positioning bushings 21 at both ends of the lock body 1 not only provide sliding guidance for the spindle 2 but also prevent external dust and rainwater from entering the lock body 1. The receiving cavity 13 isolates core components such as the friction sleeve 22 and bearings from the outside. Combined with the sealing effect of the piston 11 on the air chamber 12, it effectively prevents component jamming caused by impurities. The combined structure of the inner ring 3, outer ring 5, roller 41 and cage 4 of the bearing can reduce the frictional resistance when the spindle 2 is running and avoid wear of the components. Especially under continuous inflation, the second spring 43 abuts against the cage 4 and the outer ring 5, which can prevent the outer ring 5 from moving excessively and causing the cage 4 assembly to disengage from the raceway, ensuring that the lock can still work stably under high air pressure conditions.

[0018] As a further feature of the present invention, a gap groove is provided between the friction sleeve 22 and the positioning bushing 21, and a mating flange 32 is provided on the outer peripheral wall of the inner ring 3, which is engaged in the gap groove. The beneficial effect of this configuration is that the engagement structure of the mating flange 32 and the gap groove can precisely limit the displacement of the inner ring 3 along the axial direction of the lock body 1, and prevent the inner ring 3 from shifting due to the squeezing of the roller 41 when it is not inflated and locked. This ensures that the force centers of the outer ring 5 tapered hole, the roller 41, and the inner ring 3 are always aligned, ensuring that the force transmission path does not shift, and allowing the break groove 31 to close evenly, avoiding the locking loosening caused by uneven local force on the friction sleeve 22. This structure also improves the linkage stability between the inner ring 3 and the friction sleeve 22. When the inner ring 3 is subjected to pressure from the roller 41, the mating flange 32 can transmit the force to the friction sleeve 22 through the gap groove, so that the two deform synchronously. This ensures that the clamping force of the friction sleeve 22 on the spindle 2 is more uniform, further optimizing the conversion effect of the clearance fit to the interference fit and reducing the wobbling space of the spindle 2. Moreover, when the lock is inflated and unlocked, the mating flange 32 can limit the inner ring 3 from over-expanding and prevent it from separating from the raceway of the outer ring 5. This provides precise positioning for the component reset when locking again, and continuously ensures the locking effect and service life of the lock.

[0019] As a further feature of the present invention, the friction sleeve 22 is configured in a split manner, comprising at least two sub-sleeves, which are fitted onto the mandrel 2 and have a clearance fit with the mandrel 2. The advantages of this configuration are: by configuring the friction sleeve 22 in a split manner as at least two sub-sleeves fitted onto the mandrel 2, the performance of the pneumatic lock is significantly optimized in terms of both locking uniformity and failure tolerance. Regarding the clamping effect, multiple sub-sleeves independently form a clearance fit with the mandrel 2. When not inflated and locked, the pressure transmitted by the inner ring 3 can be distributed to each sub-sleeve, ensuring that the fracture grooves 31 of each sub-sleeve can close evenly. This avoids the problem of localized loose fit caused by uneven deformation of the integral friction sleeve 22, resulting in more balanced force on the outer peripheral wall of the mandrel 2, significantly reducing the possibility of the mandrel 2 wobbling due to localized gaps, and further enhancing locking stability. This design establishes a failure redundancy mechanism. When a sub-sleeve fails on one side due to wear, abnormal deformation, or other reasons, the remaining sub-sleeves can still normally accept the pressure of the inner ring 3 and hold the spindle 2 tightly, ensuring that the lock will not lose its locking function due to the failure of a single component. This effectively improves the safety redundancy of the equipment under long-term use or complex working conditions, and is especially suitable for scenarios such as automobiles and construction machinery where the reliability requirements of locks are extremely high, reducing safety accidents and property losses caused by sudden lock failures.

[0020] As a further feature of the invention, the cage 4 is provided with a plurality of pockets, and the roller 41 is disposed in the pockets. A retaining ring 42 is engaged with the edge of the pocket, and the edge of the retaining ring 42 abuts against the roller 41. The beneficial effects of this arrangement are: by placing the retaining ring 42 within the pocket of the cage 4 and ensuring its edge abuts against the roller 41, the positional stability of the roller 41 can be guaranteed from multiple dimensions, providing crucial support for the reliable operation of the pneumatic lock. The retaining ring 42 also reduces direct friction between the roller 41 and the inner wall of the pocket, reducing component wear, extending the service life of the cage 4 and the roller 41, and ensuring that the pneumatic lock maintains stable motion accuracy even when switching between locking / unlocking states at high frequencies, making it suitable for long-term, high-frequency use scenarios.

[0021] As a further feature of the invention, a retaining ring 52 is fitted on the inner circumferential wall of the outer ring 5, and the second spring 43 abuts against the retaining ring 52. The beneficial effect of this arrangement is that it provides a stable and precise positioning support for the second spring 43. When the pneumatic lock is continuously inflated and the outer ring 5 is pushed and moved by the piston 11, the second spring 43 needs to limit the displacement of the cage 4 assembly through compression deformation; the retaining ring 52 can firmly fix one end of the second spring 43, preventing the spring from axially shifting or radially tilting due to force, ensuring that the spring force can accurately act on the cage 4, stably limiting the relative position of the cage 4 and the raceway of the outer ring 5, and preventing the cage 4 assembly from detaching.

[0022] As a further feature of the invention, a contact step is provided on the retainer 4 corresponding to the position of the second spring 43, and the other end of the second spring 43 abuts against the contact step. The beneficial effects of this design are: the contact step 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 axial direction of the lock body 1. Simultaneously, the step provides a stable force support point for the spring, reducing contact wear between the spring and the retainer 4, preventing force attenuation due to spring displacement after long-term use, further ensuring the limiting effect of the second spring 43 on the retainer 4 assembly, and improving the structural stability and operational reliability of the pneumatic lock under high-frequency switching conditions.

[0023] 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 pneumatic lock, characterized in that: The lock body includes a lock body with positioning sleeves at both ends. A spindle that penetrates the lock body is slidably fitted within each positioning sleeve. A piston is slidably mounted on the outer peripheral wall of each positioning sleeve, dividing the lock body into an air chamber and a receiving chamber. An air inlet and an air outlet are positioned on the lock body corresponding to the positions of the air chambers. A friction sleeve is fitted between the positioning sleeves and the spindle, with a clearance fit. The friction sleeve is disposed within the receiving chamber. A bearing is also fitted between the friction sleeve and the lock body, and the bearing includes an inner ring, an outer ring, and a roller. The lock body comprises a piston and a retainer. The inner ring is fitted over the friction sleeve. Both the friction sleeve and the inner ring have break grooves along the length of the lock body. The retainer is positioned between the inner ring and the outer ring. The roller is rotatably fitted onto the retainer. A circlip is provided on the outer peripheral wall of the outer ring. A first spring abuts against the circlip and the lock body. The first spring is fitted onto the outer ring. The inner hole of the outer ring is tapered. The larger end of the inner hole abuts against the piston. A second spring abuts against the retainer and the outer ring.

2. The pneumatic lock according to claim 1, characterized in that: A clearance groove is provided between the friction sleeve and the positioning bushing, and a mating flange is provided on the outer peripheral wall of the inner ring, which is engaged in the clearance groove.

3. The pneumatic lock according to claim 1, characterized in that: The friction sleeve is configured in a split manner, forming at least two sub-sleeves, which are sleeved on the mandrel and have a clearance fit with the mandrel.

4. The pneumatic lock according to claim 1, characterized in that: The cage is provided with a plurality of pockets, the roller 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 roller.

5. The pneumatic lock according to claim 1, characterized in that: A retaining ring with a hole is fitted on the inner circumferential wall of the outer ring, and the second spring abuts against the retaining ring with the hole.

6. The pneumatic lock according to claim 5, characterized in that: The cage is provided with an abutting step corresponding to the position of the second spring, and the other end of the second spring abuts against the abutting step.

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