High-reliability heavy-load overrunning clutch

Abstract

The invention discloses a high-stability heavy-load overrunning clutch. Comprising an inner ring cam, an outer ring gear, a sliding column arranged between the inner ring cam and the outer ring gear, a spring seat and a spring connected to the spring seat and the inner ring cam, and the spring is arranged on the corresponding side, deviating from the axis or the axial center line of the sliding column, of the axial center line of the spring. And the inner ring cam and the middle input shaft gear are respectively in clearance fit and positioning connection with the positioning device. The high-reliability heavy-load overrunning clutch is long in service life, high in bearing capacity, high in reliability and capable of being suitable for various working condition environments.

Description

Technical Field

[0001] The invention relates to a loader, and in particular to a high-reliability heavy-load overrunning clutch used in a gearbox of the loader. Background Art

[0002] The working life of overrunning clutches in the current industry is generally about 3,000 hours. In order to obtain high-performance overrunning clutches, researchers have to face technical challenges such as solving structural design, core parts material selection, and improving the wear resistance of core parts to increase the working life of overrunning clutches. Among them, structural design, core parts wear resistance, and load-bearing capacity improvement are the core issues in overrunning clutch design.

[0003] However, the main problems with the existing structure of the sliding column heavy-duty overrunning clutch in the industry are: first, the axial center line of the spring or the direction line of the force point is designed to pass through the axial center line of the sliding column, and the sliding column is prone to abnormal wear on the boss surface of the inner ring cam, forming pits on the surface of the boss surface, resulting in failure of the overrunning clutch; second, when the overrunning clutch works in an environment with poor working conditions or the cleanliness of the lubricating oil in the box is not good, the spring seat is easily blocked or blocked by foreign matter, causing the spring to get stuck, affecting the movement of the sliding column, so that it cannot be reset in time, resulting in clutch failure, which is also a more prominent common problem found in the actual use of the overrunning clutch; third, the commonly used internal connection structure of the overrunning clutch in the industry is unreasonable, and the middle and inner ring cam are connected by dozens of bolts, which is very inconvenient to assemble, disassemble and replace; fourth, the number of fatigue cycles of the spring of the overrunning clutch in the industry is generally about 3 million times, and the spring is prone to failure and has a short life. Summary of the invention

[0004] The purpose of the present invention is to provide a high-stability heavy-duty overrunning clutch to solve the problems in the prior art. The high-reliability heavy-duty overrunning clutch has a long service life, strong load-bearing capacity, high reliability, and can be applied to various working environments.

[0005] The technical solution of the high-reliability heavy-load overrunning clutch of the present invention includes an inner ring cam, an outer ring gear, a sliding column arranged between the inner ring cam and the outer ring gear, a spring seat, and a spring connected to the spring seat and the inner ring cam. The spring is arranged on the side whose axial center line deviates from the axis of the sliding column or the corresponding axial center line. The inner ring cam and the intermediate input shaft gear are respectively connected to the positioning device with clearance fit.

[0006] The distance that the axial center line of the spring deviates from the axis of the sliding column or the corresponding side of the axial center line is 1.6-2.5 mm.

[0007] The gear-proximal end of the intermediate input shaft of the intermediate input shaft gear is provided with a central internal threaded hole for assisting disassembly and assembly.

[0008] The present invention achieves the following beneficial technical effects by adopting its corresponding unique technical solutions: 1. The present invention reduces the degree of wear of related components by redesigning the internal structures such as the inner ring cam and the spring seat and improving the roughness of the boss surface, greatly improving the operating performance of the clutch and extending its service life. In particular, its substantial feature is to break the traditional setting structure and design concept of the conventional design in which the spring axis is set to the axis center of the slide column. It adopts the direction line of the spring force point or its axial center line to deviate from the center of the slide column by a certain distance. After the force analysis and calculation of the assembly, the boss surface of the inner ring cam will not have abnormal wear, and the spring and the slide column will not have abnormal wear. The reset ability is better, the bearing capacity of the boss surface can be increased by about 25%, the sliding column rotates more steadily and smoothly on the inner ring cam boss surface, and the coordinated performance of the interaction force between the spring force and the sliding column and the spring seat is optimized; 2. Due to the redesign of the connection structure between the intermediate input shaft and the inner ring cam, the assembly can be very convenient to assemble and disassemble; 3. Due to the redesign of the spring seat structure, the present invention prevents foreign matter from sticking and blocking, improves the anti-fouling performance of the assembly, and effectively avoids the clutch failure caused by this; 4. Due to the improvement of the lubrication structure, the working stability of the clutch is further improved. 5. The structural spring design of the present invention uses the Korean elephant brand KIS Made of KOS piano wire, the number of spring fatigue cycles is increased, thereby increasing the working life of the spring and improving the performance of the spring. Through tests, the designed number of spring fatigue cycles reaches 4.5-5 million times; 6. Through the improved setting of the supporting wall of the spring seat, the spring support is more stable, and the spring force performance is further improved and optimized; the present invention can be widely used in 6-7T loader gearboxes, and its working life can reach 6000-7000 hours, and can be applied to various working conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0009] Figure 1 It is a schematic cross-sectional structure diagram of a high-reliability heavy-duty overrunning clutch of the present invention; Figure 2 for Figure 1 A schematic diagram of the force structure of the spring seat and the sliding column in section along the AA line; Figure 3 It is a schematic diagram of the inner ring cam structure of the high-reliability heavy-load overrunning clutch of the present invention; Figure 4 It is a schematic diagram of the structure of the variable diameter positioning pin of the high reliability heavy load overrunning clutch of the present invention; Figure 5 It is a schematic diagram of the spring seat structure of the high-reliability heavy-load overrunning clutch of the present invention; Figure 6 It is a structural schematic diagram of another embodiment of the inner ring cam of the present invention. DETAILED DESCRIPTION

[0010] In order to further understand the technical solution of the present invention, the technical solution of the present invention is now clearly and completely described through embodiments in combination with the accompanying drawings.

[0011] like Figure 1-6 The high stability heavy load overrunning clutch of the present invention comprises an intermediate input shaft gear 1, an inner ring cam 4, an outer ring gear 5, a sliding column 6 arranged between the inner ring cam 4 and the outer ring gear 5, a spring seat 7 and a spring 8 thereof, etc.

[0012] The intermediate input shaft gear 1 and the inner ring cam 4 are fixedly connected by a fastening device, a convenient disassembly positioning device, and a pre-positioning device 20. The pre-positioning device includes a convex-concave stopper provided between the intermediate input shaft gear and the inner ring cam, and the convex-concave stopper includes a concave surface or a convex surface provided on the intermediate input shaft gear, and a convex surface or a concave surface provided on the corresponding wall surface of the inner ring cam and corresponding to the concave surface or the convex surface of the intermediate input shaft gear.

[0013] The fastening device includes fastening mounting holes 4-14 which are evenly distributed on the intermediate input shaft gear 1 and the inner ring cam 4 respectively corresponding to each other, and corresponding fastening bolts connected to the intermediate input shaft gear 1 and the inner ring cam 4 through the fastening mounting holes of the intermediate input shaft gear 1 and the inner ring cam 4.

[0014] The convenient disassembly and assembly positioning device includes a positioning hole and a positioning pin connected to the positioning hole. The positioning holes include a limited positioning pin hole 10 evenly distributed between the fastening and mounting holes of the intermediate input shaft gear 1 and opened on the intermediate input shaft gear 1, and an equal-diameter positioning pin hole 4-10 evenly distributed between the corresponding fastening and mounting holes 4-14 of the inner ring cam 4 and opened on the inner ring cam 4; The limiting locating pin hole 10 of the intermediate input shaft gear 1 includes a main locating hole at one end close to the inner ring cam 1 and a reduced diameter port section at the other end thereof, and a limiting step surface 10a for limiting the connection of the variable diameter locating pin is formed by the combined plane part of the main locating hole and the reduced diameter port section; the equal diameter locating pin hole 4-10 of the inner ring cam 4 is of the same diameter as the main locating hole of the limiting locating pin hole 10 of the intermediate input shaft gear 1.

[0015] The positioning pin is a variable diameter positioning pin 11. The variable diameter positioning pin includes a tensioning section 11b and a reduced diameter section 11c with a smaller diameter than the tensioning section 11b, and the combined plane portion of the tensioning section and the reduced diameter section forms a corresponding step surface or inclined surface 11a.

[0016] The tensioning section 11b of the variable diameter positioning pin 11 is connected with the main positioning hole of the limited positioning pin hole 10 of the intermediate input shaft gear 1 by interference fit 12, and the reducing diameter section 11c of the variable diameter positioning pin 11 is connected with the equal diameter positioning pin hole 4-10 of the inner ring cam 4 by clearance fit 13.

[0017] During assembly, the corresponding end of the reducing locating pin 11 is interference fit with the limiting locating pin hole 10 of the intermediate input shaft gear, and the chamfered surface of the corresponding end of the reducing locating pin is axially positioned by the annular small limiting step surface 10a of the limiting locating pin hole 10.

[0018] Through the special matching structure of the variable diameter positioning pin 11 and the limiting positioning pin hole 10 of the convenient disassembly and assembly positioning device, while realizing accurate positioning and limiting of the fixed connection between the intermediate input shaft gear 1 and the inner ring cam 4, it provides great convenience for the disassembly, assembly and replacement of assemblies such as the intermediate input shaft gear 1 and the inner ring cam 4, simplifies the installation process, especially improves the installation and assembly accuracy, and obtains better clutch operation stability and reliability.

[0019] The gear-proximal end of the intermediate input shaft of the intermediate input shaft gear 1 is provided with a central internal threaded hole 3 for assisting disassembly and assembly. The intermediate input shaft gear 1 is provided with multiple evenly distributed enhanced lubricating oil holes. The enhanced lubricating oil holes can compensate and strengthen the lubrication of the corresponding bearings, further improving the running stability of the clutch.

[0020] A plurality of slide posts 6 are respectively arranged between the corresponding boss surfaces 2 of the inner ring cam 4 and the outer ring gear 5, and the spring seat 7 is arranged in the guide blind hole 17 of the inner ring cam 4. The outwardly extending end of the spring seat 7 is in contact connection with the outer peripheral side wall of the slide post 6. The spring seat 7 and the spring 8 (including the guide blind hole) are arranged at a certain distance 16 from the axis or axial center line of the slide post 6 or its force point direction line 15. That is, if Figure 2 As shown, on the same plane as the cross section of the sliding column 6 and the axial cross section plane of the spring 8 (including the spring seat 7), the axial center line of the spring 8 or / and the spring seat 7 or the force point direction line 15 deviates from the axis of the sliding column 6 or the corresponding side of the axial center line by a certain distance 16. The spring seat 7 forms a mutual compression with the corresponding part of the peripheral wall surface of the sliding column 6 at the end wall side away from the center of its axis. According to the force analysis and calculation of the assembly, its spring and roller reset ability is better, the plane bearing capacity of the inner ring cam boss surface can be increased by about 25%, the sliding column moves and rotates on the inner ring cam boss surface more steadily and smoothly, and the inner ring cam boss surface will not produce abnormal wear, so that it can be applied to the super-heavy load overrunning clutch assembly.

[0021] The spring of the present invention is made of a new material of Korean elephant brand KIS KOS piano wire.

[0022] The bottom wall surface 7b of the accommodating guide cavity 7a of the spring seat 7 is set to be a flat wall surface. A drainage notch 7c is provided on one side wall of the spring seat 7 near one end of the bottom wall surface of the guide cavity 7a. The spring 8 is arranged between the bottom wall surface 7b of the accommodating guide cavity of the spring seat 7 and the bottom wall surface of the guide blind hole of the inner ring cam 4. The anti-fouling spring seat structure is formed by the drainage notch 7c, which can effectively prevent the normal function of the spring force from being affected by the adhesion and blocking of the accommodating guide cavity of the spring seat, and the anti-fouling performance of the assembly can be improved by about 30%.

[0023] In another embodiment, the bottom wall surface 17a of the guide blind hole 17 of the inner ring cam 4 and the bottom wall surface of the spring receiving guide cavity of the spring seat are respectively set as flat wall surfaces, and the opposite end surfaces of the spring 8 are set as flat wall surfaces. The opposite end surfaces of the spring 8, the flat wall surface 7b of the receiving guide cavity of the spring seat 7, and the flat wall surface 17a of the guide blind hole 17 of the inner ring cam 4 are perpendicular to the axial center line or the force direction line of the spring 8. It can obtain special interactive and coordinated operation performance, can fundamentally further improve the stability of the spring support, and improve the spring force performance. The rest of the configuration structure, connection method, etc. of this example are similar to the above-mentioned embodiment.

[0024] In another embodiment, the distance 16 of the axial center line of the spring seat 7 and the spring 8 or the force point direction line 15 deviates from the corresponding side of the axis or axial center line of the sliding column 6 is 1.6-2.5 mm. An angle 18 is formed between the tangent line of the pressing contact force point 19 of the sliding column 6 and the end surface plane of the spring seat. The roughness of the boss surface of the inner ring cam 4 is designed to be Ra0.4. In this example, the angle 18 can be 0.03-0.3 degrees. The rest of the configuration structure, connection method, etc. of this example are similar to those of the above-mentioned embodiment.

Claims

1. A high-reliability heavy-duty overrunning clutch, comprising an inner ring cam, an outer ring gear, a sliding post disposed between the inner ring cam and the outer ring gear, a spring seat, and a spring connected to the spring seat and the inner ring cam, wherein the characteristics are The spring is arranged at a side of which the axial center line deviates from the axis of the sliding column or the corresponding axial center line, and the inner ring cam and the intermediate input shaft gear are respectively connected with the positioning device in a clearance fit.

2. The high reliability heavy load overrunning clutch according to claim 1 is characterized in that The distance that the axial center line of the spring deviates from the axis of the sliding column or the corresponding side of the axial center line is 1.6-2.5 mm.

3. The high reliability heavy load overrunning clutch according to claim 1 is characterized in that The gear-proximal end of the intermediate input shaft of the intermediate input shaft gear is provided with a central internal threaded hole for assisting disassembly and assembly.

Images