High-reliability heavy-load overrunning clutch

Abstract

The utility model 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 utility model 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 typical service life of overrunning clutches in the industry is around 3,000 hours. To achieve high-performance overrunning clutches, researchers face challenges such as structural design, material selection for core components, and improving the wear resistance of these components. These challenges are crucial in overrunning clutch design, including structural design, improving the wear resistance of core components, and enhancing load-bearing capacity.

[0003] However, the main problems with the current industry's sliding column heavy-duty overrunning clutch structure are: first, the spring axial center line or the force point direction line is designed to pass through the sliding column axial center line, and the sliding column is prone to abnormal wear on the inner ring cam boss surface, forming pits on the boss surface, causing the overrunning clutch to fail; second, when the overrunning clutch works in an environment with poor working conditions or the lubricating oil in the box is not clean enough, the spring seat is easily obstructed or blocked by foreign matter, causing the spring to get stuck, affecting the movement of the sliding column, and preventing it from resetting 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 current industry is unreasonable, and the middle and inner ring cam are connected with dozens of bolts, which is very inconvenient to assemble, disassemble and replace; fourth, the number of fatigue cycles of the spring of the current overrunning clutch in the industry is generally about 3 million times, and the spring is prone to failure and has a short life. Utility Model Content

[0004] The purpose of the present invention is to provide a high-stability heavy-duty overrunning clutch to address the problems of 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 where its 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 utility model has achieved the following beneficial technical effects by adopting its corresponding unique technical solutions: 1. The utility model has reduced the wear of related components and greatly improved the operating performance of the clutch and prolonged its service life due to the redesign of the internal structures of the inner ring cam, spring seat, etc., and the improvement of the roughness of the boss surface, especially the substantial feature of the utility model is to break the traditional setting structure and design concept of the spring axis being set to the axis center of the sliding column in the conventional design. It adopts the direction line of the spring force point or its axial center line to deviate from the center of the sliding 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, the spring and sliding column have better reset capabilities, the boss surface plane bearing capacity can be increased by about 25%, the sliding column rotates more steadily and smoothly on the boss surface of the inner ring cam, and optimizes the coordinated performance of the interaction force between the spring force, the sliding column and the spring seat; 2. The design of the connection structure between the intermediate input shaft and the inner ring cam makes the assembly very convenient to assemble and disassemble; 3. The utility model prevents foreign matter from sticking and blocking due to the redesign of the spring seat structure, improves the anti-fouling performance of the assembly, and effectively avoids 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 utility model is made of Korean KISKOS piano wire, which increases the number of spring fatigue cycles, 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 utility model can be widely used in 6-7T loader gearboxes, its working life can reach 6000-7000 hours, and it can be applied to various working conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0009] Figure 1 This is a schematic cross-sectional view of the high-reliability heavy-load overrunning clutch of the utility model; Figure 2 for Figure 1 Schematic diagram of the force structure of the spring seat and the sliding column along the AA line; Figure 3 This is a schematic diagram of the inner ring cam structure of the utility model's high-reliability heavy-load overrunning clutch; Figure 4 This is a schematic diagram of the structure of the variable diameter positioning pin of the high reliability heavy load overrunning clutch of the utility model; Figure 5 This is a schematic diagram of the spring seat structure of the utility model's high-reliability heavy-load overrunning clutch; Figure 6 It is a structural schematic diagram of another embodiment of the inner ring cam of the present utility model. 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 post 6, a spring seat 7 and a spring 8 disposed between the inner ring cam 4 and the outer ring gear 5, and the like.

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

[0013] The fastening device includes fastening mounting holes 4-14 that are evenly distributed on the intermediate input shaft gear 1 and the inner ring cam 4, 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 conveniently removable positioning device includes positioning holes and positioning pins connected to the positioning holes. The positioning holes include limited positioning pin holes 10 evenly distributed between the fastening mounting holes of the intermediate input shaft gear 1 and provided on the intermediate input shaft gear 1, and equal-diameter positioning pin holes 4-10 evenly distributed between the corresponding fastening mounting holes 4-14 of the inner ring cam 4 and provided on the inner ring cam 4.

[0015] 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 end 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 portion of the main locating hole and the reduced diameter end 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.

[0016] The positioning pin is a variable diameter positioning pin 11. The variable diameter positioning pin includes a tensioning section 11b and a diameter-reducing section 11c with a smaller diameter than the tensioning section 11b. The joint plane of the tensioning section and the diameter-reducing section forms a corresponding step surface or inclined surface 11a.

[0017] 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.

[0018] During assembly, the corresponding end of the variable diameter 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 variable diameter locating pin is axially positioned by the annular small limiting step surface 10a of the limiting locating pin hole 10.

[0019] 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.

[0020] The intermediate input shaft of the intermediate input gear 1 is equipped with a central internal threaded hole 3 near the gear end to assist in assembly and disassembly. The intermediate input gear 1 is also equipped with multiple, evenly distributed reinforced lubrication holes. These reinforced lubrication holes provide enhanced lubrication to the corresponding bearings, further improving clutch operation stability.

[0021] Several slide posts 6 are disposed between corresponding boss surfaces 2 of the inner ring cam 4 and the outer ring gear 5. Spring seats 7 are disposed within guide blind holes 17 of the inner ring cam 4. The outwardly extending ends of the spring seats 7 are in contact with the outer peripheral sidewalls of the slide posts 6. The spring seats 7 and springs 8 (including the guide blind holes) are disposed so that their axial centerlines or their force-bearing point direction lines 15 are offset by a certain distance 16 from the axis or axial centerline of the slide posts 6. That is, Figure 2 As shown, in the plane of the cross section of the spool 6 and the axial cross section of the spring 8 (including the spring seat 7), the axial centerline of the spring 8 and / or the spring seat 7, or the direction line of the force bearing point 15, is offset a certain distance 16 to the corresponding side of the axis or axial centerline of the spool 6. The spring seat 7 forms a pressure contact with the corresponding portion of the circumferential wall of the spool 6 at the end wall portion away from the axial center. Analysis and calculation of the assembly's loads show improved spring and roller return capabilities, an approximately 25% increase in the bearing capacity of the inner ring cam boss surface, and smoother, more stable movement and rotation of the spool on the inner ring cam boss surface. Abnormal wear of the inner ring cam boss surface is also avoided, making the device suitable for use in ultra-heavy overrunning clutch assemblies.

[0022] The spring of the utility model is made of Korean Elephant brand KIS KOS piano wire new material.

[0023] The bottom wall 7b of the accommodating guide cavity 7a of the spring seat 7 is designed to be flat. A drainage notch 7c is defined in the sidewall of the spring seat 7, adjacent to one end of the bottom wall of the guide cavity 7a. The spring 8 is positioned between the bottom wall 7b of the accommodating guide cavity of the spring seat 7 and the bottom wall of the guide blind hole of the inner ring cam 4. The drainage notch 7c forms an anti-fouling spring seat structure, effectively preventing foreign matter from adhering to and blocking the spring seat accommodating guide cavity and affecting the normal function of the spring force. This improves the anti-fouling performance of the assembly by approximately 30%.

[0024] In another embodiment, if Figure 6 As shown. The bottom wall 17a of the guide blind hole 17 of the inner ring cam 4 and the bottom wall of the spring receiving guide cavity of the spring seat are both flat, and the opposite end faces of the spring 8 are also flat. The flat end faces of the spring 8, the flat bottom wall 7b of the receiving guide cavity of the spring seat 7, and the flat bottom wall 17a of the guide blind hole 17 of the inner ring cam 4 are perpendicular to the axial centerline or force direction of the spring 8. This achieves unique interactive and coordinated operating performance, fundamentally further improving the stability of the spring support and the spring force performance. The remaining structural configuration and connection methods of this example are similar to those of the above-mentioned embodiment.

[0025] In yet another embodiment, the axial centerline of the spring seat 7 and spring 8, or the force-bearing point direction line 15 thereof, deviates from the axis or axial centerline of the spool 6 by a distance 16 of 1.6-2.5 mm. A tangent line at the point of contact 19 of the spool 6 with the spring seat 7 forms an angle 18 with the end plane of the spring seat. The boss surface roughness of the inner ring cam 4 is designed to be Ra 0.4. In this embodiment, angle 18 can be 0.03-0.3 degrees. The remaining structural configuration and connection methods of this embodiment are similar to those of the above-described embodiment.

Claims

1. A high-reliability, heavy-duty overrunning clutch comprising an inner ring cam, an outer ring gear, a slide 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, characterized in that The spring is arranged on a side of which its axial center line deviates from the axis or the corresponding axial center line of the sliding column, 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.

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