Design method of seal ring sleeve tooth-shaped chain

Abstract

The invention discloses a design method of a seal ring sleeve tooth-shaped chain, and belongs to the technical field of tooth-shaped chains. A tooth-shaped design thought of combining a transition arc structure and an inner-outer composite meshing mechanism is adopted, and the tooth-shaped included angle is reduced by optimizing the arc of a tooth part of a chain plate; continuous abrasion caused by top cutting interference between the tooth top of the chain wheel and the tooth bottom of the chain plate in the actual transmission process is avoided, and stress pitting corrosion and aggravation of abrasion caused by too small instant contact face of meshing of the chain wheel and the chain are also avoided. The sheet type designed by adding a transition circular arc and an inner-outer composite meshing mechanism has better meshing performance in actual transmission, so that the phenomena of continuous wear, aggravated wear, tooth skipping, chain falling, loud noise and the like on a non-pavement bad road surface are fundamentally solved, and further chain system model selection is provided for the majority of motorcycle users.

Description

Technical Field

[0001] This invention belongs to the field of toothed chain technology, specifically relating to a design method for a sealing ring sleeve toothed chain. Background Technology

[0002] While some existing chain drive technologies incorporate toothed chains, these designs are primarily suited for sealed oil bath environments and cannot meet the demands of exposed external drive transmissions in motorcycles. Furthermore, traditional motorcycle external drive chains suffer from the following drawbacks under high impact and high speeds: interference between the sprocket tooth tip and the chain plate tooth root during actual transmission, leading to continuous wear; insufficient instantaneous contact area between the sprocket and chain causing stress pitting, further exacerbating wear; and issues such as skipped teeth, chain slippage, and excessive noise on unpaved and rough roads. Summary of the Invention

[0003] This invention discloses a design method for a sealing ring sleeve toothed chain, aiming to solve the following problems existing in the prior art: interference between the sprocket tooth tip and the chain plate tooth bottom during actual transmission, causing continuous wear; insufficient instantaneous contact surface between the sprocket and chain causing stress pitting, which exacerbates wear; and phenomena such as tooth skipping, chain slippage, and high noise on unpaved and harsh road surfaces.

[0004] To achieve the above objectives, the technical solution of the present invention is as follows: A design method for a sealing ring sleeve toothed chain, the design method comprising: Method 1: Design methods for internal and external connecting plates; Method 2: Design method for guide plates.

[0005] Preferably, in Method 1 and Method 2, the inner chain plate, outer chain plate, and guide plate all adopt a transition arc structure + inner-outer composite meshing mechanism tooth shape, and the back of all three are reserved with weight reduction and heat dissipation arcs.

[0006] Preferably, in the method one, the design parameters of the tooth profile of the transition arc structure + inner-outer composite meshing mechanism include: hole center distance a, edge center distance f, tooth half angle a, large transition arc curvature radius R1, extension amount δ, and chain plate waist height Hy.

[0007] Preferably, the hole center distance a = p - Δ, where p is the chain pitch and Δ is a correction amount, which is 0.5-1.5 mm.

[0008] The design of the center distance f is as follows: when the chain pitch P ≤ 15.875 mm and P ≥ 12.70 mm, f = 0.385P, and the tolerance correction is designed to be ±0.05 mm. The design of the tooth profile half angle α is: α=35° or α=40°; Tooth profile arc angle αi (tooth profile arc angle refers to...)Figure 2 The angle of the transition arc of the middle chain plate tooth foot is designed, and αi = R1.5 - R2.4 is selected; Design of the radius of curvature R1 of the large transition arc: R1 = P × (1.6-1.7 interval); (1.6-1.7 interval refers to the number between 1.6 and 1.7). The protrusion amount δ = 0.15~0.35mm; The height of the chain plate waist Hy = P / 2*K, and the coefficient k is 30%-40%.

[0009] Preferably, in method two, the design steps for the guide plate tooth profile are as follows: Step 1: Given the permissible range limit of chain drive anti-skid chain height: H = ( + ); where H refers to the ultimate anti-skid chain height, h refers to the diameter of the tooth tip circle da + tooth root circle Df, da refers to the tooth tip circle diameter, and D refers to the pitch circle diameter; Step 2: Using computer-aided design software (CAD), establish the reference coordinate O, draw the involute sprocket tooth profile, and design the values ​​of number of teeth z, module m, displacement coefficient x, root circle diameter Df, and tip circle diameter Da. Step 3: Draw the pitch circle according to the pitch circle formula D=mz; Step 4: Design the chain non-derailment height H within the allowable range, establish the guide plate tooth profile, and align the center of the two holes of the designed guide plate with the circumference of the sprocket pitch circle. Check whether there is interference or poor meshing between the guide plate tooth profile and the sprocket. Step 5: Based on the changes in pitch P, substitute the values ​​into the formula H = ( + ), and perform guide plate shape correction under different pitch P; Step 6: Design of the weight reduction hole. Assume the chain pitch P is: P = 12.70mm, P = 14.29mm, or P = 15.875mm. According to the formula, Dj = -k' calculates the diameter Dj of the weight reduction hole, with coefficient k' being 0.9; the position setting is related to the vertical transition arc at the bottom of the guide plate, and is usually set to be far away from the vertical transition arc, with the distance from the center of the weight reduction hole to the bottom of the vertical transition arc being greater than or equal to 80% of the diameter Dj of the weight reduction hole; Step 7: The back of the guide plate is designed with a weight-reducing and heat-dissipating curved arc R'. Step 8: The weight-reducing and heat-dissipating arc R' is the same as the weight-reducing and heat-dissipating arcs of the inner and outer chain plates. The starting point and ending point of the arc are the intersection of the vertical lines drawn upward from the center of the guide plate hole to the back of the tooth. The reference radius of the weight-reducing and heat-dissipating arc is 0.5mm. Adjust the reference radius according to the chain load and running speed. Increase the arc angle at low speed under heavy load, and vice versa at high speed under light load. Step 9: The guide plate 3 is made of carbon steel with carbon fiber material or polymer ceramic coating material on the surface.

[0010] The beneficial effects of the design method of the sealing ring sleeve toothed chain of the present invention are as follows: The present invention adopts a tooth design concept that combines a transition arc structure with an internal-external composite meshing mechanism. By optimizing the arc of the chain plate teeth and reducing the tooth angle, it avoids the interference between the top of the sprocket teeth and the bottom of the chain plate teeth during actual transmission, which would cause continuous wear. It also avoids stress pitting caused by an insufficient instantaneous contact area between the sprocket and the chain, which would exacerbate wear. The plate design with the added transition arc and internal-external composite meshing mechanism has better meshing performance in actual transmission, thereby fundamentally solving the problems of continuous wear, accelerated wear, tooth skipping, chain derailment, and high noise on unpaved and harsh roads, providing motorcycle users with further chain system selection options. Attached Figure Description

[0011] Figure 1 It is a type of sealing ring sleeve toothed chain with inner and outer chain plates; Figure 2 It is a structural form of adjacent inner and outer chain plates of a sealing ring sleeve toothed chain; Figure 3 This is an example of a sealing ring sleeve toothed chain inner and outer chain plates and guide plates structure; Figure 4 This involves the design of key parameters for the tooth profile of a sealing ring sleeve toothed chain and sprocket. Figure 5 This is an example of a sealing ring sleeve toothed chain guide plate meshing with a sprocket.

[0012] Marked in the image: 1. Outer chain plate; 2. Inner chain plate; 3. Guide plate; 3.1 Functional chain plate; 4. Involute sprocket tooth profile; 5. Outer edge of chain plate teeth; 6. Large transition arc; 7. Vertical transition arc; P, pitch; α, hole center distance; f, edge center distance; a, tooth profile half angle; αi, tooth profile arc angle; R1, radius of curvature of large transition arc; δ, extension amount; Hy, chain plate waist height; Df, tooth root circle diameter; Da, tooth tip circle diameter; H, anti-skip tooth height; Dj, weight reduction hole diameter; Dk, chain plate hole diameter; R', chain plate back arc. Detailed Implementation

[0013] The following description is merely a preferred embodiment of the present invention and is not intended to limit the scope of protection of the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

[0014] The following embodiments can be understood as illustrating a part of the structure or method of the present invention individually, or as combining the embodiments to explain the broader structure or method of the present invention.

[0015] Example 1: A design method for a sealing ring sleeve toothed chain, such as Figure 1-5 As shown, the design method includes: Method 1: Design methods for internal and external connecting plates; Method 2: Design method for guide plates.

[0016] like Figure 1-5 As shown, in Method 1 and Method 2, the inner chain plate, outer chain plate, and guide plate all adopt a transition arc structure + inner-outer composite meshing mechanism tooth shape, and the back of all three are reserved with weight reduction and heat dissipation arcs.

[0017] Example 2: like Figure 1-5 As shown, in the method one, the design parameters of the tooth profile of the transition arc structure + inner-outer compound meshing mechanism include: hole center distance a (the distance between the centers of the two chain plate holes), edge center distance f (the vertical distance from the outer edge 5 of the chain plate tooth to the center of the chain plate hole on the same side), tooth half angle a (the included angle between the outer edges 5 of the two chain plate teeth), large transition arc curvature radius R1 (the inner edge of the chain plate tooth is the large transition arc 6), protrusion δ (the distance by which the inner edge of the outer chain plate tooth protrudes beyond the inner edge of the inner chain plate tooth when the inner and outer chain plate holes of adjacent links overlap), and chain plate waist height Hy (the vertical distance from the top of the chain plate tooth groove to the center of the chain plate hole).

[0018] The hole center distance a = p - Δ, where p is the chain pitch and Δ is a correction amount, which is 0.5-1.5 mm.

[0019] The design of the center distance f is as follows: when the chain pitch P ≤ 15.875 mm and P ≥ 12.70 mm, f = 0.385P, and the tolerance correction is designed to be ±0.05 mm. The design of the tooth profile half angle α is: α=35° or α=40°; For the tooth profile radius αi design, αi = R1.5 - R2.4 is selected; Design of the radius of curvature R1 of the large transition arc: R1 = P × (1.6 to 1.7); The protrusion amount δ = 0.15~0.35mm; The chain plate waist height Hy = P / 2 * K, where the coefficient k is 30%-40%; like Figure 3 As shown, the back of the inner chain plate 2 and the outer chain plate 1 adopts a weight-reducing arc design to further reduce the weight of the chain and improve heat dissipation during transmission (because the arc-shaped concave surface increases the surface area of ​​the chain plate).

[0020] Example 3: like Figure 3-5As shown, in method two, the design steps for the toothed guide plate 3 are as follows: Step 1: Given the permissible range limit of chain drive anti-skid chain height: H = ( + ); where H refers to the ultimate anti-skid chain height, h refers to the diameter of the tooth tip circle da + tooth root circle Df, da refers to the tooth tip circle diameter, and D refers to the pitch circle diameter; Step 2: Using computer-aided design software (CAD), establish the reference coordinate O, draw the involute sprocket tooth profile 4, and design the values ​​of the number of teeth z, module m, displacement coefficient x, root circle diameter Df, and tip circle diameter Da. Step 3: Draw the pitch circle according to the pitch circle formula D=mz; Step 4: Design the chain non-derailment height H within the allowable range, establish the 3-tooth profile of the guide plate, and align the center of the two holes of the designed guide plate with the circumference of the sprocket pitch circle. Check whether there is interference or poor meshing between the guide plate teeth and the sprocket. Step 5: Based on the changes in pitch P, substitute the values ​​into the formula H = ( + ), and perform three-piece correction of the guide plate under different pitches P; Step 6: Design of the weight reduction holes (weight reduction holes refer to those set in the lower part of the guide plate). The size of the weight reduction hole Dj is usually proportional to the chain pitch P and fatigue strength. As the pitch P increases, the chain strength is higher, and the hole diameter Dj should be larger. This design proposes three commonly used pitches: P=12.70mm, P=14.29mm, or P=15.875mm. According to the formula, Dj= -k' calculates the diameter Dj of the weight reduction hole, with coefficient k' being 0.9; the position setting is related to the vertical transition arc 7 at the bottom of the guide plate 3. Generally, the weight reduction hole should be set far away from the vertical transition arc, and the distance from the center of the weight reduction hole to the bottom of the vertical transition arc should be greater than or equal to 80% of the diameter Dj of the weight reduction hole. Step 7: The back of guide plate 3 is designed with a weight-reducing and heat-dissipating arc R' to reduce the weight of the parts and improve the heat dissipation of the transmission. Step 8: The weight-reducing heat dissipation arc R' is the same as the weight-reducing heat dissipation arc of the inner chain plate 2 and the outer chain plate 1. The starting point and ending point of the arc are the intersection of the vertical line from the center of the guide plate hole upward to the back of the tooth. The reference radius of the weight-reducing heat dissipation arc is 0.5mm. The transition is natural. The reference radius is adjusted according to the load and running speed of the chain. The arc angle is increased at low speed under heavy load, and the opposite is true at high speed under light load. Step 9: The guide plate 3 is made of carbon steel with a carbon fiber coating or a polymer ceramic coating. This further improves lightweighting and enhances lateral wear resistance.

[0021] Based on the above method, complete the design of inner chain plate 2, outer chain plate 1, and guide plate 3. Combine the commonly used parts of the sealing ring toothed chain: sleeve, pin, and sealing ring, and assemble them into a sealing ring sleeve toothed chain that meshes with the involute sprocket.

Claims

1. A design method for a sealing ring sleeve toothed chain, characterized in that, The design method includes: Method 1: Design methods for internal and external connecting plates; Method 2: Design method for guide plates; In Method 1 and Method 2, the inner chain plate, outer chain plate, and guide plate all adopt a transition arc structure + inner-outer composite meshing mechanism tooth shape, and the back of all three are reserved with weight reduction and heat dissipation arcs.

2. The design method of the sealing ring sleeve toothed chain as described in claim 1, characterized in that, In the first method, the design parameters of the tooth profile of the transition arc structure + inner-outer compound meshing mechanism include: hole center distance a, edge center distance f, tooth half angle a, large transition arc curvature radius R1, extension amount δ, and chain plate waist height Hy.

3. The design method of the sealing ring sleeve toothed chain as described in claim 2, characterized in that, The hole center distance a = p - Δ, where p is the chain pitch and Δ is a correction amount, which is 0.5-1.5 mm. The design of the center distance f is as follows: when the chain pitch P ≤ 15.875 and P ≥ 12.70, f = 0.385P, and the tolerance correction is designed to be ±0.

05. The design of the tooth profile half angle α is: α=35° or α=40°; For the tooth profile radius αi design, αi = R1.5 - R2.4 is selected; Design of the radius of curvature R1 of the large transition arc: R1 = P × (1.6 to 1.7); The protrusion amount δ = 0.15~0.35mm; The height of the chain plate waist is Hy = P / 2 * K, and the coefficient k is 30%-40%.

4. The design method of the sealing ring sleeve toothed chain as described in claim 3, characterized in that, In method two, the design steps for the guide plate tooth profile are as follows: Step 1: Given the permissible range limit of chain drive anti-skid chain height: H = ( + ); where H refers to the ultimate anti-skid chain height, h refers to the diameter of the tooth tip circle da + tooth root circle Df, da refers to the tooth tip circle diameter, and D refers to the pitch circle diameter; Step 2: Using computer-aided design software (CAD), establish the reference coordinate O, draw the involute sprocket tooth profile, and design the values ​​of number of teeth z, module m, displacement coefficient x, root circle diameter Df, and tip circle diameter Da. Step 3: Draw the pitch circle according to the pitch circle formula D=mz; Step 4: Design the chain non-derailment height H within the allowable range, establish the guide plate tooth profile, and align the center of the two holes of the designed guide plate with the circumference of the sprocket pitch circle. Check whether there is interference or poor meshing between the guide plate tooth profile and the sprocket. Step 5: Based on the changes in pitch P, substitute the values ​​into the formula H = ( + ), and perform guide plate shape correction under different pitch P; Step 6: Design of the weight reduction hole. Assume the chain pitch P is: P = 12.70mm, P = 14.29mm, or P = 15.875mm. According to the formula, Dj = -k' calculates the diameter Dj of the weight reduction hole, with coefficient k' being 0.9; the position setting is related to the vertical transition arc at the bottom of the guide plate, and is usually set far away from the transition arc, with the distance from the center of the weight reduction hole to the bottom of the vertical transition arc being greater than or equal to 80% of the diameter Dj of the weight reduction hole; Step 7: The back of the guide plate is designed with a weight-reducing and heat-dissipating curved R'. Step 8: The weight-reducing and heat-dissipating arc R' is the same as the weight-reducing and heat-dissipating arcs of the inner and outer chain plates. The starting point and ending point of the arc are the intersection of the vertical lines drawn upward from the center of the guide plate hole to the back of the tooth. The reference radius of the weight-reducing and heat-dissipating arc is 0.5mm. Adjust the reference radius according to the chain load and running speed. Increase the arc angle at low speed under heavy load, and vice versa at high speed under light load. Step 9: The guide plate material is carbon steel base with carbon fiber material or polymer ceramic coating material on the surface.

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