A high-performance processing method of a drum gear

Abstract

The present application relates to the technical field of coupling gear, and discloses a high-performance gear processing method, which comprises the following steps: step one, processing a conventional gear by hobbing; step two, processing the conventional gear again by using a gear shaping cutter (3); and step three, calculating the gap of the gear, wherein the tooth thickness at the pitch circle of the gear, the coordinates of the involute on the y-axis, and the pressure angle at any position on the tooth profile are calculated first to obtain an involute l0 equation, and then the equation of the intersection curve G of the gear root and the inner tooth top is obtained according to the running track of the involute l0 on the gear surface, and finally, the minimum design gap of the gear is calculated based on the maximum coordinates of the curve G on the x-axis before and after rotation. The present application can effectively improve the gap of the conventional gear under the misalignment condition, and the movement of the gear shaping cutter parallel to the x-axis helps the entire gear surface to obtain mutually parallel involutes, which is helpful to improve the contact area of the gear and the carrying capacity of the gear.

Description

Technical Field

[0001] This invention relates to the field of coupling drum-shaped gear technology, specifically a method for machining high-performance drum-shaped gears. Background Technology

[0002] Gear couplings are widely used in various machinery industries, including metallurgy, mining, hoisting and transportation, petroleum, and shipbuilding, due to their compact structure, high load-bearing capacity, wide operating speed range, and reliable operation. Crank gear couplings are often machined using the gear hobbing method. This machining method results in the root of the cranked tooth and the tip of the internal tooth contacting first under misalignment conditions, thus limiting the misalignment angle of the crank gear coupling. For example, the allowable misalignment angle for crank gear couplings used in metallurgy is typically less than 1.5°, and generally does not exceed 2.5° under extreme conditions, severely restricting their application in transmission systems. Summary of the Invention

[0003] The purpose of this invention is to provide a high-performance method for machining drum-shaped teeth to solve the problems mentioned in the background art.

[0004] To solve the above-mentioned technical problems, the present invention provides the following technical solution: A method for machining high-performance drum-shaped teeth, the specific steps of which are as follows: Step 1: Machining conventional drum-shaped teeth using the gear hobbing method: ① Determine the radius of the travel circle of the gear hobbing cutter: , in: m Modulus, mm; z Number of teeth; R 1 represents the radius of the arc, in mm.

[0005] ② Define the machining path of the hobbing cutter on the hob teeth: .

[0006] Step 2: Perform secondary machining on conventional drum-shaped teeth using a gear shaper: ① Define the motion trajectory of the gear shaping cutter: .

[0007] ② The gear shaping cutter should always be kept parallel to the ground. y The orientation of the axis.

[0008] Step 3: Calculate the clearance of the drum-shaped teeth of the present invention: ① Calculate the tooth thickness at the pitch circle of the drum-shaped tooth. s : .

[0009] ② Calculate the tip circle diameter of the drum-shaped teeth and internal teeth to determine the involute curve. y coordinates of the axis y 1: , in: f This is the tooth tip height coefficient; C 1. C 2 represents the displacement coefficient of the drum-shaped teeth and the internal teeth; p 1 represents the tooth height variation coefficient.

[0010] ③ Calculate the pressure angle at any position on the tooth profile. α y : , in: r Let be the distance between the center of the coordinate system circle and any point on the involute.

[0011] ④ Calculate the distance from a point on the involute to the center point of the drum-shaped gear ring. y Angle between axes θ : , in: α This is the standard pressure angle; ⑤ Obtain z Involute at =0 l Equation 0: .

[0012] ⑥ Since the root of the drum-shaped tooth first contacts the tip of the inner tooth, the minimum design clearance should be designed based on the curve G where the root of the drum-shaped tooth intersects the tip of the inner tooth.

[0013] ⑦ The drum-shaped tooth surface of the present invention is composed of involutes l 0. Moving a certain distance along the trajectory of the gear shaper cutter, we obtain the equation of the curve G where the root of the drum-shaped tooth intersects the tip of the internal tooth: .

[0014] ⑧ Define the drum-shaped tooth winding y Axis rotation β The angle is obtained after rotation, assuming an equivalent actual misalignment condition. x The coordinates of the axis: .

[0015] ⑨ Based on the curve G before and after rotation x The maximum coordinate on the axis is used to calculate the minimum design clearance of the drum-shaped teeth. e : .

[0016] Compared with the prior art, the beneficial effects of the present invention are: This invention can effectively improve the clearance of traditional drum-shaped teeth under misalignment conditions, with the gear shaping cutter parallel to... y The movement of the shaft helps the entire drum-shaped tooth surface to obtain mutually parallel involutes, which helps to increase the contact area of ​​the drum-shaped teeth and improve their load-bearing capacity. Attached Figure Description

[0017] Picture 1 This is a diagram showing the travel path of the hobbing cutter and the gear shaping cutter of the present invention; Picture 2 This is a schematic diagram illustrating the forming principle of the drum-shaped teeth of the present invention.

[0018] In the diagram: 1—Gear hobbing cutter; 2—Gear hobbing wheel; 3—Gear shaping cutter; 4—Involute. Detailed Implementation

[0019] The following is in conjunction with the appendix Picture 1 —2 and the embodiments will be described in detail below.

[0020] In the first embodiment, a drum-shaped tooth with a module of 5mm, 50 teeth, a pressure angle of 20°, and a misalignment angle of 1.5° is used for calculation and analysis.

[0021] 1) Conventional drum-shaped teeth are machined using the gear hobbing method: ① Determine the radius of the travel circle of the gear hobbing cutter 1: (1) ② Define the machining path of hobbing cutter 1 on hob teeth 2: (2) 2) Use three gear shaper cutters to perform secondary machining on conventional drum-shaped teeth: ① Define the motion trajectory of the gear shaper 3: (3) ② For example Picture 1 As shown, the gear cutter 3 always remains parallel to... y The orientation of the shaft is used to obtain high-performance drum-shaped teeth.

[0022] 3) Calculate the clearance of the drum-shaped teeth of the present invention: ① Calculate the tooth thickness at the pitch circle of the drum-shaped tooth: (4) ② Take f It is 1.0. C 1. C 2 is 0, p 1 is 0. Calculate the tip circle diameter of the drum-shaped teeth and internal teeth to determine the involute curve 4. y The coordinates of the axis: (5) in: f C1 is the tooth tip height coefficient; C2 and C3 are the displacement coefficients of the convex tooth and the internal tooth, respectively. p 1 represents the tooth height variation coefficient.

[0023] ③ According to y The initial value of 1 is selected. r The value range is [118, 132]. A point is selected every 0.5 mm to calculate the pressure angle at any position on the involute 4: (6) α y / °: 5.475, 7.591, 9.223, 10.598, 11.806, 12.894, 13.89, 14.814, 15.677, 16.49, 17.259, 17.991, 18.689, 19.358, 20, 20.618, 21.214, 21.79, 22.348, 22.888, 23.412, 23.922, 24.418, 24.901, 25.371, 25.83, 26.278, 26.716, 27.144.

[0024] ④ Calculate the distance from a point on involute 4 to the center point of the drum-shaped gear ring. y Angle between axes θ : (7) q / °: 2.637, 2.609, 2.573, 2.531, 2.484, 2.432, 2.375, 2.315, 2.251, 2.183, 2.112, 2.038, 1.962, 1.882, 1.8, 1.715, 1.628, 1.539, 1.447, 1.353, 1.258, 1.16, 1.06, 0.958, 0.854, 0.749, 0.642, 0.533, 0.423.

[0025] ⑤ According to z Involute at =0 l Equation 0 calculates the tooth surface coordinates: (8) Table 1 Involute Coordinates 1 5.11059 120.285 0 11 3.75533 125.3952 0 2 5.01272 120.7995 0 12 3.57892 125.904 0 3 4.90543 121.3126 0 13 3.39586 126.4126 0 4 4.78925 121.8246 0 14 3.20626 126.9208 0 5 4.66459 122.336 0 15 3.01025 127.4287 0 6 4.53181 122.8468 0 16 2.80793 127.9363 0 7 4.39121 123.3571 0 17 2.59939 128.4436 0 8 4.24305 123.8671 0 18 2.38474 128.9506 0 9 4.08756 124.3768 0 19 2.16404 129.4572 0 10 3.92492 124.8862 0 20 1.93739 129.9634 0 ⑥ Calculate the coordinates based on the equation of the curve G where the root of the drum-shaped tooth intersects the internal tooth tip: (9) Table 2. Coordinates of points on curve G 1 5.11059 120 8.275338 11 3.75533 120 36.38631208 2 5.01272 120 13.87504 12 3.57892 120 38.1028184 3 4.90543 120 17.79704 13 3.39586 120 39.75088424 4 4.78925 120 21.00567 14 3.20626 120 41.33865498 5 4.66459 120 23.79264 15 3.01025 120 42.87279012 6 4.53181 120 26.29313 16 2.80793 120 44.35884458 7 4.39121 120 28.58289 17 2.59939 120 45.80137648 8 4.24305 120 30.70934 18 2.38474 120 47.20439239 9 4.08756 120 32.70449 19 2.16404 120 48.57119984 10 3.92492 120 34.59119 20 1.93739 120 49.90473665 ⑦ Define the drum-shaped tooth winding y Axis rotation β The (1.5°) angle is calculated based on the equivalent actual misalignment condition, after rotation. x The coordinates of the axis: (10) Table 3 Curve G around y Coordinates of the point after rotating the axis by 1.5° <![CDATA[ X 2 / mm]]> 5.32546 5.37421 5.36962 5.33747 5.28581 5.21853 5.13792 NO. 8 9 10 11 12 13 14 <![CDATA[ X 2 / mm]]> 5.04547 4.94226 4.82907 4.70653 4.57511 4.43525 4.28728 NO. 15 16 17 18 19 20 <![CDATA[ X 2 / mm]]> 4.1315 3.96815 3.79744 3.61959 3.43474 3.24308 ⑧ Obtained from Tables 3 and 2 X 2max For 5.37421mm and x max Given a value of 5.11059 mm, calculate the minimum design clearance for the drum-shaped teeth: (11) In the second embodiment, a drum-shaped tooth with a module of 2mm, 30 teeth, a pressure angle of 20°, and a misalignment angle of 1.5° is used for calculation and analysis.

[0026] 1) Conventional drum-shaped teeth are machined using the gear hobbing method: ① Determine the radius of the travel circle of the gear hobbing cutter 1: (12) ② Define the machining path of hobbing cutter 1 on hob teeth 2: (13) 2) Use three gear shaper cutters to perform secondary machining on conventional drum-shaped teeth: ① Define the motion trajectory of the gear shaper 3: (14) ② For example Picture 1 As shown, the gear cutter 3 always remains parallel to... y The orientation of the shaft is used to obtain high-performance drum-shaped teeth.

[0027] 3) Calculate the clearance of the drum-shaped teeth of the present invention: ① Calculate the tooth thickness at the pitch circle of the drum-shaped tooth: (15) ② Take f It is 1.0. C 1. C 2 is 0, p 1 is 0. Calculate the tip circle diameter of the drum-shaped teeth and internal teeth to determine the involute curve 4. y The coordinates of the axis: (16) in: f C1 is the tooth tip height coefficient; C2 and C3 are the displacement coefficients of the convex tooth and the internal tooth, respectively. p 1 represents the tooth height variation coefficient.

[0028] ③ According to y The initial value of 1 is selected. r The value range is [28, 33]. A point is selected every 0.2 mm to calculate the pressure angle at any position on the involute 4: (17) α y / °: 1.465, 6.959, 9.704, 11.806, 13.567, 15.108, 16.49, 17.751, 18.915, 20, 21.018, 21.978, 22.888, 23.754, 24.58, 25.371, 26.13, 26.86, 27.563, 28.241, 28.897, 29.531, 30.146, 30.742, 31.321.

[0029] ④ Calculate the distance from a point on involute 4 to the center point of the drum-shaped gear ring. y Angle between axes θ : (18) q / °: 3.854, 3.82, 3.76, 3.684, 3.595, 3.494, 3.383, 3.263, 3.135, 3, 2.858, 2.709, 2.553, 2.392, 2.226, 2.054, 1.878, 1.696, 1.511, 1.32, 1.126, 0.928, 0.725, 0.519, 0.31.

[0030] ⑤ According to z Involute at =0 l Equation 0 calculates the tooth surface coordinates: (19) Table 4 Involute Coordinates 1 1.89438 28.16489 0 14 1.28562 30.77398 0 2 1.89161 28.33938 0 15 1.20399 30.97738 0 3 1.87537 28.54027 0 16 1.11836 31.18067 0 4 1.85034 28.74205 0 17 1.02879 31.3838 0 5 1.81803 28.94435 0 18 0.93537 31.58675 0 6 1.77933 29.14703 0 19 0.83816 31.78949 0 7 1.7348 29.34998 0 20 0.73722 31.99198 0 8 1.68486 29.55315 0 21 0.6326 32.1942 0 9 1.62983 29.75648 0 22 0.52436 32.3961 0 10 1.56996 29.95992 0 23 0.41253 32.59766 0 11 1.50544 30.16343 0 24 0.29715 32.79885 0 12 1.43646 30.36697 0 25 0.17827 32.99963 0 13 1.36314 30.57049 0 ⑥ Calculate the coordinates based on the equation of the curve G where the root of the drum-shaped tooth intersects the internal tooth tip: (20) Table 5. Coordinates of points on curve G 1 1.89438 28 3.04319 14 1.28562 28 12.76863 2 1.89161 28 4.37269 15 1.20399 28 13.25134 3 1.87537 28 5.52694 16 1.11836 28 13.71985 4 1.85034 28 6.48887 17 1.02879 28 14.17543 5 1.81803 28 7.33317 18 0.93537 28 14.61926 6 1.77933 28 8.09626 19 0.83816 28 15.05230 7 1.7348 28 8.79894 20 0.73722 28 15.47536 8 1.68486 28 9.45456 21 0.6326 28 15.88919 9 1.62983 28 10.07214 22 0.52436 28 16.29439 10 1.56996 28 10.65818 23 0.41253 28 16.69154 11 1.50544 28 11.21751 24 0.29715 28 17.08112 12 1.43646 28 11.75384 25 0.17827 28 17.46355 13 1.36314 28 12.27008 ⑦ Define the drum-shaped tooth winding y Axis rotation β The (1.5°) angle is calculated based on the equivalent actual misalignment condition, after rotation. x The coordinates of the axis: (twenty one) Table 6 Curve G around y Coordinates of the point after rotating the axis by 1.5° <![CDATA[ X 2 / mm]]> 1.973 2.005 2.019 2.020 2.009 1.991 1.965 1.932 NO. 9 10 11 12 13 14 15 16 <![CDATA[ X 2 / mm]]> 1.893 1.848 1.799 1.744 1.684 1.619 1.550 1.477 NO. 17 18 19 20 21 22 23 <![CDATA[ X 2 / mm]]> 1.400 1.318 1.232 1.142 1.048 0.951 0.849 ⑧ Obtained from Tables 3 and 2 X 2max For 2.020mm and x max Given a clearance of 1.894 mm, calculate the minimum design clearance for the drum-shaped teeth: (twenty two) In the two sets of embodiments described above, the gear cutter is parallel to... y The movement of the shaft helps the entire drum-shaped tooth surface obtain mutually parallel involutes, which helps to increase the contact area of ​​the drum-shaped teeth, improve their load-bearing capacity, strengthen the application of the drum-shaped tooth coupling in the transmission system, and calculate the minimum design clearance of the drum-shaped tooth coupling of the present invention, thereby determining the key design parameters of the drum-shaped teeth of the present invention. At the same time, it can ensure the reasonable distribution of the load-bearing performance of each circumferential tooth pair, greatly improving the load-bearing performance of the drum-shaped tooth coupling.

[0031] The above description is merely a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. A method for machining high-performance drum-shaped teeth, characterized in that, Includes the following steps: Step 1: Machining conventional drum-shaped teeth using the gear hobbing method: ① Determine the radius of the travel circle of the hobbing cutter (1): ， in: m Modulus, mm; z Number of teeth; R 1 represents the radius of the arc, in mm; ② Define the machining path of the hobbing cutter (1) on the hobbing gear teeth (2): ； Step 2: Use a gear shaper (3) to perform secondary machining on the conventional drum-shaped teeth: ① Define the motion trajectory of the gear shaper (3): ； ② The gear shaping cutter should always be kept parallel to the ground. y The orientation of the axis; Step 3: Calculate the clearance of the drum-shaped teeth of the present invention: ① Calculate the tooth thickness s at the pitch circle of the drum-shaped tooth: ； ② Calculate the tip circle diameter of the drum-shaped teeth and internal teeth to determine the involute curve. y The coordinate of the axis y1: ， in: f This is the tooth tip height coefficient; C 1. C 2 represents the displacement coefficient of the drum-shaped teeth and the internal teeth; p 1 represents the tooth height variation coefficient; ③ Calculate the pressure angle at any position on the tooth profile. α y : ， in: r Let be the distance between the center of the coordinate system circle and any point on the involute. ④ Calculate the distance from a point on the involute to the center point of the drum-shaped gear ring. y Angle between axes θ : ， in: α This is the standard pressure angle; ⑤ Obtain z Involute at =0 l Equation 0: ； ⑥ Since the root of the convex tooth first contacts the tip of the inner tooth, the minimum design clearance should be designed based on the curve G where the root of the convex tooth intersects the tip of the inner tooth. ⑦ The drum-shaped tooth surface of the present invention is composed of involutes l 0. Moving a certain distance along the trajectory of the gear shaper cutter, the equation of the curve G intersecting the root and tip of the drum-shaped tooth is obtained: ； ⑧ Define the drum-shaped tooth winding y Axis rotation β The angle is obtained after rotation, assuming an equivalent actual misalignment condition. x The coordinates of the axis: ； ⑨ Based on the curve G before and after rotation x The maximum coordinate on the axis is used to calculate the minimum design clearance e of the drum-shaped teeth: 。

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