Design by wear gear _3709

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Design by Gear Wear

m) (1) where: IP - lubrication parameters, LP = m × 10 \(u +1); where: a - center distance, mu w-tooth of a gear ratio on the surface of the load per unit width; Received rl of; 1996-03-08, revised manuscript received H of: 19,[link widoczny dla zalogowanych],960,409 Union Male .】 955 years old. Associate Professor; Wuhan. hinder Ding, Wuhan University (43 /) 073), Wuhan Institute of spinning classes W = 106 (u +1 j / (uahcos ~) where: T2 - driven wheel torque,[link widoczny dla zalogowanych], N'Ill ; b - tooth width, m; mouth - helix angle,[link widoczny dla zalogowanych], by; 12 comprehensive roughness roughness is to calculate the thickness d comprehensive than the other ~ parameters. The formula for the =(+)( m) where.,[link widoczny dla zalogowanych], said driving and driven wheel surface roughness, and processing methods related to Richard from Table 1. Table 1, Table 1.3 Roughness ratio of film thickness ratio of film thickness: = Iml / will (3lJ dry one (1) order, may a ~ = 'A where: A = 25D? 5 (1) 12u-O.92 () 0.08 (LP.n2) - tooth width coefficient, = b/a2 wear calculation according to [2], gear The wear volume can be calculated. kFN,, q and i where: - engagement cycles; F. - Festival Tangent load, N; - gear material yield limit, N / ram; k - wear rate, values in Table 2. Table 2 Wear rate (6) organize,[link widoczny dla zalogowanych], get k (1 +11) N Canton (2) (3) (4) (5) (6) (7) 1996 Wuhan Institute of Textile Moment mean or linear interpolation. 324 Access (9) Calculate the aM5t (I】 79 × Jn... 005/02 Ⅱ], 1】 4j / / f-224lf6U910f2) 5102 ×】 0''I eleven thousand one hundred eleven 111111111111 Il'3 Chung Figure 2 Figure 325 to determine k values are the same strong conventional design. 33 trial design example of a mechanical gear drive design. known n2 = 70r/rain. Torque T2 = 670N'm, gear ratio u111/28, limit wear to O6mm, every single shift working, term l5 solution in c: choose pinion 45 steel (quenched and tempered). 45 steel gear selection (normalizing), gear. = 294N/mm2. Let section line speed <25m / s, 120 selected industrial gear oil; oil temperature is 5O ℃. computation of the parameters in Table 3: H 3 are the same routine: a little 2-way Union : design by wear gear 414 discussion from (10) to know; when combined factor M given time, there must be minimum) 'rain and maximum k ..., Q-points in Figure 1, which is the design operating point of dangerous. examples from the calculation to see: the original design center distance of 180mm, in this case the critical center distance ao is 205ram, which shows the design according to wear slightly larger than the size of the conventional design. (6) in the middle of the material yield limit of the original, the author hardened gear that should be the yield limit, if the yield limit with the hardened generation in this case, the critical center distance a-】 almost close to the center distance of conventional design. This shows that: on closed soft-tooth gear, lubrication well, if designed according to wear by pitting smaller than the size of the design means that pitting damage occurs preferentially, or else wear will be the main failure mode, therefore,} jj soft tooth transmission, should also press two methods to design, comparison, whichever is greater. For closed hard gear, worn the possibility of small, the risk of broken teeth relatively large, should be designed according to traditional methods.