Wenzhou Baoerte Autopart CO.,LTD was established in 1998,located in the east sea coast and China Auto & Motocycle parts metroplice city Rui'an, with convenient transportation access. The company is a trading company, engaged in tensioner pulley, Gas Spring, clutch bearing . All of our products comply with international quality standards.
510010410 Clutch Bearing,Clutch Slave Cylinder For Alfa Romeo,Central Slave Cylinder Opel,Clutch Central Slave Cylinde
510010410 Clutch Bearing,Clutch Slave Cylinder For Alfa Romeo,Central Slave Cylinder Opel,Clutch Central Slave Cylinde Wenzhou Baoerte Autopart CO.,LTD , https://www.baoerteautopart.com
The disc spring should use the third series of standard springs with less stiffness. The rated force Pf=0.75h should be about 50 larger than the F value calculated according to the formula; if the rated force of one spring is not enough, two discs can be used. The springs are superimposed. The round nut should be tightened so that the disc spring force is slightly greater than the F value; it is best to determine the degree of tightening by testing. During the test, fix the shaft of the pinion and apply grease between the teeth and the spiral spline to reduce the friction coefficient and approach the actual working conditions. Then use a torque wrench or other method to intermittently move the large gear. Apply the rated torque in the forward and reverse directions, and use a dial gauge to measure the disc spring at the end of the corresponding force, and feel a slight axial movement. It should be pointed out that when the above-mentioned damping device is used for an involute helical gear or a circular arc gear, when calculating the axial force F of the disc spring, the pinion gear should be axially moved due to the existence of the gear helix angle. The force Fc is superimposed. The force Fc can also be calculated with reference to the formula, except that r should be understood as the pitch radius of the pinion, and B should be understood as the helix angle of the pinion. It should be noted in the calculation that Fc and F will only be added when the helix angle of the pinion is opposite to the helix angle of the helical spline. At this time, the helix angle of the helical spline can be reduced or even reduced to zero; The helix angle of the pinion is the same as the direction of the spline helix angle, so the self-locking phenomenon may occur when the two forces cancel each other out; in addition, it should be noted that the friction coefficient of the gear is much smaller than that of the helical spline.
Effect of axial high-frequency vibration on the pitting corrosion resistance of the gear When the vibration damping device is used, the pinion gear has to perform axial high-frequency vibration with small amplitude due to the existence of high-pulsation dynamic load. This kind of vibration is to make the lubricating oil film existing between the teeth due to mutual rolling subject to additional shearing action, so as to cause the oil film to heat up and change the law of pressure distribution; theoretical analysis proves that this will make the gear resist pitting Increased carrying capacity. In order to clarify the mechanism, we first approximate the temperature rise caused by the relative sliding in the oil film.
According to Newton's formula, S=G0eapuh(2) where S, shear stress G0 in oil film, dynamic viscosity of lubricating oil at normal temperature and pressure a, pressure coefficient of lubricating oil p, pressure in oil film u, tooth surface The average relative axial sliding speed h, the frictional power N per unit area of ​​the oil film thickness can be calculated by the following formula: N = Su = G0eapu2h (3) If the unit tooth width and the oil film thickness K times are taken, the two teeth are examined. The time vt when the surface misses the interval is vt=khu(4) where k is the undetermined proportional constant. If the heat transfer loss is not counted, the local temperature rise vT in the oil film can be calculated as follows: vT=Nhvtkh2Cc(5) Lubricating oil density c, lubricating oil specific heat capacity Substituting formula (3) and formula (4) into the above formula can obtain vT=G0eapuhCc(6) If Pmax=500MPa is taken according to the relevant data, take a=2.3@108m2/N, then Obtain eapmaxU105; and take G0=0.04Pas; u=0.5m/s; h=1@106m; c=2@103j/(kge); C=900kg/m3 according to the usual situation; It can be calculated that the temperature rise vT of the oil film pressure peak can reach the order of 103e (the actual temperature rise is much lower due to the sharp decrease of the lubricating oil viscosity G0 due to the sharp heating surface and the strong heat exchange); At the pressure of one-half of the peak, the eap will be reduced to 102.5, and the adiabatic temperature rise will be reduced to about 3e. It can be seen that under the influence of axial sliding friction, then under the influence of the above temperature rise, the viscosity G0 and the pressure coefficient a of the lubricating oil at the peak of the pressure will decrease, which will drastically reduce the absolute value of the pressure gradient. Thus, the pressure peak will become dull and the peak band will become wider. For the gear of each material, under the allowable load, the maximum pressure Pmax in the oil film should be equal to the allowable contact stress of the material, and thus a certain value; then the greater the width of the pressure peak band, the greater the bearing capacity of the oil film. Therefore, the above temperature distribution is very favorable for improving the oil film carrying capacity.
Tests have shown that when the teeth are meshed outside the joint, no reasonable explanation has been found for this. Due to the limited conditions, the proposed damping device could not be trial-produced and further studied; whether it can achieve the expected results remains to be tested. However, theoretical analysis proves that when the high-speed gear adopts the device, the anti-gluing bearing capacity can be significantly improved because the dynamic load can be significantly reduced; when the low-speed gear adopts the device, the anti-point of the joint is weakened due to the dynamic load reduction. The eccentric load capacity can be increased by more than 60, so it is expected to nearly double the pitting resistance of the entire gear transmission. It can be seen that it has great potential economic value, so it is hoped that conditional gear researchers will conduct further research and exploration on the device.