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The input shaft 1 is a prime mover in a planetary gear-slider mechanism with a small-tooth difference, and it and the eccentric pin 8 constitute a planet carrier in the mechanism. When the car is turning, the driver gives the steering wheel a steering force. This force is transmitted to the front wheel steering gear and to the input shaft 1 in the rear wheel steering gear. When working, the shaft rotates around its axis O. Rotating; fixed inner ring 2 is a small-toothed planetary gear) central wheel in the slider mechanism, and planetary gear 3 is a follower in the mechanism. The planetary gear 3 meshes with the fixed internal ring gear 2, which revolves around the axis O of the input shaft 1 under the driving of the carrier while rotating about the axis P of the eccentric pin 8, the planetary gear 3 being centered around the center The center of the wheel is a rotary motion, and the movement of the other points is a plane motion; the eccentric pin 7 on the planetary gear 3 moves the slider 4 along the x (crossbar 5) and the plane movement with the planetary gear 3 y (guide block 6) moves in both directions))) The movement in the x direction causes the tie rod to translate left and right, and the movement in the y direction causes the slider 4 to slide up and down in the guide block 6. Compared with the general planetary gear transmission mechanism with less tooth difference, its output is different: the output of the general small-tooth difference planetary gear transmission is the rotation of the shaft equal to the angular velocity of the planetary gear to form an isosceles ratio mechanism; In this mechanism, its output is converted into the translation of the slider 4 by means of the planar motion of the planetary gears, and the translation of the slider 4 drives the tie rods 5 through the guide blocks 6 to drive the deflection of the rear wheels of the vehicle. It can be seen that as long as the slider 1 drives the tie rod to move left and right, the rear wheel of the vehicle can be deflected in different directions.
Schematic diagram of a small tooth difference planetary gear-slider mechanism 1, eccentric shaft 2, fixed inner ring gear 3, planetary gear 4, slider 5, tie rod 6, guide block 7, input shaft eccentric pin 8, planetary gear eccentric pin slip Block-rear wheel mechanism diagram 3 Analysis of steering characteristics by a small-tooth difference planetary gear-slider mechanism Although the rear wheel can be deflected with the rotation of the steering wheel driven by the slider mechanism of the small-tooth differential planetary gear, is it The high-speed steering can be achieved in the same direction as the front wheel and the low-speed (or in-situ) to the small wheel and the front wheel is deflected in the opposite direction. In the rear wheel steering gear, the gear ratio of the planetary gear transmission is I12 is the transmission ratio of the planetary gear to the planet carrier; n1 is the rotation speed of the planet carrier (the input shaft 1 and the eccentric pin 8) about the input shaft axis O; n3 is the rotation speed of the planetary gear 3 about the axis P; z2 and z3 respectively The number of teeth of the gear 2 and the planetary gear 3 is fixed. The gear ratio is negative, indicating that the planetary gear rotation direction is opposite to the input shaft rotation direction. If the transmission ratio i12=-3, the input shaft 1 rotates 270b in a certain direction about its axis O under the steering force, and the planetary gear 3 rotates in the opposite direction about the axis P while rotating accordingly. 90b. It can thus be proved that such a mechanism can be used to achieve the requirements of rear wheel steering.
When the eccentric pin 7 on the planetary gear 3 rotates about the axis P, the displacement curve in the x direction is as shown by the broken line 2 in the figure; the eccentric pin 7 drives the slider to displace in the x direction with respect to the axis O. The synthesis is shown in solid line 3 in the figure.
The output characteristic of the small tooth difference star gear-slider mechanism is that if the rotation angle D of the middle input shaft 1 is converted into the rotation angle H of the steering wheel, the displacement s of the slider along the x direction is converted into the deflection angle AA of the rear wheel of the automobile. At the same time, the change of the front wheel deflection angle AB with the steering wheel angle is also indicated. It is not difficult to see that when the rotation angle of the steering wheel is H=0, the rotation angles of the front wheel and the rear wheel are all zero, namely: AB=AA=0; when the rotation angle of the steering wheel is H>0, the rotation angle of the front wheel AB>0 And increases with the increase of the steering wheel angle, and the rear wheel is at the corner H0 of the steering wheel. At this time, the rear wheel is deflected in the same direction as the front wheel, but at the steering wheel angle H