SU1312285A1 - Turn-over device frame turning mechanism - Google Patents

Abstract

This invention relates to lifting devices. The device allows to increase the resource and the accuracy of installation of the frame of the tilter in the specified position. For this, the rotation mechanism includes a housing 1, a gear shaft 2 interacting with the rack 3, hydraulic cylinders 4 and 5 for moving the rack 3. The rotation mechanism is equipped with additional hydraulic cylinders 6 and 7 that interact with the rack 3 and are installed with the possibility of Press the rails 3 to the gear shaft 2 with a variable force proportional to the force in the gearing and exceed the radial component of the latter. Each additional cylinder 6 and 7 contains two pistons forming cavities, each of which is hydraulically connected to the working cavity of one of the hydraulic cylinders 4 or 5. 4 Il. 7 v s (g from Y to to oo ate

Description

The invention relates to lifting devices, in particular, to turning mechanisms with alternating moment of resistance, mainly for tilters.

The purpose of the invention is to increase the resource and turning accuracy.

FIG. 1 shows the proposed device; in fig. 2 shows section A-A in FIG. I; in fig. 3 - plots of pressure change in the working cavities of the cylinders of the forward and reverse stroke of the rail and the pressure of the rail against the gear shaft on the angle of rotation of the center point of the frame of the turning device counterclockwise .; figure 4 is the same, with the direction of rotation clockwise.

The rotation mechanism of the frame of the collar includes a housing 1 housed in the housing so as to rotate the shaft gear 2, associated with a rotary frame of the turning device (not shown), a rack 3, engaged with the shaft gear 2 and placed in the housing with the possibility of reciprocating movements, hydraulic cylinders 4 and 5 of the forward and reverse stroke of the rail 3, up to FIG. 3 for the conditions described above, the dependence of the force F is given

supplementary hydraulic cylinders 6 and 7,

mounted on the body of the perpendicular 30, clamping the toothed rack 3 to the wap of the pin and the rail interacting with it. stubble 2, defined as the difference

In the cylinders 6 and 7, the main piston 8 is placed. And in addition, the force developed by the hydrocylinins 6 and 7 and the radial component is in engagement. The value of F

nyu 9, interacting with his shto- (minimum clamping force) defined Wff f f f "kl H-G / CHTCH TGGT." "Q-gI o O ril-UH. Jj

a lump with the main piston 8 and forming the cavities of the working chambers a and b, each of which communicates with the working chamber of the hydraulic cylinders 4 and 5 of the stroke

reiki. I

In addition, the mechanism provided. hydraulic distributor, two hydraulic valves 10 pressure, equipped with check valves, and a system of hydraulic lines 11.

The mechanism of rotation of the frame tilter works as follows.

When the working medium is supplied from the injection line through the hydraulic one, it is the ratio of the working diameters of the cylinders 4 and 5, the cylinders 6 and 7, and the angle of engagement of the rack 3 with the shaft-gear-vjO 2. The pressing force F is incremented by setting the pressure valves 10 .

45

FIG. Figure 4 shows the same relationship for the case where the rotation is clockwise.

As can be seen from FIG. 3 and 4 pressure in the working cavity of the hydraulic cylinder 5 (when rotated clockwise, it

the limiter in the post and one of the 50 is connected with the discharge line) on all ro cylinders 4 or 5 (the turning path is equal to or greater than the LR.

the position of the hydraulic distributor), the toothed rack 3 is moved and the shaft-pinion shaft 2, which interacts with the rack 3, is moved by means of gearing and connected to the rotary frame of the turning device. The pressure required to move the tooth. When rotated counterclockwise (Fig. 3), the pressure in the working cavity of the hydraulic cylinder 4 (in this case, it is 55 connected with a pressure line) is all the way equal to or greater than P

Thus, the speed of rotation depends only on the feed

rail 3, there is the magnitude of the variable liquid in the discharge line and not

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on and depends on the magnitude and direction of the moment of resistance to rotation. FIG. Figure 4 shows the dependences of the change in pressure in the working cavities of hydraulic cylinders 4 and 5 on the angle of rotation C of the center of gravity of the revolving frame O in the direction of rotation clockwise (indicated by an arrow).

P - pressure in the working cavity

hydraulic rod 4, P - pressure in the working cavity of the hydraulic cylinder 5, JP - pressure drop, due to the setting of the hydraulic valves 10 pressure. Hydraulic cylinders 6 and 7 move

gear rail 3 relative to hydraulic cylinders 4 and 5, thereby selecting a gap in the gearing of the gear shaft 2 and rail 3.

Pistons 8 of the same area each form two working chambers a and b in hydraulic cylinders 6 and 7, which provides the amount of force developed by hydraulic cylinders corresponding to the greater pressure in the working cavities of hydraulic cylinders 4 and 5 and proportional to the force in the gearing of the toothed rack 3 and gear shaft 2

FIG. 3 for the conditions described above, the dependence of the force F is given

between the force developed by the cylinders 6 and 7 and the radial component in the engagement. The value of F

(minimum clamping force) defined by JJ

It is the ratio of the working diameters of the hydraulic cylinders 4 and 5, the hydraulic cylinders 6 and 7, and the angle of engagement of the rack 3 with the shaft-gear-vjO 2. The pressing force F increment is determined by the setting of the hydraulic valves 10 pressure.

45

FIG. Figure 4 shows the same relationship for the case where the rotation is clockwise.

When turning counterclockwise (Fig. 3), the pressure in the working cavity of the hydraulic cylinder 4 (in this case, it is 55 associated with the injection line) is all the way equal to or greater than P

Thus, the speed of rotation depends only on the feed

313

depends on the magnitude and direction of the moment of resistance to rotation.

From the dependences of the length of the clamp F, shown in FIG. 3 and 4, it can be seen that it also does not depend on the magnitude and direction of the moment of turning resistance, but is determined by the design parameters of the device and the setting of the hydraulic valves 10 pressure. This makes it possible to manufacture a device with a minimum-large clamping force of the rack to the gear shaft 2 and with high efficiency.

Claims (1)

Invention Formula A panii tilting mechanism comprising a housing housed in the housing so as to rotate a pinion shaft, a toothed rack, hooked onto the pinion shaft and mounted in the housing to be able to 54 reciprocating movement, forward and reverse hydraulic cylinders of the rail and at least one additional hydraulic cylinder mounted on the housing perpendicular to the rail and interacting with it to press the rail to the gear shaft, which is characterized by the fact that resource and accuracy of rotation, it is equipped with an additional piston placed in an additional hydraulic cylinder and interacting with its rod with the main piston of the secondary hydraulic cylinder, and the strength limited by the body of the additional hydraulic ilindra and additional porschnem, and the cavity delimited by the additional cylinder body, its primary and secondary pistons, communicate with sootvetstvukschim of said cylinders running rail. LA FIG. 2 sh Compiled by A. Mazilkin Editor P.Gereti Tehred M.Hodanich Order 1951/33 Tyrals 812. Subscription VNIIPI USSR State Committee for inventions and discoveries 113035, Moscow, Zh-35, Raushsk nab., 4/5 Production printing enterprise, Uzhgorod, st. Project, 4 90 figl Iwf Proofreader A. Vorovich