CN205331348U - Velocity ratio transmission such as trend change of times wheel base - Google Patents

Abstract

The utility model discloses a based on the velocity ratio transmission such as trend change of times wheel base of parallelogram and isosceles triangle combination, mainly be applied to in two smooth roll breakers of material processing in small, broken bits the equal velocity ratio transmission of two smooth rolls. Left input gear and right output gear including the mutual disposition, left side input gear is fixed axis rotation for the frame, right side output gear fixed mounting steps down slider slidable mounting in the frame on the slider of stepping down, still include the first planet wheel with left input gear engaged with to and and right output gear engaged with second planet wheel, support by parallelogram mechanism between a left side input gear, first planet wheel, second planet wheel and the frame, support by isosceles triangle mechanism between second planet wheel, right output gear and the frame. The utility model discloses both having solved enough big problems of wheel base change volume, and have sufficient space again and solve equicohesive problem, and vertical size being less relatively, vertical length of box is more reasonable with comparing of lateral length.

Description

The speed ratio transmission devices such as a kind of time-varying wheelbase

Technical field

This utility model relates to disintegrating machine technical field, specifically the speed ratio transmission device such as a kind of time-varying wheelbase based on the combination of parallelogram and isosceles triangle, the speed ratio transmission such as grade being mainly used in double; two beam roller crushers of material processing in small, broken bits two smooth rolls。

Background technology

Double; two beam roller crushers are widely used in the processing in small, broken bits of various mineral。Double; two beam roller crushers can adopt Dual-motors Driving, namely a motor is by one roller of deceleration rear drive, another motor passes through another roller of deceleration rear drive, the shortcoming of the method is that two rollers are difficult to that rotating speed is equal in magnitude, turn to contrary, thus brings the Fast Wearing of two roller surfaces。Double; two beam roller crushers can also adopt motor to drive, and motor passes through one roller of deceleration rear drive, and motion and power are passed on by another roller by drive mechanism, the rotating speed of this roller and first roller equal in magnitude, turn on the contrary。Whether double; two beam roller crushers of Dual-motors Driving, or single motor-driven pair of beam roller crusher, the axis of two rollers must be one and make fixing, and another is made and can step down。Double; two beam roller crushers will be crushed in the way of extruding by the material between dead axle line roller and moving axis line roller, owing to extrusion stress is big, exceed the shearing limit of the material that is broken, so, the rotating speed of two rollers is equal in magnitude, it is contrary to turn to, to avoid two roller surfaces and the roller surfaces Fast Wearing being broken between material to produce relative sliding and causing；Again owing to the material that is broken there will be foreign body unavoidably, namely be not raw meal particle size excessive, just be non-broken material or feed too much, at this moment, extruding can not be continued, otherwise, may result in that roller surfaces damages by pressure, the spring bearing of roller destroys or driveline damage etc., for this, in two rollers need to be made dead axle line, another make moving axis line。When material is carried out attrition crushing by two rollers; when the foreign body that hardness is bigger enters or material is too much; crushing force exceedes the value of setting; moving axis line roller is stepped down; they are let slip, thus protecting drive mechanism etc. to avoid damaging, after foreign body is let slip; moving axis line roller resets, and is again introduced into normal broken state。Step down and reseting procedure, if crushing force is relatively little, it is possible to realized by spring mechanism；If crushing force is relatively very big, it is possible to realized by oil cylinder mechanism。

In single motor-driven pair of beam roller crusher, it is proposed that the problem of the speed ratio drive mechanisms such as time-varying wheelbase。In early days, have been used up long tooth transmission and solve this problem, the advantage of long tooth transmission is that the wheelbase variable quantity that mechanism is simple, shortcoming allows for is too little, wheelbase change time tooth surface abrasion fast and be susceptible to broken teeth accident。Later, have employed five bar four gears and become the speed ratio drive mechanisms such as wheelbase, it solves the problem that wheelbase variable quantity is too little up hill and dale, but higher pair therein constraint is still that a weak link, gear in higher pair occurs broken teeth phenomenon often, and does not have enough spaces to strengthen the physical dimension of higher pair to improve intensity。3rd step have employed six bar four gears exactly and becomes the speed ratio drive mechanisms such as wheelbase, and it solves the problem that wheelbase variable quantity is too little equally, the weak link also do not deposited in intensity, but longitudinal size is relatively large, adds the volume of casing。

Summary of the invention

For solving above-mentioned technical problem, this utility model provides the speed ratio transmission devices such as a kind of time-varying wheelbase based on parallelogram and isosceles triangle combination。

This utility model is achieved through the following technical solutions: the speed ratio transmission devices such as a kind of time-varying wheelbase, including left input gear positioned opposite and right output gear；Described left input gear dead axle is arranged in frame, and the output shaft of left input gear drives left smooth roll；Described right output gear is fixedly mounted on steps down on slide block, described in skid of stepping down be arranged in frame, the output shaft of right input gear drives right smooth roll；

Also include the first row star-wheel being meshed with described left input gear and the second planetary gear being meshed with described right output gear；

It is connected to the first rocking bar between described left input gear rotating shaft and first planet wheel rotating shaft；It is connected to first connecting rod between the wheel rotating shaft of described first planet and the second planetary gear rotating shaft；It is connected to second rocking bar parallel with the first rocking bar between described second planetary gear rotating shaft and frame；Described first rocking bar, first connecting rod, the second rocking bar and frame composition parallel-crank mechanism；

It is connected to the second connecting rod isometric with the second rocking bar between described right output gear rotating shaft and the second planetary gear rotating shaft；The isosceles triangle mechanism that described second rocking bar, second connecting rod and frame composition are the end with frame。

It is further: described slide block one end of stepping down is connected to oil cylinder of stepping down, and the oil cylinder other end of stepping down is connected in frame。

This utility model is the speed ratio transmission devices such as a kind of time-varying wheelbase based on parallelogram and isosceles triangle combination, for the speed ratio transmission such as grade of two smooth rolls in double; two beam roller crushers of material processing in small, broken bits。The bar linkage structure of isosceles triangle for obtaining the wheelbase variable quantity of two rollers, wheelbase variable quantity up to normal axis from 50%；Isosceles triangular structure is equal in magnitude for the rotating speed obtaining two rollers with the combination of parallelogram sturcutre, it is contrary to turn to。This utility model had both solved the problem that wheelbase variable quantity is sufficiently large, has again enough spaces and solves equicohesive problem, and longitudinal size is relatively small, and the longitudinal length of casing is more reasonable with the ratio of lateral length。

Accompanying drawing explanation

Fig. 1 is structural representation during this utility model normal operation；

Fig. 2 be this utility model meet with foreign body time wheelbase generation large change time structural representation。

In figure: 1, left input gear；2, the first rocking bar；3, the first row star-wheel；4, the first bearing pin；5, first connecting rod；6, the second rocking bar；7, the second planetary gear；8, the second rocking bar upper pin；9, second connecting rod；10, right output gear；11, step down piston rod bearing pin；12, step down piston rod；13, step down cylinder body；14, step down cylinder body bearing pin；15, frame；16, step down slide block；17, step down the bearing pin of slide block and second connecting rod；18, the second rocking bar lower bearing pin；19, the first rocking bar lower bearing pin；

Detailed description of the invention

The following is a specific embodiment of the present utility model, in conjunction with accompanying drawing, the utility model is described in further detail。

As depicted in figs. 1 and 2, the speed ratio transmission device such as a kind of time-varying wheelbase, including the left input gear 1 being arranged symmetrically with in the same plane and right output gear 10；Left input gear 1 dead axle is arranged in frame 15；Right output gear 10 dead axle is arranged on steps down on slide block 16, and slide block 16 of stepping down is slidably mounted in frame 15。In use, the synchronized rotation coaxial with dead axle line roller of left input gear 1, the synchronized rotation coaxial with moving axis line roller of right output gear 10。The first row star-wheel 3 engages with left input gear 1, and the second planetary gear 7 engages with right output gear 10, and the first row star-wheel 3 being meshed and the second planetary gear 7 are also arranged symmetrically with in the same plane。

The first rocking bar 2 it is connected between the rotating shaft of left input gear 1 and the first row star-wheel 3 rotating shaft；It is connected to first connecting rod 5 between the first row star-wheel 3 rotating shaft and the second planetary gear 7 rotating shaft；It is connected between second planetary gear 7 rotating shaft and frame 15 and the first parallel the second isometric rocking bar 6 of rocking bar 2。First rocking bar 2 two ends are first rocking bar lower bearing pin the 19, first bearing pin 4 respectively；Second rocking bar 6 two ends are second rocking bar lower bearing pin the 18, second rocking bar upper pin 8 respectively。First rocking bar 2, first connecting rod the 5, second rocking bar 6 and frame 15 form parallel-crank mechanism。

The second connecting rod 9 isometric with the second rocking bar 6 it is connected between the rotating shaft of right output gear 10 and the second planetary gear 7 rotating shaft；Second connecting rod 9 two ends are slide block bearing pin the 17, second rocking bar upper pin 8 with second connecting rod of stepping down respectively；The isosceles triangle mechanism that it is the end with frame 15 that second rocking bar 6, second connecting rod 9 and frame 15 form。

Step down slide block 16 one end be connected to driven slide oil cylinder of stepping down；Piston rod 12 end of stepping down is hinged on is stepped down on slide block 16 by piston rod bearing pin 11 of stepping down；Cylinder body 13 one end of stepping down is hinged in frame 15 by cylinder body bearing pin 14 of stepping down。

Shown in Fig. 1, Fig. 2, ω₁Rotating speed for left input gear；ω₁₀Rotating speed for right output gear；With the wheelbase of time correlation when S (t) is double; two roller work；ω₂It it is the rotating speed of the first rocking bar；ω₆It it is the rotating speed of the second rocking bar；ω₉Rotating speed for second connecting rod；Z₁The number of teeth for left input gear；Z₃The number of teeth for the first row star-wheel；Z₇It it is the number of teeth of the second planetary gear；Z₁₀The number of teeth for right output gear。

This actuating device removes the movable link number n=9 of oil cylinder mechanism of stepping down, revolute pair number P_LR=10, moving sets number P_LP=1, lower pair number P_L=P_LR+P_LP=11, higher pair number P_H=3, number of degrees of freedom, F=3n 2P_L–1P_H=3 × 92 × 11 1 × 3=2。One of them is the input speed of the actively left input gear 1 of degree of freedom, and another is the time-varying displacement of the lines of slide block 16 of stepping down of passive freedom degree。

This drive mechanism adds the movable link number n=11, revolute pair number P of oil cylinder mechanism of stepping down_LR=12, moving sets number P_LP=2, lower pair number P_L=P_LR+P_LP=14, higher pair number P_H=3, number of degrees of freedom, F=3n 2P_L–1P_H=3 × 11 2 × 14 1 × 3=2。One of them is the input speed of the actively left input gear 1 of degree of freedom, and another is the reciprocating motion with drawback cylinder of stepping down of passive freedom degree。

The ω of this drive mechanism is determined by specific dimensions₂=ω₆=ω₉；ω₅=0；The number of teeth relation of gear is z₁=z10, z3⁼z7。

In this combined mechanism, left input gear 1 and the first row star-wheel 3 relative to the angular velocity relation between the first rocking bar 2 are

$i_{1,3}^2=\frac{{\mathrm{\ω}}_1-{\mathrm{\ω}}_2}{{\mathrm{\ω}}_3-{\mathrm{\ω}}_2}=-\frac{z_3}{z_1}---\left(1\right)$

In this combined mechanism, the first row star-wheel 3 and the second planetary gear 7 relative to the angular velocity relation between first connecting rod 5 are

$i_{3,7}^5=\frac{{\mathrm{\ω}}_3-{\mathrm{\ω}}_5}{{\mathrm{\ω}}_7-{\mathrm{\ω}}_5}=-\frac{z_7}{z_3}---\left(2\right)$

In this combined mechanism, the second planetary gear 7 and right output gear 10 relative to the angular velocity relation between second connecting rod 9 are

$i_{7,10}^9=\frac{{\mathrm{\ω}}_7-{\mathrm{\ω}}_9}{{\mathrm{\ω}}_{10}-{\mathrm{\ω}}_9}=-\frac{z_{10}}{z_7}---\left(3\right)$

Obtained with ω 5=0 by formula (2) $i_{3,7}^5=\frac{{\mathrm{\ω}}_3-{\mathrm{\ω}}_5}{{\mathrm{\ω}}_7-{\mathrm{\ω}}_5}=\frac{{\mathrm{\ω}}_3-0}{{\mathrm{\ω}}_7-0}=-1,$ ω₃=-ω₇

By formula (3) and ω₃=ω₇、ω₉=ω₂?

$\frac{{\mathrm{\ω}}_7-{\mathrm{\ω}}_9}{{\mathrm{\ω}}_{10}-{\mathrm{\ω}}_9}=\frac{-{\mathrm{\ω}}_3+{\mathrm{\ω}}_2}{{\mathrm{\ω}}_{10}+{\mathrm{\ω}}_2}=-\frac{z_{10}}{z_7}---\left(4\right)$

By in formula (1)With in formula (4)Zuo Xiang, right item are mutually multiplied respectively

$\frac{{\mathrm{\ω}}_1-{\mathrm{\ω}}_2}{{\mathrm{\ω}}_3-{\mathrm{\ω}}_2}\frac{-{\mathrm{\ω}}_3+{\mathrm{\ω}}_2}{{\mathrm{\ω}}_{10}+{\mathrm{\ω}}_2}=-\frac{z_3}{z_1}(-\frac{z_{10}}{z_7})=1$

(ω₃-ω₂)(ω₁₀+ω₂)=(ω₁-ω₂)(-ω₃+ω₂)

${\mathrm{\ω}}_3{\mathrm{\ω}}_{10}+{\mathrm{\ω}}_3{\mathrm{\ω}}_2-{\mathrm{\ω}}_2{\mathrm{\ω}}_{10}-{\mathrm{\ω}}_2^2=-{\mathrm{\ω}}_1{\mathrm{\ω}}_3+{\mathrm{\ω}}_1{\mathrm{\ω}}_2+{\mathrm{\ω}}_2{\mathrm{\ω}}_3-{\mathrm{\ω}}_2^2$

ω₃ω₁₀-ω₂ω₁₀=-ω₁ω₃+ω₁ω₂

ω₁(-ω₃+ω₂)=ω₁₀(ω₃-ω₂)

-ω₁(ω₃-ω₂)=ω₁₀(ω₃-ω₂)

ω₁=-ω₁₀

So, under above parameter, left input gear 1 is equal in magnitude with right output gear 10 rotating speed, it is contrary to turn to。ω₁=ω₁₀Unrelated with the centre-to-centre spacing size between left input gear 1 and right output gear 10。The roller of left input gear 1 and dead axle line is connected, and the roller of right output gear 10 and moving axis line is connected, and so, double; two smooth rolls are the speed ratio transmission such as work under time-varying wheelbase。

Claims (2)

1. the speed ratio transmission device such as time-varying wheelbase, including left input gear (1) positioned opposite and right output gear (10)；Described left input gear (1) dead axle is arranged in frame (15)；Described right output gear (10) dead axle is arranged on slide block of stepping down (16), described in slide block (16) of stepping down be slidably mounted in frame (15)；

It is characterized in that:

Also include the first row star-wheel (3) being meshed with described left input gear (1) and the second planetary gear (7) being meshed with described right output gear (10)；

It is connected to the first rocking bar (2) between rotating shaft and the rotating shaft of the first row star-wheel (3) of described left input gear (1)；It is connected to first connecting rod (5) between described the first row star-wheel (3) rotating shaft and the second planetary gear (7) rotating shaft；Second rocking bar (6) parallel with the first rocking bar (2) it is connected between the rotating shaft of described second planetary gear (7) and frame (15)；Described first rocking bar (2), first connecting rod (5), the second rocking bar (6) and frame (15) composition parallel-crank mechanism；

The second connecting rod (9) isometric with the second rocking bar (6) it is connected between described right output gear (10) rotating shaft and the second planetary gear (7) rotating shaft；The isosceles triangle mechanism that described second rocking bar (6), second connecting rod (9) and frame (15) are is the end with frame (15)。

2. the speed ratio transmission device such as a kind of time-varying wheelbase according to claim 1, it is characterised in that: described slide block of stepping down (16) one end is connected to oil cylinder of stepping down, and the oil cylinder other end of stepping down is connected in frame (15)。