CN1055227A - Speed variator - Google Patents

Abstract

A speed variator features that the roller with adjustable eccentricity is installed to input axle, and the eccentricities alternatively push the overrunning clutches installed to output axle to output rotation speed. The speed ratio can be changed by changing the eccentricity. The invention can realize automatic stepless or other-action stepless speed change. The invention has simple structure, reliable work and low cost; the transmission chain is short, the mechanism efficiency is improved, and energy conservation is realized. Can be widely applied to speed changing places matched with engines and motors.

Description

Speed changer

The present invention relates to speed changer, particularly automatic stepless, his moving stepless or step change transmission.

In the known automatic stepless speed variator, comparatively it is desirable to hydraulic mechanical type, by speeder, fluid coupling or torque-converters, gear-shift transmission and hydraulic element are formed.Its complex structure, transmission efficiency is low, the manufacture cost height, maintenance difficult, energy saving is poor, can not extensive use.In the known stepless speed variator, using maximum is mechanical friction type, is made up of friction wheel and friction element etc.Its transmission efficiency is low, short also unsuitable extensive use of life-span.

In the known retarder, using maximum is gear type, its complex process, and volume is big, and velocity ratio is little, uses also to be subjected to certain restriction.

Purpose of the present invention overcomes above deficiency, provides a kind of simple in structure, reliable operation, the efficient height, the maintenance easy operation, can widespread usage at the speed changer in multiple field.

Speed changer principle of the present invention is " a reducing method ", promptly changes the turning radius of driving wheel or the reciprocally swinging radius of follower, or changes the what is called " compound reducing " of reciprocally swinging radius of the turning radius, the follower of driving wheel simultaneously.

The turning radius that changes driving wheel is that " span-adjustable " is: adjustable roller of one or several eccentric distance es or slide block are housed on input shaft, change eccentric distance e, just changed the angle of oscillation β of the swing part that matches with roller or slide block, pass through clutch, also just having changed swing part is the working angle of output shaft to revolving part, single or several swing parts are to the one after the other effect of running shaft, and the unidirectional rotation speed ratio of output shaft also just obtains changing, thereby reach the purpose of speed change.

Changing driven member reciprocally swinging radius is that " path transfer formula " is: one or several throw of eccentric fixing roller or slide block are housed on input shaft, roller or slide block can move along the input shaft axis, the reciprocally swinging radius that is follower is changing, angle of oscillation also changes thereupon, the same described purpose that just reaches speed change.

Compound reducing method is: the turning radius of driving wheel, the reciprocally swinging radius of follower are changing simultaneously.

Wherein span-adjustable is preferable.

The variation of eccentric distance e can be from zero to maximum, and when eccentric distance e equalled zero, promptly angle of oscillation β also equalled zero, and then input shaft is in idle running, and it is big that e becomes, and β becomes greatly thereupon, and the output shaft rotation speed n also becomes greatly thereupon, otherwise then opposite.

The variation of eccentric distance e is controlled by the axial displacement of speed governing key.The axial displacement of speed governing key acts on axial thrust load on the speed governing key by what centrifugal speed governor produced, and the power opposite with the speed regulator axial thrust load that governor spring acts on the speed governing key decides.

The invention has the advantages that this apparatus structure is simple, component are few, and required precision is not high, thereby reduced manufacture cost, use maintenance easy, thereby because the short mechanical efficiency that improved of Transmitted chains, good energy saving property, the work noise free can be applied in multiple field widely.

The present invention has the following drawings.

Fig. 1, span-adjustable automatic stepless speed variator structural representation.Wherein: 1. input shaft, 2. centrifugal governor, 3. speed governing key, 4. adjustable eccentric is apart from disk, 5. roller (self-aligning bearing formula), 6. swing part, 7. governor spring, 8. output shaft, 9. controllable bidirectional free wheel device, N-counterweight type speed regulator, β-angle of oscillation, e-adjustable eccentric distance.

Fig. 2, path transfer formula automatic stepless speed variator structural representation.Wherein: E-is throw of eccentric fixedly.

Fig. 3, wheelbase formula automatic stepless speed variator structural representation.Wherein: h-axis distance, W-balanced type arrangements for speed regulation, 10. support.

Fig. 4, canard automatic stepless speed change differential design schematic representation.Wherein: W-balanced type arrangements for speed regulation, 6.3 swinging chutes.

Fig. 5, breast-stroke automatic stepless speed change differential design schematic representation.

Fig. 6, horse formula automatic stepless speed change differential design schematic representation.Wherein: Middle force transmission element.

Fig. 7, linkage type automatic stepless speed variator structural representation.Wherein:

Connecting rod.

Fig. 8, frame type automatic stepless speed variator structural representation.Wherein:

Framework, Thumb wheel.

Fig. 9, hinge frame automatic stepless speed variator structural representation.

Elaborate embodiments of the invention below in conjunction with accompanying drawing.

Embodiment 1, as shown in Figure 1: 2. the input shaft that is bearing on the casing is equipped with centrifugal governor on 1., adjustable eccentric apart from the e disk 4., 1. 4. disk rotate with input shaft, and the speed governing key is housed 3. in junction, disk 4. periphery self-aligning bearing is housed roller 5., 5. roller is contained in the straight line type groove of swing part, revolving part and output shaft be one 8., revolving part 8. and swing part the controllable bidirectional free wheel device is housed 9. between 6., 9. because controlled, 8. output shaft when one-way rotation, just becomes mono-directional overrun clutch to clutch.

1. 4. disk have the existence of eccentric distance e with input shaft, when 1. 4. disk rotate with input shaft, 6. swing part planar makes the reciprocally swinging at 2 β angles, 9. make output shaft 8. be the folk prescription of pulse feature by clutch to rotation, if when output shaft system's rotary inertia 8. was enough big, then output shaft rotation uniformity 8. was also just in permission range.

The variation of angle of oscillation β is determining the variation of speed ratio.The variation at β angle relies on the axial displacement 3. of speed governing key to control, and 7. the axial displacement 3. of speed governing key decided speed governing key elastic force 3. by axial thrust load and the governor spring that 3. the speed governing key go up that act on that 2. speed regulator produces, 3. 2. speed regulator move to right key to the axial thrust load attempt that 3. the speed governing key produces, and 3. governor spring elastic force attempt 7. moves to left key, the difference of two power deducts the frictional force of key again, make key 3. produce mobile power exactly, speed regulator is to the axial thrust load of key, it is the variation that square is directly proportional with input shaft rotating speed 1., acting on the elastic force that 3. key go up simultaneously is to change according to Hooke's law, key just moves along indicated direction energetically like this, up to balance between two forces for extremely.

When 1. input shaft did not rotate, because speed regulator centrifugal force 2. equals zero, then 3. the speed governing key, moved to left to making the null limit position of disk eccentric distance e 4. 7. under the effect of elastic force at governor spring, and promptly disk is 4. 1. concentric with input shaft.

After 1. input shaft begins to rotate, but when rotating speed was lower than a certain required numerical value, promptly 2. centrifugal speed governor acted on speed governing key axial thrust load 3. when being less than or equal to governor spring 7. to 3. pretension elastic force of key, and eccentric distance e still equals zero, angle of oscillation β also equals zero, and promptly input shaft is 1. in idle running.

Because 2. centrifugal speed governor acts on axial thrust load that 3. the speed governing key go up is the growth that square is directly proportional by input shaft rotating speed 1., so, when input shaft rotating speed 1. is higher than a certain required numerical value, centrifugal speed governor 2. act on axial force that 3. the speed governing key go up greater than governor spring 7. to key 3. elastic force and during the frictional force sum of key, 3. the speed governing key just moves to right, eccentric distance e begins to become big by zero, angle of oscillation also begins to become big by zero, output shaft rotating speed 8. also begins to become big by zero, input shaft rotating speed 1. is high more, output shaft rotating speed 8. is also just big more, otherwise opposite.Because key displacement 3. is an automatic stepless, so angle of oscillation β, the variation of the rotation speed n of output shaft etc. also is an automatic stepless.

When 2. centrifugal speed governor acts on the axial force that 3. the speed governing key is gone up, when equaling governor spring and 7. acting on the elastic force that 3. the speed governing key go up, transient equilibrium just appears, and output shaft rotating speed 8. also just occurs instantaneous stable.

Whole speed regulation process is followed P=FV; Wherein: the P-engine power.The outer load of F-acts on the resistance on the output shaft.V-output shaft roulette speed.Under same power, external resistance F is big more, and then the rotating speed of output shaft is that rotational line speed V is also just low more, otherwise opposite, during variable power, all the other two parameters also change thereupon, but change come what may, always FV=P.

Owing to come speed change, so name span-adjustable by regulating throw of eccentric.

Embodiment 2, as shown in Figure 2, basic structure, working principle, transmission principle and embodiment 1 are similar, do not exist together is that 4. disk is changeless with input shaft eccentric distance e 1., 1. 4. disk rotate with input shaft, speed change is 2. 7. to promote disk with governor spring by centrifugal speed governor 4. to produce displacement at input shaft on 1., promptly changes swing part pendulum radius 6. and realizes, roller radial central planes B 5. ₁B ₁More near oscillation center O ₁, then the output shaft rotating speed is higher, otherwise opposite.Work as B ₁B ₁Move to left to A ₁A ₁Beyond the line, just become idle running.

Owing to come speed change, so name path transfer formula by changing the swing part radius.

Embodiment 3, as shown in Figure 3, working principle, speed-change process and embodiment 1 are similar, structural do not exist together be input shaft 1. with output shaft axis 8. at a distance of h, be called the axis distance.On output shaft axis 8., three swing parts are arranged side by side 6., 9. each swing part 6. periphery all has a controllable bidirectional free wheel device, three 9. public revolving parts of clutch also be output shaft 8., three adjustable eccentrics apart from the disk of e 4. by 5. being contained in three swing parts straight line type groove 6. movingly of roller, generally, three disks are that axisymmetric distributes with input shaft axis 1., promptly Zhong Jian disc centre line is in a side of input shaft axis 1., 3. the disc centre line on both sides is controlled its eccentric distance e by public speed governing key and is kept equating at the opposite side of input shaft axis 1..

The remarkable advantage of this structure is that balance is good, and the equivalent contact ratio is chosen suitable axis apart from h greater than 1, and eccentric distance e then can obtain required equivalent contact ratio.

Owing between input shaft and output shaft the axis distance is arranged, so name wheelbase formula.

Above-mentioned automatic stepless speed variator mainly is applicable to the motor to be the motor vehicle and the apparatus of power, and when being used for motor vehicle, the output shaft among the embodiment 1,2 is exactly the housing of differential mechanism.3 of embodiments are applicable to all speed change apparatuses.

Embodiment 4, as shown in Figure 4, working principle, speed-change process and embodiment 1 are similar, and essence is the combination of two mechanisms among the embodiment 1, and different is self-aligning bearing

Self-aligning, be not to realize, but connect swinging chute by bearing commonly used by spherical bearing 6. realize that with swing part arrangements for speed regulation have become balanced type, 8. two swing parts 6. one after the other act on affiliated output shaft, like the duck sample of walking, so a canard.

Embodiment 5, as shown in Figure 5, working principle, speed-change process and embodiment 1 are similar.8. two output shafts are gone up, respectively adorn a controllable bidirectional free wheel device 9., two 9. public swing parts of clutch 6., 1. counterweight type speed regulator N is housed at input shaft on, the rotation by 1. input shaft transmits has just become two output shafts unidirectional pulse rotations 8. through said mechanism, jump like frog, so the name breast-stroke, enough greatly the time, two output shafts rotation uniformity 8. just can be in permission range with rotary inertia that should system.

Embodiment 6, as shown in Figure 6, and working principle, speed-change process and embodiment 1 are similar, not existing together is that 8. two output shafts are gone up, and is respectively installed with two controllable bidirectional free wheel devicees 9., and there is a public middle force transmission element four clutch centres 9. that 8. two output shafts are gone up

, the swing of any swing part of two swing parts in 6. is by middle force transmission element

All pass to two output shafts simultaneously 8., two swing part one after the other effects 6., then 8. two output shafts just obtain unidirectional continuous rotation simultaneously, and similar horse walks, so name Ma Shi.

In the foregoing description 4,5,6, when two output shafts rotating speed 8. was variant, rotating speed output shaft faster just surmounted automatically by affiliated free wheel device, thereby reached the automatic stepless speed change purpose of automatic differential again.

In the foregoing description 4,5,6, when being used for being the motor vehicle of power with the motor, then 8. output shaft is exactly the semiaxis in the back axle.

Fig. 7, Fig. 8, Fig. 9 are the subforms of Fig. 3, utilize aforementioned principles to develop and the form of various different structures.

Embodiment 7, structural type shown in Figure 3, take down automatic speed governing device with input shaft rotating speed proportion relation 1., change into and unallied his the dynamic formula arrangements for speed regulation of input shaft rotating speed 1., as control the axial displacement of speed governing key with modes such as mechanical, manual, liquid gas, electromagnetism and combinations thereof, to reach the purpose of speed change, promptly become his dynamic formula stepless speed variator.

It is in the apparatus of power that this class speed changer is mainly used in the motor, and rotates the place that coefficient of uniformity is had relatively high expectations, as fields such as lathe, engineering machinery, mining machinery, petroleum machineries.Its distinguishing feature is the speed change of not stopping that can realize under the load.

Embodiment 8, two output shafts in Fig. 4 structural type, change an output shaft of two clutches of series connection into, and automatic speed governing device is changed into aforesaid his dynamic formula arrangements for speed regulation, also become his dynamic formula stepless speed variator.

It is power that this class speed changer is mainly used in the motor, and the general field of output shaft rotation coefficient of uniformity requirement, as some lathe, crushing mechanism, Mixing Machine etc.This class speed changer can be realized the speed change of not stopping under the load too.

Embodiment 9, Fig. 1, structure shown in Figure 2, as described above, become automatic speed governing device into his moving arrangements for speed regulation, also become his dynamic formula stepless speed variator.

This class speed changer is applicable to the motor to be power, and the output shaft rotary inertia is big and rotate the lower field of uniformity requirement, as bicycle, motorcycle, naval vessel, train, farm machinery etc.The characteristics that have the speed change of under load, not stopping equally.

Embodiment 10, and his the dynamic formula stepless speed variator described in the embodiment 7,8,9 takes down all arrangements for speed regulation, disk eccentric distance e is 4. remained unchanged, and the pendulum radius among Fig. 2 is constant, then becomes to decide ratio speed reducer, be applicable to the motor to be power, and the output shaft rotating speed place that need not change.As some farm machinery, brick making machine, pumping unit, winch, crane, cable car etc.

Claims (9)

1, a kind of speed changer, by input shaft 1., 8. output shaft waits composition, it is characterized in that being equipped with on input shaft 1. adjustable eccentric 4. apart from the disk of e, 5. disk periphery 4. is equipped with roller or slide block, 3. 4. disk be equipped with the speed governing key with input shaft connection place 1., the axial displacement 3. of speed governing key by centrifugal speed governor 2., governor spring is control automatically 7., 5. roller or slide block are contained in the swing part straight line or arc line type groove 6., revolving part and output shaft be one 8., revolving part 8. and swing part is equipped with unidirectional between 6. or the controllable bidirectional free wheel device 9..

2, speed changer as claimed in claim 1, it is characterized in that input shaft 1. with output shaft 8. not on same axis, on output shaft axis 8., be installed with three swing parts side by side 6., each swing part 6. straight line or the arc line type groove in an adjustable eccentric is housed 5. apart from the roller of e or slide block, middlely 5. normally be symmetrically distributed with input shaft axis 1. with rollers both sides or slide block, three 6. public revolving parts of swing part 8..

3, speed changer as claimed in claim 1 is characterized in that 4. disk fix with input shaft eccentric distance e 1., and 1. 4. disk can move along input shaft.

4, speed changer as claimed in claim 1 is characterized in that 8. going up at two output shafts and a controllable bidirectional free wheel device respectively is housed 9., is contained in the swing part that 9. two clutches go up and 6. in turn 8. revolving part is acted on.

5, speed changer as claimed in claim 1 is characterized in that 8. going up at two output shafts and a controllable bidirectional free wheel device respectively is housed 9., and 6. 9. two clutches have only a public swing part.

6, speed changer as claimed in claim 1 is characterized in that 8. going up at two output shafts, is set with two controllable bidirectional free wheel devicees 9., and there is a public force transmission element clutch of two groups of suits centre 9. , two swing parts are 6. in turn to force transmission element

Effect.

7,, it is characterized in that being equipped with automatic speed governing device with input shaft rotating speed proportion relation 1. as claim 1 or the described speed changer of claim 2.

8,, it is characterized in that being equipped with he the dynamic formula arrangements for speed regulation irrelevant with input shaft rotating speed 1. as claim 1 or the described speed changer of claim 2.

9, as claim 1 or the described speed changer of claim 2, it is characterized in that not having arrangements for speed regulation.

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