CN102588546A

CN102588546A - Differential-type efficient electrodeless transmission

Info

Publication number: CN102588546A
Application number: CN2012100596449A
Authority: CN
Inventors: 胡泓海
Original assignee: Individual
Current assignee: Individual
Priority date: 2012-03-08
Filing date: 2012-03-08
Publication date: 2012-07-18

Abstract

The invention discloses a novel differential-type efficient electrodeless transmission mainly comprising an asymmetric bevel gear transmission with output shafts at the same end, an intermediate gear connection mechanism and a friction reducing speed regulating mechanism. The effective radiuses of left and right cone reducing wheels connected with friction roller can be changed by adjusting the angles of the friction rollers in the friction reducing speed regulating mechanism, so that two large and small groups of planet wheels in the asymmetric bevel gear transmission can rotate at certain speed other than performing revolution around a planet shaft, thus forming different rotating speeds of the output shafts and achieving the purpose of electrodeless transmission.

Description

The efficient buncher of differential speed type

Technical field

The present invention relates to a kind of buncher; Specifically be a kind ofly to regulate two-way planetary pinion rotating speed in the differential mechanism according to friction reducing principle; Make that it on business changes, rotation is different and produce speed difference; Output shaft with this two-way rotating speed different (or identical) in the differential mechanism is incorporated on the output shaft through specific friction variable speed equipment again, realizes the transmission of moment of torsion and the electrodeless variation of rotating speed output.

Background technique

Buncher is applied in the industry (particularly automotive industry), and it is with hydraulic automatic speed variator, electronic controlled transmission and friction reducing speed changer that the buncher of extensive use at present mainly contains three kinds of forms.Efficient is low, energy consumption is higher because of hydraulic automatic speed variator power is passed on; Electronic controlled transmission to raw material have relatively high expectations, structure is complicated; Friction reducing speed changer is difficult to realize the reasons such as transmission of power of high pulling torque again, makes above-mentioned three kinds of speed changers all can only on the car of less discharge capacity, use, and is difficult to extensive popularization.

Summary of the invention

The purpose of this invention is to provide that a kind of transmitting torque is big, energy loss is little, slewing range is wide, simple in structure, raw material are easy to get, processing technology require low, overall cost is few, can widely used buncher.

For realizing above technological scheme, the present invention is achieved in that the efficient buncher of differential speed type, and he forms by class differential mechanism, attachment portion, middle part and friction reducing arrangements for speed regulation three parts.Said type differential mechanism part with the main distinction of differential mechanism commonly used is: two groups of planetary radii size do not wait and one of two-semiaxle linking to each other with corresponding output shaft gear separately passes another inside; Attachment portion, said middle part mainly is by the change gear group, and another example is made up of gear and connecting rod, is used for connecting type differential mechanism and transfers device with the friction reducing; Said friction reducing arrangements for speed regulation have two kinds of forms: a kind of semi-round ring shape of mainly being made up of two four fens these cirque body rotates contacted, the rotating friction roller of the individual and this combined semi ring rotation compound body of compound body and two (or many) and forms; Another kind of mainly by two groups identical and can deciliter the hydraulic-pressure pump and the metal tape (or belt) of diameter-changing wheel, control diameter-changing wheel deciliter form.

Adopt the efficient buncher of differential speed type of the present invention, simple in structure, with low cost, energy transmission efficient is high, loss is low, and slewing range is wide and steady; Adopt asymmetric double input but the output torque of torque because of the variable part and only concentrate on the same axle of the big input shaft of torque, solid requirement to the friction reduced diameter portion is the end of than, weares and teares less and has bigger torque to export; Available common used material manufacturing, technology is simple, overall cost is few.

Adopt the efficient buncher of differential speed type of the present invention to be mainly used in various large vehicles and to need on the various heavy mechanical equipments of speed change, thoroughly go out the bottleneck of current this " friction reducing buncher can not high-powerly be exported ".

Description of drawings

Below in conjunction with accompanying drawing and embodiment the present invention is described further.

Fig. 1 is a structure diagram of realizing the efficient buncher of this differential speed type.

Fig. 2 is a structure diagram of realizing another embodiment of the efficient buncher of this differential speed type.

Embodiment:

Like Fig. 1

1. structure explanation: input shaft 1 is connected with differential casing 2; The larger-

diameter planet wheel

4,5 that is connected with planet pin 3 and rotate flexibly than the

planet wheel

6,7 of the minor diameter planet pin 3 of can having mercy on separately.Output differential gear 8 is with 4,5 engagements of major planets wheel and with the footpath; Output shaft gear 9 is with small

planetary gear

6,7 engagements and with the footpath.Output semiaxis 10 connects output differential gear 8 and penetrates in the output semiaxis 11 of hollow.Output differential gear 9, axle 11, output shaft gear 12 consubstantialities and hollow all.Gear 12,15 and

gear

13,14 engagements,

gear

12,13,14,15 is formed a gear train, to guarantee to export semiaxis 11 and coupling shaft 16 switched in opposite.The coupling shaft about 16 of hollow connects the gear 15 and diameter-changing wheel 17 of same hollow respectively.Output semiaxis 10

passes

3,9,11,12,15,16,17 respectively, links to each other with diameter-changing wheel 18 at last; The total output shaft 21 of square is switched through on diameter-changing wheel 18 right sides.The axial section of circular cone diameter-changing

wheel

17,18 all is a quadrant, and they two combine and form a semi-round ring shape and rotate compound body;

Friction roller

19,20 is positioned at this

sphere.Friction roller

19,20 is a pair of collaborative rotational speed regulation wheel, inserts high pressure and initiatively utilizes the frictional force of contact can work in coordination with the effective contact radius that is adjusted on 19,20 behind the oil pump.

2. working condition explanation: the moment of torsion that front end robot transfers drives 2 through 1 and rotates.When the disk when 19,20 was parallel to 10,8 and 4,5 and 9 and 6,7 were not all had and relatively rotate in the differential carrier, and promptly differential mechanism is inoperative, only played the moment of torsion transfer function.Collaborative 19,20 the angle of regulating when two-wheeled is positioned at 17 effective radius greater than the effective radius that is positioned on 18, makes that 8 and 4,5 and 9 and 6,7 all relatively rotate in the differential carrier, and 21 rotating speed is greater than 1 rotating speed at this moment; When two-wheeled is positioned at 17 effective radius less than the effective radius that is positioned on 18 one of (as shown in the figure position), make that also 8 and 4,5 and 9 and 6,7 all relatively rotate in the differential carrier, the rotating speed of this moment 21 is less than 1 rotating speed;

3. speed change situation analysis: establish input shaft 1 and import with rotation speed n.

3.1 establish: when the disk when 19,20 was parallel to 10, effective radius all was r again.This moment is inoperative because of the differential mechanism part, so 10,11 rotating speed also is n, the output speed of output shaft 21 also is n.

3.2 regulate 19,20 and angle, compare with 3.1, be set in 17 effective radius and reduced 1/10, be 9r/10, then 18 is 11r/10.The radius of the

gear

12,15 that connects because of the centre all is symmetrical, by the rotary speed property of differential mechanism: " the rotating speed sum of two output semiaxis is 2n, and is irrelevant with the planetary pinion speed of autorotation "; The rotating speed that can know output shaft gear 9 then is 11n/10, and the rotating speed of output shaft gear 8 then is 9n/10.Like this, planetary gear set 6,7 and

planetary gear set

4,5 also have certain rotation except that rich planet pin 3 revolution.At this moment, the rotating speed of output shaft 21 is 9n/10, is the output of slowing down.

3.3 regulate 19,20 and angle, compare with 3.1, establishing 17 effective radiuses has increased by 1/10, is 11r/10, and then 18 is 9r/10.In like manner, can be known by the rotary speed property of differential mechanism: the rotating speed of output shaft gear 9 then is 9n/10, and the rotating speed of output shaft gear 8 then is 11n/10, and like this, planetary gear set 6,7 and planetary gear set 4,5 also have certain rotation except that rich planet pin 3 revolution.At this moment, the rotating speed of output shaft 21 is 11n/10, for quickening output.

Can find out by above analysis: under the situation of certain rotation speed n input, after the efficient buncher speed change of this differential speed type, can be to be greater than or less than input speed n output speed.So slewing range is wide.

4 torque distribution analyses.

If the radius of

planet wheel

4,5 is 2R in the differential mechanism, the radius of

planet wheel

6,7 is R, and the torque of input shaft 1 is M ₀Then according to differential mechanism torque distribution characteristic: " no matter whether the rotating speed of two groups of planet wheels is identical, and when radius was identical, it is very little that torque differs, can think mean allocation ".According to lever principle, the torque that axle 10 obtains is about 2 M again ₀/ 3, the torque that axle 11 obtains is about M ₀/ 3.Like this, the torque of 18 acquisitions also is about 2 M ₀The torque of/3,17 acquisitions is about M ₀/ 3.Wherein 17 sizes that obtained are M ₀/ 3 moment of torsion under

continuous rotation

19,20 and the transmission, finally is incorporated into 21, and total size also is M ₀(above do not remember everywhere frictional loss).

Can find out by above analysis, in fact less through the moment of torsion of 19,20 transmissions.So the efficient buncher of this differential speed type can be used for various large vehicles and needs on the heavy mechanical equipment of speed change, thoroughly go out the bottleneck of current this " the torque output greatly of friction reducing electrodeless variable-speed ".

Another form of the present invention such as Fig. 2.

When input shaft 1 rotates, drive differential carrier 2 and do to rotate with angle speed with planet wheel shaft 3.This moment if in the speed change nationality 26 belts (or metal tape) 27 be positioned at (forming) by speed change fixed wheel 17 and speed change driving wheel 18 upward under effective radius and (forming) of speed change wheels by speed change fixed wheel 20 and speed change driving wheel 19 effective radius of speed change wheels identical; At this moment, 4,5 of identical, the planet wheels that can 3 rotate for axle of size do not have with output differential gear 8 (with 4,5 engagements and with the footpath) and relatively rotate; 6,7 of planet wheels that size is identical, can 3 rotate for axle do not have with output differential gear 9 (with 6,7 engagements and with the footpath) yet and relatively rotate.The torque that differential gear 8 obtains acts on speed change fixed wheel 20 and speed change driving wheel 19 by planet wheel shaft 3 and the little output differential gear 9 of hollow, right output semiaxis 11 and the gear of shouting 12 arranged in output semiaxis 10 warps.The torque that minor semiaxis gear 9 obtains through a pair of gear that is meshed 12,13, through a pair of gear that is meshed 15,16, acts on speed change fixed wheel 17 and speed change driving wheel 18 by bar 23 by connecting rod 14 by output semiaxis 11 again.Belt (or metal tape) 27 plays speed change and torque transmission.These two groups of torques are at last jointly by output shaft 28 outputs.When pump 21 drive speed change driving wheels 18 moved in

groove

24,22 of pumps drove speed change driving wheel 19 is made reverse and same distance in groove 25 displacement; When two-wheeled was apart from change big (or little) in the feasible last speed change wheels of synergy like this, the distance of two-wheeled diminished (or big) in next reducing wheels, thereby the effective radius of the belt (or metal tape) that is connected with upper and lower wheels is changed thereupon.No matter which kind of result of variations all will make in the

differential carrier

4,5 and 6,7 except that with 3 together the revolution, 8 and 4,5 and 9 and 6,7 all relatively rotate.Its final result is exactly: output shaft 28 is serially to be greater than or less than the rotational speed of input shaft 1.

Its speed change situation analysis and torque distribution analysis are referring to precedent.

Above-mentioned described embodiment just describes structural principle mode of execution of the present invention; Design of the present invention and scope are not limited; Under the preceding topic that does not break away from the present invention's design, to distortion and the improvement that the present invention makes, all should be as protection scope of the present invention.The technology contents of application protection of the present invention is all described at claims.

Claims

1. one kind is on business changeed, certainly then the efficient buncher of differential speed type that the speed difference of generation is processed according to two-way planetary pinion in friction reducing principle and the differential mechanism; It is characterized in that: regulate the planetary revolution of two-way, rotation rotating speed in the differential mechanism by the friction diameter changing device, thereby the rotating speed that makes output shaft less than, be equal to or greater than input shaft rotational speed; Parallelly connected energy by the two-way planetary pinion is passed on finally meets at output shaft.

2. according to claim 1, in conjunction with Fig. 1, Fig. 2, it is characterized in that: the speed governing part in the efficient buncher of this differential speed type can mainly be made up of a pair of circular cone diameter-changing wheel and friction roller; Or mainly form by two pairs of speed change wheels and the belt (or metal tape) that is attached thereto.

3. according to claim 1, it is characterized in that: in the described differential mechanism part, the radius of left and right two-semiaxle gear 8,9 can be inequality; The continuous respectively output semiaxis 10,11 of two-semiaxle gear is positioned at the same side therewith.

4. according to claim 1,3, it is characterized in that: in the described differential mechanism part, output shaft gear 8 is with 4,5 engagements of major planets wheel and with the footpath; Output shaft gear 9 is with small planetary gear 6,7 engagements and with the footpath.

5. according to claim 1,3,4; It is characterized in that: in the described differential mechanism part; Output semiaxis 10 passes planet pin 3, output shaft gear 9, output semiaxis 11, output shaft gear 12 etc. respectively, in order to form two-way moment of torsion outgoing route in the same side with another output semiaxis 11.

6. according to claim 1,3,4,5, it is characterized in that: output shaft gear 12 back connect by 12,13,14,15 forms turn to commutating tooth wheels (like Fig. 1) or connection by 13,14,15 linkage mechanisms (like Fig. 2) formed.