CN103511566B - Double-planet train formula stepless auto gear - Google Patents

Double-planet train formula stepless auto gear Download PDF

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Publication number
CN103511566B
CN103511566B CN201310498751.6A CN201310498751A CN103511566B CN 103511566 B CN103511566 B CN 103511566B CN 201310498751 A CN201310498751 A CN 201310498751A CN 103511566 B CN103511566 B CN 103511566B
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gear
sun gear
output
contained
gear ring
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CN103511566A (en
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徐攀
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/58—Gearings having only two central gears, connected by orbital gears with sets of orbital gears, each consisting of two or more intermeshing orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/76—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with an orbital gear having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears

Abstract

Double-planet train formula stepless auto gear, including input and output two set planet circular system, two set planet circular systems all include sun gear, planetary gear, external toothing and planet carrier, two sun gears fill on center shaft, central shaft is contained on machine case, and input gear engages with the sun gear in input system, and the sun gear of output system engages with output gear, power shaft is contained on machine case, and output shaft is contained on machine case by one-way clutch；Two planet carriers are affixed, and two gear rings are affixed；Gear ring in two set planet circular systems is unequal with the gear ratio of sun gear.The present invention is by creating one only by the internal power recycle stream of external rotating angular velocity or torque influence outside main power cycle stream, by changing the size of inner loop stream and then obtaining output moment of torsion and the rotational angular velocity being suitable for, it is capable of automatic, electrodeless variable-speed function, and without fluid power mechanism, there is higher economic relative property and wider practicality.

Description

Double-planet train formula stepless auto gear
Technical field
The present invention relates to gear, be specifically related to include the stepless auto gear of double-planet train.
Background technology
Gear is a kind of in the case of power shaft rotating speed or moment of torsion are constant, makes output shaft obtain different rotating speeds or torque transmission device, i.e. by speed change or bending moment, with the needs of satisfied different operating modes, is widely used in various occasion.
As a example by automotive field, in order to meet under the conditions of starting to walk, accelerate, travel and overcome different kinds of roads obstruction light difference to travel the needs driving net tractive force of wheel and speed difference to require, between electromotor and drive axle, it is generally equipped with variator.Development along with auto industry, automotive transmission experienced by non-automatic gear to automatic transmission, from having level to stepless development, the most traditional belt wheel transmission mechanism, gear drive etc., the gear ratio of this kind of gear is single for step speed change, but low cost of manufacture, and technique is the most ripe；Such as based on moment speed change hydraulic automatic speed variator (AT), can independently realize electrodeless variable-speed, but mechanism is complicated, complex process, manufacturing cost is high, and due to fluid coupling in use automobile output energy some be converted into oil temperature, so economy is relatively poor.The fully-automatic gearbox of comparative maturity also has mechanical stepless automatic speed changer (CVT), electric-controlled mechanical automatic speed transmission (AMT) the most in the world except above-mentioned points, the former takes turns based on a pair V-belt, steel belt and a set of hydraulic pressure and computer micro-controller system realize electrodeless fluid drive, this transmission technology content is high, manufacture complexity, cost is high, transmission tape lifetime is relatively short, maintenance cost is high, and owing to being subject to such as many-sided technical restrictions such as material property, it is currently mainly limited on small-power automobile use；The latter realizes having level, fluid drive based on the automatic manipulation mechanism that conventional transmissions and computer control, although its easily fabricated and low cost, but its shift property is poor, pause and transition in rhythm or melody sense is had during gearshift, time low-grade, pause and transition in rhythm or melody sense is especially apparent, it addition, this variator can only realize step speed change, and electrodeless variable-speed can not be realized, and extraneous intervention need to be introduced.
Summary of the invention
The applicant improves for disadvantages mentioned above of the prior art, it is provided that a kind of double-planet train formula stepless auto gear, and it is capable of automatic, electrodeless speed changing function, and eliminates fluid power of the prior art mechanism, has higher economic relative property.
Technical scheme is as follows:
nullDouble-planet train formula stepless auto gear，Including line of input star wheel series、Output planetary train，Described line of input star wheel series includes the first sun gear、The first row star-wheel with the first sun gear external toothing、The first gear ring with the first row star-wheel internal messing，The first row star-wheel is contained in the first row carrier by bearing，Described output planetary train includes the second sun gear、The second planetary gear with the second sun gear external toothing、The second gear ring with the second planetary gear internal messing，Second planetary gear is contained on the second planet carrier by bearing，First sun gear、Second sun gear is filled on center shaft by bearing，Central shaft two ends are contained on machine case by bearing，Input gear on power shaft and the engagement of the first sun gear，Second sun gear engages with the output gear on output shaft，Power shaft is contained on machine case by bearing，Output shaft is contained on machine case by one-way clutch；The first row carrier is fixing with the second planet carrier to be connected；First gear ring and the second gear ring are fixed and are connected, and the first gear ring and the second gear ring are contained on machine case by bearing, and the gear ratio of the first gear ring and the gear ratio of the first sun gear and the second gear ring and the second sun gear is unequal.
Its further technical scheme is:
The periphery of the fixing coupling part of the first gear ring and the second gear ring is provided with external tooth, drive idler gear engages with the external tooth on described fixing coupling part, drive idler gear fills on the mounting shaft by sliding bearing, installing axle to be installed on machine case, drive idler gear is connected by sliding on the mounting shaft with described two set planet circular systems or disconnects.
The first row carrier of described fixing connection is structure as a whole with the second planet carrier.
First gear ring and second gear ring of described fixing connection are structure as a whole.
The technique effect of the present invention:
nullThe present invention uses input and output totally two set planet circular system，The first sun gear in wherein said line of input star wheel series is input，The second sun gear in described output planetary train is outfan，The fixing connection of planet carrier in two set planet circular systems，And gear ring that two in set planet circular system is fixing connects，Make whole mechanism outside the main power cycle stream from input to outfan，Also between two set planet circular systems, form one only by extraneous rotational angular velocity or the internal power recycle stream of torque influence，This inner loop power stream has a style of one's own，When described idling mechanism remains off with described two set planet circular systems，Whole gear only one of which output stream，I.e. exported by output planetary train，When described idling mechanism keeps connection status with described two set planet circular systems，Whole change acceleration mechanism has two output streams，I.e. from the output of output planetary train and export from described idling mechanism.When gear speed change of the present invention, owing to input power is known constant, in the case of described two overlap planet circular system and described idling mechanism disconnects, now, the moment of torsion of two factors of the output in power conservation law, i.e. output planetary train outfan and the most inversely proportional relation of rotational angular velocity.Gear of the present invention is on the basis of creating an internal power recycle stream being only subject to extraneous rotational angular velocity demand or torque influence, moment of torsion according to gear outfan or the demand status of rotational angular velocity, obtain, by changing the size of inner loop stream, output moment of torsion or the output rotational angular velocity being suitable for, thus achieve automatic speed changing function；On the other hand, the demand of various rotating speed and moment of torsion can be met in the case of coupling between without changing mechanism due to gear, thus achieve electrodeless variable-speed function；Output shaft is provided with one-way clutch, it can be ensured that whole gear outbound course uniquely determines.The present invention is compared to fluid power of the prior art mechanism, it is being capable of automatically equally, under electrodeless speed changing function, eliminate fluid torque-converter, compared to mechanical stepless automatic speed changer of the prior art, then can realize automatically controlling and adjusting without extra hydraulic pressure and computer micro-controller system, the present invention is for existing variator, it is capable of electrodeless and fluid drive truly, and without cutting off power in speed-change process, connection between changing mechanism, and speed-change process is without pause and transition in rhythm or melody sense, simplify structure and the making of gear, there is higher economy and wider practicality.
Accompanying drawing explanation
Fig. 1 is the structural representation of the present invention.
Fig. 2 is the theory structure schematic diagram of the present invention.
Fig. 3 is the easy structure schematic diagram of single row star wheel series, shows the stressing conditions of single planetary bevel gear in figure.
Fig. 4 is with two kinds of different accelerator drive automobiles and to make Automobile drive moment of torsion, automobile running resistance square and the relation schematic diagram of automobile driving speed under the final at the uniform velocity driving cycle of automobile.
Wherein: 1, the first sun gear；2, the first row star-wheel；3, the first gear ring；4, the first row carrier；5, the second sun gear；6, the second planetary gear；7, the second gear ring；8, the second planet carrier；9, central shaft；10, machine case；11, power shaft；12, input gear；13, output shaft；14, output gear；15, one-way clutch；16, drive idler gear；17, sliding bearing；18, axle is installed；100, sun gear；200, planetary gear；300, gear ring；400, main power cycle stream；500, internal power recycle stream.
Detailed description of the invention
Letter and symbol in the formula now used the present invention are explained as follows.
Pr represents input power, Pc represents that output, Mr represent that input torque, Wr represent input rotational angular velocity, Mc represents output moment of torsion, Wc represents output rotational angular velocity, and Mr and Wr is known constant, and Pd represents the power by the output of described idling mechanism, Mz represents intermediate torque, Wz represents central rotational angular velocity, Mz and Wz is middle free variable, a, b, a1、b1Being constant factor, Ps represents the power of gear internal losses；
In single row star wheel series, Wt represents sun gear rotational angular velocity, and Wx represents planet carrier rotational angular velocity, and Wq represents ring gear against rotation angular velocity, Rt represents sun gear joint degree radius of circle, Rx represents planetary gear joint degree radius of circle, and Rq represents gear ring joint degree radius of circle, and k represents the ratio of Rq Yu Rt, Mt represents the moment of torsion of sun gear, Mq represents the moment of torsion of gear ring, and Mx represents the moment of torsion of planet carrier, F1For the sun gear active force to planetary gear, F2For the gear ring active force to planetary gear, F3For the planet carrier active force to planetary gear；
In described input with output planetary train, Wt1Represent the rotational angular velocity of the first sun gear, Wx1Represent the rotational angular velocity of the first row carrier, Wq1Represent the rotational angular velocity of the first gear ring, Wt2Represent the rotational angular velocity of the second sun gear, Wx2Represent the rotational angular velocity of the second planet carrier, Wq2Represent the rotational angular velocity of the second gear ring, Mt1Represent the moment of torsion of the first sun gear, Mx1Represent the moment of torsion of the first row carrier, Mq1Represent the moment of torsion of the first gear ring, Mt2Represent the moment of torsion of the second sun gear, Mx2Represent the moment of torsion of the second planet carrier, Mq2Represent the moment of torsion of the second gear ring, Rt1Represent the first sun gear joint degree radius of circle, Rx1Represent the first row star-wheel joint degree radius of circle, Rq1Represent the first gear ring joint degree radius of circle, Rt2Represent the second sun gear joint degree radius of circle, Rx2Represent the second planetary gear joint degree radius of circle, Rq2Represent the second gear ring joint degree radius of circle, k1Represent Rq1With Rt1Ratio, k2Represent Rq2With Rt2Ratio, and k1It is not equal to k2, Mf represents that engine torque, Mn represent Automobile drive moment of torsion, Wf represents engine rotation angular velocity, and Wn represents that automobile driving speed, j, p, s, t are constant factor, Mu represents automobile running resistance square, and Mu follows automobile driving speed and becomes big and become big, and Ma represents acceleration moment of torsion.
Below in conjunction with the accompanying drawings, the detailed description of the invention of the present invention is described.
nullSee Fig. 1，The present invention includes line of input star wheel series、Output planetary train，Described line of input star wheel series includes the first sun gear 1、The first row star-wheel 2 with the first sun gear 1 external toothing、The first gear ring 3 with the first row star-wheel 2 internal messing，Multiple the first row star-wheels 2 are contained in the first row carrier 4 by bearing，Described output planetary train includes the second sun gear 5、The second planetary gear 6 with the second sun gear 5 external toothing、The second gear ring 7 with the second planetary gear 6 internal messing，Multiple second planetary gears 6 are contained on the second planet carrier 8 by bearing，First sun gear 1、Second sun gear 5、The first row carrier 4 and the second planet carrier 8 are all contained on central shaft 9 by bearing，Central shaft 9 two ends are contained on machine case 10 by bearing，Input gear 12 on power shaft 11 engages with the first sun gear 1，Specifically，Increase the axial length of the first sun gear 1，Axially extended described line of input star wheel series will be made to sense along by first sun gear 1，Described extension is made to engage with input gear 12，Or axially it is connected with an idler gear with the first sun gear 1，Described idler gear is made to engage with input gear 12，Second sun gear 5 engages with the output gear 14 on output shaft 13，In like manner，The concrete engagement system of the second sun gear 5 and output shaft 13 is with reference to the concrete engagement system of the first sun gear 1 with input gear 12，Power shaft 11 is contained on machine case 10 by bearing，Output shaft 13 is contained on machine case 10 by one-way clutch 15；The first row carrier 4 is fixing with the second planet carrier 8 to be connected, it is preferable that the first row carrier 4 of described fixing connection is structure as a whole with the second planet carrier 8；First gear ring 3 is fixing with the second gear ring 7 to be connected, first gear ring 3 and the second gear ring 7 are contained on machine case 10 by bearing, first gear ring 3 of the most described fixing connection is structure as a whole with the second gear ring 7, and the first gear ring 3 is unequal with the gear ratio of the second sun gear 5 with the gear ratio of the first sun gear 1 and the second gear ring 7.
nullFurther，The working condition requirement of the provisional parking of automobile is turned in order to meet low engine speed，It is provided with external tooth in the periphery of the first gear ring 3 and the fixing coupling part of the second gear ring 7，Drive idler gear 16 engages with the external tooth on described fixing coupling part，Specifically，An idler gear can also be set between the first gear ring 3 and the second gear ring 7，This idler gear and the first gear ring 3、Second gear ring 7 is the most affixed，And this idler gear engages with drive idler gear 16，Drive idler gear 16 is contained on installation axle 18 by sliding bearing 17，Axle 18 is installed be installed on machine case 10，Drive idler gear 16、Sliding bearing 17、Axle 18 is installed and constitutes idling mechanism，Drive idler gear 16 is connected by sliding on installation axle 18 with described two set planet circular systems or disconnects，Make described idling mechanism and described input、Output planetary train connects or disconnects.
Disconnecting with described input, output planetary train and described idling mechanism and illustrating, gear of the present invention meets three below condition:
①Mr=aMc+bMz
②Wr=a1Wc+b1Wz
③Mr*Wr=Mc*Wc
Above-mentioned 3. formula is to be drawn by power conservation law, for theoretically, gear internal loss power P s is there is also between input power and output, power attenuation Ps mostlys come from gear shaft with between machine case and internal friction, based on current production technology, this friction factor can control the least, and can't there is the situation much larger than input rotational angular velocity in the rotational angular velocity of train in the middle of in use, therefore the least by fricative power attenuation Ps, whether ignored and can't be changed final result, thus obtain above-mentioned 3. formula；When described input, output planetary train and described idling mechanism are in connection status, input power some export through described idling mechanism, the most now, above-mentioned 3. formula is expressed as following formula:
Mr*Wr=Mc*Wc+Pd
Above-mentioned 1. formula and 2. formula are based in single row star wheel series between the rotational angular velocity/moment of torsion of sun gear, planetary gear and this three of gear ring on the basis of relation, the relation of rotational angular velocity/moment of torsion that the two of gear of the present invention overlaps the input/output of planet circular systems carries out mathematical reckoning and obtains, and concrete reckoning process is as follows:
Seeing that Fig. 3, Fig. 3 are typical single row star wheel series, including sun gear 100 and the planetary gear 200 of sun gear 100 external toothing, with the gear ring 300 of planetary gear 200 internal messing, planetary gear 200 is contained on planet carrier (not shown in Fig. 3), O in Fig. 31It is sun gear 100, gear ring 300 and the centre of motion of planet carrier, O2The rotation center of planetary gear 200, B and A represent planetary gear 200 respectively with sun gear 100, the meshing point of gear ring 300, in single row star wheel series, there is following rationale relation:
④Wt+kWq=(1+k)Wx
⑤Mt+Mq/k=Mx/(1+k)
Above-mentioned 4. formula is to draw based on Principles of Gear Connection (i.e. equal in engagement place speed), if sun gear 100 rotation direction is positive direction, planetary gear 200 rotational angular velocity is Wx, with planetary gear 200 as object of reference, then sun gear 100 rotational angular velocity be (Wt-Wx), external toothing 300 rotational angular velocity be (Wq-Wx), then can obtain following 6. formula according to Principles of Gear Connection:
6. Wq-Wx=-Rt*(Wt-Wx)/Rq
Giving k=Rq/Rt, and k ＞ 1, the most above-mentioned 6. formula can be reduced to above-mentioned 4. formula:
Above-mentioned 5. formula is that planet circular system draws when being in poised state, sees Fig. 3, according to the moment equilibrium condition of planetary gear 200, under different stressing conditions, all there is the mathematical relationship of above-mentioned 5. formula, and the concrete process of argumentation is as follows:
1, when the sun gear 100 directed force F to planetary gear 2001Less than the gear ring 300 directed force F to planetary gear 2002, one will be constructed with B as the centre of gyration, with O2, A be the system of torsional forces application point.
Within the system, by O2The power equivalence of point transfers to A point has A point suffered with joint efforts: F2+F3/ 2, and B point is suffered with joint efforts for F1, it is zero according to the planetary gear i.e. resultant torque of at the uniform velocity autobiography, available following relationship:
(F2+F3/2)Rx-F1*Rx=0
Above formula simplifies can obtain following formula:
.(F2-F1) * 2+F3=0
If the torque of sun gear 100, gear ring 300 and planet carrier is respectively Mt, Mq, Mx, with B as the centre of gyration, with O2, A be torsional forces application point system in, the sun gear 100 directed force F to planetary gear 2001In opposite direction with Mt, the gear ring 300 directed force F to planetary gear 2002Identical with Mq direction, train do the equilibrium condition of uniform rotation, available following four relationships:
F1=-Mt/Rt
F2=Mq/Rq
F3=-Mx/(Rt+Rx)
Rx=(Rq-Rt)/2
Convert according to above-mentioned two relational expressions below and can obtain following formula:
ⅱ.F3=-2*Mx/(Rt+Rq)
Formula of formula being brought into converts and can obtain following formula:
.Mt/Rt+Mq/Rq=Mx/(Rt+Rq)
K=Rq/Rt is substituted into above-mentioned formula, can obtain above-mentioned 5. formula:
2, when the sun gear 100 directed force F to planetary gear 2001More than the gear ring 300 directed force F to planetary gear 1002, one will be constructed with A as the centre of gyration, with O2, B be the system of torsional forces application point.
Within the system, by O2The power equivalence of point transfers to B point has B point suffered with joint efforts: F1+F3/ 2, and A point is suffered with joint efforts for F2, it is zero according to the planetary gear i.e. resultant torque of at the uniform velocity autobiography, available following relationship:
(F1+F3/2)Rx-F2*Rx=0
Above formula simplifies can obtain following formula:
.(F1-F2) * 2+F3=0
If the torque of sun gear 100, gear ring 300 and planet carrier is respectively Mt, Mq, Mx, with A as the centre of gyration, with O2, B be torsional forces application point system in, the sun gear 100 directed force F to planetary gear 2001Identical with Mt direction, the gear ring 300 directed force F to planetary gear 2002In opposite direction with Mq, train do the equilibrium condition of uniform rotation, available following four relationships:
F1=Mt/Rt
F2=-Mq/Rq
F3=-Mx/(Rt+Rx)
Rx=(Rq-Rt)/2
Convert according to above-mentioned two relational expressions below and can obtain following formula:
ⅴ.F3=-2*Mx/(Rt+Rq)
Formula of formula being brought into converts and can obtain following formula:
.Mt/Rt+Mq/Rq=Mx/(Rt+Rq)
K=Rq/Rt is substituted into above-mentioned formula, above-mentioned 5. formula can be obtained equally.
According to the above-mentioned equalising torque analysis about single row star wheel series, it is known that, for there is the rationale relation of above-mentioned 5. formula between each moment of single planetary bevel gear system as shown in Figure 3.
On the basis of the above-mentioned 4. formula of single row star wheel series and the rationale relation of 5. formula, the relation of rotational angular velocity/moment of torsion that the two of gear of the present invention overlaps the input/output of planet circular systems calculates, can obtain the conclusion of above-mentioned 1. formula and 2. formula, concrete calculate that process is as follows:
In gear of the present invention, the first sun gear 1 is input (i.e. Wt1=Wr,Mt1=Mr), the second sun gear 5 is outfan (i.e. Wt2=Wc,Mt2=Mc), except there is in single row star wheel series the mathematical relationship of 4. formula and 5. formula, also as the first row carrier 4 and the second fixing connection of planet carrier 8, therefore the two rotational angular velocity and moment of torsion are the most equal, first gear ring 3 is fixing with the second gear ring 7 to be connected, and therefore both rotational angular velocity and moment of torsion are the most equal.
First, utilize above-mentioned 4. formula to be analyzed calculating based on rotational angular velocity, the satisfied following four groups of relations of gear of the present invention:
Ⅰ.Wt1+k1Wq1=(1+k1)Wx1
Ⅱ.Wt2+k2Wq2=(1+k2)Wx2
Ⅲ.Wx1=Wx2
Ⅳ.Wq1=Wq2
Integrated conversion obtained following 7. formula by above-mentioned I formula, II formula, III formula, IV formula:
⑦(1+k2)Wt1=(1+k1)Wt2+ (k2-k1) Wq2
By coefficient a after all coefficients in above-mentioned 7. formula are integrated1、b1Represent, Wq2Represent with intermediate torque Wz, Wt1For input rotational angular velocity Wr, Wt2For output rotational angular velocity Wc, the most above-mentioned 7. formula is above-mentioned 2. formula:
②Wr=a1Wc+b1Wz
Secondly, utilize above-mentioned 5. formula to be analyzed calculating based on moment of torsion, the satisfied following four groups of relations of gear of the present invention:
Ⅰ.Mt1+Mq1/k1=Mx1/(1+k1)
Ⅱ.Mt2+Mq2/k2=Mx2/(1+k2)
Ⅲ.Mx1=Mx2
Ⅳ.Mq1=Mq2
Integrated conversion obtained following 8. formula by above-mentioned I formula, II formula, III formula, IV formula:
⑧(1+k1)Mt1=(1+k2)Mt2+[(k1-k2)/k1k2]Mq2
Represented by coefficient a, b after all coefficients in above-mentioned 8. formula are integrated, Mq2Represent with intermediate torque Mz, Mt1For input rotational angular velocity Mr, Mt2For output rotational angular velocity Mc, the most above-mentioned 8. formula is above-mentioned 1. formula:
①Mr=aMc+bMz
Owing to the first gear ring 3 is unequal with the gear ratio of the second sun gear 5 with the gear ratio of the first sun gear 1 and the second gear ring 7, according to the relation that gear ratio in gear train assembly is equal with radius ratio, then k1It is not equal to k2, and both of which is more than 1, and therefore, coefficient a, b, a after above-mentioned 7. formula and 8. formula integration1、b1All it is not zero.
In three relationships of above-mentioned 1. formula, 2. formula, 3. formula that the present invention meets, owing to Wr, Mr are known constant, Wz, Mz are middle free variable, when determining the value of Wc or Mc any of which one, the value that all can search out Wz, Mz and Mc that only one determines or Wc for above-mentioned 1. formula, 2. formula, 3. formula makes these three relationship set up, gear the most of the present invention relies on outfan rotational angular velocity/moment of torsion and the most automatically adjusts output moment of torsion/rotational angular velocity, it is achieved that speed changing function automatically.
Fig. 2 is the theory structure schematic diagram of the present invention, the present invention uses input and output totally two set planet circular system, the first sun gear 1 in wherein said line of input star wheel series is input, the second sun gear 5 in described output planetary train is outfan, the fixing connection of planet carrier in two set planet circular systems, and gear ring that two in set planet circular system is fixing connects, make whole mechanism outside the main power cycle stream 400 from input to outfan, also between two set planet circular systems, form an internal power recycle stream 500 only affected by extraneous rotational angular velocity Wc demand or moment of torsion Mc.In Fig. 2, the straight line of band arrow is the path of power stream, internal power recycle stream 500 is in the train of mechanism of closing, and whole gear is when by ectocine, i.e. during Mc or Wc change, internal power stream 500 can be automatically adjusted, i.e. by changing the middle free variable Wq of 7. formula and 8. formula2And Mq2And then change output rotational angular velocity or output moment of torsion, realize automatic speed changing function with this.Gear of the present invention is on the basis of creating internal power recycle stream 500, moment of torsion according to gear outfan or the demand status of rotational angular velocity, output moment of torsion or the output rotational angular velocity being suitable for is obtained, it is achieved that automatic speed changing function by changing the size of inner loop stream 500；On the other hand, the demand of various rotating speed and moment of torsion can be met due to gear in the case of coupling between without changing mechanism, it is achieved that electrodeless variable-speed function.
For automotive transmission, gear input torque Mr depends on the converter torque ratio of engine torque Mf and gear, gearbox output torque Mc determines Automobile drive moment of torsion Mn, variator input rotational angular velocity Wr depends on the gear ratio of engine speed Wf and gear, variator output speed Wc determines automobile driving speed Wn, in like manner, according to above-mentioned 1. formula, 2. formula, 3. formula, it can be deduced that following four relational expression:
Ⅴ.Mf=jMn+pMz
Ⅵ.Wf=sWn+tWz
Idling mechanism described in VII .Mf*Wf=Mn*Wn(remains open with described two set planet circular systems)
Idling mechanism described in VIII .Mf*Wf=Mn*Wn+Pd(keeps being connected with described two set planet circular systems)
Automobile have in the process of moving parking, speed change, at the uniform velocity, these several states of moveing backward, car-backing function the most more improves and ripe, in the condition advanced, i.e. add tumbler gear, it is not discussed at this, therefore, automobile variable speed mechanism is required to meet the working condition requirement under above-mentioned different conditions, is described as follows:
1. parked state, includes that the most again engine stop and low engine speed rotate two states:
Engine stop: i.e. automobile flameout, therefore Wf=0, VII formula derived above understanding car speed Wn is zero；
Low engine speed rotates: i.e. the provisional parking of automobile, then input power is not zero, it is in connection status with described two set planet circular systems now by idling mechanism described in Artificial Control, the most above-mentioned VIII formula is set up, if now Mn is less than or equal to Mu, Mu refers in particular to automobile from the zero to transition resistance square when travelling herein, then automobile driving speed Wn is zero, and the most above-mentioned VIII formula and 2. formula are changed into following relationship respectively:
Ⅸ.Pd=Mf*Wf
Ⅹ.Wr=b1Wz
Now, auto idle speed, and above-mentioned 1. formula, 2. formula, 3. formula still set up.
2, speed change state (automobile accelerates, slows down):
From running car principle: Automobile drive moment of torsion Mn is equal to accelerating moment of torsion Ma and form drag square Mu sum, wherein, Mu becomes big along with automobile driving speed and becomes big.
Work as Mn > Mu, automobile accelerates, then automobile driving speed Wn increases, according to above-mentioned VII formula, then Automobile drive moment of torsion Mn diminishes, and running resistance square Mu increases along with Wn, until reaching balance, i.e. Automobile drive moment of torsion Mn is equal to running resistance square Mu, i.e. variator and realizes accelerating function；
Otherwise, when Mn ＜ Mu, Wn reduce, and Mn increases, and Mu reduces along with Wn, until reaching balance, i.e. Automobile drive moment of torsion Mn realizes deceleration equal to running resistance square, i.e. variator.
Whole process described above is all carried out under firm power, it is not necessary to extraneous control, then speed-change process is automatic, and whole change procedure gear does not has situation about coupling between changing mechanism, can realize infinitely variable speeds.
3, at the uniform velocity transport condition:
Seeing Fig. 4, when automobile is driven with less throttle, automobile can be with less speed Wn after accelerating1At the uniform velocity travel, if now opening the throttle, i.e. input power becomes big, and according to above-mentioned VII formula, Automobile drive moment of torsion Mn can become big immediately, this will cause Mn to be more than running resistance square Mu, thus automobile accelerates, i.e. automobile driving speed Wn can increase, and driving moment Mn diminishes, running resistance square Mu increases straight until equal with car driving torque Mn thus reach balance, and now automobile driving speed is Wn2, and Wn2More than Wn1, i.e. automobile can be with bigger speed Wn after accelerating2At the uniform velocity travel.It follows that driver can pass through throttle (input power) controls the speed that automobile at the uniform velocity travels.
Above description is explanation of the invention, is not the restriction to invention, and limited range of the present invention sees claim, within protection scope of the present invention, can make any type of amendment.

Claims (4)

  1. null1. double-planet train formula stepless auto gear，Including line of input star wheel series、Output planetary train，Described line of input star wheel series includes the first sun gear (1)、The first row star-wheel (2) with the first sun gear (1) external toothing、The first gear ring (3) with the first row star-wheel (2) internal messing，The first row star-wheel (2) is contained in the first row carrier (4) by bearing，Described output planetary train includes the second sun gear (5)、The second planetary gear (6) with the second sun gear (5) external toothing、The second gear ring (7) with the second planetary gear (6) internal messing，Second planetary gear (6) is contained on the second planet carrier (8) by bearing，It is characterized in that: the first sun gear (1)、Second sun gear (5) is contained on central shaft (9) by bearing，Central shaft (9) two ends are contained on machine case (10) by bearing，Input gear (12) on power shaft (11) engages with the first sun gear (1)，Second sun gear (5) engages with the output gear (14) on output shaft (13)，Power shaft (11) is contained on machine case (10) by bearing，Output shaft (13) is contained on machine case (10) by one-way clutch (15)；The first row carrier (4) is fixing with the second planet carrier (8) to be connected；First gear ring (3) is fixing with the second gear ring (7) to be connected, first gear ring (3) and the second gear ring (7) are contained on machine case (10) by bearing, and the first gear ring (3) is unequal with the gear ratio of the second sun gear (5) with the gear ratio of the first sun gear (1) and the second gear ring (7).
  2. 2. the double-planet train formula stepless auto gear as described in claim 1, it is characterized in that: the first gear ring (3) is provided with external tooth with the periphery of the fixing coupling part of the second gear ring (7), drive idler gear (16) engages with the external tooth on described fixing coupling part, drive idler gear (16) is contained in installation axle (18) by sliding bearing (17), installing axle (18) to be installed on machine case (10), drive idler gear (16) is by being connected upper slip of installation axle (18) with described double-planet train or disconnect.
  3. 3. the double-planet train formula stepless auto gear as described in claim 1, it is characterised in that: the first row carrier (4) of described fixing connection is structure as a whole with the second planet carrier (8).
  4. 4. the double-planet train formula stepless auto gear as described in claim 1, it is characterised in that: first gear ring (3) of described fixing connection is structure as a whole with the second gear ring (7).
CN201310498751.6A 2013-10-22 2013-10-22 Double-planet train formula stepless auto gear Expired - Fee Related CN103511566B (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101303064A (en) * 2007-05-11 2008-11-12 杨国辉 Differential feedback stepless speed changer
CN101327729A (en) * 2007-06-22 2008-12-24 丰田自动车株式会社 Power output apparatus and hybrid vehicle with power output apparatus
EP2584220A1 (en) * 2011-10-20 2013-04-24 Eurocopter Deutschland GmbH Planetary gear for variable transmission
CN103249966A (en) * 2010-12-15 2013-08-14 大众汽车有限公司 Transmission gear and differential gear, and motor unit and gear unit
CN203548743U (en) * 2013-10-22 2014-04-16 徐攀 Double-planet wheel system stepless automatic speed change mechanism

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101303064A (en) * 2007-05-11 2008-11-12 杨国辉 Differential feedback stepless speed changer
CN101327729A (en) * 2007-06-22 2008-12-24 丰田自动车株式会社 Power output apparatus and hybrid vehicle with power output apparatus
CN103249966A (en) * 2010-12-15 2013-08-14 大众汽车有限公司 Transmission gear and differential gear, and motor unit and gear unit
EP2584220A1 (en) * 2011-10-20 2013-04-24 Eurocopter Deutschland GmbH Planetary gear for variable transmission
CN203548743U (en) * 2013-10-22 2014-04-16 徐攀 Double-planet wheel system stepless automatic speed change mechanism

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