CN103511563B - Double-planet train formula stepless auto gear - Google Patents
Double-planet train formula stepless auto gear Download PDFInfo
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- CN103511563B CN103511563B CN201310499327.3A CN201310499327A CN103511563B CN 103511563 B CN103511563 B CN 103511563B CN 201310499327 A CN201310499327 A CN 201310499327A CN 103511563 B CN103511563 B CN 103511563B
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Classifications
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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
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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
- F16H3/76—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
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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
- 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 planetary train, two set planet circular systems all include sun gear, planetary gear, gear ring and planet carrier, two sun gears fill on center shaft, input gear engages with the gear ring of input system, the gear ring of output system engages with output gear, and central shaft and power shaft are contained on machine case, and output shaft is contained on machine case by one-way clutch；Two sun gears are affixed, and two fixing connections of planet carrier, the 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 speed 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 relativity and wider practicality.
Description
Technical field
The present invention relates to gear, be specifically related to include the electrodeless automatic transmission 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 difference
Rotating speed or torque transmission device, i.e. by speed change or bending moment, with the needs of satisfied different operating modes, extensively should
For various occasions.
As a example by automotive field, starting to walk, accelerating, travelling and overcoming different kinds of roads obstruction light to meet
To the needs driving net tractive force of wheel and speed difference to require under the conditions of different travelings, at engine and drive axle
Between be generally equipped with speed changer.Along with the development of auto industry, automotive transmission experienced by non-automatic variable-speed motor
Structure is to automatic transmission, from having level to the most traditional belt wheel transmission mechanism of stepless development, gear drive
Mechanism etc., the gear ratio of this kind of gear is single for step speed change, but low cost of manufacture, Er Qiegong
Skill is the most ripe；Such as based on moment speed change hydraulic automatic speed variator (AT), can independently realize nothing
Pole speed change, but mechanism is complicated, complex process, and manufacturing cost is high, and owing to fluid coupling makes
During with 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 the most in the world except above-mentioned points
(CVT), electric-controlled mechanical automatic speed transmission (AMT), the former takes turns based on a pair V-belt, steel belt with
And a set of hydraulic pressure and computer micro-controller system realize electrodeless fluid drive, this transmission technology content is high,
Manufacturing complexity, cost is high, and transmission tape lifetime is relatively short, and maintenance cost is high, and due to by such as material
Many-sided technical restrictions such as material performance, it is currently mainly limited on small-power automobile use；After
Person realizes having level, fluid drive based on the automatic manipulation mechanism that conventional transmissions and computer control, though
So its easily fabricated and low cost, but its shift property is poor, has pause and transition in rhythm or melody sense, time low-grade during gearshift
Pause and transition in rhythm or melody sense is especially apparent, it addition, this speed changer can only realize step speed change, and can not realize electrodeless change
Speed, 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 without
Level automatic transmission, by creating one only by external rotating angular speed or torsion outside main power cycle stream
The internal power recycle stream of square impact, by changing the size of inner loop stream and then obtaining the output torsion being suitable for
Square and rotational angular velocity, it is possible to realize automatic, electrodeless variable-speed function, and without fluid power mechanism, have higher
Economic relativity and wider practicality.
Technical scheme is as follows:
Double-planet train formula stepless auto gear, including line of input star wheel series, output planetary train, institute
State line of input star wheel series and include the first sun gear and the first row star-wheel and first of the first sun gear external toothing
First gear ring of planetary gear internal messing, the first row star-wheel is contained in the first row carrier by bearing, described output
Planet circular system includes the second sun gear and the second planetary gear of the second sun gear external toothing and the second planetary gear
Second gear ring of internal messing, the second planetary gear is contained on the second planet carrier by bearing, the first sun gear and
Two sun gears fill on center shaft by bearing, and central shaft two ends are contained on machine case by bearing, input
Input gear on axle and the engagement of the first gear ring, the second gear ring engages with the output gear on output shaft, input
Axle is contained on machine case by bearing, and output shaft is contained on machine case by one-way clutch；First too
Sun wheel is fixing with the second sun gear to be connected, and the first row carrier is fixing with the second planet carrier to be connected；First gear ring with
Second gear ring is contained on machine case by bearing, the first gear ring and the gear ratio of the first sun gear and the second tooth
Enclose unequal with the gear ratio of the second sun gear.
Its further technical scheme is:
The first row carrier is provided with external tooth, drive idler gear and institute with the described fixing coupling part of the second planet carrier
Stating the external tooth engagement on fixing coupling part, drive idler gear fills on the mounting shaft by sliding bearing, installs axle
Being installed on machine case, drive idler gear is connected with described two set planet circular systems by sliding on the mounting shaft
Or disconnect.
Described the first row carrier and the second planet carrier are all filled on center shaft by bearing.
The technique effect of the present invention:
The present invention uses input and output totally two set planet circular systems, first in wherein said line of input star wheel series
Gear ring is input, and the second gear ring in described output planetary train is output, in two set planet circular systems
Sun gear is fixing to be connected, and the fixing connection of planet carrier in two set planet circular systems, makes whole mechanism from input
End arrives outside the main power cycle stream of output, also forms one only by the external world turn between two set planet circular systems
Dynamic angular speed or the internal power recycle stream of torque influence, this inner loop power stream has a style of one's own, when described
When idling mechanism remains off with described two set planet circular systems, whole gear only one of which exports
Stream, is i.e. exported by output planetary train, when described idling mechanism keeps connecting shape with described two set planet circular systems
During state, whole change acceleration mechanism has two output streams, i.e. from the output of output planetary train with from described idling machine
Structure exports.When gear speed change of the present invention, owing to input power is known constant, described
In the case of two set planet circular systems disconnect with described idling mechanism, now, the output work in power conservation law
The moment of torsion of two factors of rate, i.e. output planetary train output and the most inversely proportional relation of rotational angular velocity.
Gear of the present invention is creating one only by extraneous rotational angular velocity demand or torque influence
On the basis of internal power recycle stream, according to moment of torsion or the demand shape of rotational angular velocity of gear output
Condition, obtains, 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, couple between without changing mechanism due to gear
In the case of can meet the demand of various rotating speed and moment of torsion, thus achieve electrodeless variable-speed function；At output shaft
It is provided with one-way clutch, it can be ensured that whole gear outbound course uniquely determines.The present invention compared to
Fluid power of the prior art mechanism, under being capable of automatic, electrodeless speed changing function equally, eliminates liquid
Power torque-converters, compared to mechanical stepless automatic speed changer of the prior art, it is not necessary to extra hydraulic pressure and electricity
Brain micro-controller system then can realize automatically controlling and adjusting, and the present invention is for existing speed changer, it is possible to
Realize in electrodeless and fluid drive, and speed-change process truly without cutting off between power, changing mechanism
Connection, and speed-change process is without pause and transition in rhythm or melody sense, simplifies structure and the making of gear, has higher warp
Ji property 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 under the final the most at the uniform velocity driving cycle of automobile turn round
The relation schematic diagram of square, automobile running resistance square and automobile driving speed.
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 that input power, Pc represent that power output, Mr represent that input torque, Wr represent that input rotates
Angular speed, Mc represents output moment of torsion, and Wc represents output rotational angular velocity, and Mr and Wr is known constant,
Pd represents the power by the output of described idling mechanism, and Mz represents that intermediate torque, Wz represent intermediate rotational angular
Speed, Mz and Wz is middle free variable, a, b, a1、b1Being constant factor, Ps represents speed change
The power of in-house loss；
In single row star wheel series, Wt represents sun gear rotational angular velocity, and Wx represents planet carrier angle of rotation speed
Degree, Wq represents ring gear against rotation angular speed, and Rt represents sun gear joint degree radius of circle, and Rx represents planetary gear joint degree
Radius of circle, Rq represents gear ring joint degree radius of circle, and k represents the ratio of Rq Yu Rt, and Mt represents the torsion of sun gear
Square, Mq represents the moment of torsion of gear ring, and Mx represents the moment of torsion of planet carrier, F1For the sun gear effect to planetary gear
Power, 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, Wx1Table
Show the rotational angular velocity of the first row carrier, Wq1Represent the rotational angular velocity of the first gear ring, Wt2Represent second too
The rotational angular velocity of sun wheel, Wx2Represent the rotational angular velocity of the second planet carrier, Wq2Represent turning of the second gear ring
Dynamic angular speed, Mt1Represent the moment of torsion of the first sun gear, Mx1Represent the moment of torsion of the first row carrier, Mq1Represent the
The moment of torsion of one gear ring, Mt2Represent the moment of torsion of the second sun gear, Mx2Represent the moment of torsion of the second planet carrier, Mq2Table
Show 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, Rx2
Represent the second planetary gear joint degree radius of circle, Rq2Represent the second gear ring joint degree radius of circle, k1Represent Rq1With Rt1
Ratio, k2Represent Rq2With Rt2Ratio, and k1≠k2, Mf represents that engine torque, Mn represent vapour
Car driving torque, Wf represents engine rotation angular speed, and Wn represents automobile driving speed, j, p, s, t
Being constant factor, Mu represents automobile running resistance square, and Mu follows automobile driving speed and becomes big and become big,
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.
See that Fig. 1, the present invention include line of input star wheel series, output planetary train, described line of input star wheel series bag
Include in the first sun gear 1 and the first row star-wheel 2 of the first sun gear 1 external toothing and the first row star-wheel 2
First gear ring 3 of engagement, multiple the first row star-wheels 2 are contained in the first row carrier 4 by bearing, described defeated
Planet wheels system includes the second sun gear 5 and the second planetary gear 6 of the second sun gear 5 external toothing and
Second gear ring 7 of two planetary gear 6 internal messing, multiple second planetary gears 6 are contained in the second planet carrier by bearing
On 8, the first sun gear 1 and the second sun gear 5 are contained on central shaft 9 by bearing, central shaft 9 two ends
Being contained on machine case 10 by bearing, the input gear 12 on power shaft 11 engages with the first gear ring 3,
Second gear ring 7 engages with the output gear 14 on output shaft 13, and power shaft 11 is contained in machine by bearing
On housing 10, output shaft 13 is contained on machine case 10 by one-way clutch 15；First sun gear 1
Fixing with the second sun gear 5 and be connected, the first row carrier 4 is fixing with the second planet carrier 8 to be connected；First gear ring
3 and second gear ring 7 be contained on machine case 10 by bearing, the first gear ring 3 and tooth of the first sun gear 1
Number than and the second gear ring 7 unequal with the gear ratio of the second sun gear 5, wherein, the first sun gear 1 and the
Two sun gears 5, the first row carrier 4 and the second planet carrier 8 are preferably fashioned as integrative-structure.
Further, in order to meet the working condition requirement of automobile provisional parking when low engine speed rotates, the
The fixing coupling part of one planet carrier 4 and the second planet carrier 8 is provided with external tooth, and drive idler gear 16 is with described
External tooth engagement on fixing coupling part, specifically, it is also possible at the first row carrier 4 and the second planet carrier 8
Between set an idler gear, this idler gear is the most affixed with the first row carrier the 4, second planet carrier 8, and
This idler gear engages with drive idler gear 16, and drive idler gear 16 is contained in installation axle 18 by sliding bearing 17
On, axle 18 is installed and is installed on machine case 10, drive idler gear 16, sliding bearing 17, installation axle
18 constitute idling mechanism, and drive idler gear 16 is by sliding with described two set planet circular systems even on installation axle 18
Connect or disconnect, making described idling mechanism be connected with described input, output planetary train or disconnect.
Disconnect with described input, output planetary train and described idling mechanism and illustrating, of the present invention
Gear 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, theoretically for, input power and power output it
Between there is also gear internal loss power P s, power attenuation Ps mostlys come from the same machine of gear shaft
With internal friction between device housing, based on current production technology, this friction factor can control the least,
And the rotational angular velocity of train can't occur much larger than input rotational angular velocity in the middle of in use
Situation, therefore the least by fricative power attenuation Ps, whether ignored can't change final
As a result, above-mentioned 3. formula is thus obtained；It is in even with described idling mechanism in described input, output planetary train
When connecing state, 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 be based in single row star wheel series sun gear, planetary gear and this three of gear ring turn
Between dynamic angular speed/moment of torsion on the basis of relation, the two of gear of the present invention are overlapped planet circular systems
The relation of the rotational angular velocity/moment of torsion of input/output carries out mathematical reckoning and obtains, and concrete reckoning process is such as
Under:
See that Fig. 3, Fig. 3 are typical single row star wheel series, including sun gear 100 and sun gear 100 outside
The planetary gear 200 of engagement, with the gear ring 300 of planetary gear 200 internal messing, planetary gear 200 is contained in planet carrier (figure
Not shown in 3) on, O in Fig. 31It is sun gear 100, gear ring 300 and the centre of motion of planet carrier, O2
The rotation center of planetary gear 200, B and A represent planetary gear 200 respectively with sun gear 100, gear ring 300
Meshing point, in single row star wheel series, there is following basic theory 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, and 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 root
Following 6. formula can be obtained 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 planetary gear 200
, under different stressing conditions, all there is the mathematical relationship of above-mentioned 5. formula, specifically proved in moment equilibrium condition
Journey is as follows:
1, when the sun gear 100 directed force F to planetary gear 2001Less than gear ring 300 to planetary gear 200
Directed force F2, 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 makes a concerted effort for F1, it is zero according to the planetary gear i.e. resultant torque of at the uniform velocity autobiography, available following mathematical relationship
Formula:
(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 for returning
Turn center, with O2, A be torsional forces application point system in, the sun gear 100 effect to planetary gear 200
Power F1In opposite direction with Mt, the gear ring 300 directed force F to planetary gear 2002Identical with Mq direction, by taking turns
The equilibrium condition of uniform rotation is done by system, 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 gear ring 300 to planetary gear 100
Directed force F2, 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 makes a concerted effort 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 for returning
Turn center, with O2, B be torsional forces application point system in, the sun gear 100 effect to planetary gear 200
Power F1Identical with Mt direction, the gear ring 300 directed force F to planetary gear 2002In opposite direction with Mq, by taking turns
The equilibrium condition of uniform rotation is done by system, 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 list as shown in Figure 3
The basic theory relation of above-mentioned 5. formula is there is between each moment of planet circular system.
On the basis of the above-mentioned 4. formula of single row star wheel series and the basic theory relation of 5. formula, to institute of the present invention
The relation of the rotational angular velocity/moment of torsion stating the input/output of two set planet circular systems of gear 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 gear ring 3 is input (i.e. Wq1=Wr,Mq1=Mr), second
Gear ring 7 is output (i.e. Wq2=Wc,Mq2=Mc), except there is 4. formula and 5. formula in single row star wheel series
Mathematical relationship, also as the first sun gear 1 and the second sun gear 5 is fixing connects, the therefore rotating speed of the two
And moment of torsion is the most equal, the first row carrier 4 is fixing with planet carrier 8 to be connected, the therefore rotational angular velocity of both
And moment of torsion is the most equal.
First, above-mentioned 4. formula is utilized to be analyzed calculating based on rotational angular velocity, gear of the present invention
Four groups of relations below meeting:
Ⅰ.Wt1+k1Wq1=(1+k1)Wx1
Ⅱ.Wt2+k2Wq2=(1+k2)Wx2
Ⅲ.Wt1=Wt2
Ⅳ.Wx1=Wx2
Integrated conversion obtained following 7. formula by above-mentioned I formula, II formula, III formula, IV formula:
⑦k1*Wq1=k2*Wq2+ (k1-k2) Wx1
By coefficient a after all coefficients in above-mentioned 7. formula are integrated1、b1Represent, Wx1Use intermediate torque Wz
Represent, Wq1For input rotational angular velocity Wr, Wq2For output rotational angular velocity Wc, the most above-mentioned 7. formula is
State 2. formula:
②Wr=a1Wc+b1Wz
Secondly, utilize above-mentioned 5. formula to be analyzed calculating based on moment of torsion, gear of the present invention meet with
Lower four groups of relations:
Ⅰ.Mt1+Mq1/k1=Mx1/(1+k1)
Ⅱ.Mt2+Mq2/k2=Mx2/(1+k2)
Ⅲ.Mt1=Mt2
Ⅳ.Mx1=Mx2
Integrated conversion obtained following 8. formula by above-mentioned I formula, II formula, III formula, IV formula:
⑧Mq1/k1=Mq2/k2+[1/(1+k1)-1/(1+k2)]Mx1
Represented by coefficient a, b after all coefficients in above-mentioned 8. formula are integrated, Mx1With intermediate torque Mz table
Show, Mq1For input rotational angular velocity Mr, Mq2For output rotational angular velocity Mc, the most above-mentioned 8. formula is above-mentioned
1. formula:
①Mr=aMc+bMz
Due to the first gear ring 3 and the gear ratio of the first sun gear 1 and the second gear ring 7 and the second sun gear 5
Gear ratio is unequal, according to the relation that gear ratio in gear train assembly is equal with radius ratio, then and 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、b1The most not
It is zero.
In three relationships of above-mentioned 1. formula, 2. formula, 3. formula that the present invention meets, due to Wr, Mr
For known constant, Wz, Mz are middle free variable, when determining the value of Wc or Mc any of which one,
Wz, Mz and Mc or the Wc that only one determines all can be searched out for above-mentioned 1. formula, 2. formula, 3. formula
Value make these three relationship set up, gear the most of the present invention rely on output rotational angular velocity
/ moment of torsion adjusts output moment of torsion/rotational angular velocity the most automatically, it is achieved that speed changing function automatically.
Fig. 2 is the theory structure schematic diagram of the present invention, and the present invention uses input and output totally two set planet circular system,
The first gear ring 3 in wherein said line of input star wheel series is input, second in described output planetary train
Gear ring 7 is output, the fixing connection of sun gear in two set planet circular systems, and the row in two set planet circular systems
Carrier is fixing to be connected, and makes whole mechanism outside the main power cycle stream 400 from input to output, goes back
Between two set planet circular systems, formation one is only affected by extraneous rotational angular velocity Wc demand or moment of torsion Mc
Internal power recycle stream 500.In Fig. 2, the straight line of band arrow is the path of power stream, internal power recycle stream
500 trains of mechanism being in closing, whole gear is when by ectocine, i.e. Mc or Wc changes
Time, internal power stream 500 can be automatically adjusted, i.e. by changing the middle free variable Wx of 7. formula and 8. formula1
And Mx1And then change output rotational angular velocity or output moment of torsion, realize automatic speed changing function with this.The present invention
Described gear is on the basis of creating internal power recycle stream 500, according to gear output
Moment of torsion or the demand status of rotational angular velocity, be suitable for by changing the size of inner loop stream 500
Output moment of torsion or output rotational angular velocity, it is achieved that automatic speed changing function；On the other hand, due to variable-speed motor
Structure can meet the demand of various rotating speed and moment of torsion in the case of coupling between without changing mechanism, it is achieved that nothing
Pole speed changing function.
For automotive transmission, gear input torque Mr depends on engine torque Mf and speed change
The converter torque ratio of mechanism, gearbox output torque Mc determines Automobile drive moment of torsion Mn, and speed changer input rotates
Angular speed Wr depends on the gear ratio of engine speed Wf and gear, and speed changer output speed Wc is certainly
Determine 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 is the most relatively
For improving and ripe, in the condition advanced, i.e. add tumbler gear, be not discussed at this, therefore, automobile
Gear 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, is understood car speed Wn by VII formula derived above
It is zero；
Low engine speed rotates: i.e. the provisional parking of automobile, then input power is not zero, now by manually
Controlling described idling mechanism and be in connection status with described two set planet circular systems, the most above-mentioned VIII formula is set up, now
If Mn is less than or equal to Mu, Mu refers in particular to automobile from the zero to transition resistance square when travelling, then garage herein
Sailing 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, and according to above-mentioned VII formula, then automobile drives
Dynamic torque 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. speed changer 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. speed changer.
Whole process described above is all carried out under firm power, it is not necessary to extraneous control, then speed-change process is certainly
Moving, whole change procedure gear does not has situation about coupling between changing mechanism, can realize stepless change
Speed.
3, at the uniform velocity transport condition:
Seeing Fig. 4, when automobile is driven with less throttle, automobile can be with a less speed after accelerating
Degree Wn1At the uniform velocity travelling, if now opening the throttle, i.e. input power becomes big, and according to above-mentioned VII formula, automobile drives
Dynamic torque Mn can become big immediately, and this will cause Mn to be more than running resistance square Mu, and thus automobile accelerates, i.e. vapour
Car travel speed Wn can increase, and driving moment Mn diminishes, and running resistance square Mu increases straight until driving with car
Dynamic torque Mn is equal thus reaches 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 be led to
Cross throttle (input power) and control 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 is joined
See claim, within protection scope of the present invention, any type of amendment can be made.
Claims (4)
- 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) and the second sun gear (5) are 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 gear ring (3)，Second gear ring (7) 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)；First sun gear (1) is fixing with the second sun gear (5) to be connected, and the first row carrier (4) is fixing with the second planet carrier (8) 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)；The first row carrier (4) is provided with external tooth with the periphery of the described fixing coupling part of the second planet carrier (8), 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.
- 2. the double-planet train formula stepless auto gear as described in claim 1, it is characterised in that: described the first row carrier (4) and the second planet carrier (8) are all contained on central shaft (9) by bearing.
- 3. the double-planet train formula stepless auto gear as described in claim 1, it is characterised in that: first sun gear (1) of described fixing connection is structure as a whole with the second sun gear (5).
- 4. 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).
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| DE102016225169A1 (en) * | 2016-12-15 | 2018-06-21 | Zf Friedrichshafen Ag | Gear for a bike |
| CN107120396B (en) * | 2017-06-13 | 2023-08-08 | 中南林业科技大学 | Three-stage planetary gear train automatic transmission |
| CN109442009A (en) * | 2018-12-20 | 2019-03-08 | 潍柴动力股份有限公司 | A kind of variable transmission mechanism and in-wheel driving are mechanical |
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| CN2526595Y (en) * | 2002-03-02 | 2002-12-18 | 申万华 | Planetary gear type buncher |
| CN2773407Y (en) * | 2005-03-23 | 2006-04-19 | 田家铭 | Cyclic accelerated speed variator |
| KR20060103252A (en) * | 2006-08-03 | 2006-09-28 | 강헌국 | Stepless speed change gear |
| CN102661368A (en) * | 2012-04-22 | 2012-09-12 | 崔永兴 | Continuously variable transmission for dual planetary gear |
| CN203548738U (en) * | 2013-10-22 | 2014-04-16 | 徐攀 | Double-planetary gear train type continuously variable transmission mechanism |
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