CN103511568B - Double-planet train formula stepless auto gear - Google Patents
Double-planet train formula stepless auto gear Download PDFInfo
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- CN103511568B CN103511568B CN201310499998.XA CN201310499998A CN103511568B CN 103511568 B CN103511568 B CN 103511568B CN 201310499998 A CN201310499998 A CN 201310499998A CN 103511568 B CN103511568 B CN 103511568B
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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
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Abstract
Double-planet train formula stepless auto gear, comprise input and output two and overlap planetary gear train, two sun gears are contained on the central shaft of machine case, input gear or output gear engage with the sun gear in the first train, planet carrier in second train engages with output gear or input gear, and input shaft is contained on machine case, and output shaft is contained on machine case by overrunning clutch, the planet carrier of the first train and the sun gear of the second train affixed, and two gear rings are fixedly connected with.The present invention by creating one only by the internal power circular flow that external torque or rotational angular velocity affect outside main power cycle stream, the output torque be applicable to by the size and then obtain changing inner loop stream and rotational angular velocity, automatic, electrodeless variable-speed function can be realized, and without the need to fluid power mechanism, there is higher economic relativity and wider practicability.
Description
Technical field
The present invention relates to gear, be specifically related to the electrodeless automatic transmission comprising double-planet train.
Background technique
Gear be a kind of when input shaft rotating speed or moment of torsion constant, make output shaft obtain different rotating speeds or torque transmission device, namely by speed change or bending moment, with the needs of satisfied different operating mode, be widely used in various occasion.
For automotive field, in order to meet starting to walk, accelerating, travel and overcoming the needs to driving net tractive force of wheel and the requirement of speed of a motor vehicle difference under the different driving conditions of different kinds of roads obstruction light, between motor and ransaxle, usually speed changer is housed.Along with the development of automotive industry, automotive transmission experienced by non-automatic gear to automatic transmission, from having level to stepless development, such as traditional belt wheel transmission mechanism, gear drive etc., the gear ratio of this kind of gear is single is step change, but low cost of manufacture, and technique is comparatively ripe; Again such as based on the hydraulic automatic speed variator (AT) of moment speed change, independently can realize electrodeless variable-speed, but mechanism is complicated, complex process, manufacture cost is high, and due to hydraulic couplers in use automobile export 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) in the world at present 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 automatic speed changing, this transmission technology content is high, manufacture complicated, cost is high, the driving belt life-span is relatively short, maintenance cost is high, and owing to being subject to as many-sided technical restrictions such as material properties, it is mainly limited at present on small-power automobile and uses; The latter realizes having level, automatic speed changing based on the automatic manipulation mechanism of conventional transmissions and conputer controlled, although it is easy to manufacture and cost is low, 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 obvious, and in addition, this speed changer can only realize step change, and electrodeless variable-speed can not be realized, and extraneous the intervention need be introduced.
Summary of the invention
The applicant improves for above-mentioned shortcoming of the prior art, a kind of double-planet train formula stepless auto gear is provided, by creating the internal power circular flow that is only subject to external rotating angular velocity or torque influence outside main power cycle stream, the output torque be applicable to by the size and then obtain changing inner loop stream and rotational angular velocity, automatic, electrodeless speed changing function can be realized, and eliminate fluid power of the prior art mechanism, there is higher economic relativity.
Technological scheme of the present invention is as follows:
Double-planet train formula stepless auto gear, comprise first planet train, second planetary gear train, described first planet train comprises the first sun gear, with the first row star-wheel of the first sun gear outer gearing, with the first gear ring of the first row star-wheel internal messing, the first row star-wheel is contained in the first row carrier by bearing, described second planetary gear train comprises the second sun gear, with the second planet wheel of the second sun gear outer gearing, with the second gear ring of the second planet wheel internal messing, second planet wheel is contained on the second planet carrier by bearing, first sun gear and the second sun gear fill on center shaft by bearing, central shaft two ends are contained on machine case by bearing, the first gear on first jack shaft engages with the first sun gear, second sun gear is fixedly connected with the first row carrier, second planet carrier is connected with the 3rd gear, the second gears meshing on 3rd gear and the second jack shaft, first jack shaft and the second jack shaft are contained on machine case all rotationally, first gear ring is fixedly connected with the second gear ring, and the first gear ring and the second gear ring are contained on machine case by bearing.
Its further technological scheme is:
First gear ring is provided with external tooth with the periphery being fixedly connected with part described in the second gear ring, drive idler gear engages with the described external tooth be fixedly connected with in part, drive idler gear fills on the mounting shaft by sliding bearing, installation shaft is installed on machine case, and drive idler gear overlaps planetary gear train by sliding on the mounting shaft with described two and is connected or disconnects.
Described the first row carrier, the second planet carrier and the 3rd gear are all filled on center shaft by bearing.
Described first jack shaft is input shaft, and the second jack shaft is output shaft, and the second jack shaft is contained on machine case by overrunning clutch.
Described first jack shaft is output shaft, and the second jack shaft is input shaft, and the first jack shaft is contained on machine case by overrunning clutch.
The described the first row carrier that is fixedly connected with and the second sun gear are structure as a whole.
Described the first gear ring of being fixedly connected with and the second gear ring are structure as a whole.
Technique effect of the present invention:
The present invention uses two cover planetary gear train, two cover planetary gear train are the relation of line of input star wheel series and output planetary train, wherein, first planet can be made to take turns and to be wheel for inputting system and the first sun gear is input end, second planetary gear train is output wheel train and the second planet carrier is output terminal, also first planet can be made to take turns and to be output wheel train and the first sun gear is output terminal, second planetary gear train is for input train and the second planet carrier is input end, except the relation of input and output is not identical, all the other annexations are constant, in the embodiment that above-mentioned two kinds of constrained input annexations are formed, the first row carrier is fixedly connected with the second sun gear, first gear ring is fixedly connected with the second gear ring, make whole mechanism outside the main power cycle stream from input end to output terminal, also between two cover planetary gear train, form the internal power circular flow that is only subject to extraneous rotating speed or torque influence, this inner loop power stream has a style of one's own, when described idling mechanism remains open state with described two cover planetary gear train, whole gear only has an output stream, namely exported by output planetary train, when described idling mechanism keeps coupled condition with described two cover planetary gear train, whole change acceleration mechanism has two output streams, namely export from output planetary train and export from described idling mechanism.When gear speed change of the present invention, because input power is known constant, when described two cover planetary gear train and described idling mechanism disconnect, now, two factors of the output power in power conservation law, the i.e. moment of torsion of output planetary train output terminal and rotational angular velocity then inversely proportional relation.Gear of the present invention is only subject on the basis of the internal power circular flow of extraneous rotational angular velocity demand or torque influence establishment one, according to the moment of torsion of gear output terminal or the demand status of rotational angular velocity, the output torque be applicable to by the size thus obtain changing inner loop stream or export rotational angular velocity, thus achieves automatic speed changing function; On the other hand, due to the demand of various rotating speed and moment of torsion can be met gear connects between without the need to changing mechanism, electrodeless variable-speed function is thus achieved; Output shaft is provided with overrunning clutch, can guarantees that whole gear outbound course is uniquely determined.The present invention is compared to fluid power mechanism of the prior art, can realize 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 adjustment without the need to extra hydraulic pressure and computer micro-controller system, the present invention is for existing speed changer, electrodeless and automatic speed changing truly can be realized, and without the need to 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 practicability.
Accompanying drawing explanation
Fig. 1 is structural representation of the present invention.
Fig. 2 is the theory structure schematic diagram of Fig. 1.
Fig. 3 is the easy structure schematic diagram of single planetary gear train, there is shown the stressing conditions of single planetary bevel gear.
Fig. 4 is with two kinds of different accelerator drive automobiles and the relation schematic diagram of Automobile drive moment of torsion, automobile running resistance square and automobile driving speed under making the final at the uniform velocity driving cycle of automobile.
Fig. 5 is the theory structure schematic diagram of another embodiment of the present invention.
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 planet wheel; 7, the second gear ring; 8, the second planet carrier; 9, central shaft; 10, machine case; 11, the first jack shaft; 12, the first gear; 13, the second jack shaft; 14, the second gear; 15, overrunning clutch; 16, drive idler gear; 17, sliding bearing; 18, installation shaft; 19, the 3rd gear; 100, sun gear; 200, planet wheel; 300, external toothing; 400, main power cycle stream; 500, internal power circular flow.
Embodiment
Now the letter in the formula of the present invention's employing and symbol are explained as follows.
Pr represents input power, Pc represents output power, and Mr represents input torque, and Wr represents input rotational angular velocity, Mc represents output torque, Wc represents output rotational angular velocity, and Mr and Wr is known constant, and Pd represents the power exported by described idling mechanism, Mz represents intermediate torque, Wz represents central rotational angular velocity, Mz and Wz is middle free variable, a, b, a
1, b
1be constant factor, Ps represents the power of gear internal losses;
In single planetary gear train, 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 circle radius, Rx represents planet wheel joint degree circle radius, and Rq represents gear ring joint degree circle radius, and k represents the ratio of Rq and 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, F
1for sun gear is to the active force of planet wheel, F
2for gear ring is to the active force of planet wheel, F
3for planet carrier is to the active force of planet wheel;
In described constrained input planetary gear train, Wt
1represent the rotational angular velocity of the first sun gear, Wx
1represent the rotational angular velocity of the first row carrier, Wq
1represent the rotational angular velocity of the first gear ring, Wt
2represent the rotational angular velocity of the second sun gear, Wx
2represent the rotational angular velocity of the second planet carrier, Wq
2represent the rotational angular velocity of the second gear ring, Mt
1represent the moment of torsion of the first sun gear, Mx1 represents the moment of torsion of the first row carrier, Mq
1represent the moment of torsion of the first gear ring, Mt
2represent the moment of torsion of the second sun gear, Mx
2represent the moment of torsion of the second planet carrier, Mq
2represent the moment of torsion of the second gear ring, Rt
1represent the first sun gear joint degree circle radius, Rx
1represent the first row star-wheel joint degree circle radius, Rq
1represent the first gear ring joint degree circle radius, Rt
2represent the second sun gear joint degree circle radius, Rx
2represent the second planet wheel joint degree circle radius, Rq
2represent the second gear ring joint degree circle radius, k
1represent Rq
1with Rt
1ratio, k
2represent Rq
2with Rt
2ratio, Mf represents Engine torque, and Mn represents Automobile drive moment of torsion, Wf represents engine rotation angular velocity, and Wn represents automobile driving speed, and j, p, s, t are constant factor, Mu represents automobile running resistance square, and Mu follows automobile driving speed becomes large and become large, and Ma represents acceleration moment of torsion.
Below in conjunction with accompanying drawing, the specific embodiment of the present invention is described.
See Fig. 1, the present invention includes first planet train, second planetary gear train, first planet train comprises the first sun gear 1, with the first row star-wheel 2 of the first sun gear 1 outer gearing, with the first gear ring 3 of the first row star-wheel 2 internal messing, multiple the first row star-wheel 2 is contained in the first row carrier 4 by bearing, second planetary gear train comprises the second sun gear 5, with the second planet wheel 6 of the second sun gear 5 outer gearing, with the second gear ring 7 of the second planet wheel 6 internal messing, multiple second planet wheel 6 is contained on the second planet carrier 8 by bearing, 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, the first gear 12 on first jack shaft 11 engages with the first sun gear 1, particularly, increase the axial length of the first sun gear 1, be made into by the first sun gear 1 and stretch out described line of input star wheel series vertically, described extension is engaged with the first gear 12, or be axially connected with an intermediate gear with the first sun gear 1, described intermediate gear is engaged with the first gear 12, second sun gear 5 is fixedly connected with the first row carrier 4, preferably, the described the first row carrier 4 that is fixedly connected with and the second sun gear 5 are structure as a whole, second planet carrier 8 is connected with the 3rd gear 19,3rd gear 19 engages with the second gear 14 on the second jack shaft 13, first jack shaft 11 and the second jack shaft 13 are contained on machine case 10 all rotationally, and the first row carrier 4, second planet carrier 8 and the 3rd gear 19 are all contained on central shaft 9 by bearing, first gear ring 3 is fixedly connected with the second gear ring 7, and the first gear ring 3 and the second gear ring 7 are contained on machine case 10 by bearing, and the first gear ring 3 be fixedly connected with preferably and the second gear ring 7 are structure as a whole.
Further, in order to meet the working condition requirement of automobile provisional parking when low engine speed is rotated, external tooth is provided with the periphery being fixedly connected with part of the second gear ring 7 at the first gear ring 3, drive idler gear 16 engages with the described external tooth be fixedly connected with in part, particularly, also an intermediate gear can be established between the first gear ring 3 and the second gear ring 7, this intermediate gear and the first gear ring 3, second gear ring 7 is all affixed, and this intermediate gear engages with drive idler gear 16, drive idler gear 16 is contained in installation shaft 18 by sliding bearing 17, installation shaft 18 is installed on machine case 10, drive idler gear 16, sliding bearing 17, installation shaft 18 forms idling mechanism, drive idler gear 16 overlaps planetary gear train by sliding in installation shaft 18 with described two and is connected or disconnects, make described idling mechanism and described input, output planetary train connects or disconnects.
Two cover planetary gear train in the present invention are the relation of line of input star wheel series and output planetary train, the input end of line of input star wheel series and gear is rotationally connected, the output terminal of output planetary train and gear is rotationally connected, gear of the present invention comprises two embodiments, namely two cover planetary gear train all can as line of input star wheel series or output planetary train, and other annexations are constant, Fig. 2 is a kind of embodiment of the present invention, namely first planet wheel is wheel for inputting system and the first sun gear 1 is input end, second planetary gear train is output wheel train and the second planet carrier 8 is output terminal, particularly, first jack shaft 11 is input shaft, second jack shaft 13 is output shaft, second jack shaft 13 is contained on machine case 10 by overrunning clutch 15, Fig. 5 is another embodiment of the present invention, namely first planet wheel be output wheel train and the first sun gear 1 be output terminal, the second output wheel train is for input train and the second planet carrier 8 is input end, particularly, first jack shaft 11 is output shaft, second jack shaft 13 is input shaft, and the first jack shaft 11 is contained on machine case 10 by overrunning clutch 15.
Disconnect with described input, output planetary train and described idling mechanism and being described, gear of the present invention meets following three conditions:
①Mr=aMc+bMz
②Wr=a
1Wc+b
1Wz
③Mr*Wr=Mc*Wc
Above-mentioned 3. formula is drawn by power conservation law, theoretically, a gear internal loss power P s is also there is between input power and output power, power loss Ps mainly comes from gear shaft with between machine case and inner friction, based on current production technology, this friction factor can control very little, and in use can't there is the situation much larger than input rotational angular velocity in the rotational angular velocity of train, therefore very little by fricative power loss Ps, whether ignored and can't be changed final result, obtain above-mentioned 3. formula thus, when described input, output planetary train and described idling mechanism are in coupled condition, input power some export through described idling mechanism, namely now, above-mentioned 3. formula is expressed as following formula:
Mr*Wr=Mc*Wc+Pd
Above-mentioned 1. formula and 2. formula are on the basis of relation between the rotational angular velocity/moment of torsion based on sun gear in single planetary gear train, planet wheel and this three of gear ring, carry out mathematical reckoning to the relation of the rotational angular velocity/moment of torsion of the I/O of two cover planetary gear train of gear of the present invention and obtain, concrete reckoning process is as follows:
See Fig. 3, Fig. 3 is typical single planetary gear train, comprise sun gear 100, with the planet wheel 200 of sun gear 100 outer gearing, with the gear ring 300 of planet wheel 200 internal messing, planet wheel 200 is contained on planet carrier (not shown in Fig. 3), O in Fig. 3
1the centre of motion of sun gear 100, gear ring 300 and planet carrier, O
2the rotation center of planet wheel 200, B and A represent planet wheel 200 respectively with the contact points of sun gear 100, gear ring 300, in single planetary gear train, there is following basic theory relation:
④Wt+kWq=(1+k)Wx
⑤Mt+Mq/k=Mx/(1+k)
Above-mentioned 4. formula draws based on Principles of Gear Connection (namely equal in engagement place speed), if sun gear 100 sense of rotation is postive direction, planet wheel 200 rotational angular velocity is Wx, with planet wheel 200 for object of reference, then sun gear 100 rotational angular velocity is (Wt-Wx), external toothing 300 rotational angular velocity is (Wq-Wx), then can obtain following 6. formula according to Principles of Gear Connection:
⑥Wq-Wx=-Rt*（Wt-Wx）/Rq
Give k=Rq/Rt, and k > 1, then above-mentioned 6. formula can be reduced to above-mentioned 4. formula:
Above-mentioned 5. formula is that planetary gear train draws when being in state of equilibrium, and see Fig. 3, according to the moment equilibrium condition of planet wheel 200, under different stressing conditions, all there is the mathematical relationship of above-mentioned 5. formula, the concrete process of argumentation is as follows:
1, when the directed force F of sun gear 100 pairs of planet wheels 200
1be less than the directed force F of gear ring 300 pairs of planet wheels 200
2, be gyration center by structure one with B, with O
2, A is the system of torque force point of action.
Within the system, by O
2the power equivalence of point transfers to A point has A point with joint efforts suffered: F
2+ F
3/ 2, and make a concerted effort for F suffered by B point
1, according to planet wheel at the uniform velocity autobiography and resultant torque be zero, following relationship can be obtained:
(F
2+F
3/2)Rx-F
1*Rx=0
Above formula simplifies can obtain following I formula:
ⅰ.（F
2-F
1）*2+F
3=0
If the torque of sun gear 100, gear ring 300 and planet carrier is respectively Mt, Mq, Mx, be gyration center with B, with O
2, A is in the system of torque force point of action, the directed force F of sun gear 100 pairs of planet wheels 200
1contrary with Mt direction, the directed force F of gear ring 300 pairs of planet wheels 200
2identical with Mq direction, done the equilibrium conditions of uniform rotation by train, following four relationships can be obtained:
F
1=-Mt/Rt
F
2=Mq/Rq
F
3=-Mx/（Rt+Rx）
Rx=（Rq-Rt）/2
Convert according to above-mentioned two relations below and can obtain following II formula:
ⅱ.F
3=-2*Mx/（Rt+Rq）
II formula is brought into the conversion of I formula and can obtain following III formula:
ⅲ.Mt/Rt+Mq/Rq=Mx/（Rt+Rq）
K=Rq/Rt is substituted into above-mentioned III formula, above-mentioned 5. formula can be obtained:
2, when the directed force F of sun gear 100 pairs of planet wheels 200
1be greater than the directed force F of gear ring 300 pairs of planet wheels 100
2, be gyration center by structure one with A, with O
2, B is the system of torque force point of action.
Within the system, by O
2the power equivalence of point transfers to B point has B point with joint efforts suffered: F
1+ F
3/ 2, and make a concerted effort for F suffered by A point
2, according to planet wheel at the uniform velocity autobiography and resultant torque be zero, following relationship can be obtained:
(F
1+F
3/2)Rx-F
2*Rx=0
Above formula simplifies can obtain following iv formula:
iv.（F
1-F
2）*2+F
3=0
If the torque of sun gear 100, gear ring 300 and planet carrier is respectively Mt, Mq, Mx, be gyration center with A, with O
2, B is in the system of torque force point of action, the directed force F of sun gear 100 pairs of planet wheels 200
1identical with Mt direction, the directed force F of gear ring 300 pairs of planet wheels 200
2contrary with Mq direction, done the equilibrium conditions of uniform rotation by train, following four relationships can be obtained:
F
1=Mt/Rt
F
2=-Mq/Rq
F
3=-Mx/（Rt+Rx）
Rx=（Rq-Rt）/2
Convert according to above-mentioned two relations below and can obtain following V formula:
v.F
3=-2*Mx/（Rt+Rq）
V formula is brought into the conversion of iv formula and can obtain following VI formula:
vi.Mt/Rt+Mq/Rq=Mx/（Rt+Rq）
K=Rq/Rt is substituted into above-mentioned VI formula, above-mentioned 5. formula can be obtained equally.
According to the above-mentioned equalising torque analysis about single planetary gear train, known, there is the basic theory relation of above-mentioned 5. formula between each moment for single planetary bevel gear system as shown in Figure 3.
In the above-mentioned 4. formula of single planetary gear train and the basis of the 5. basic theory relation of formula, two relations of overlapping the rotating speed/moment of torsion of the I/O of planetary gear train of Fig. 1 and described gear embodiment illustrated in fig. 2 are calculated, can obtain the conclusion of above-mentioned 1. formula and 2. formula, concrete reckoning process is as follows:
In Fig. 1 and gear embodiment illustrated in fig. 2, the first sun gear 1 is input end (i.e. Wt1=Wr, Mt
1=Mr), the second planet carrier 8 is output terminal (i.e. Wx
2=Wc, Mx
2=Mc), except there is in single planetary gear train the mathematical relationship of 4. formula and 5. formula, also because the first row carrier 4 is fixedly connected with the second sun gear 5, therefore the two rotational angular velocity and moment of torsion all equal, first gear ring 3 is fixedly connected with the second gear ring 7, rotational angular velocity therefore both and moment of torsion all equal.
First, utilize above-mentioned 4. formula to carry out analysis based on rotational angular velocity and calculate, gear described in this embodiment meets following four groups of relations:
I.Wt
1+k
1Wq
1=(1+k
1)Wx
1
II.Wt
2+k
2Wq
2=(1+k
2)Wx
2
III.Wx
1=Wt
2
IV.Wq
1=Wq
2
Integrated conversion obtained following 7. formula by above-mentioned I formula, II formula, formula III, IV formula:
⑦Wt
1=(1+k
1+K
2+k
1k
2)Wx
2-（k
2+k
1k
2+k
1）Wq
1
By coefficient a after all coefficients in above-mentioned 7. formula are integrated
1, b
1represent, Wq
1represent with intermediate torque Wz, Wt
1for input rotational angular velocity Wr, Wx
2for exporting rotational angular velocity Wc, then above-mentioned 7. formula is above-mentioned 2. formula:
②Wr=a
1Wc+b
1Wz
Secondly, utilize above-mentioned 5. formula to carry out analysis based on moment of torsion and calculate, gear of the present invention meets following four groups of relations:
I.Mt1+Mq
1/k
1=Mx
1/(1+k
1)
II.Mt
2+Mq
2/k
2=Mx
2/(1+k
2)
III.Mx
1=Mt
2
IV.Mq
1=Mq
2
Integrated conversion obtained following 8. formula by above-mentioned I formula, II formula, formula III, IV formula:
⑧(1+k
1)Mt
1=Mx
2/(1+k
2)-(1+1/k
1+1/k
2)Mq
1
Represented by coefficient a, b after all coefficients in above-mentioned 8. formula are integrated, Mq
1represent with intermediate torque Mz, Mt
1for input rotational angular velocity Mr, Mx
2for exporting rotational angular velocity Mc, then above-mentioned 8. formula is above-mentioned 1. formula:
①Mr=aMc+bMz
Because the first gear ring 3 and the gear ratio of the first sun gear 1 and the gear ratio of the second gear ring 7 and the second sun gear 5 are all greater than 1, the relation equal with radius ratio according to gear ratio in gear train assembly, then k
1and k
2value be all greater than 1, therefore, above-mentioned 7. formula and 8. formula integrate after coefficient a, b, a
1, b
1all non-vanishing.
In three relationships of above-mentioned 1. formula, 2. formula, 3. formula that Fig. 1 and gear embodiment illustrated in fig. 2 meet, because Wr, Mr are known constant, Wz, Mz are middle free variable, when determine Wc or Mc wherein the value of arbitrary time, the value that all can search out unique Wz, Mz and Mc determined or Wc for above-mentioned 1. formula, 2. formula, 3. formula makes these three relationships set up, namely gear of the present invention relies on output terminal rotational angular velocity/moment of torsion and correspondingly automatically adjusts output torque/rotational angular velocity, achieves automatic speed changing function.
Fig. 2 is theory structure schematic diagram embodiment illustrated in fig. 1, this embodiment uses input and output totally two cover planetary gear train, wherein first planet wheel is wheel for inputting system and the first sun gear 1 is input end, second planetary gear train is output wheel train and the second planet carrier 8 is output terminal, second sun gear 5 is fixedly connected with the first row carrier 4, and the gear ring in two cover planetary gear train is fixedly connected with, make whole mechanism outside the main power cycle stream 400 from input end to output terminal, also between two cover planetary gear train, form one only by the internal power circular flow 500 that extraneous rotational angular velocity Wc demand or moment of torsion Mc affect.Straight line with arrow in Fig. 2 and Fig. 5 is the path of poower flow, internal power circular flow 500 is in closed train of mechanism, whole gear when being subject to ectocine, namely Mc or Wc change time, automatically internal power stream 500 can be regulated, namely by changing the middle free variable Wq of 7. formula and 8. formula
1and Mq
1and then change output rotational angular velocity or output torque, realize automatic speed changing function with this.Gear of the present invention is on the basis creating internal power circular flow 500, according to the moment of torsion of gear output terminal or the demand status of rotational angular velocity, the output torque be applicable to by the size thus obtain changing inner loop stream 500 or export rotational angular velocity, achieves automatic speed changing function; On the other hand, due to the demand of various rotating speed and moment of torsion can be met gear connects between without the need to changing mechanism, electrodeless variable-speed function is achieved.
Fig. 5 shows the theory structure schematic diagram of another embodiment of the present invention, this embodiment uses input and output totally two cover planetary gear train equally, wherein first planet wheel is output wheel train and the first sun gear 1 is output terminal, second planetary gear train is for input train and the second planet carrier 8 is input end, second sun gear 5 is fixedly connected with the first row carrier 4, and the gear ring in two cover planetary gear train is fixedly connected with, compared with the embodiment shown in Fig. 2, except the relation change of constrained input, other annexations are constant, this embodiment forms one only by the rotational angular velocity demand in the external world or the internal power circular flow 500 of torque influence equally between two cover planetary gear train, and internal power circular flow 500 has a style of one's own, variable-speed torque-converting is realized by changing the size flowing through the internal power stream of described bending moment mechanism, embodiment shown in Fig. 5 meets above-mentioned 1. formula equally, 2. formula, 3. these three relationships of formula, the concrete process of argumentation can with reference to the above-mentioned process of argumentation about the embodiment shown in Fig. 2.
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, speed changer input rotational angular velocity Wr depends on the gear ratio of engine speed Wf and gear, speed changer output speed Wc determines automobile driving speed Wn, in like manner, according to above-mentioned 1. formula, 2. formula, 3. formula, following four relations can be drawn:
V.Mf=jMn+pMz
VI.Wf=sWn+tWz
Idling mechanism described in VII.Mf*Wf=Mn*Wn(and described two overlaps planetary gear train and remains open)
Idling mechanism described in VIII.Mf*Wf=Mn*Wn+Pd(and described two overlaps planetary gear train and keeps being connected)
Automobile have in the process of moving parking, speed change, at the uniform velocity, this several state of moveing backward, car-backing function is comparatively perfect and ripe, namely in the condition of advancing, tumbler gear is added, be not discussed at this, therefore, automobile variable speed mechanism needs can meet the working condition requirement under above-mentioned different conditions, are described as follows:
1. parked state, now comprises again engine stop and low engine speed rotation two states:
Engine stop: i.e. automobile flameout, therefore Wf=0 is zero by the known car speed Wn of VII formula derived above;
Low engine speed is rotated: i.e. the provisional parking of automobile, then input power is non-vanishing, now overlap planetary gear train by idling mechanism described in manual control and described two and be in coupled condition, then above-mentioned VIII formula is set up, if now Mn is less than or equal to Mu, herein Mu refer in particular to automobile from zero to travel time critical resistance square, then automobile driving speed Wn is zero, then above-mentioned VIII formula and 2. formula change following relationship respectively into
IX.Pd=Mf*Wf
X.Wr=b
1Wz
Now, auto idle speed, and above-mentioned 1. formula, 2. formula, 3. formula are still set up.
2, speed change state (automobile acceleration, deceleration):
From automobile running principle: Automobile drive moment of torsion Mn equals to accelerate moment of torsion Ma and form drag square Mu sum, wherein, Mu becomes large along with automobile driving speed and becomes large.
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 reach balance, namely Automobile drive moment of torsion Mn equals running resistance square Mu, and namely speed changer realizes accelerating function;
Otherwise when Mn < Mu, Wn reduce, Mn increases, and Mu reduces along with Wn, until reach balance, namely Automobile drive moment of torsion Mn equals running resistance square, and namely speed changer realizes deceleration.
Whole process described above is all carried out under firm power, and control without the need to the external world, then speed-change process is automatic, and whole change procedure gear does not have situation about connecting between changing mechanism, can realize stepless change.
3, at the uniform velocity travelling state:
See Fig. 4, when automobile is driven with less throttle, automobile is understood with a less speed Wn after accelerating
1at the uniform velocity travel, if now open the throttle, namely input power becomes large, and according to above-mentioned VII formula, Automobile drive moment of torsion Mn can become large immediately, this will cause Mn to be greater than running resistance square Mu, automobile accelerates thus, and namely 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 Wn
2, and Wn
2be greater than Wn
1, namely automobile is understood with a larger speed Wn after accelerating
2at the uniform velocity travel.It can thus be appreciated that driver can pass through throttle (input power) and control the speed that automobile at the uniform velocity travels.
More than describing is explanation of the invention, and be not the restriction to invention, limited range of the present invention, see claim, within protection scope of the present invention, can do any type of amendment.
Claims (7)
1. double-planet train formula stepless auto gear, comprise first planet train, second planetary gear train, described first planet train comprises the first sun gear (1), with the first row star-wheel (2) of the first sun gear (1) outer gearing, with first gear ring (3) of the first row star-wheel (2) outer gearing, the first row star-wheel (2) is contained in the first row carrier (4) by bearing, described second planetary gear train comprises the second sun gear (5), with second planet wheel (6) of the second sun gear (5) outer gearing, with second gear ring (7) of the second planet wheel (6) outer gearing, second planet wheel (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, the first gear (12) on first jack shaft (11) engages with the first sun gear (1), second sun gear (5) is fixedly connected with the first row carrier (4), second planet carrier (8) is connected with the 3rd gear (19), 3rd gear (19) engages with the second gear (14) on the second jack shaft (13), first jack shaft (11) and the second jack shaft (13) are contained on machine case (10) all rotationally, first gear ring (3) is fixedly connected with the second gear ring (7), and the first gear ring (3) and the second gear ring (7) are contained on machine case (10) by bearing, first jack shaft (11) and the second jack shaft (13) are respectively input shaft, the output shaft of described double-planet train formula stepless auto gear, or the first jack shaft (11) and the second jack shaft (13) are respectively output shaft, the input shaft of described double-planet train formula stepless auto gear.
2. by double-planet train formula stepless auto gear according to claim 1, it is characterized in that: the first gear ring (3) is provided with external tooth with the periphery being fixedly connected with part described in the second gear ring (7), drive idler gear (16) engages with the described external tooth be fixedly connected with in part, drive idler gear (16) is contained in installation shaft (18) by sliding bearing (17), installation shaft (18) is installed on machine case (10), and drive idler gear (16) passes through slip in installation shaft (18) and is connected with described double-planet train or disconnects.
3., by double-planet train formula stepless auto gear according to claim 1, it is characterized in that: described the first row carrier (4), the second planet carrier (8) and the 3rd gear (19) are all contained on central shaft (9) by bearing.
4. by double-planet train formula stepless auto gear according to claim 1, it is characterized in that: described first jack shaft (11) is input shaft, second jack shaft (13) is output shaft, and the second jack shaft (13) is contained on machine case (10) by overrunning clutch (15).
5. by double-planet train formula stepless auto gear according to claim 1, it is characterized in that: described first jack shaft (11) is output shaft, second jack shaft (13) is input shaft, and the first jack shaft (11) is contained on machine case (10) by overrunning clutch (15).
6., by double-planet train formula stepless auto gear according to claim 1, it is characterized in that: described in the first row carrier (4) that is fixedly connected be structure as a whole with the second sun gear (5).
7., by double-planet train formula stepless auto gear according to claim 1, it is characterized in that: described in the first gear ring (3) of being fixedly connected be structure as a whole with the second gear ring (7).
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| CN201310499998.XA CN103511568B (en) | 2013-10-22 | 2013-10-22 | Double-planet train formula stepless auto gear |
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| CN201310499998.XA CN103511568B (en) | 2013-10-22 | 2013-10-22 | Double-planet train formula stepless auto gear |
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| CN103511568B true CN103511568B (en) | 2016-03-30 |
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| CN106864258A (en) * | 2017-04-14 | 2017-06-20 | 重庆青山工业有限责任公司 | A kind of bi-motor stepless speed-change automobile dynamical system |
| CN107020944A (en) * | 2017-05-19 | 2017-08-08 | 重庆青山工业有限责任公司 | A kind of variable speed hybrid power automobile power assembly |
| CN107176024A (en) * | 2017-07-03 | 2017-09-19 | 重庆青山工业有限责任公司 | A kind of variable speed hybrid power automobile power assembly |
| CN107199876A (en) * | 2017-07-03 | 2017-09-26 | 重庆青山工业有限责任公司 | A kind of hybrid power automobile power system |
| CN108263197B (en) * | 2017-12-19 | 2020-08-28 | 重庆大学 | Multi-gear power coupling transmission system |
| CN110030340A (en) * | 2019-04-17 | 2019-07-19 | 王世峰 | Centrifugal force automatic transmission |
| CN116464742A (en) * | 2023-01-13 | 2023-07-21 | 王彦 | Self-adaptive stepless speed change mechanism, working condition determining method thereof, motor and drilling device |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2169734Y (en) * | 1993-01-20 | 1994-06-22 | 孙维节 | Stepless speed changing device for motor vehicles |
| CN1280078A (en) * | 1999-07-08 | 2001-01-17 | 现代自动车株式会社 | Gear driving system of automatic driving device |
| CN101487525A (en) * | 2009-02-06 | 2009-07-22 | 付广振 | Self-coupling continuously variable transmission |
| CN203548741U (en) * | 2013-10-22 | 2014-04-16 | 徐攀 | Double-planetary gear train type continuously variable transmission mechanism |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0571601A (en) * | 1991-09-18 | 1993-03-23 | Kawatetsu Techno Res Corp | Reversible stepless speed reducer |
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2013
- 2013-10-22 CN CN201310499998.XA patent/CN103511568B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2169734Y (en) * | 1993-01-20 | 1994-06-22 | 孙维节 | Stepless speed changing device for motor vehicles |
| CN1280078A (en) * | 1999-07-08 | 2001-01-17 | 现代自动车株式会社 | Gear driving system of automatic driving device |
| CN101487525A (en) * | 2009-02-06 | 2009-07-22 | 付广振 | Self-coupling continuously variable transmission |
| CN203548741U (en) * | 2013-10-22 | 2014-04-16 | 徐攀 | Double-planetary gear train type continuously variable transmission mechanism |
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