CN103511568A - Double planetary gear train type stepless automatic speed change mechanism - Google Patents
Double planetary gear train type stepless automatic speed change mechanism Download PDFInfo
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- CN103511568A CN103511568A CN201310499998.XA CN201310499998A CN103511568A CN 103511568 A CN103511568 A CN 103511568A CN 201310499998 A CN201310499998 A CN 201310499998A CN 103511568 A CN103511568 A CN 103511568A
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- gear train
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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
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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
A double planetary gear train type stepless automatic speed change mechanism comprises an input planetary gear train and an output planetary gear train. Two sun gears are installed on a center shaft of a machine shell, input gears or output gears are meshed with the sun gear in the first gear train, the planetary carrier of the second gear train is meshed with the output gears or the input gears, an input shaft is installed on the machine shell, and an output shaft is installed on the machine shell through a one-way clutch. The planetary carrier of the first gear train is fixedly connected with the sun gear of the second gear train, and two gear rings are fixedly connected. According to the double planetary gear train type stepless automatic speed change mechanism, an internal power circulation flow which is only affected by the external torque or the rotation angular speed is established beside a main power circulation flow, the suitable output torque and the suitable rotation angular speed can be acquired by changing the internal circulation flow, the automatic stepless speed change function can be achieved, a hydraulic mechanism is not needed, and the double planetary gear train type stepless automatic speed change mechanism has relatively high economy and wide practicality.
Description
Technical field
The present invention relates to gear, be specifically related to comprise the electrodeless automatic transmission of double-planet train.
Background technique
Gear is a kind ofly at input shaft rotating speed or moment of torsion, constant in the situation that, to make output shaft obtain different rotating speeds or torque transmission device,, by speed change or bending moment, to meet the needs of different operating modes, is widely used in various occasions.
To take automotive field as example, in order meeting starting to walk, accelerate, travel and overcome the needs to driving net tractive force of wheel and the different requirements of the speed of a motor vehicle under the different driving conditions of different kinds of roads obstruction light, speed changer to be housed between motor and ransaxle conventionally.Development along with automotive industry, automotive transmission has experienced 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 class gear is single is step change, but low cost of manufacture, and technique is comparatively ripe; Such as the hydraulic automatic speed variator based on moment speed change (AT), can independently realize electrodeless variable-speed, but mechanism is complicated again, complex process, manufacture cost is high, and some is converted into oil temperature due to the hydraulic couplers energy that in use automobile is exported, 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 realizes electrodeless automatic speed changing based on a pair of V-belt wheel, steel belt and a set of hydraulic pressure and computer micro-controller system, this speed changer is with high content of technology, 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, its current major limitation is used on small-power automobile; The automatic manipulation mechanism of the latter based on traditional speed changer and computer control realized level, automatic speed changing, although its be easy to manufacture and cost low, but its shift property is poor, during gearshift, there is pause and transition in rhythm or melody sense, when low-grade, pause and transition in rhythm or melody sense is especially obvious, and in addition, this speed changer can only be realized step change, and can not realize electrodeless variable-speed, and need to introduce extraneous the intervention.
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 create an internal power circular flow that is only subject to external rotating angular velocity or torque influence outside main power cycle stream, by changing the size of inner loop stream and then obtaining applicable output torque and rotational angular velocity, can realize automatic, electrodeless speed changing function, and save fluid power mechanism of the prior art, there is higher economic relativity.
Technological scheme of the present invention is as follows:
Double-planet train formula stepless auto gear, comprise the first row star wheel series, the second planetary gear train, described the first row star wheel series comprises the first sun gear, the first row star-wheel with the first sun gear outer gearing, with the first gear ring meshing in the first row star-wheel, the first row star-wheel is contained on the first planet carrier by bearing, described the second planetary gear train comprises the second sun gear, the second planet wheel with the second sun gear outer gearing, with the second gear ring meshing in the second planet wheel, the second planet wheel is contained on the second planet carrier by bearing, the first sun gear and the second sun gear are contained on central shaft by bearing, central shaft two ends are contained on machine case by bearing, the first gear on the first jack shaft and the engagement of the first sun gear, the second sun gear is fixedly connected with the first planet carrier, on the second planet carrier, be connected with the 3rd gear, the second gear engagement on the 3rd gear and the second jack shaft, the first jack shaft and the second jack shaft are all contained on machine case rotationally, the 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:
The first gear ring is provided with external tooth with the periphery that is fixedly connected with part described in the second gear ring, drive idler gear with described in be fixedly connected with the engagement of external tooth in part, drive idler gear is contained in installation shaft by sliding bearing, installation shaft is installed on machine case, and drive idler gear is connected or disconnects with described two cover planetary gear train by sliding in installation shaft.
Described the first planet carrier, the second planet carrier and the 3rd gear are all contained on central shaft by bearing.
Described the 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 the 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.
Described the first planet carrier being fixedly connected with and the second sun gear are structure as a whole.
Described the first gear ring 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, can make the first row star-wheel is that wheel for inputting system and the first sun gear are input end, the second planetary gear train is that output wheel train and the second planet carrier are output terminal, also can make the first row star-wheel is that output wheel train and the first sun gear are output terminal, the second planetary gear train is input end for inputting train and the second planet carrier, except the relation of input and output is not identical, all the other annexations are constant, in the embodiment who forms in above-mentioned two kinds of inputs and output annexation, the first planet carrier is fixedly connected with the second sun gear, the 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 an 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, by output planetary train, exported, when described idling mechanism keeps coupled condition with described two cover planetary gear train, whole change acceleration mechanism has two output streams, from output planetary train output with from the output of described idling mechanism.When gear speed change of the present invention, because input power is known constant, at described two cover planetary gear train with the disconnection of described idling mechanism in the situation that, 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 inversely proportional relation.Gear of the present invention is creating on the basis of an internal power circular flow that is only subject to extraneous rotational angular velocity demand or torque influence, according to the demand status of the moment of torsion of gear output terminal or rotational angular velocity, thereby by changing the size of inner loop stream, obtain applicable output torque or output rotational angular velocity, realized thus automatic speed changing function; On the other hand, because gear can meet the demand of various rotating speeds and moment of torsion without the inter-agency connection of change in the situation that, realized thus electrodeless variable-speed function; On output shaft, be provided with overrunning clutch, can guarantee that whole gear outbound course is unique definite.The present invention is than fluid power mechanism of the prior art, can realize equally automatically, under electrodeless speed changing function, save fluid torque converter, than mechanical stepless automatic speed changer of the prior art, without extra hydraulic pressure and computer micro-controller system, can realize automatic control and adjustment, the present invention is for existing speed changer, can realize electrodeless and automatic speed changing truly, and in speed-change process without cutting off power, change inter-agency connection, and speed-change process is without pause and transition in rhythm or melody sense, structure and the making of gear have been simplified, 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 for two kinds of different accelerator drive automobiles and make the schematic diagram that is related to of Automobile drive moment of torsion, automobile running resistance square and automobile driving speed under 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 planet 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
Letter and symbol in the formula now the present invention being adopted are explained as follows.
Pr represents input power, Pc represents output power, and Mr represents input torque, and Wr represents to input rotational angular velocity, Mc represents output torque, Wc represents to export rotational angular velocity, and Mr and Wr be known constant, and Pd represents by the power of described idling mechanism output, moment of torsion in the middle of Mz represents, rotational angular velocity in the middle of Wz represents, free variable in the middle of Mz and Wz are, 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 gear ring rotational 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 the active force of sun gear to planet wheel, F
2for the active force of gear ring to planet wheel, F
3for the active force of planet carrier to planet wheel;
In described input and output planetary train, Wt
1the rotational angular velocity that represents the first sun gear, Wx
1the rotational angular velocity that represents the first planet carrier, Wq
1the rotational angular velocity that represents the first gear ring, Wt
2the rotational angular velocity that represents the second sun gear, Wx
2the rotational angular velocity that represents the second planet carrier, Wq
2the rotational angular velocity that represents the second gear ring, Mt
1the moment of torsion that represents the first sun gear, Mx1 represents the moment of torsion of the first planet carrier, Mq
1the moment of torsion that represents the first gear ring, Mt
2the moment of torsion that represents the second sun gear, Mx
2the moment of torsion that represents the second planet carrier, Mq
2the moment of torsion that represents 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, 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 change greatly and change is large, and Ma represents to accelerate 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 the first row star wheel series, the second planetary gear train, the first row star wheel series comprises the first sun gear 1, the first row star-wheel 2 with the first sun gear 1 outer gearing, the first gear ring 3 with the 2 interior engagements of the first row star-wheel, a plurality of the first row star-wheels 2 are contained on the first planet carrier 4 by bearing, the second planetary gear train comprises the second sun gear 5, the second planet wheel 6 with the second sun gear 5 outer gearings, the second gear ring 7 with the second planet wheel 6 interior engagements, a plurality of the second planet wheels 6 are contained on the second planet carrier 8 by bearing, 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 the first jack shaft 11 and the first sun gear 1 engagement, particularly, increase the axial length of the first sun gear 1, soon the first sun gear 1 is made into and stretches out vertically described line of input star wheel series, make described extension and the first gear 12 engagements, or be axially connected with an intermediate gear with the first sun gear 1, make described intermediate gear and the first gear 12 engagements, the second sun gear 5 is fixedly connected with the first planet carrier 4, preferably, described the first planet carrier 4 being fixedly connected with and the second sun gear 5 are structure as a whole, on the second planet carrier 8, be connected with the 3rd gear 19, the second gear 14 engagements on the 3rd gear 19 and the second jack shaft 13, the first jack shaft 11 and the second jack shaft 13 are all contained on machine case 10 rotationally, and the first planet carrier 4, the second planet carrier 8 and the 3rd gear 19 are all contained on central shaft 9 by bearing, the 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 and the second gear ring 7 that are fixedly connected with described in are preferably structure as a whole.
Further, the working condition requirement of the provisional parking of automobile while rotating in order to meet low engine speed, at the first gear ring 3, be provided with external tooth with the periphery that is fixedly connected with part of the second gear ring 7, drive idler gear 16 with described in be fixedly connected with the engagement of external tooth in part, particularly, also can between the first gear ring 3 and the second gear ring 7, establish an intermediate gear, this intermediate gear and the first gear ring 3, the second gear ring 7 is all affixed, and this intermediate gear and drive idler gear 16 engagements, 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 is connected or disconnects with described two cover planetary gear train by sliding in installation shaft 18, make described idling mechanism and described input, output planetary train connects or disconnects.
In the present invention two cover planetary gear train is 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, two cover planetary gear train all can be used 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, be that the first row star-wheel is that wheel for inputting system and the first sun gear 1 are input end, the second planetary gear train is that output wheel train and the second planet carrier 8 are output terminal, particularly, the first jack shaft 11 is input shaft, the second jack shaft 13 is output shaft, the second jack shaft 13 is contained on machine case 10 by overrunning clutch 15, Fig. 5 is another embodiment of the present invention, be that the first row star-wheel is that output wheel train and the first sun gear 1 are that output terminal, the second output wheel train are that input train and the second planet carrier 8 are input end, particularly, the first jack shaft 11 is output shaft, the second jack shaft 13 is input shaft, and the first jack shaft 11 is contained on machine case 10 by overrunning clutch 15.
With described input, output planetary train and described idling mechanism, disconnect and describing, 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 to be drawn by power conservation law, theoretically, between input power and output power, also there is a gear internal loss power P s, power loss Ps mainly comes from gear shaft with between machine case and inner friction, based on current production technology, this friction factor can be controlled very littlely, and in use, the rotational angular velocity of train can't occur much larger than the situation of input rotational angular velocity, therefore very little by fricative power loss Ps, whether ignored and can't be changed final result, obtain thus above-mentioned 3. formula, in described input, output planetary train and described idling mechanism during in coupled condition, input power some through the output of described idling mechanism, 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, planet wheel and this three of gear ring in single planetary gear train, relation to the rotational angular velocity/moment of torsion of the I/O of two cover planetary gear train of gear of the present invention is carried out mathematical reckoning and obtains, and the process of specifically calculating 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 gearings, with the gear ring 300 of planet wheel 200 interior engagements, it is upper that planet wheel 200 is contained in 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 is to draw based on Principles of Gear Connection (Ji engagement place speed equates), if sun gear 100 sense of rotation are postive direction, planet wheel 200 rotational angular velocities are Wx, take planet wheel 200 as object of reference, sun gear 100 rotational angular velocities are that (Wt-Wx), external toothing 300 rotational angular velocities are (Wq-Wx), according to Principles of Gear Connection, can obtain following 6. formula:
⑥Wq-Wx=-Rt*（Wt-Wx）/Rq
Give k=Rq/Rt, and k > 1, above-mentioned 6. formula can be reduced to above-mentioned 4. formula:
Above-mentioned 5. formula is that planetary gear train draws when state of equilibrium, sees Fig. 3, according to the moment equilibrium condition of planet wheel 200, under different stressing conditions, all has the mathematical relationship of above-mentioned 5. formula, and the concrete process of argumentation is as follows:
1, when the directed force F of 100 pairs of planet wheels 200 of sun gear
1be less than the directed force F of 300 pairs of planet wheels 200 of gear ring
2, will construct one and take B as gyration center, with O
2, A is the system of torque force point of action.
In this system, by O
2the power equivalence of point is transferred to A point has A point suffered with joint efforts: F
2+ F
3/ 2, and B point is suffered, make a concerted effort for F
1, according to planet wheel at the uniform velocity autobiography be that resultant torque is zero, can obtain following relationship:
(F
2+F
3/2)Rx-F
1*Rx=0
Above formula is simplified 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, take B as gyration center, with O
2, A is in the system of torque force point of action, the directed force F of 100 pairs of planet wheels 200 of sun gear
1with Mt opposite direction, the directed force F of 300 pairs of planet wheels 200 of gear ring
2identical with Mq direction, by train, done the equilibrium conditions of uniform rotation, can obtain following four relationships:
F
1=-Mt/Rt
F
2=Mq/Rq
F
3=-Mx/（Rt+Rx）
Rx=（Rq-Rt）/2
According to above-mentioned two relations below, convert and can obtain following II formula:
ⅱ.F
3=-2*Mx/（Rt+Rq）
Bring II formula the conversion of into I formula and can obtain following III formula:
ⅲ.Mt/Rt+Mq/Rq=Mx/（Rt+Rq）
By the above-mentioned III formula of k=Rq/Rt substitution, can obtain above-mentioned 5. formula:
2, when the directed force F of 100 pairs of planet wheels 200 of sun gear
1be greater than the directed force F of 300 pairs of planet wheels 100 of gear ring
2, will construct one and take A as gyration center, with O
2, B is the system of torque force point of action.
In this system, by O
2the power equivalence of point is transferred to B point has B point suffered with joint efforts: F
1+ F
3/ 2, and A point is suffered, make a concerted effort for F
2, according to planet wheel at the uniform velocity autobiography be that resultant torque is zero, can obtain following relationship:
(F
1+F
3/2)Rx-F
2*Rx=0
Above formula is simplified 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, take A as gyration center, with O
2, B is in the system of torque force point of action, the directed force F of 100 pairs of planet wheels 200 of sun gear
1identical with Mt direction, the directed force F of 300 pairs of planet wheels 200 of gear ring
2with Mq opposite direction, by train, done the equilibrium conditions of uniform rotation, can obtain following four relationships:
F
1=Mt/Rt
F
2=-Mq/Rq
F
3=-Mx/（Rt+Rx）
Rx=（Rq-Rt）/2
According to above-mentioned two relations below, convert and can obtain following V formula:
v.F
3=-2*Mx/（Rt+Rq）
Bring v formula the conversion of into iv formula and can obtain following VI formula:
vi.Mt/Rt+Mq/Rq=Mx/（Rt+Rq）
By the above-mentioned VI formula of k=Rq/Rt substitution, can obtain equally above-mentioned 5. formula.
According to the above-mentioned equalising torque analysis about single planetary gear train, known, between each moment for single planetary bevel gear system as shown in Figure 3, there is the basic theory relation of above-mentioned 5. formula.
In the above-mentioned 4. formula of single planetary gear train with 5. on the basis of the basic theory relation of formula, relation to the rotating speed/moment of torsion of the I/O of two cover planetary gear train of Fig. 1 and described gear embodiment illustrated in fig. 2 is calculated, can obtain above-mentioned 1. formula and the 2. conclusion of formula, specifically calculate that process is as follows:
In Fig. 1 and gear embodiment illustrated in fig. 2 the first sun gear 1 for input end (be Wt1=Wr, Mt
1=Mr), the second planet carrier 8 is that output terminal (is Wx
2=Wc, Mx
2=Mc), except there is 4. formula and the 5. mathematical relationship of formula in single planetary gear train, also because the first planet carrier 4 is fixedly connected with the second sun gear 5, therefore the rotational angular velocity of the two and moment of torsion all equate, the first gear ring 3 is fixedly connected with the second gear ring 7, so the rotational angular velocity of these two and moment of torsion all equate.
First, based on rotational angular velocity, utilize above-mentioned 4. formula to analyze reckoning, gear meets following four groups of relations described in this embodiment:
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
By above-mentioned I formula, II formula, III formula, IV formula, integrated to convert and obtain following 7. formula:
⑦Wt
1=(1+k
1+K
2+k
1k
2)Wx
2-（k
2+k
1k
2+k
1）Wq
1
After all coefficients in above-mentioned 7. formula are integrated by coefficient a
1, b
1represent Wq
1with middle moment of torsion Wz, represent Wt
1for input rotational angular velocity Wr, Wx
2for output rotational angular velocity Wc, above-mentioned 7. formula is above-mentioned 2. formula:
②Wr=a
1Wc+b
1Wz
Secondly, based on moment of torsion, utilize above-mentioned 5. formula to analyze reckoning, 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
By above-mentioned I formula, II formula, III formula, IV formula, integrated to convert and obtain following 8. formula:
⑧(1+k
1)Mt
1=Mx
2/(1+k
2)-(1+1/k
1+1/k
2)Mq
1
After being integrated, all coefficients in above-mentioned 8. formula represented Mq by coefficient a, b
1with middle moment of torsion Mz, represent Mt
1for input rotational angular velocity Mr, Mx
2for output rotational angular velocity Mc, above-mentioned 8. formula is above-mentioned 1. formula:
①Mr=aMc+bMz
Because the gear ratio of the first gear ring 3 and 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 equating with radius ratio according to gear ratio in gear train assembly, k
1and k
2value be all greater than 1, therefore, coefficient a, b, a after above-mentioned 7. formula and 8. formula are integrated
1, b
1all non-vanishing.
The above-mentioned 1. formula that Fig. 1 and gear embodiment illustrated in fig. 2 meet, 2. formula, 3. in three relationships of formula, because Wr, Mr are known constant, Wz, Mz are middle free variable, when determining that Wc or Mc are wherein during the value of arbitrary, for above-mentioned 1. formula, 2. formula, value that 3. formula all can search out unique definite Wz, a Mz and Mc or Wc are set up this three relationships, be that gear dependence output terminal rotational angular velocity/moment of torsion of the present invention is correspondingly adjusted output torque/rotational angular velocity automatically, realized 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 the first row star-wheel is that wheel for inputting system and the first sun gear 1 are input end, the second planetary gear train is that output wheel train and the second planet carrier 8 are output terminal, the second sun gear 5 is fixedly connected with the first planet 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 an internal power circular flow 500 that affected by extraneous rotational angular velocity Wc demand or moment of torsion Mc.Straight line with arrow in Fig. 2 and Fig. 5 is power Liu path, the train of mechanism of internal power circular flow 500 in sealing, whole gear is when being subject to ectocine, when Mc or Wc change, can automatically regulate internal power stream 500, by changing 7. formula and the 8. middle free variable Wq of formula
1and Mq
1and then change output rotational angular velocity or output torque, with this, realize automatic speed changing function.Gear of the present invention is creating on the basis of internal power circular flow 500, according to the demand status of the moment of torsion of gear output terminal or rotational angular velocity, thereby by changing the size of inner loop stream 500, obtain applicable output torque or output rotational angular velocity, realized automatic speed changing function; On the other hand, because gear can meet the demand of various rotating speeds and moment of torsion without the inter-agency connection of change in the situation that, realized electrodeless variable-speed function.
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 the first row star-wheel is that output wheel train and the first sun gear 1 are output terminal, the second planetary gear train is input end for inputting train and the second planet carrier 8, the second sun gear 5 is fixedly connected with the first planet carrier 4, and the gear ring in two cover planetary gear train is fixedly connected with, compare with the embodiment shown in Fig. 2, except input and the relation of exporting change, other annexations are constant, this embodiment forms an internal power circular flow 500 that is only subject to extraneous rotational angular velocity demand or torque influence equally between two cover planetary gear train, and internal power circular flow 500 has a style of one's own, by the flow through size of internal power stream of described bending moment mechanism of change, realize variable-speed torque-converting, 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 be 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 has determined 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 has determined automobile driving speed Wn, in like manner, according to above-mentioned 1. formula, 2. formula, 3. formula, can draw following four relations:
V.Mf=jMn+pMz
VI.Wf=sWn+tWz
Described in VII.Mf*Wf=Mn*Wn(, idling mechanism and described two cover planetary gear train remain open)
Described in VIII.Mf*Wf=Mn*Wn+Pd(, idling mechanism keeps being connected with described two cover planetary gear train)
Automobile have in the process of moving parking, speed change, at the uniform velocity, these several states of moveing backward, car-backing function comparatively improves and is ripe, in the condition of advancing, add tumbler gear, at this, be not discussed, therefore, automobile variable speed mechanism needs to meet the working condition requirement under above-mentioned different conditions, is described as follows:
1. parking state, now comprises again that engine stop and low engine speed rotate two states:
Engine stop: i.e. automobile flameout, therefore Wf=0 is zero by the known car speed Wn of the VII formula of deriving above;
Low engine speed is rotated: i.e. the provisional parking of automobile, input power is non-vanishing, now by idling mechanism described in manual control and described two, overlap planetary gear train in coupled condition, 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 the critical resistance square when travelling, automobile driving speed Wn is zero, above-mentioned VIII formula and 2. formula change respectively following relationship into
IX.Pd=Mf*Wf
X.Wr=b
1Wz
Now, auto idle speed, and above-mentioned 1. formula, 2. formula, 3. formula is still set up.
2, speed change state (automobile accelerates, slows down):
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 is along with automobile driving speed becomes large and becomes large.
Work as Mn > Mu, automobile accelerates, and automobile driving speed Wn increases, according to above-mentioned VII formula, Automobile drive moment of torsion Mn diminishes, and running resistance square Mu is along with Wn increases, until reach balance, Automobile drive moment of torsion Mn equals running resistance square Mu, and speed changer is realized and accelerated function;
Otherwise as Mn < Mu, Wn reduces, Mn increases, and Mu is along with Wn reduces, until reach balance, Automobile drive moment of torsion Mn equals running resistance square, and speed changer is realized deceleration.
Whole process is all carried out under firm power as mentioned above, without the external world, controls, and speed-change process is that whole change procedure gear does not change the situation of inter-agency connection, can realize stepless change automatically.
3, travelling state at the uniform velocity:
See Fig. 4, when automobile is driven with less throttle, automobile can be with a less speed Wn after accelerating
1at the uniform velocity travel, if now open the throttle, be that input power becomes greatly, according to above-mentioned VII formula, it is large that Automobile drive moment of torsion Mn can become immediately, this will cause Mn to be greater than running resistance square Mu, automobile accelerates thus, and automobile driving speed Wn can increase, and driving moment Mn diminishes, thereby running resistance square Mu increases, equate to reach balance with car driving torque Mn, now automobile driving speed is Wn
2, and Wn
2be greater than Wn
1, automobile can be with a larger speed Wn after accelerating
2at the uniform velocity travel.Hence one can see that, and driver can control the speed that automobile at the uniform velocity travels by throttle (input power).
More than describing is explanation of the invention, is not the restriction to invention, and limited range of the present invention, referring to claim, within protection scope of the present invention, can be done any type of modification.
Claims (7)
1. double-planet train formula stepless auto gear, comprise the first row star wheel series, the second planetary gear train, described the first row star wheel series comprises the first sun gear (1), the first row star-wheel (2) with the first sun gear (1) outer gearing, the first gear ring (3) with the first row star-wheel (2) outer gearing, the first row star-wheel (2) is contained on the first planet carrier (4) by bearing, described the second planetary gear train comprises the second sun gear (5), the second planet wheel (6) with the second sun gear (5) outer gearing, the second gear ring (7) with the second planet wheel (6) outer gearing, the 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 the first jack shaft (11) and the first sun gear (1) engagement, the second sun gear (5) is fixedly connected with the first planet carrier (4), on the second planet carrier (8), be connected with the 3rd gear (19), the 3rd gear (19) meshes with the second gear (14) on the second jack shaft (13), the first jack shaft (11) and the second jack shaft (13) are all contained on machine case (10) rotationally, the first gear ring (3) is fixedly connected with the second gear ring (7), and the first gear ring (3) is contained on machine case (10) by bearing with the second gear ring (7).
2. by double-planet train formula stepless auto gear claimed in claim 1, it is characterized in that: the first gear ring (3) is provided with external tooth with the periphery that is fixedly connected with part described in the second gear ring (7), drive idler gear (16) with described in be fixedly connected with the engagement of external tooth in part, drive idler gear (16) is contained in installation shaft (18) by sliding bearing (17), it is upper that installation shaft (18) is installed on machine case (10), and drive idler gear (16) is by being connected or disconnecting with described two cover planetary gear train upper slip of installation shaft (18).
3. by double-planet train formula stepless auto gear claimed in claim 1, it is characterized in that: described the first planet 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 claimed in claim 1, it is characterized in that: described the first jack shaft (11) is input shaft, the 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 claimed in claim 1, it is characterized in that: described the first jack shaft (11) is output shaft, the 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 claimed in claim 1, it is characterized in that: described in the first planet carrier (4) of being fixedly connected be structure as a whole with the second sun gear (5).
7. by double-planet train formula stepless auto gear claimed in 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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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN108263197A (en) * | 2017-12-19 | 2018-07-10 | 重庆大学 | A kind of more gear power coupling transmission systems |
| 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 |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0571601A (en) * | 1991-09-18 | 1993-03-23 | Kawatetsu Techno Res Corp | Reversible stepless speed reducer |
| 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 |
-
2013
- 2013-10-22 CN CN201310499998.XA patent/CN103511568B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0571601A (en) * | 1991-09-18 | 1993-03-23 | Kawatetsu Techno Res Corp | Reversible stepless speed reducer |
| 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 |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN108263197A (en) * | 2017-12-19 | 2018-07-10 | 重庆大学 | A kind of more gear power coupling transmission systems |
| 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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| CN103511568B (en) | 2016-03-30 |
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