CN203548742U - Double-planet wheel system stepless automatic speed change mechanism - Google Patents
Double-planet wheel system stepless automatic speed change mechanism Download PDFInfo
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- CN203548742U CN203548742U CN201320654166.6U CN201320654166U CN203548742U CN 203548742 U CN203548742 U CN 203548742U CN 201320654166 U CN201320654166 U CN 201320654166U CN 203548742 U CN203548742 U CN 203548742U
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Abstract
A double-planet wheel system stepless automatic speed change mechanism comprises an input planet wheel system and an output planet wheel system each of which comprises a sun wheel, a planet wheel, a gear ring and a planet frame; the two sun wheels are arranged on a central shaft arranged on a machine shell; an input gear is meshed with a gear on the planet frame of the input planet wheel system; a gear on the planet frame of the output planet wheel system is meshed with an output gear; an input shaft is arranged on the machine shell; an output shaft is arranged on the machine shell by a one-way clutch; the two sun wheels are fixedly connected; the two gear rings are fixedly connected; the gear ratios of the gear rings to the sun wheels in the two planet wheel systems are different. An internal power circulation flow only influenced by an external rotary angle speed or torque is established outside a main power circulation flow, a proper output torque and a proper rotary angle speed are obtained by changing the size of the internal power circulation flow, and the double-planet wheel system stepless automatic speed change mechanism can realize automatic and stepless speed change functions without a hydraulic mechanism and has higher economic relativity and wider practicability.
Description
Technical field
The utility model relates to gear, is 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.
Take automotive field as example, in order to meet 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 is housed between motor and ransaxle conventionally.Along with the development of automotive industry, automotive transmission experienced non-automatic gear to automatic transmission, from have 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; Again such as the hydraulic automatic speed variator based on moment speed change (AT), can independently realize electrodeless variable-speed, but mechanism's complexity, complex process, manufacture cost is high, and due to the hydraulic couplers energy that in use automobile is exported, some is 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 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.
Model utility content
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 variable-speed function, and without fluid power mechanism, there is higher economic relativity and wider practicability.
The technical solution of the utility model is as follows:
Double-planet train formula stepless auto gear, comprise line of input star wheel series, output planetary train, described line of input 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 engaging in the first row star-wheel, the first row star-wheel is contained on the first planet carrier by bearing, described output planetary train comprises the second sun gear, the second planet wheel with the second sun gear outer gearing, with the second gear ring engaging 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 planet carrier is connected with the first gear, the second planet carrier is connected with the second gear, input gear on input shaft engages with the first gear, output gear on output shaft engages with the second gear, input shaft is contained on machine case by bearing, output shaft is contained on machine case by overrunning clutch, the first sun gear is fixedly connected with the second sun gear, 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, and the gear ratio of the gear ratio of the first gear ring and the first sun gear and the second gear ring and the second sun gear is unequal.
Its further technological scheme is:
The first gear ring with described in the second gear ring, be fixedly connected with part and be provided with external tooth, drive idler gear with described in the external tooth that is fixedly connected with in part engage, 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 and the first gear, the second planet carrier and the second gear are all contained on central shaft by bearing.
Technique effect of the present utility model:
The utility model is used input and output totally two cover planetary gear train, the first planet carrier in wherein said line of input star wheel series is input end, the second planet carrier in described output planetary train is output terminal, sun gear in two cover planetary gear train is fixedly connected with, and the gear ring in two cover planetary gear train is fixedly connected with, 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 rotational angular velocity 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 described in the utility model, 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, i.e. inversely proportional relation of the moment of torsion of output planetary train output terminal and rotational angular velocity.Gear described in the utility model is only subject to one of establishment on the basis of internal power circular flow of 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 is without changing the demand that can meet various rotating speeds and moment of torsion inter-agency connection 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 utility model 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 utility model is for existing speed changer, can realize electrodeless and automatic speed changing truly, and in speed-change process without cut 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 utility model.
Fig. 2 is theory structure schematic diagram of the present utility model.
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 makes 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.
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, input shaft; 12, input gear; 13, output shaft; 14, output gear; 15, overrunning clutch; 16, drive idler gear; 17, sliding bearing; 18, installation shaft; 19, the first gear; 20, the second gear; 100, sun gear; 200, planet wheel; 300, gear ring; 400, main power cycle stream; 500, internal power circular flow.
Embodiment
Letter and symbol in the formula now the utility model 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
1represent the rotational angular velocity of the first sun gear, Wx
1represent the rotational angular velocity of the first planet 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,
represent the moment of torsion of the first sun gear,
represent the moment of torsion of the first planet carrier,
represent the moment of torsion of the first gear ring,
represent the moment of torsion of the second sun gear,
represent the moment of torsion of the second planet carrier,
represent 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, and k
1≠ k
2, 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, embodiment of the present utility model is described.
See Fig. 1, the utility model comprises line of input star wheel series, output planetary train, described line of input star wheel series comprises the first sun gear 1, the first row star-wheel 2 engaging with the first sun gear 1, the first gear ring 3 engaging with the first row star-wheel 2, multiple the first row star-wheels 2 are contained on the first planet carrier 4 by bearing, described output planetary train comprises the second sun gear 5, the second planet wheel 6 engaging with the second sun gear 5, the second gear ring 7 engaging with the second planet wheel 6, multiple 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 planet carrier 4 is connected with the first gear 19, the second planet carrier 8 is connected with the second gear 20, the first planet carrier 4 and the first gear 19, the second planet carrier 8 and the second gear 20 are preferably made as integrative-structure, input gear 12 on input shaft 11 engages with the first gear 19, output gear 14 on output shaft 13 engages with the second gear 20, input shaft 11 is contained on machine case 10 by bearing, output shaft 13 is contained on machine case 10 by overrunning clutch 15, the first planet carrier 4 and the first gear 19, the second planet carrier 8 and the second gear 20 are all contained on central shaft 9 by bearing, the first sun gear 1 is fixedly connected with the second sun gear 5, the first gear ring 3 is fixedly connected with the second gear ring 7, the first gear ring 3 and the second gear ring 7 are contained on machine case 10 by bearing, the gear ratio of the gear ratio of the first gear ring 3 and the first sun gear 1 and the second gear ring 7 and the second sun gear 5 is unequal, wherein, the first gear ring 3 and the second gear ring 7, the second sun gear 5 and the first sun gear 1 are preferably made into integrative-structure.
Further, the working condition requirement of the provisional parking of automobile while rotating in order to meet low engine speed, being fixedly connected with of the first gear ring 3 and the second gear ring 7, in part, be provided with external tooth, drive idler gear 16 with described in the external tooth that is fixedly connected with in part engage, 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 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 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.
With described input, output planetary train and described idling mechanism, disconnect and describing, gear described in the utility model 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, the relation of the rotational angular velocity/moment of torsion of the I/O of the two cover planetary gear train to gear described in the utility model 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, comprises sun gear 100, the planet wheel 200 with sun gear 100 outer gearings, and with the interior gear ring engaging 300 of planet wheel 200, 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 (equating in engagement place speed), 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 sun gear 100 to planet wheel 200
1be less than the directed force F of gear ring 300 to planet wheel 200
2, will construct one 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 sun gear 100 to planet wheel 200
1with Mt opposite direction, the directed force F of gear ring 300 to planet wheel 200
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 above-mentioned k=Rq/Rt substitution III formula, can obtain above-mentioned 5. formula:
2, when the directed force F of sun gear 100 to planet wheel 200
1be greater than the directed force F of gear ring 300 to planet wheel 100
2, will construct one 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 sun gear 100 to planet wheel 200
1identical with Mt direction, the directed force F of gear ring 300 to planet wheel 200
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 above-mentioned k=Rq/Rt substitution VI formula, can obtain equally above-mentioned 5. formula.
According to the above-mentioned equalising torque analysis about single planetary gear train, known, between the 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, the relation of the rotational angular velocity/moment of torsion of the I/O of the two cover planetary gear train to gear described in the utility model is calculated, can obtain above-mentioned 1. formula and the 2. conclusion of formula, specifically calculate that process is as follows:
In gear described in the utility model, the first planet carrier 4 is that input end (is Wx
1=Wr, Mx
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 sun gear 1 is fixedly connected with the second sun gear 5, therefore the rotating speed of the two and moment of torsion all equate, the first gear ring 3 is fixedly connected with the second gear ring 7, and therefore 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 described in the utility model 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.Wt
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:
⑦(1+k
1)Wx
1=(1+k
2)Wx
2+（k
1-k
2）Wq
2
After all coefficients in above-mentioned 7. formula are integrated by coefficient a
1, b
1represent Wq
2represent Wx with middle moment of torsion Wz
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 described in the utility model meets following four groups of relations:
Ⅰ.Mt
1+Mq
1/k
1=Mx
1/(1+k
1)
Ⅱ.Mt
2+Mq
2/k
2=Mx
2/(1+k
2)
Ⅲ.Mt
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:
⑧Mx
1/(1+k
1)=Mx
2/(1+k
2)+(1/k
2-1/k
1)Mq
2
After being integrated, all coefficients in above-mentioned 8. formula represented Mq by coefficient a, b
2represent Mx with middle moment of torsion Mz
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
Due to 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 unequal, the relation equating with radius ratio according to gear ratio in gear train assembly, k
1be not equal to k
2, and the two is all greater than 1, therefore, and coefficient a, b, a after above-mentioned 7. formula and 8. formula are integrated
1, b
1all non-vanishing.
Above-mentioned 1. formula that the utility model meets, 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 described in the utility model is correspondingly adjusted output torque/rotational angular velocity automatically, realized automatic speed changing function.
Fig. 2 is theory structure schematic diagram of the present utility model, the utility model is used input and output totally two cover planetary gear train, the first planet carrier 4 in wherein said line of input star wheel series is input end, the second planet carrier 8 in described output planetary train is output terminal, sun gear in two cover planetary gear train is fixedly connected with, 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 is the path of power stream, 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
2and Mq
2and then change output rotational angular velocity or output torque, with this, realize automatic speed changing function.Gear described in the utility model 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 is without changing the demand that can meet various rotating speeds and moment of torsion inter-agency connection in the situation that, realized electrodeless variable-speed function.
For automotive transmission, gear input torque Mr depends on the converter torque ratio of Engine torque Mf and gear, gearbox output torque Mc 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 engine stop and low engine speed rotation two states:
Engine stop: i.e. automobile flameout, therefore Wf=0, by the VII formula of deriving above, known car speed Wn is zero;
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 described above is all carried out under firm power, 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 at the uniform velocity travel with a larger speed Wn2 after accelerating.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 to explanation of the present utility model, is not the restriction to model utility, and the utility model limited range, referring to claim, within protection domain of the present utility model, can be done any type of modification.
Claims (5)
1. double-planet train formula stepless auto gear, comprise line of input star wheel series, output planetary train, described line of input star wheel series comprises the first sun gear (1), the first row star-wheel (2) with the first sun gear (1) outer gearing, with the first gear ring (3) engaging in the first row star-wheel (2), the first row star-wheel (2) is contained on the first planet carrier (4) by bearing, described output planetary train comprises the second sun gear (5), the second planet wheel (6) with the second sun gear (5) outer gearing, with the second gear ring (7) engaging in the second planet wheel (6), 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 planet carrier (4) is connected with the first gear (19), the second planet carrier (8) is connected with the second gear (20), input gear (12) on input shaft (11) engages with the first gear (19), output gear (14) on output shaft (13) engages with the second gear (20), input shaft (11) is contained on machine case (10) by bearing, output shaft (13) is contained on machine case (10) by overrunning clutch (15), the first sun gear (1) is fixedly connected with the second sun gear (5), the first gear ring (3) is fixedly connected with the second gear ring (7), the first gear ring (3) is contained in machine case (10) above with the second gear ring (7) by bearing, and the first gear ring (3) is unequal with the gear ratio of the second sun gear (5) with gear ratio and second gear ring (7) of the first sun gear (1).
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 the external tooth that is fixedly connected with in part engage, 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) and the first gear (19), the second planet carrier (8) and the second gear (20) 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 in the first sun gear (1) of being fixedly connected be structure as a whole with the second sun gear (5).
5. 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).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320654166.6U CN203548742U (en) | 2013-10-22 | 2013-10-22 | Double-planet wheel system stepless automatic speed change mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320654166.6U CN203548742U (en) | 2013-10-22 | 2013-10-22 | Double-planet wheel system stepless automatic speed change mechanism |
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| Publication Number | Publication Date |
|---|---|
| CN203548742U true CN203548742U (en) | 2014-04-16 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320654166.6U Expired - Fee Related CN203548742U (en) | 2013-10-22 | 2013-10-22 | Double-planet wheel system stepless automatic speed change mechanism |
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| CN (1) | CN203548742U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103511562A (en) * | 2013-10-22 | 2014-01-15 | 徐攀 | Double planetary gear train type stepless automatic speed change mechanism |
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2013
- 2013-10-22 CN CN201320654166.6U patent/CN203548742U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103511562A (en) * | 2013-10-22 | 2014-01-15 | 徐攀 | Double planetary gear train type stepless automatic speed change mechanism |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140416 Termination date: 20151022 |
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| EXPY | Termination of patent right or utility model |