CN85108083A - Two differential speed gears inertia stepless moment variator - Google Patents
Two differential speed gears inertia stepless moment variator Download PDFInfo
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- CN85108083A CN85108083A CN 85108083 CN85108083A CN85108083A CN 85108083 A CN85108083 A CN 85108083A CN 85108083 CN85108083 CN 85108083 CN 85108083 A CN85108083 A CN 85108083A CN 85108083 A CN85108083 A CN 85108083A
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Abstract
Two differential speed gears inertia stepless moment variator is made up of two groups of differential speed gears.The central gear of these two groups of differential speed gears is constrained each other, and makes and wherein have the transmission of a pair of one-tenth gear ratio at least.The planet carrier of one differential speed gears is made input shaft, and the planet carrier of another differential speed gears is made output shaft.Because certain equation of motion is satisfied in the motion of each gear, can make the input shaft rotational speed of this coupled system.The time and definite fully by output shaft, Shi Erneng arbitrarily improves under action of prime mover, thereby produces the effect that stepless inertia increases square.This torque-converters can be used as the usefulness of the speed changer of automotive machinery, replaces traditional clutch speed-changer.
Description
The present invention relates to a kind of inertia pulsation step-less moment variator, it can be used as the usefulness of the clutch speed-changer of automobile and tractor class machinery.
The inertia stepless torque converter is seen the various ways that has of work report, no matter the sort of form, all has in the following shortcoming one or several.1. have 1 or several free wheel devicees; 2. have one or several flywheels; 3. pulsation is uneven; 4. can not reverse transmission; 5. the sound is big, and transmission efficiency is low, and working life is short; 6. overall weight and size are big, or the like.Therefore in the automobile of producing in batches, also do not adopt inertia pulsation step-less moment variator.
The objective of the invention is to make a kind of inertia stepless moment variator of novelty, make it have good performance, to replace traditional automobile clutch transmission system mechanically using of automotive-type.
Realization of the present invention: this contrivance is made up of two groups of differential gear systems, and each group differential speed gears has a planet carrier, two central gears.With driving mechanism wheel in each of a differential speed gears all is tied with a central gear of another differential speed gears.Form two pairs of corresponding central gears like this, make the angle position of every pair of central gear only represent with a coordinate.And it is transient change that these two pairs of central gears have a pair of transmission speed ratio at least, and this speed ratio satisfies certain relation.Two differential mechanisms of Zu Chenging like this, the planet carrier of its differential mechanism as input shaft, the planet carrier of another differential mechanism as output shaft.Device from the above mentioned, its input shaft, output shaft, each planetary pinion, the motion of each central gear is binary, but because aforesaid a pair of central gear is arranged is to meet the gear ratio transmission of certain rule referring to Fig. 1.This makes that input shaft and freedom of movement output shaft are one sometimes, is two sometimes.Be input shaft rotational speed sometimes be output the axle rotating speed determine, sometimes under action of prime mover arbitrarily the raising.See hereinafter formula (6).Input shaft rotational speed continuously is such variation like this: be elevated to high rotating speed arbitrarily from a certain with the output shaft corresponding rotating speeds, drop to again and the output shaft corresponding rotating speeds, be elevated to high rotating speed arbitrarily again, drop to again and the output shaft corresponding rotating speeds ...This process constantly goes on, and the rising constantly of this input shaft rotational speed reduces the inertial force that produces and makes mechanism produce the effect of stepless torque changing.Said and output shaft corresponding rotating speeds promptly are the rotating speeds that input shaft is determined by output shaft when the motion of input shaft and output shaft has only one degree of freedom in this section sentence; Arbitrarily high rotating speed is meant, when the motion of input shaft and output shaft was two degrees of freedom, input shaft quickened the rotating speed that obtains under the dynamic action of prime mover.
Good effect of the present invention is the stepless torque converter that has produced a kind of novelty, and steam supply car tractor class machinery is selected for use.
Embodiments of the invention:
Fig. 1 is a schematic diagram of mechanism of the present invention.
8 is that planet carrier and input shaft 6 are fixed, and 9 is that planet carrier and output shaft 10 are fixed.2 is central gear, fixed with gear 1, and they can rotate on axle 6.The 14th, central gear is consolidated with gear 15, can rotate on axle 10.The 4th, central gear, fixed with non-garden gear 5, can on axle 6, rotate.The 12nd, central gear, 11 right and wrong garden gears, they are fixed mutually, can rotate on axle 10.3, the 13rd, belong to the planetary pinion of two differential speed gears.This device divides differential mechanism I and differential mechanism II two-part.An inertia stepless moment variator is formed in the motion restriction of this two-part differential mechanism by central gear.This restriction of Fig. 1 is like this: gear 1 and gear 15 engagements, gear ratio can be decided to be 3: 2.Non-garden gear 5 and 11 engagements of non-garden gear; Non-garden gear 5 turns around, and non-garden gear 11 also turns around, and their instantaneous speed ratio is the function of a non-garden gear corner.
Below use R
iSequence number is the joint garden radius of the gear of i among presentation graphs 1 and Fig. 2 Fig. 3; Use n
iSequence number is the rotating speed with respect to support of 1 member among presentation graphs 1 and Fig. 2, Fig. 3.Can list equation of motion by the characteristics of differential mechanism I among Fig. 1
1/2 (n
+ n4)=and ns, can be changed into n
+ n
=2ns (1)
In like manner, can list equation of motion by the characteristics of differential II
n
+n11＝2n10 （2）
Because of R1=3/2 R15 gets n15=3/2 n1 (3)
The speed ratio of 11 and 5 liang of non-garden gears is
i（ψ）＝ (n1)/(n5) （4）
Wherein ψ is the corner of gear 5, i(ψ) for ψ be the continuous function in cycle with 2 π, can make i(ψ) span be
3/2 ≥i（ψ）≥ 1/2
Get n11=i(ψ by (4)) n
Following formula and (3) formula substitution (2) formula are got
3/2 n1+i（ψ）n
＝2n10 （5）
Take advantage of (1) formula both sides-3/2 to be added to after (5) formula
3n6-2n10＝〔 3/2 -1（ψ）〕n9 （6）
Analysis equation (6) now.
N6 is the rotating speed of input shaft 6, and n10 is output shaft 10 rotating speeds, and n9 is the rotating speed of central gear 5.Central gear 5 turns around, promptly during 2 π radians, and i(ψ) to get all values all over closed interval (3/2,1/2).
When the rotation speed n 10 of output shaft 10 is determined by working machine (n10 has just determined when the speed of a motor vehicle is determined concerning automobile), input shaft 6 is binary with the motion of central gear 5.The characteristics of motion of binary system can be determined by kinetic equations.Equation (6) has characteristics, as central gear 5 i(ψ ' when a certain angle position is ψ=ψ ')=2/2, by (6) formula, n
Just determined by n10 fully, at this moment n
Has only one degree of freedom with n10, i.e. ns=2/3 n
Central gear 5 is constantly to rotate, when corner ψ is ψ ', ψ '+2x, and ψ '+4 π ... the time, n6=2/3 n
; When corner ψ is ψ ", ψ
+ 2 π, ψ
+ 4 π ..., and 1(ψ
) ≠ 3/2 o'clock, the rotating speed of input shaft 6 is determined by the dynamics of this mechanism, is another rotating speed that is different from 2/3 n10.The rotating speed of input shaft 6, (this time is 1/ (n1)) changes rapidly at short notice, and the scope of this variation is determined by the dynamic property of this train of gearings, this inertia stepless of just having realized this mechanism becomes torsion effect.
By above explanation and Fig. 1 as can be seen, input shaft 6, output shaft 10, the mean speed of central gear 5
There is relation
This mean speed is that gear 5 changes the mean value of integer circle in the used time lag.
The explanation of (6 ') formula is for identical
Big more then speed ratio is also big more.
The key that device as shown in Figure 1 can play the effect of inertia bending moment is: 1. the ratio of input shaft and the mean speed of output shaft is that rotating speed with this central gear changes in a central gear changes time lag of integer circle; 2. when the heart was taken turns a certain angle position hereinto, input shaft rotational speed was determined by output shaft just can become an inertia stepless moment variator if the combination of two groups of differential mechanisms can be satisfied this 2 requirements fully.
The schematic diagram of mechanism of Fig. 1 is changed, and the gear ratio transmission that central gear 4,12 is produced by non-garden gear 5,11 becomes by crank shown in Figure 2, whitworth mechanism (being designated hereinafter simply as crankrocker mechanism) and realizes.
It is identical with the member of same sequence number among Fig. 1 that sequence number among Fig. 2 is 4,6,10,12 member.Central gear 4 and 12 transmission restriction realize by crank rocker.Crank 19,16 is cemented in respectively on the central gear 12,4 of oneself, its crank Xiao is respectively at rocking bar 20, with slide in 21 the groove, rocking bar 20 and 21 is on a rigid body, the center of rotation of this rigid body is 18, this center of rotation can change the position by Effector, to change function i(ψ in (6) formula) character, thereby the performance of torque-converters is improved.A, B are respectively the centers of rotation of crank 16 and 19 among Fig. 2, just central gear 4 and 12 center of rotation.
Fig. 3 is another embodiment.
Its feature is that two planet carriers are arranged point-blank.
Include the II differential mechanism among Fig. 3 in the double dot dash line, double dot dash line includes the IV differential mechanism outward.Sequence number be 3,6,7,8,9,10 member with among Fig. 1 with the member of sequence number.The 23rd, planet carrier and 9, the 10th, one.The 24th, central gear is consolidated with central gear 22, can rotate with respect to support 7 and input shaft 6; Central gear 27 is fixed with central gear 28, and they can rotate with respect to support 7 and axle 6, and central gear 27 and 28 gear ratio transmission can realize by crank rocker.This crankrocker mechanism can be done following variation referring to Fig. 2; 20 of Fig. 2,21 the angle that interlaces becomes about 180 °: the A among Fig. 2, B are overlapped to a bit, center 18 and its skew, 18 side-play amount still can be by the Effector adjustment, crank 16,19 fixed respectively the central gear 27,28 among Fig. 3.Central gear 27 and 28 makes it to reach requirement by after such transmission: central gear 27 turns around, 28 also turn around, but its instantaneous speed ratio changes, and variation must have certain scope, and this scope also can change among Fig. 2 18 skew by Effector and makes it to change.The planet wheel of differential mechanism IV has two cover teeth 25 and 26, and the central gear 22 and 28 with IV meshes respectively.
Ask motion of mechanism relation shown in Figure 3 now.Symbol is with above same.
Have from the differential mechanism IV:
(n22-n23)/(n26-n23) ＝- (R23×R22)/(R22×R26) （7）
Fig. 3 has proportionate relationship R
: R26=1: 0.5
R23∶R22＝1∶0.8
Substitution (7) formula gets (n22-n23)/(n28-n23)=-8/5
Be exactly n
+ 8/5 n23=13/5 n10 (8)
From III n is arranged
+ n27=2n6 (9)
Because n23=i(ψ) n27 (10)
Substitution (8) gets n2+ 8/5 i(ψ) n
=13/5 n10 (11)
(9)-(11) And transplant 2n6-13/5 n10=(1-8/5 i(ψ)) n27 (12)
Formula (12) is quite analogous to formula (6).Therefore as long as selected i(ψ) make it to meet some requirements the effect that the mechanism of Fig. 3 just can product product inertia bending moment.The i(ψ here) is the instantaneous speed ratio of central gear 28 and 27.
Again for an embodiment:
Fig. 1, and mechanism shown in Figure 3, a pair of central gear is a fixed speed ratio, another is the speed ratio of transient change to central gear.It all is the transient change speed ratio that this embodiment makes two pairs of central gears by mechanism.Wall such as this two pairs of central gears all pass through as Fig. 2, or the crankrocker mechanism that the mechanism of Fig. 2 does some variation is realized instantaneous gear ratio transmission.And the rocking bar central position is adjustable, constantly each is adjusted the speed ratio rule of central gear by automatic pilot, and inertia stepless bending moment characteristic is improved.Here to emphasize a bit: make a pair of central gear not change, when another each central gear to central gear changes the integer circle, the mean speed speed ratio of input shaft and output shaft is different from, make another that central gear is not changeed, the speed ratio of the input shaft when this each central gear to central gear changes the integer circle and the mean speed of output shaft.This can reach by design.
To above all literal, the accompanying drawing of formula and indication remakes following some explanation:
1. a pair of central gear that the gear ratio drive connection is arranged of this invention might not rotate, but this not rotate be unsettled, as the structure of Fig. 2, as long as change the position at center 18, this will rotate central gear.
2. input shaft rotational speed just changes frequently, prime mover can be by an elastic axis and input shaft binding.This can make the rotation speed change of prime mover small, and rotating speed equals the mean speed of input shaft.
3. this torque-converters partial component can be made into and has certain elasticity, makes this torque-converters each moving element when unidirectional delivery power that the impact that causes because of matching gap not take place, and makes dynamic property good.As the gear among Fig. 11 binding with gear 2, similarly, 4 with 5,15 with 14,12 and 11 and Fig. 3 in 22 and 24, reach their the fixed binding that can be made into the energy elastic torsion of 4 and 16,12 and 19 among Fig. 2 or the like.The effect of this elastic torsion can make the kinematic relation of (6) formula destroy, but still in full force and effect as bending moment.
4. mechanism as shown in Figure 3 can make step change and inertia stepless speed change unite use.Gear 28 and 27 constraint can make gear 28 and 27 with the speed rotation by operating device by the operating device adjustment.Coupled system like this can produce three fixing speed ratios as the mechanism of Fig. 3.
1) make gear 25 fixing with planet carrier 23.
2) gear 22 is fixed with support.
3) gear 26 is fixed with support.
Can improve the using scope of this torque converter like this.
5. input shaft of the present invention and output shaft are the planet carriers of two different differential mechanisms.When the reverse transmission of power, still can play the inertia stepless bending moment.
6. the restriction of two pairs of central gears can be instantaneous gear ratio, and this gear ratio be adjustable.By automatic pilot, constantly adjust, the input shaft rotating speed amplitude of variation of this torque converter is reduced.
Claims (8)
1, the coupled system of forming by two groups of differential gear systems.It is characterized in that:
A. a planet carrier of these two groups of differential gear systems is made input shaft, and another planet carrier is made output shaft.
B. each central gear of arbitrary group of differential gear system, all with a central gear of another group differential gear system by member with constraint.
C. when disregarding the elasticity effect of member, input shaft rotational speed is determined by the rotating speed of the axle of exporting constantly fully at some.
D. input shaft rotational speed can not be determined by output shaft constantly at some.
2, as described two differential speed gears of claim 1., the axis of their two planet carriers is approximately parallel, or approximate coincidence.
3, as the described system of claim 1., the constraint of its a pair of central gear is to realize by the non-garden gear of a pair of conjugation.
4, the constraint of its a pair of central gear of the system as claimed in claim 1 is by crank, and the mechanism of rotating guide-bar realizes that perhaps the constraint of its two pairs of central gears is by two different cranks, and rotating guide-bar is realized.
5, as the described crank of claim 4., the off-centre of whitworth mechanism is adjustable.
6, as having 1 or many in its member of the described system of claim 1., has the elasticity of artificial design.
7, can limit the motion of some member as the described system of claim 1., can get one or more constant speed and compare transmission.
8, the system as claimed in claim 1, the planet wheel of its differential speed gears and central gear are the garden bevel gears, and perhaps this planet wheel and central gear are the garden stud wheels; The two all straight-tooth or helical tooth.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 85108083 CN85108083A (en) | 1985-10-26 | 1985-10-26 | Two differential speed gears inertia stepless moment variator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 85108083 CN85108083A (en) | 1985-10-26 | 1985-10-26 | Two differential speed gears inertia stepless moment variator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN85108083A true CN85108083A (en) | 1986-07-02 |
Family
ID=4795894
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 85108083 Pending CN85108083A (en) | 1985-10-26 | 1985-10-26 | Two differential speed gears inertia stepless moment variator |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN85108083A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106240358A (en) * | 2016-08-11 | 2016-12-21 | 贾陆军 | The steering and driving axle of double differectial structure |
-
1985
- 1985-10-26 CN CN 85108083 patent/CN85108083A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106240358A (en) * | 2016-08-11 | 2016-12-21 | 贾陆军 | The steering and driving axle of double differectial structure |
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| WD01 | Invention patent application deemed withdrawn after publication |