CN87101597A - The two-freedom gear inertia step-less moment variator that the freewheel rotating speed is frequently determined by output shaft - Google Patents
The two-freedom gear inertia step-less moment variator that the freewheel rotating speed is frequently determined by output shaft Download PDFInfo
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Abstract
This is a kind of inertia stepless moment variator.Disclosed Chinese patent application numbers 85108083, name is called the invention of the inertia stepless moment variator of two differential speed gears, exists the big shortcoming of input shaft rotating speed wave range.The present invention adopts the key element method of replacement, and this shortcoming is overcome fully.The invention allows for and manyly similarly can find out three members can produce these mechanism kinematics of Two-Degree-of-Freedom mechanism of stepless torque changing effect the time, satisfy an equation of motion.The speed of a certain member of this three member is determined by the speed of other two member, then definite fully sometimes by the speed of member institute.Make this torque-converters, had simple, reliable characteristics, can be used as some mechanical transmission part.
Description
The present invention relates to the technical field of inertia stepless moment variator.
The inertia torque-converters generally all is provided with free wheel device.Though the inertia stepless moment variator that Chinese patent application CN85108083A proposes has overcome above-mentioned shortcoming, also exists the input shaft rotational speed wave range big, to such an extent as to input shaft must link by elastic torsion shaft and engine flywheel.
The objective of the invention is to produce well behaved inertia stepless moment variator steam supply car selects for use.
The two differential speed gears inertia stepless moment variator that realization of the present invention: Chinese patent application CN85108083A proposes, its input shaft and output shaft are settled again, a planet carrier can freely be dallied, a central gear links to each other with input shaft, one planet carrier links to each other with output shaft, has just finished the present invention.
Though the present invention just does some simple substitution to its invention, has but reached special effect, still can under very wide variator ratio range, work reposefully when the input shaft rotational speed fluctuation is very little.
Fig. 1 is the schematic diagram of mechanism of torque-converters of the present invention, partly is made up of differential mechanism I, differential mechanism II, the instantaneous gear ratio of central gear mechanism III etc. three.Input shaft 16(links to each other with the engine flywheel of automobile) fixed central gear 9, chute dish 14; Planet carrier 8 link to each other with output shaft (transmission shaft of the automobile of ining succession); The central gear 11 of differential mechanism I is fixed with the central gear 10 of differential mechanism II.The central gear 9 of differential mechanism I links to each other with the central gear 12 of differential mechanism II by the instantaneous gear ratio of central gear mechanism III: second reel 13 is contained on the adjustable support 2, this dish (13) is rotated around axis A, when adjusting adjustable support 2, axis A and input shaft 16 apart from S variable (excursion is 0 to one enough values); Second reel 13 is provided with the stylus pin 1 in the groove that is inserted in chute dish 14, and the positions of 180 degree of being separated by are provided with groove to be inserted in wherein stylus pin 3 to slide; Stylus pin 3 is fixed by stylus pin arm 4 and central gear 12.Like this, sequence number is that 14,1,13 member has formed rotating guide mechanism; Same sequence number is that 13,3,4,12 member has also formed rotating guide mechanism.(the also available double-crank fourbar linkage of this rotating guide mechanism replaces, and has removed sliding pair like this, has all adopted revolute pair can use needle bearing; Also available crank-rocker mechanism, oscillating guidebar mechanism, or other quadratic crank mechanism replaces)
When distance S is transferred to a definite number, the rotation speed n of central gear 4 (4) has functional relation with the rotation speed n (9) of central gear 9: n(4)=f(φ) n(9), wherein φ is the corner of central gear 9, f(φ) being is the continuous function in cycle with 2 π, span is closed interval (1/2,2) (at this moment suppose central gear 11, the number of teeth of central gear 9 is respectively 48,24) or bigger.
Selected apart from S by the driver, (or adjusting selected automatically).Corresponding to different S values, f(φ) formation one family of functions, f
1(φ), f
2(φ) ..., or the like.These functions all are to be the continuous function in cycle with 2 π, but the span of function is inequality.Adjustment as selected distance S, makes 1/2＜f apart from the performance that S can change torque-converters
N(φ)＜2 o'clock then can not output torque, as " neutral gear "; Work as f
NMinimum value (φ) equals then can play the stepless torque changing effect at 1/2 o'clock; Work as f
NMinimum value (φ) can also then can also play the hypervelocity transferring power or swing to transferring power, (when helping power source with energy-storing flywheel as the power source formula of automobile is attached, swinging to the Brake Energy of stepless torque changing transmission recoverable automobile) less than 1/2 o'clock.Sequence number is that 6,7,15 member is respectively planet wheel 6, planet wheel 7, bearing 15 among Fig. 1.
When distance S is zero, can limits the motion of some parts and obtain constant speed and compare transmission; Central gear 11 is fixing with support 15, and speed ratio is 3; Central gear 11 is fixing with central gear 9, and speed ratio is 1; Planet carrier 5 is fixed to such an extent that speed ratio-3 is a reverse gear with bearing 15.
This embodiment's mechanism can do a lot of the variation and draw similar embodiment: the differential speed gears of I, II all can adopt the differential speed gears of arbitrary form; Central gear 10, central gear 11 also can adopt instantaneous gear ratio mechanism to link to each other; Input shaft and output shaft are commutative.
Postscript: embodiment 1 has made complete invention.From kinematic viewpoint, input shaft 16 is binary with the planet carrier 8 that output shaft is connected forever.The planetary transmission of automobile is a neutral gear when two degrees of freedom according to general knowledge! Can not output torque.Therefore be necessary say one say the working principle of this torque-converters.As the rotary inertia of each member of schematic diagram of mechanism shown in Figure 1, input torque, output torque, and other data substitution kinetic equations solve, just can select the rotary inertia of each member, and bright superperformance from this torque-converters.Hereinafter with the mode that is easily understood working principle is described, And provides rough design and calculation method.
Use n(ⅰ) represent that sequence number is the rotating speed of the member of ⅰ with respect to bearing 15, can list equation
n（11）-n（8）＝- 1/2 〔n（9）-n（8）〕 （1）
n（4）-n（5）＝-〔n（11）-n（5）〕 （2）
n（4）＝f（φ）·n（9） （3）
Can be changed into
2n（11）+n（9）＝3n（8） （4）
f（φ）·n（9）+n（11）＝2n（5） （5）
Equation (5) surplus-2 adds equation (4) through putting in order
〔-2f（φ）+1〕n（9）＝3n（8）-4n（5） （6）
The time making sequence number in design is 16,14,9 member, and sequence number is 8 member, sequence number is that the rotary inertia of 11 member is big as much as possible, n(9 like this) and n(8) at short notice it is constant substantially (to ward off as in 0.02 second or in 0.1 second) rotating speed in the time of turning around as central gear 9, (automobile also is that so the speed of automobile or the rotating speed of flywheel can not suddenly change when actual travel).When central gear 9 turned around, chute dish 14 also made a circle, f(φ) get maximum value and minimum value most.Determine to make f(φ apart from S) minimum value be 1/2, maximum value is assumed to the characteristics of 2(by the speed changing structure at III position, maximum value can be other number).
Suppose certain instantaneous n(9) be commentaries on classics in a minute 1500.Central gear 9 turns around in the time lag about 0.04 second, f(φ) to get maximum value and minimum value, according to formula (6), excursion n(5) is like this: ()/() 3/4 (n(8)+n(9) 3/4 n(8)) (one)
As seen the rotation speed n of planet carrier 5 (5) is from 3/4 n(8) increase to 3/4 (n(8)+n(9)) time, the kinetic energy of planet carrier 5 increases, and can think that 5 works done increase the kinetic energy of planet carrier 5 to input shaft to planet carrier; When the rotation speed n (5) of planet carrier 5 is determined (promptly as f(φ)=1/2 by the rotating speed of planet carrier 8) to fall the end be 3/4 n(8) time kinetic energy reduce, can think that it is output shaft that kinetic energy has been passed to planet carrier 8.Therefore the working principle of torque-converters of the present invention, can sketch and be: the power of motor is passed to input shaft, and the kinetic energy of planet carrier 5 is increased, and this kinetic energy has just been passed to planet carrier 8 to overcome the running resistance of automobile when the rotating speed of planet carrier 5 is determined by planet carrier 8.(notes)
When the rotation speed n (8) of planet carrier 8 is zero, n(9) still can not wait zero, so variator ratio range is very wide.
If f(is φ) can select f in this family of functions
N(φ) value in the square brackets on the left side of equation (6) can and be equalled zero greater than zero, then kinetic force is swung to transmission (planet carrier 5, planet carrier 8 planet carrier 5 when being in one degree of freedom has the highest kinetic energy).
The rotator inertia of planet carrier 5 determines it is important when design, a kind of rough computational methods are: the merit that motor turns around and done, the rotating speed that equals planet carrier 5 is from 3/4 n(8) bring up to 3/4 (n(8)+n(9)) kinetic energy increment (this kinetic energy increment should comprise that also sequence number is 6,4,12,13 member).Therefore the rotary inertia of planet carrier 5 can be traded off selectedly, makes automobile all suitable under various driving conditions.After the rotary inertia of planet carrier 5 was selected, other was 16,14,9 member as sequence number, and sequence number is 18 member, and sequence number is that the rotary inertia of 11 member is all should be than the rotary inertia of planet carrier 5 much bigger or more greatly.
Annotate: mechanism as shown in Figure 1 loads onto overrunning clutch between planet carrier 8 and output shaft, and power can only be passed to output shaft from planet carrier 8; Overrunning clutch also is housed between input shaft 16 and motor, makes and start function to input shaft 16 transmitted powers.The rotating speed of planet carrier 5 increases the power that can only absorb motor like this, must be to have transmitted energy to output shaft at the bottom of the speed drop of planet carrier 5.
Also can do such experiment: referring to Fig. 2
Consider the such particle system of Fig. 2.
Fig. 2 is the schematic diagram of mechanism of two differential speed gears, is made up of differential speed gears I, II two-part, and their central gear is constrained each other.A pair of for constant speed than 2: 1; Another is to being instantaneous gear ratio, and span is 2-1/2, and average speed ratio is 1.The rotary inertia of supposing planet carrier 19 is very big, and the rotary inertia of planet carrier 17 is it half, and the rotator inertia of other each member is its ten thousand/or littler.
At a time planet carrier 17, and the rotating speed of planet carrier 19 is respectively-2W and W, do not produce transmission of movement after this manner speed running always when planet carrier 17, planet carrier 19 are in one degree of freedom or two degrees of freedom like this.At this moment the rotating speed of central gear 18 has also been determined, for-4W.Have moment of face that central gear 18 is made positive work now, the time of effect is bordering on the time that central gear 20 turns around than short circuit.This moment of face can make the kinetic energy of system increase.Extrernal resistance moment is arranged again, the rotating speed of planet carrier 19 is not improved remain W.The rotating speed of planet carrier 17 still became-2W when the central gear 20 of differential mechanism I made a circle like this, thereby the rotating speed of central gear 18 still is-4W.This explanation moment of face is to central gear 18 works done of system, and the kinetic energy of system does not improve, and has overcome resisting moment to external world by planet carrier 19.This description of test the central gear of this invention torque-converters and planet carrier can transmitting torque when being in two degrees of freedom, and be different from general vehicle planetary speed changer, when spending, be neutral gear two!
So far, can understand that realization of the present invention can be summarized with a word:
Two members of the epicyclic gear train of a two-freedom, two members with the epicyclic gear train of another two-freedom form constraint respectively, it is transient change that this member that retrains mutually has a pair of its speed of related movement at least, the rule of this variation makes the system that is made up of two degrees of freedom epicyclic gear trains like this that two degrees of freedom be arranged, and can find the two member a, the b that belong to two different epicyclic gear trains, their (with respect to the motion of support) speed sometimes (as f(φ) equals a certain when several) one determined by another part.Mechanical structure with such characteristic, respectively as output (going into) axle and input (going out) axle, the torque-converters (speed changer) that forms transferring power or motion just becomes the present invention its member a or b and other member of selecting.
(torque-converters of the present invention is used for winch, and the occasion of hoist crane and other transferring power also is a purpose of the present invention.）
Language with mathematics illustrates top the words now.
The epicyclic gear train of a two-freedom can be selected three members, writes out an equation about three unknown numbers of rotating speed, and two such epicyclic gear trains can be write out two equations of six unknown numbers, and the constraint of above-mentioned this two pairs of members can be write out two equations.Like this, have six unknown numbers, the set of equation of four equation compositions becomes the equation that three unknown numbers are arranged through conversion, and the form of this equation is formula (6) as mentioned.Owing to selected the rule of constraint, can make some the time (when a certain gear is in certain corner) this equation become the equation of two unknown numbers, the rotating speed of such member a has just been determined by the rotating speed of another member b.
Understand these explanations, can draw the structure of example 1 and example 2.And other many structures the more.
Example 1, referring to Fig. 3, Fig. 3 is a schematic diagram of mechanism, is made up of epicyclic gear train I, II.22 one-tenth gear ratio transmissions of planet carrier 21 and central gear, n(21)=f(φ) n(22); Central gear 25 is constant speed transmission n(26 with central gear 26)=-n(25).(sequence number is that 23,24 member is respectively central gear, planet carrier.）
Epicyclic gear train I, II can get two equatioies respectively
n（26）+n（23）＝2n（21）;n（25）+n（22）＝2n（24）;
Like this, 4 equatioies can get equation through computing
〔1-2f（φ）〕n（22）＝2n（24）-n（23）
Can select central gear 23 or planet carrier 24 according to this equation and make output (going into) axle, choose out sequence number wantonly and be 25,26,21,22 member and make output shaft.(central gear 22 is represented with the constraint with dashed lines Z of planet carrier 21 in the accompanying drawing 3, can lead to a pair of external gear pump and a pair of non-garden gear realizes, also but crank rocker realization-central gear 22 rotates, and planet carrier 21 swings are to satisfy 1-2f(φ) when being in a certain corner, central gear 22 can equal zero.）
Example 2, referring to Fig. 4, Fig. 4 is a schematic diagram of mechanism, and the epicyclic gear train I is similar to the epicyclic gear train of K-H-V shape, and II is similar to 2H-K shape epicyclic gear train.The member that this two epicyclic gear train retrains mutually is: central gear 31 rotates with speed with planet carrier 30, n(31)=n(30); 28 one-tenth gear ratio transmissions of central gear 27 and planet wheel n(28)=and f(φ) n(27), (this transmission is easy to realize: the constant speed unit V of I is cancelled, central gear 28 is established chute, central gear 27 is established stylus pin, form a whitworth mechanism and just become, at this moment f(φ) independent variable φ be the corner of planet wheel 28 with respect to planet carrier 30).
Such 4 equations are:
(n(31)-n(32))/(n(27)-n(32))=-2; (there is number of teeth relation in the supposition II)
(n(28)-n(30))/(n(29)-n(30))=4/3; (there is number of teeth relation in the supposition I)
n（31）＝n（30）;
n（28）＝f（φ）n（27）;
Can draw equation through computing
（f（φ）- 2/3 ）·n（27）＝ 4/3 n（29）-n（32）
This equation and formula 6 are similar.
Core out wheel 29 or planet carrier 32 are made output (going into) axle, and optional sequence number is 31,30,27,28 member do input (going out) axle, just becomes the present invention.
Can analogize a lot of schemes according to example 1, example 2: because two degrees of freedom epicyclic gear train commonly used just has 2H-K shape, K-H-V shape, and the turnover speed changer (each group of Simpson type) of automobile, it is just more that the differential mechanism of automobile etc. is added the epicyclic gear train that is of little use, appoints to take out two (can repeat to get) and select member constrained each other again and just made the present invention from these binary epicyclic gear trains.A lot of better schemes are not repeated.
The a of ※ Fig. 5, b, c are the schematic diagram of mechanisms of epicyclic gear train, the two degree freedom system that these mechanisms all are made up of three members.
Schematic diagram of mechanism shown in Figure 6 also contains three members, and two degrees of freedom are arranged.(three revolute pairs, a sliding pair are arranged among Fig. 6)
Every two degree freedom system of forming by the member more than three or three, select two members, two members selecting with another coupled system of being made up of the member more than three or three form constraint respectively, and the characteristic that has of the H of mechanism of Zu Chenging is like this:
1. must found out the set of equation that contains six unknown numbers (six members are with respect to the movement velocity of support), four equations;
2. can obtain an equation F who contains three unknown numbers to this set of equation computing;
If 3. have among the H of this mechanism a pair of above member be instantaneous gear ratio (be exactly two members be not constant with respect to support or with respect to the ratio of the movement velocity of other member, be the function of the corner of a certain member), then when the rule of gear ratio is reasonable in design, when being in a certain corner, certain member among the H of mechanism, the movement velocity of a member a is determined by the movement velocity of another member b according to equation F.
But the such H of mechanism transferring power: a of mechanism is made input shaft, the popularization of member b as the invention of output shaft-Here it is Chinese patent application CN85108083, can produce multiple torque-converters, this also is another object of the present invention.Member a or member b are made input shaft (or output shaft), select other member and make output shaft (or input shaft)-Here it is the freewheel rotating speed frequently by epicyclic gear train step-less moment variator of output (going into) axle decision.
The every K of mechanism that two-freedom is arranged of ※ can found out the speed n(a about three member a, b, c), n(b), b(c) an equation:
F(φ) n(a)=F{n(b), n(c), g(d), q(w) ... ... (land)
Wherein F { } is a function of many variables formulas, f(φ), g(a), q(w) ... the function of the corner of different component (position) among the outgoing mechanism K.
If f(φ is often arranged during the K of mechanism motion)=0, utilize the K of this mechanism can make inertia stepless moment variator so.
Explanation (changeing the 18th page down) gives an actual example
Understood above explanation, just be easy to draw a lot of other similar structures according to reasoning from logic.These structures much simple than shown in the schematic diagram of mechanism of Fig. 1, but reach the purpose of inertia stepless bending moment too.
Figure middle gear 35 is central gears, and can be used as " inertia freewheel " number of teeth is Z(35), gear 37 is that the planet wheel number of teeth is Z(37) this two gear intermeshes; Planet carrier 34 is also referred to as input shaft 34; Output shaft 40 is equipped with crank 39, stylus pin 38; Guide rod 36 tightens together with gear 37.Sequence number is 40,39,38,36 member formation rotating guide mechanism.If n(35), n(34), n(40), n(37) be the rotating speed (with respect to the rotating speed of bearing 15) of the member of corresponding sequence number, φ is the corner of guide rod 36 with respect to input shaft 34.
When input shaft 34 static with respect to support 15, promptly as n(34)=0 the time, relation is arranged:
(n(35))/(n(37))=(Z(37))/(Z(35))=K(K is a gear ratio, is constant)
(n(40))/(n(37))=and f(φ) (f(φ) be the function of φ, determined by the characteristic of " rotating guide mechanism ")
When output shaft 34 rotates with respect to support 15, i.e. n(34) ≠ 0 o'clock, above relation becomes
(n（35）-n（34）)/(n（37）-n（34）) ＝K……21
(n（40）-n（34）)/(n（37）-n（34）) ＝f（φ）……22
Just
n（35）-n（34）＝K·n（37）-K·n（34）
n（40）-n（34）＝f（φ）·n（37）-f（φ）·n（34）
Cancellation n(37) gets after the arrangement
f（φ）n（35）-Kn（40）＝（f（φ）-K）·n（34）
……（23）
(this formula be exactly above the special shape of equation (land))
(also can cancellation n(34 for set of equation 21,22) obtains
〔K-f（φ）〕n（37）＝〔1-f（φ）〕·n（35）+（K-1）·n（40）
……（23′）
Still with above equation (land) is similar for this formula.
From formula 23 and 23 ' all can find out, as f(φ)=during K, n(35)=n(40); And member 34 residing to 37 " status " is similar, and equation 23 hereinafter only is discussed, and to equation 23 ' can make similar conclusion, the implementer can derive voluntarily).
The number of teeth of gear 35 is greater than the number of teeth of gear 37, thus have K＜1(when K value and 1 very near the time, self-locking will take place in the relative movement of some member in some cases).
F(φ) characteristics by rotating guide mechanism are determined, f(φ) be to be the continuous function in cycle with 2 π, its span greater than 1 and less than 1 between, this scope should comprise the K value.
As previously mentioned, this rotating guide mechanism can replace with " double-crank fourbar linkage ".Fig. 9 is the sketch of double-crank fourbar linkage, O
1Be the rotatingshaft of gear 37, O
2It is the rotatingshaft of output shaft 40.
According to equation (23), the motion of the member of each sequence number is binary, but when φ be a certain corner, make f(φ)=during K, n(40 is arranged then)=n(35), promptly gear 35 has only one degree of freedom with output shaft 40.(at this moment the invention of Chinese patent application numbers 85108083 obtains promoting: except that two differential speed gears, also have a lot of Two-Degree-of-Freedom mechanisms still can reach " two members sometimes are two degrees of freedom, sometimes have only one degree of freedom ".Respectively as input shaft and output shaft or as output shaft and input shaft, is exactly gear 35 and output shaft 40 inertia stepless moment variator similar with application number 85108083.This torque-converters can produce special effect as the torque-converters of bicycle ,-utilized the inertial force of people's leg, conform to the movement rhythm of human body, make stepping bicycle become free and relaxed) as playing football.
Learn that from equation 23 motion of each member is binary, the motion of each member, the transmission that reaches kinetic energy, merit is determined by kinetics equation.Can be output shaft 40 as input shaft, input shaft 34 as output shaft.Also can change other " instantaneous gear ratio mechanism " to " rotating guide mechanism " into, or by other member, make average speed ratio n(35): n(40) (ratio of the corner of gear 35 and the corner of output shaft 40 when φ increases to φ '+2 π from φ ') is not equal to 1.
Also can draw and Fig. 8 kindred organization.As Figure 10, shown in Figure 11.Figure 10, Figure 11 are schematic diagram of mechanisms, and the meaning of the member of each sequence number and Fig. 8 are suitable with sequence number.At this moment also can found out similar equation (23) (guide rod 36 has been located on the gear 37).
By three or three two-freedom mechanisms that above member is formed, wherein have at least the relative movement of a pair of member to be " instantaneous gear ratio ", and this " instantaneous gear ratio " conforms to certain rules, makes that member a, member b sometimes are two-freedoms, sometimes become one degree of freedom; Such mechanism is exactly the present invention.Select member a, member b as the popularization (promptly being generalized to by three and three other Two-Degree-of-Freedom mechanisms that do not need two groups of differential speed gears that above member is formed) that input shaft and output shaft then are Chinese patent application numbers 85108083 as from " two differential speed gears ", member a(or b) and mechanism in other member of selecting as output shaft and input shaft or input shaft and output shaft, after then being the popularization of Chinese patent application numbers 86108083, reach the simple replacement of new effect.
The present invention can be used in automobile, on bicycle, the hoisting machine.Also can be used on (comprise the Screw setting and loosening machine that other is electronic) on the tire screw disassembly-and-assembly machine and " shaft joint " of linking to each other with high capacity motor with the starting current of the starter motor of minimizing motor on, these application all are the characteristics of having utilized " stepless torque changing ".
The present invention also can be used for the occasion of " stepless change ", makes the rotating speed of output shaft arbitrarily be adjusted at a scope, as the usefulness of transmitting movement.Like this, the present invention can be on automatic conveying belt as the usefulness of stepless speed variator.
It is adjustable at any time to make the rotating speed of output shaft can keep stablizing ， And, and this way is a lot:
1. change " instantaneous gear ratio mechanism "-at f(φ) family of functions in constantly select suitable f(φ).Be exemplified below.
Referring to Figure 12, Figure 12 is the easy structure figure that is similar to Fig. 8 schematic diagram of mechanism.
The stylus pin 38 of its " instantaneous gear ratio mechanism "-" rotating guide mechanism " is adjustable with the distance H of output shaft 40.Stylus pin 38 is contained on the crank 39 by eccentric shaft 42, and when gear 43 rotated, eccentric shaft 42 rotated, and distance H has just changed.Gear 43 and gear 44 engagements, (only need the angle of changeing less, just can cause the variation of H) when gear 44 moves axially on output shaft 40, rotated by the effect of the set spiral of output shaft 40 (skewed slot, among the figure shown in the dotted line).Moving axially of gear 44 by automatic speed governor control (as: output shaft rotating speed reduction, flyball closes up, and gear 44 is moved or the like), each f(φ when H changes like this) be inequality, thereby inertia freewheel (gear 37) absorbs, and the function of emitting is different.
2. change the rotary inertia of freewheel.
4 pages of last sections such as this specification: the motor merit done (contrast accompanying drawing 8 is interpreted as f(φ) that turns around is finished one-period, and promptly φ increases to φ '+2 π from φ ', and just input shaft 34 makes a circle the merit of being done with respect to output shaft 40).Planet carrier 5(is interpreted as member such as Fig. 8 of all rotating speed frequent variations corresponding to Fig. 8, and sequence number is 35,36,37 member among Figure 10,11) be called freewheel.The variation of freewheel rotary inertia can change the power that motor spreads out of.Because speed ratio has been variable, adding power also is variable (variable power does not cause power loss, as then fuel injection quantity minimizing of diesel engine, as then electric current minimizing of motor), therefore can make output shaft constant in a speed range.(when output shaft at a certain rotating speed, and resisting moment changes the rotary inertia of freewheel when reducing, and the power of motor output is reduced, like this, because power-balance, output shaft still is in this rotating speed.）
The method that changes the freewheel rotary inertia has:
A, movably " mass " be set on freewheel.
Referring to accompanying drawing 13.Figure 13 is a schematic representation.
Have flyball 46 on the freewheel, when sliding sleeve 47 slided on axle, flyball can open and close up, thereby changes the whole freewheel rotary inertia of (comprising rotatable parts such as flyball, rod member, sliding sleeve), with the output power of control motor, make the output shaft of this stepless speed variator keep stabilization of speed.
B, several separable rotating disks are set, are combined into one with freewheel in case of necessity, to increase the rotary inertia of whole freewheel.Then reduced the rotary inertia of freewheel in the time of separately.
The objective of the invention is to improve the performance of the step-less moment variator of Chinese patent application numbers 85108083, make this class torque-converters can be, and the tire screw disassembly-and-assembly machine, wait the driving mechanism of a lot of transferring power as bicycle, automobile, motorcycle.Also make this step-less moment variator can be used for the occasion of transmitting movement, as replacing used stepless speed variator on the automatic control line.
Like this, good effect of the present invention is clearly.
Accompanying drawing 14 explains orally:
Mechanism shown in Figure 8, input shaft 34, internal gear 35 is jointly as input shaft, its schematic diagram of mechanism as shown in figure 14: power is distributed in input shaft 34 by differential mechanism, on the internal gear 35.The stylus pin 38 of " rotating guide mechanism " among Figure 14 is located on the gear 37.The number of teeth of gear 37 can also be less than half of the number of teeth of internal gear 35.
Accompanying drawing 15 explains orally:
In the mechanism shown in Figure 8, external gear 37 retrains by " gear pair " with internal gear 35, and has used stable drive ratio K, as adopts non-garden gear, then becomes instantaneous variable ratio K(θ).Adopt pivot pin 48 among Figure 15, it is 35,37 member (effect of these members is same as among Fig. 8 the member with sequence number) that link rod 49 makes sequence number, forms instantaneous variable ratio K(θ).Like this, the formula that is similar to equation 23 becomes
f（φ）·n（35）-K（θ）·n（40）＝〔f（φ）-K（θ）〕·n（34）
The schematic diagram of mechanism of Figure 15 ' and this are similar.The member of sequence number 35 becomes colyliform: its rotation axis C can with the dead in line of input shaft 34, a segment distance is perhaps arranged, perhaps this distance still be adjustable, to change the characteristic of torque-converters; Wherein be carved with groove, to form rotating guide mechanism with pivot pin 48.
Accompanying drawing 16 explains orally:
Among Figure 16, differential mechanism I, II, and II, III all form application number 85108083 described " two differential speed gears inertia stepless moment variator ".Respectively the planet carrier of differential mechanism I, III as input shaft and output shaft, suppose that again its rotating speed is respectively per minute 1000 and changes with per minute 100 and change, and rotating speed constant at short notice (when rotary inertia is big, just can accomplish).The planet carrier of differential mechanism II has certain rotary inertia.Like this, when the planet carrier of differential mechanism I, II becomes one degree of freedom, the rotating speed of the planet carrier of differential mechanism II is that per minute 1000 changes, when the planet carrier of differential mechanism II, III becomes one degree of freedom, the rotating speed of the planet carrier of differential mechanism II is kept to per minute 100 to be changeed, and promptly kinetic energy has been passed to output shaft.From accompanying drawing, find out significantly, three planet carriers can not become one degree of freedom simultaneously, be the state that one degree of freedom can not appear in input shaft, output shaft, the situation of " being determined by the rotating speed of output shaft during input shaft rotational speed " just can not occur.Improve from the bending moment performance.From having found out another kind of realizing method of the present invention here again:
Constitute the little torque-converters of this input shaft rotating speed wave range with two groups by the 9th page of capable described mechanism of 11-17 of this specification, the method that constitutes is: member a, b, c, member b as input shaft, the similar component c of member c and another similar means fixed (rotating speed is constrained each other) or just the similar component b of member c as another similar means, like this, the member c of this similar means as output shaft.
That is to say that the torque-converters of Shi Xianing can be told two groups of the 9th page of described mechanisms in this way, and can seek out and belong to this member of two groups.
Enumerate an embodiment with this way, referring to accompanying drawing 17.
Schematic diagram of mechanism 17 is made up of as the similar torque-converters of Fig. 8 two groups of I, II.The same Fig. 8 of the title of the parts of each sequence number.The output shaft 34 of I group is fixed with the internal gear 35 of II group, is called public freewheel 40-35; This input shaft of two groups 34 is also fixed.(rotating guide mechanism does not draw among the figure).
The axle of the internal gear 35 of I group as the power input, the output shaft 40 of II group is just as output shaft.
Its working principle is: during the rotating speed of public freewheel 40-35 and determined by input shaft (internal gear 35), the time and determined by output shaft 40.
Schematic diagram of mechanism 17 will be noted a bit, the internal gear 35 of I group, never should with 34 one-tenth ones degree of freedom of output shaft of II group.This can accomplish: (not fixed as this input shaft of two groups 34, can relatively rotate, then use other method.）
If " crank throw " of two fixed planet carriers (input shaft 34) in one plane.Referring to Figure 18, the stylus pin of public freewheel 40-35 or groove (to form rotating guide mechanism) are positioned on the ray A, and external gear 37 is when public freewheel 40-35 rolls along the joint garden so, and the ray B at its stylus pin or groove place overlaps with ray A never.(ray B has only three positions among Figure 18, does not overlap with ray A.
Accompanying drawing 19 explains orally:
Referring to accompanying drawing 8, internal gear 35, in the moment inequality, the time determine the rotating speed of a, the time and determine the rotating speed of b.The mean speed of a, b is identical.A, b make speed synthetic by " differential mechanism ", by an axle output.Like this internal gear 35 as input shaft, its fluctuation of speed is also very little.
(being right after the 9th page) Fig. 7 comes to this and at will gives an example.In the schematic diagram of mechanism 7, external gear a is carved with radial groove, forms rotating guide mechanism with crank b.It can found out equation of motion:
4/3 n
1F(φ)-n
3=n
4(4/3 f(φ)-1) ... similar formula (6)
Wherein 4/3 is the gear ratio of hypothesis: n
1, n
3, n
4Be respectively the rotating speed of gearwheel, crank b, planet carrier; F(φ) is the function of gear a with respect to the corner φ of planet carrier.Generally have three and three Two-Degree-of-Freedom mechanisms that above member is formed, can both found out the equation about speed that contains three members, this equation is similar to following formula when the constraint satisfaction certain condition.
The inertia stepless transmission principle of mechanism is like this: can often equal zero in following formula the right, work as n like this
4, n
1When equating with the rotating speed of prime mover, working machine respectively, n
3Sometimes can improve arbitrarily, sometimes again by n
1Determine.Absorb the merit of prime mover during raising, by n
1Then kinetic energy is passed to working machine when determining.The screw folding dress that this mechanism also can be used for repairing automobile, motorcycle mechanically.
Claims (3)
1, a kind of mechanical transmission.It is characterized in that:
A, be provided with double differectial mechanism; This double differectial mechanism is made up of two groups of differential mechanisms.Two central gears of-one group of differential mechanism all are provided with constraint with another central gear of organizing differential mechanism respectively.The constraint that wherein has a pair of central gear at least is instantaneous gear ratio.And the set of the numerical value of instantaneous gear ratio and another intersection of sets collection to the numerical value of the speed ratio of central gear are not empty sets.
B or can tell two groups of double differectial mechanisms.In these two groups of double differectial mechanisms one group of public differential mechanism is arranged; Perhaps its input shaft and output shaft are respectively a planet carrier, a central gear or planet wheel or other other member except that planet carrier.
2, mechanical transmission according to claim 1 is characterized in that, by founding out similar equation
〔-2f（φ）+1〕n（9）＝3n（8）-4n（5）
Other mechanism substitute double differectial mechanism.
3, mechanical transmission according to claim 1 and 2 is characterized in that the instantaneous gear ratio mechanism's right and wrong garden gear or " fourbar linkage " that wherein are provided with.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 87101597 CN87101597A (en) | 1987-02-26 | 1987-02-26 | The two-freedom gear inertia step-less moment variator that the freewheel rotating speed is frequently determined by output shaft |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 87101597 CN87101597A (en) | 1987-02-26 | 1987-02-26 | The two-freedom gear inertia step-less moment variator that the freewheel rotating speed is frequently determined by output shaft |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN87101597A true CN87101597A (en) | 1988-10-19 |
Family
ID=4813551
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 87101597 Pending CN87101597A (en) | 1987-02-26 | 1987-02-26 | The two-freedom gear inertia step-less moment variator that the freewheel rotating speed is frequently determined by output shaft |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN87101597A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100414142C (en) * | 2005-12-09 | 2008-08-27 | 史建新 | Free type full automatic non-stage transmission |
| CN107269781A (en) * | 2011-02-24 | 2017-10-20 | 杨泰和 | Controllable epicyclic wheel group arrangement of clutch and apply dynamical system |
| CN108814824A (en) * | 2017-05-10 | 2018-11-16 | 国家康复辅具研究中心 | A kind of wheelchair |
-
1987
- 1987-02-26 CN CN 87101597 patent/CN87101597A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100414142C (en) * | 2005-12-09 | 2008-08-27 | 史建新 | Free type full automatic non-stage transmission |
| CN107269781A (en) * | 2011-02-24 | 2017-10-20 | 杨泰和 | Controllable epicyclic wheel group arrangement of clutch and apply dynamical system |
| CN108814824A (en) * | 2017-05-10 | 2018-11-16 | 国家康复辅具研究中心 | A kind of wheelchair |
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