CN1865733A - Diameter-variable diving wheel and driving mechanism equipped therewith - Google Patents
Diameter-variable diving wheel and driving mechanism equipped therewith Download PDFInfo
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- CN1865733A CN1865733A CNA2005100710177A CN200510071017A CN1865733A CN 1865733 A CN1865733 A CN 1865733A CN A2005100710177 A CNA2005100710177 A CN A2005100710177A CN 200510071017 A CN200510071017 A CN 200510071017A CN 1865733 A CN1865733 A CN 1865733A
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- traction belt
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/52—Pulleys or friction discs of adjustable construction
- F16H55/54—Pulleys or friction discs of adjustable construction of which the bearing parts are radially adjustable
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
- F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
- F16H9/24—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using chains or toothed belts, belts in the form of links; Chains or belts specially adapted to such gearing
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Abstract
The invention discloses a reducing transmission wheel and relative transmission device. Wherein, said transmission device is formed by a reducing transmission wheel, a middle transmission band, and relative shifter; the wheel drawing band is winded to form the working surface of reducing transmission wheel, while the non-transmission part is winded in the wheel center; the wheel drawing band and the transmission wheel transmit torque via the drawing support that radial moving on the transmission disk; the position of drawing support decides the nodal circle radius of transmission wheel; the reducing wheel via amplifying wheel device and the reducing wheel device realize the change of transmission nodal circle; said transmission device utilizes the change of nodal circle radius to shift the speed. The invention can be used in vehicle.
Description
Technical field
The present invention relates to mechanical transmission, particularly a kind of drive wheel and this driving mechanism of taking turns of application that changes the wheel radius.
Background technique
The transmission of power of prime mover is being given in the process of work mechanism, and transmission device plays important effect.With the automobile is example: what meet the vehicle dynamic quality requirement most is the constant power motor, but what in fact generally use is that volume is little, the internal-combustion engine that efficient is high, and internal-combustion engine must be equipped with the defective that speed changer just can overcome the unique characteristics curve.
Relevant automotive research theory shows: make motor car engine can both send peak output under any speed of a motor vehicle, the transmission ratio i of its outfit
gShould press the following formula rule with the speed of a motor vehicle changes: i
g=0.377rn
p/ i
0u
a(r is a radius of wheel in the formula, n
pRotating speed during for maximum power, i
0Be main reducing gear velocity ratio, u
aBe car speed).By following formula as can be known, optimal automotive transmission should be a stepless speed variator.
It needs to be noted: have only transmission efficiency height to arrive approaching with general gear-shift transmission when stepless speed variator, and during velocity ratio Changing Pattern conversion velocity ratio as requested, just can reach requirement, if ineligible, the automobile that stepless speed variator is housed may reduce the power character of automobile on the contrary.
The stepless speed variator of extensive use is a fluid torque converter on the car, but torque converter drive efficient is low.Just be able to popular because of it has starting advantage steady, easy and simple to handle, that riding comfort is good.Also has steel-belt type stepless speed variator (CVT) in addition; This speed changer transmission efficiency is higher, but because it relies on the frictional force transferring power, its transmission power is limited, and because of they are many to hydraulic pressure, electronic technology dependence, practical application is less.
What automobile was the most frequently used is the gear type step change transmission, and this speed changer is durable, the transmission efficiency height.Theoretically: the gear type step change transmission should be equipped with more gear to adapt to the needs of the different operating modes of automobile.But actual conditions are: the step change transmission gear number surpasses five (forward gear), will make structure greatly complicated, and operating mechanism is also complicated accordingly simultaneously.Most widely used manual step change transmission in use needs the engagement clutch shift hunting, and driver's physical output is big, and requires that certain operating technology and experience are arranged, and uses very inconvenient.
Summary of the invention
For overcoming the defective of prior art, the invention provides a kind of automatic mechanical transmission with high transmission efficiency.
A kind of diameter-variable driving wheel is by hitch frame 1, wheel table traction belt 3, expand wheel apparatus and the wheel apparatus that contracts is formed; Wherein hitch frame 1 is installed on the wheel body 5, and can move radially thereon; 3 one of wheel table traction belts are connected on the hitch frame 1, and 7 axis coiling forms the drive wheel working surface around the shaft, and wheel table traction belt 3 passes through the transmission that hitch frame 1 is realized moment with wheel body 5; Under the cooperation of expanding the wheel apparatus and the wheel apparatus that contracts, hitch frame 1 moves radially on wheel body 5, to change the size of the arm of force between wheel table traction belt 3 and the rotating shaft 7, wheel table traction belt 3 is regulated the length that it participates in transmission with the change of hitch frame 1 position, reaches the purpose that changes drive wheel surface perimeter and drive wheel wheel radius.
A kind of transmission device uses above-mentioned diameter-changing wheel to do drive wheel, utilizes diameter-changing wheel and middle driving belt 14 can constitute variable speed drive; When deciding the radius wheel with a diameter-changing wheel and one and form variable speed drive, two-wheeled centre distance can be taken turns the corresponding adjustment of variation of radius with diameter-changing wheel; Diameter-changing wheel can be used as driving wheel or follower arbitrarily; Diameter-changing wheel goes to the non-cornerite zone of middle driving belt 14 at its reducing opening and expands wheel or the reducing operation of the wheel that contracts.
Description of drawings
Fig. 1 (a)-(c) is the basic block diagram of diameter-variable driving wheel.
Fig. 2 (a)-(c) is the plan view and the subdivision graph of diameter-variable driving wheel.
Fig. 3 (a)-(c) is the schematic diagram that diameter-variable driving wheel changes the wheel footpath.
Fig. 4 is that two round end chains are the straight-line transmitting actuation mechanism transmission principle figure of wheel table traction belt and driving belt.
Fig. 5 is the variable transmission mechanism that is made of the diameter-changing wheel that two two round end chains are wheel table traction belt.
Fig. 6 is a variable transmission mechanism entity exploded view.
Fig. 7 (a)-(c) is the assembling and the exploded view of two round end chain type wheel table traction belts.
Fig. 8 (a)-(e) is that two round end chains are the driver schematic diagram and the link configuration figure of wheel table traction belt and driving belt.
Fig. 9 (a)-(f) is the structural representation that the spoke rod-type expands wheel apparatus.
Figure 10 (a)-(c) is the micro-shift transmission External view.
Figure 11 (a)-(c) is micro-shift transmission partial cutaway component and bottom half sterogram.
Figure 12 is micro-shift transmission inner each block diagram when maximum transmission ratio.
Figure 13 (a) and (b) are micro-shift transmission basic driving component relative position schematic representation when maximum transmission ratio.
Figure 14 (a)-(f) is two structural representations of deciding the radius drive wheel of micro-shift transmission.
Figure 15 (a)-(h) is a main shaft broken away view in the middle of the micro-shift transmission.
Figure 16 is the plan view of principle axis shafting in the middle of the micro-shift transmission.
Figure 17 (a) and (b) are that the folder of three on the main shaft rises the dish subdivision graph in the middle of the micro-shift transmission.
Figure 18 (a) and (b) are micro-shift transmission gear shift device sterogram and plan view.
Figure 19 is micro-shift transmission gear shift rotating shaft and auxiliary spindle and corresponding annex map.
Figure 20 (a)-(c) is a micro-shift transmission gear shift device subdivision graph.
Figure 21 is micro-shift transmission inner each block diagram when fastest ratio.
Figure 22 (a) and (b) are micro-shift transmission basic driving component relative position schematic representation when fastest ratio.
Figure 23 (a) and (b) are micro-shift transmission relative dimensions schematic diagram datas.
Figure 24 is the counter-rotating and the differential mechanism of micro-shift transmission clutch end.
Embodiment
Below in conjunction with accompanying drawing, diameter-variable driving wheel and this transmission device of taking turns of use are done detailed explanation with several case study on implementation.
Fig. 1--Fig. 8 be a kind of be the diameter-variable driving wheel and the transmission device of wheel table traction belt with two round end chains;
Fig. 9 is that a kind of spoke rod-type expands wheel apparatus;
Figure 10--Figure 24 is a kind of integrated type micro-shift transmission that uses diameter-variable driving wheel;
Case 1: a kind of is the diameter-variable driving wheel and the transmission device of wheel table traction belt with two round end chains;
Fig. 1 (a)-(c) is that the two round end chains of a kind of usefulness are wheel table traction belt, makes to expand the diameter-variable driving wheel of wheel apparatus with a pair of conical surface dish.(a) figure has shown the basic structure of diameter-changing wheel: hitch frame 1 is contained on a pair of awl dish 5, and 3 one of wheel table traction belts are connected on the hitch frame 1, and the other end connects and furls backguy 2, and wheel table traction belt 3 forms pulled surface around one week of core wheel.A pair ofly can constitute the expansion wheel apparatus at the awl dishes 5 that rotating shaft 7 is axially moved in opposite directions; Inside is equipped with the reel 4 of clockwork spring and is furled backguy 2 and constitutes the wheel apparatus that contracts; Wheel table traction belt 3 sides evenly are furnished with conehead pin 6, and the cone match of the conical surface of this pin and awl dish 5 forms sliding pair; The wheel radius is adjusted to maximum among the figure.(b) figure is that diameter-changing wheel wheel radius contracts to situation hour, and hitch frame 1 has slided into minimum point for 10 times along oblique hitch frame chute, and wheel table traction belt inoperative is partly reeled and is stored on reel 4.8 is that awl coils the secondary conical surface among the figure, the 9th, and main cone face, the 11st, the transition inclined-plane the during turnover of conehead pin.Cut the awl dish in left side among the figure, can see the structure of the awl dish work conical surface.(c) figure is the structural drawing that wheel table traction belt launches, this part is one section chain that is formed by connecting by two round end carrier bars and chain link, on the hitch frame with V-arrangement frame structure 1 that the one head is connected on, the other end is connected on the reel 4 with furling backguy 2, take turns 4 inside clockwork spring is housed, can rotate with respect to rotating shaft 7.
Fig. 2 (a)-(c) is the plan view and the subdivision graph of diameter-variable driving wheel.(a) figure is the plan view that a pair of conical surface folder rises dish, and the secondary as we can see from the figure conical surface 8, main cone face 9, oblique hitch frame chute 10 and transition inclined-plane 11 have also shown the conical surface of the conehead pin 6 on the wheel table traction belt chain link and the situation that main cone face 9 cooperatively interacts among the figure.The secondary conical surface 8 has identical cone angle with main cone face 9.(b) figure is that a pair of folder shown in (a) figure rises the situation that dish has been installed wheel table traction belt, hitch frame 1 and rotating shaft 7.In conjunction with (a) figure as can be seen, wheel table traction belt divides wide joint 12 and narrow joint 13 from structure, and the conehead pin conical surface of wherein wide joint 12 both sides cooperates with the secondary conical surface 8, and the conehead pin conical surface of narrow joint 13 both sides cooperates with main cone face 9.
(c) figure is the subdivision graph of a pair of disc, as we can see from the figure the situation that matches with the awl dish conical surface of the relative position of wheel table traction belt 3, reel 4, rotating shaft 7 and conehead pin 6.
Fig. 3 (a)-(c) is the schematic diagram that diameter-variable driving wheel changes the wheel footpath.To being with each conehead pin to compile number in the wheel table traction, wherein 0 is towing pin on the hitch frame among the figure.Situation when (a) figure is wheel footpath maximum, wheel table traction belt total length is pulled out.(c) figure is a wheel footpath situation hour: the part that wheel table traction belt participates in transmission is wound into a circle, forms the drive wheel working surface; Inoperative is partly reeled and is stored in core wheel.(b) figure is in taking turns the footpath process extremely minimum by maximal regulated, the motion track figure of each conehead pin, and 0-0 is the movement locus of towing pin on the hitch frame among the figure, this is a drive wheel radius radially.Line 1-1,2-2 among the figure ... it is respectively conehead pin 1,2 ... movement locus when the regulating wheel radius.
Fig. 4 is that two round end chains are the straight-line transmitting actuation mechanism transmission principle figure of wheel table traction belt and driving belt.This device is only a direction transferring power.3-1 is the wheel table traction belt of the application of force among the figure, and 3-2 is stressed wheel table traction belt.The 14th, driving belt also is one section two round end chain.Arrow has marked transmission direction v among the figure.Power is passed on the stressed hitch frame 1-2 by wheel table traction belt 3-1, driving belt 14, wheel table traction belt 3-2 by application of force hitch frame 1-1 input.Driving belt 14 constitutes engagement pair with wheel table traction belt 3-1, the 3-2 on both sides.This transmission device can transmit big load.
Fig. 5 is the variable transmission mechanism that is made of the diameter-changing wheel that two two round end chains are wheel table traction belt.This device is made of two diameter-changing wheels and driving belt 14, and this mechanism only transmits unidirectional torque, and a left side is a driving wheel, and the right side is a follower.4-1 and 4-2 are the reels of two-wheeled wheel table traction belt, the 2nd, and the coiling backguy.Arrow has marked the moving direction of each driving component among the figure, and v is the moving direction of driving belt 14.Be called the reducing opening near hitch frame 1-1 left side with near the interface section of hitch frame 1-2 right side, wheel table traction belt among the figure, wheel table traction belt passes in and out from here; Here also be the separation of wheel table traction belt working portion and inoperative part.Diameter-changing wheel can become the radius operation in rotation process, but must be to forward non-cornerite district at the reducing opening.Among the figure, the reducing opening of left side driving wheel is about to enter the cornerite district, can not carry out the reducing operation; The reducing opening of the right follower just leaves the cornerite district, can carry out the reducing operation.The coiling direction of driving wheel and follower wheel table traction belt is opposite among the figure, only in this way could guarantee that load born by hitch frame 1-1 and 1-2 fully.2 pairs of flexible pulling force of wheel table traction belt of coiling backguy, the power that this power is transmitted much smaller than variable transmission mechanism, traction belt tightens as long as this power can make the wheel table.
Fig. 6 is a variable transmission mechanism entity exploded view.This figure is the sterogram of speed change gear shown in Figure 5, has split conical disc, wheel table traction belt among the figure.As can be seen from the figure; Wheel table traction belt is wound into a circle, forms the drive wheel working surface, and the working surface of this surface and driving belt forms engagement pair.Can see by the right side follower; Wheel table lead is pulled out from the crossbeam of hitch frame bottom, is connected in the coiling backguy.The effect of the secondary conical surface 8 is set: the inoperative part of wheel table traction belt here in conjunction with Fig. 1 (a), Fig. 2 (a) and (b) explanation conical disc, be to furl backguy 2 by what end connected, be pulled to core wheel through hitch frame 1 base cross members, for the conehead pin 6 that prevents wheel table traction belt both sides is stuck on the main cone face 9, the spy is provided with the secondary conical surface 8 (see figure 2)s, to form the passageway of broad, make wheel table traction belt when coming in and going out, not have movement interference.The corresponding part of wheel table traction belt also is provided with wide pitch chain bar 12 and cooperates with the secondary conical surface 8.
Fig. 7 (a)-(c) is the assembling and the exploded view of two round end chain type wheel table traction belts.(a) and (b) are respectively the integral body and the broken away view of wheel table traction belt.Wheel table traction belt front end is connected on the hitch frame 1 by transition carrier bar 16 and towing pin 15, and end is connected on the reel 4 by furling backguy 2 by minor details 17, and there is clockwork spring caulking groove 20 reel inside, and there is backguy groove 19 outside.Wheel table traction belt structurally is divided into wide joint and narrow joint, and wide joint is made up of wide chain link 24, carrier bar 21 and conehead pin 6; Narrow joint is made up of main chain joint 22, carrier bar 21 and conehead pin 6; Two-part are connect by cranked link 23.(c) figure is a plan view, can be clearly seen that wheel table traction bandwidth joint and narrow joint, and piece mark is consistent with (a) and (b) figure among the figure.
Fig. 8 (a)-(e) is that two round end chains are the driver schematic diagram and the link configuration figure of wheel table traction belt and driving belt.(a) and (b) theory of engagement figure among the figure, (a) figure is a drive wheel radius situation hour in this example; (b) figure is the infinitely-great situation of drive wheel radius.Drive wheel adopts two round end chain type wheel table traction belts 3, and driving belt 14 also adopts the two round end chains that match with it; In transmission process, among the middle part concave arc R2 of engaging-in driving belt 14 carrier bars of carrier bar round end R01 of wheel table traction belt 3, the carrier bar round end R02 of driving belt 14 is engaging-in to take turns among the middle part concave arc R1 that shows traction belt 3 carrier bars, and the engagement pair that constitutes relies on the extruding transferring power between the carrier bar round end like this; It is smooth-going that this structure has engagement, the advantage of reliable transmission.Among the figure, all carrier bar two blunt end center of circle spacings all are L.The least radius of concave arc R1 depends on the drive wheel maximum radius, can hold round end R02 under this situation for suitable; The least radius of concave arc R2 depends on the drive wheel least radius, can hold round end R01 under this situation for suitable.Be manufacturing and easy for installation, can wheel table traction belt and the unification of driving belt chain link model, i.e. R1=R2, R01=R02.Two round end carrier bar two hole circle hearts all are on drive wheel pitch circle and the driving belt nodel line, and pitch circle and nodel line are tangent.Figure (c) and (d) be the fractionation and the ssembly drawing of basic chain link (e) is an individual sectional view, has cut main chain joint, carrier bar and conehead pin, and wherein a is the cone angle of conehead pin.
Case 2: a kind of spoke rod-type expands wheel apparatus;
Fig. 9 (a)-(f) is the structural representation that the spoke rod-type expands wheel apparatus.This expansion wheel apparatus adopts spoke bar bracing type structure: in (d) figure, wheel table traction belt 3-3 is propped up by a plurality of supports 30; With reference to figure (a), (c), spoke bar 26 two are hinged with spoke bar capstan winch 27 and support 30 respectively, and a pair of spoke bar capstan winch 27 arranges that in wheel body 25 bilateral symmetry when two dishes were mobile in opposite directions, support 30 rose, and wheel is shown traction belt 3-3 pull out, and reaches the purpose that enlarges the wheel footpath.(a) and (d) figure is the situation of wheel footpath when maximum; 1-3 is a hitch frame, slides in groove 29.(d) figure has removed wheel body.(b) and (e) figure is a wheel footpath situation hour, and (e) figure has removed wheel body 25.(c) be the situation that (d) figure takes out axle.(f) be to cut part shown in (e) figure open see situation, among the figure: the part volume that wheel table traction belt 3-3 does not participate in transmission is hidden in the hollow shaft.
Case 3: the integrated type micro-shift transmission that uses diameter-variable driving wheel;
Figure 10--Figure 24 is an integrated type micro-shift transmission for the use diameter-variable driving wheel of Automobile Design.
The transmission system of Hyundai Motor generally is made of speed changer, main reducing gear; The automobile that has also is furnished with transfer case or auxiliary transmission.The resultant gear ratio i of automobile
c=i
ki
Kzi
Kf, i in the formula
kBe transmission ratio, i
KzBe the main reducing gear velocity ratio, i
KfBe transfer case or auxiliary transmission velocity ratio.Automobile maximum transmission ratio and fastest ratio are meant i
cValue, the selection of its value has material impact to the power performance of automobile integral body.Automobile maximum transmission ratio i
Max, on car, be about 12～18, on light medium truck, be about 35～50, fastest ratio i
Min, being about 3～6 at car and pick up truck, medium and heavy lorry is about 6～15.
The integrated type micro-shift transmission that this case provides is applied on the automobile and will replaces speed changer, and saves main reducing gear and auxiliary transmission, relatively is fit to the car of front-wheel drive.This speed changer is made up of the two-stage gear, its resultant gear ratio i
c=i
qi
h, i wherein
qBe the prime transmission ratio, i
hIt is back level transmission ratio.Speed changer is provided with 37 gears, maximum transmission ratio i
MaxBe 10.2, fastest ratio i
MinBe 2.55.This 37 stage gear ratio distributes by geometric progression, and common ratio is 1.04, and this shift of transmission need not clutch, can not interrupt power and advance retaining continuously; In conjunction with simple electric controller, can realize automatic speed changing.
Below in conjunction with accompanying drawing and form this integrated type micro-shift transmission is described in detail:
Figure 13 (a) and (b) are micro-shift transmission basic driving component relative position schematic representation when maximum transmission ratio: (a) being plan view, (b) is plan view.This speed changer is composed in series by two forward and backward two-stage speed changers, only transmits unidirectional torque.The prime speed changer is formed by deciding radius driving wheel 58, driven diameter-changing wheel 3-2 and prime driving belt 56; Back level speed changer by active diameter-changing wheel 3-1, decide radius wheel follower 53 and a back grade driving belt 45 is formed.On the main shaft 60, its physical dimension was identical in the middle of two diameter-changing wheel 3-2 of forward and backward level and 3-1 were contained in same.The hitch frame of two diameter-changing wheels is respectively 1-2 and 1-1.Shown in the figure is the situation of speed changer when reaching maximum transmission ratio, and the wheel of the driven diameter-changing wheel 3-2 of prime has directly diffused into maximum, and the back level initiatively wheel of diameter-changing wheel 3-1 directly has been reduced to minimum.Arrow has been indicated driving component moving direction among the figure; The reducing opening that active hitch frame 1-1 upside and driven hitch frame 1-2 upside are respectively two diameter-changing wheel 3-1 and 3-2; The reducing opening of two diameter-changing wheels has forwarded to and the non-cornerite district of driving belt separately simultaneously among the figure, can carry out the reducing operation this moment synchronously.After the wheel footpath changed, middle main shaft was wanted horizontal left, changes two speed changer centre distance.Label and figure (a) are unified among the figure (b).
Figure 12 is micro-shift transmission inner each block diagram when maximum transmission ratio.Left side folder rises dish 69, middle double conical surface folder and rises dish 73, right folder to rise dish 70 and fork plate 55 be the main middle main shaft system that constituted.Left side folder rises dish 69, and middle double conical surface folder rises the left conical surface of dish 73, the driven diameter-changing wheel that wheel table traction belt 3-2 has constituted prime, and this is taken turns with prime driving belt 56 and driving wheel 58 and has constituted the prime speed changer; Right folder rises disc 70, and middle double conical surface folder rises the right conical surface of dish 73, has constituted the initiatively expansion wheel apparatus of diameter-changing wheel of back level.Back level diameter-changing wheel, back level driving belt 45 and follower 53 have been formed back level speed changer; When the figure illustrates speed changer and reaching maximum transmission ratio, each position component situation.When needs reduced resultant gear ratio, middle main shaft was to move along institute's target d direction among the figure; Meanwhile, the displacement of D direction takes place in shift fork guide plate 34 guiding fork plates 55, and promotes middle double conical surface folder liter dish 73 also toward the translation of D direction, and this directly reduces the driven diameter-changing wheel 3-2 wheel of prime in left side, and the initiatively diameter-changing wheel wheel footpath increase of the back level on right side; The synchronous reducing of two-wheeled reaches the purpose that changes resultant gear ratio.
Figure 10 (a)-(c) is the micro-shift transmission External view.(a) among the figure, the 39th, power input shaft, the 36th, the left half axle of pto.40,41 is respectively transfer the files rotating shaft and auxiliary spindle, and diaxon has identical rotating speed with being with 32 to interrelate synchronously; The sliding rail that skewed slot 35 is shift fork guide plates 34 at casing top; The 31st, the outlet of gear shift backguy; The 37th, counter-rotating, differential mechanism shell; 38 is cylinders, is used for controlling the pto backward rotation.(b) figure looks from the rear portion, and the general picture figure of casing, casing divide top main box body and bottom hub 42, and the back level is decided the radius follower and is loaded in the hub 42; The 43rd, the right axle shaft of pto, with left half axle 36 on an axis.(c) figure is a plan view, can be clearly seen that skewed slot 35 and shift fork guide plate 34 at the casing top, and 32 is synchronous bands among the figure.
Figure 11 (a)-(c) is micro-shift transmission partial cutaway component and bottom half sterogram.(a) figure is the partial cutaway component of speed changer.48 is gear shift devices among the figure, and a pair of thrust-bearing 51 of gear shift rotating shaft 40 usefulness is installed on the casing.Speed changer relies on the synchronous rotation of gear shift rotating shaft 40, auxiliary spindle 41 to realize gear shift operation.During gear shift, the tooth 46 that the relevant apparatus in the gear shift device 48 is stirred in the gear shift rotating shaft 40 rotates axle 40, and pin interacts in spiral chute 47 on the axle 40 and the pin cover 49, and left shaft holder 50 along continuous straight runs of main shaft move in the middle of promoting; 41 of right side auxiliary spindles promote the right bearing seat and move in the same way.45 is level driving belts behind the speed changer among the figure.(b) and (c) figure is respectively the rear oblique view and the plan view of bottom half.
Figure 14 (a)-(f) is two structural representations of deciding the radius drive wheel of micro-shift transmission.Among the figure shown in (a)-(c) is the structural drawing of driving wheel 58 among Figure 13; (c)-(f) shown in is the structural drawing of follower 53 among Figure 13.From figure (b), (c), (f) as can be seen, the pulled surface of deciding the radius drive wheel also is made of two round end chains, and available common flat-headed pin 64 connects between the chain link, and one week of wheel body evenly is furnished with pin head bayonet socket 63, and wheel table traction belt connects from beginning to end at breach 62 places.(a) and (e) be wheel body; (c) and (f) be the situation that wheel body has installed wheel table traction belt additional; (b) be the steamboat wheel body of taking wheel table traction belt apart; (d) figure has cut the bull wheel wheel body.
Figure 15--Figure 17 is the structure principle chart of main shaft system in the middle of the integrated type micro-shift transmission.
Middle main shaft is to be most important parts in the integrated type micro-shift transmission.The driven diameter-changing wheel of prime speed changer and the active diameter-changing wheel of back level speed changer are installed, and the physical dimension of two cover diameter-changing wheels is identical; Two covers expand wheel apparatus and are made of one the formula structure, with reference to Figure 12, two diameter-changing wheels expand wheel apparatus and rise dish 73 and right folder and rise dish 70 and constitute by risen dish 69, middle double conical surface folder by left side folder, and in the gear shift process, left side folder rises dish 69 and right folder and rises 70 on dish and move along the d direction with middle main shaft; And middle double conical surface folder rise dish 73 with middle main shaft when the d direction moves, also to move along the D direction, to realize the change of three awl dish 69,73,70 axial spacings, reach the purpose that changes the wheel radius.In conjunction with Figure 11, the cam that left side folder rises dish 69 avris also will drive gear shift device 48, makes the rotating shaft 40 of its group modulation retaining.The required power of speed changer gear shift obtains from middle main shaft.
Figure 15 (a)-(h) is a main shaft broken away view in the middle of the micro-shift transmission.With reference to Figure 12, this figure (c), (d), (e) are respectively that left side folder rises dish 69, middle double conical surface folder rises dish 73 and right folder rises dish 70, (h) is fork plate 55.This figure (b), (f) are a pair of thrust-bearings.(a), (g) is can be along the left and right spindle bearing holder of d direction slip.(a) among the figure, the 65th, the sliding pair of left shaft holder horizontal slip in casing; The 48th, the gear shift device; The 66th, set screw.(c) 54 and 54 ' be that left side folder rises the gear shift cam on the dish among the figure.(d), among (e) two figure, the 60th, in the middle of main shaft, 1-2 and 4-2 are respectively the hitch frame and the reels of the driven diameter-changing wheel of prime, 1-1 and 4-1 are respectively the initiatively hitch frame and the reels of diameter-changing wheel of back level.Among the figure, the driven diameter-changing wheel wheel of the prime in left side radius has diffused into maximum, and the back level on right side initiatively diameter-changing wheel wheel radius has been reduced to minimum; This is that transmission ratio reaches peaked situation.(h) figure has shown shift fork guide plate 34 and shift fork 67.
Figure 16 is the plan view of principle axis shafting in the middle of the micro-shift transmission.Middle main shaft 60 is installed in left shaft holder 50 and the right bearing seat 71 by a pair of thrust-bearing 72.Middle double conical surface folder rise dish 73 and left and right folder rise dish 69,70 be contained in same in the middle of on the main shaft 60, coiling 73 middle parts has grooving 74, shift fork 67 acts in the groove 74, can promote folder and rise dish 73 and move axially.The conical surface of conehead pin 6 rises the dish conical surface formation sliding pair that matches with folder.In the middle of being placed in, reel 4 on the main shaft 60, is in the core wheel position.Left side folder rises dish 69 1 sides two gear shift cams 54 and 54 ', and the gear shift device is installed on the left shaft holder 50, and the 40th, the gear shift rotating shaft.Upper case half 68 and bottom half 75 connect by one group of bolt 76.
Figure 17 (a) and (b) are that the folder of three on the main shaft rises the dish subdivision graph in the middle of the micro-shift transmission.(a) among the figure, the vertical section of using axis rises dish 69, middle double conical surface folder with left side folder and rises dish 73 and right folder and rise dish 70 and cut open.Folder rises the work conical surface and the grooving 74 of dish as we can see from the figure, and there is an angle of eccentricity in the relative sectional elevation with 54 ' middle part of gear shift cam 54 that left side folder rises on the dish.77-2 is that middle double conical surface folder rises the secondary conical surface in dish 73 left sides.(b) figure rises the situation that both sides, rim hitch frame chute center line is cut open with middle double conical surface folder, and the hitch frame chute of and arranged on left and right sides is not a symmetric arrangement, on card angle of cut of existence.Among the figure, 11-1,11-2 are respectively the transition inclined-planes of and arranged on left and right sides, and 77-1,77-2 are respectively the secondary conical surfaces of and arranged on left and right sides.The 78th, awl dish main cone face.
Figure 18--Figure 20 is the gear shift device structure principle chart of integrated type micro-shift transmission
The gear shift device is to realize the device that gear is regulated in the integrated type micro-shift transmission.Following elder generation illustrates basic principle in conjunction with Figure 12: it is the critical pieces that change the wheel radius that middle double conical surface folder rises dish 73, and its mobile meeting in the D direction changes the wheel footpath size of two diameter-changing wheels simultaneously.In the gear shift process, when two diameter-changing wheels wheel footpath changed on the middle main shaft, the centre distance of forward and backward two-stage speed changer also will be adjusted accordingly thereupon, and whole jack shaft is the displacement that the d direction will take place.Therefore, middle double conical surface folder rises dish 73 in the gear shift process, has the displacement of D and d both direction concurrently.
With reference to Figure 11 and Figure 12, introduce the gear shift means of speed changer here: gear shift rotating shaft 40 and auxiliary spindle 41 rotate, and can only regulate drive wheel centre distance, and main shaft moves to the d direction in the middle of making.When gear shift rotating shaft 40 was rotated, pin overlapped 49 li pin 57 effects on its spiral chute 47 and the left bearing cover 50, makes bearing housing 50 obtain the power that the d direction moves.Gear shift device 48 rises to coil from left side folder and obtains to regulate the required power of gear 69 cams that rotate, can gearshift continuously under the situation of not interrupting the power normal delivery.
Figure 18 (a) and (b) are micro-shift transmission gear shift device sterogram and plan view.(a) figure is the sterogram of gear shift device, the 79th, and gear shift device cover plate; Gear shift rotating shaft 40 is passed from gear shift device middle part through hole; The gear shift device is laterally zygomorphic parts, and two gear shift push rods that can move back and forth are arranged, and push rod cup 84 ' locates to be equipped with rectangle spring 83, and gear shift pressing plate 81 can will be sold 82 synchronously and depress under the pulling of gear shift backguy 80.(b) figure is a gear shift device plan view, gear shift device up-down structure symmetry.The gear shift process is as follows: during the speed changer running, and gear shift push rod 84 to-and-fro motion under the cam that rotates promotes; When not needing gear shift, pin is upspring under spring action synchronously, and claw plate 91 is motionless; When the needs gear shift, gear shift backguy 80 pulling gear shift plates 81 press down synchronous pin, and when synchronous pin snapped in the breach of claw plate 91, claw plate 91 was driven slippage left, and in this process, ratchet 86 will promote the tooth 46 in the gear shift rotating shaft, and the gear shift rotating shaft is rotated.When needs gear shift rotating shaft backward rotation, can operate the identical device in separated time below in the device of transferring the files.Because of kinetic property is opposite fully, two parts mechanism of transferring the files does not allow to operate simultaneously up and down.
Figure 19 is micro-shift transmission gear shift rotating shaft and auxiliary spindle and corresponding annex map.Transfer the files to have on tooth 46, spiral chute 47, the gear shift device auxiliary spindle 41 in the device rotating shaft 40 and have only spiral chute 86, diaxon is by being with 32 transmissions synchronously, its synchronization.33 is synchronous pulleys among the figure, the 44th, be with back-up ring synchronously.Diaxon is installed on the casing by low thrust bearing 51.Interactional with spiral chute is a transmission pin 57, and this part is fixing with a screw 87.Bearing 51 usefulness collars 89 are fixing.
Figure 20 (a)-(c) is a micro-shift transmission gear shift device subdivision graph.(a) figure is an overall diagram, (b) is subdivision graph, by seeing push rod 84 among this figure, claw plate 91 and ratchet 86.(c) the further subdivision of figure push rod, can see the narrow groove on synchronous pin 82, spring 90 and the claw plate 91 that is mounted thereon, sell 82 synchronously and can just head into this groove, head into rear push-rod and will drive claw plate 91 and move.
Figure 21 is micro-shift transmission inner each block diagram when fastest ratio.Situation when contrasting maximum transmission ratio shown in Figure 12, transmission ratio are in being changed to minimum process by maximum, middle main shaft system has been moved horizontally to back stop along the d direction; Middle double conical surface folder rises the effect that dish 73 is subjected to shift fork 67, has moved to right stop along the D direction, and the driven diameter-changing wheel wheel of the prime in left side radius fades to minimum by maximum; The back level on right side initiatively diameter-changing wheel wheel radius fades to maximum by minimum.Decide the relative position relation between radius driving wheel 58, prime driving belt 56 and the back level driving belt 45 as can be seen from FIG..
Figure 22 (a) and (b) are micro-shift transmission basic driving component relative position schematic representation when fastest ratio.(a) arrow has been indicated transmission direction among the figure; Be positioned at the driven diameter-changing wheel hitch frame of prime 1-2, back level initiatively the reducing opening of diameter-changing wheel hitch frame 1-1 one side all be in and the non-cornerite district of driving belt separately, can carry out the reducing operation simultaneously.(b) figure is a plan view, and corresponding (a) figure can see the position of hitch frame 1-1 and hitch frame 1-2.
Figure 23 (a) and (b) are micro-shift transmission relative dimensions schematic diagram datas.Figure (a) has marked important sized data: during 1 retaining, middle spindle axis is positioned at the o1 place, and the driven diameter-changing wheel wheel of prime this moment radius maximum is 229.26,72 pitch chains joint on the pitch circle, and prime centre distance o1o3 is 304, back level centre distance o1o4 is 674.96.During the 37th retaining, middle spindle axis is positioned at the o2 place, and back level active this moment diameter-changing wheel wheel radius becomes maximum, is 229.26,72 pitch chains joint on the pitch circle, and the value of prime centre distance o2o3 is 533.93, the value of back level centre distance o2o4 is 510.
Circle o3 is the pitch circle that prime is decided the radius driving wheel, and this has taken turns 16 pitch chains joint, and Pitch radius is 51.26; Circle o4 is the pitch circle that the back level is decided the radius follower, and this has taken turns 82 pitch chains joint, and Pitch radius is 261.08.The pitch of all two round end chain chain links all is 20 among the figure.Drawn 37 lines altogether between from o1o4 to o2o4 among the figure, indicated from 1 and kept off the shift processes of 37 retainings 37 corresponding centre distance of back level.(b) figure has shown that with partial view middle double conical surface folder rises dish in the position of middle main shaft, has represented among the figure that when 1 retaining, the back level on the driven diameter-changing wheel of the prime in left side, right side is the position of the wheel watch chain joint of diameter-changing wheel initiatively.The step cone footpath is maximum before this moment, and Pitch radius is 229.26, and wheel watch chain number successively is 72 joints; Back step cone footpath is minimum, and Pitch radius is 114.74, and wheel watch chain number successively is 36 joints.The right side is also indicated when the 37th keeps off with dotted line among the figure, the position that middle double conical surface folder rises dish.It is consistent that d among the figure among d and D and Figure 12, Figure 21 and D mark direction.
Figure 24 is the counter-rotating and the differential mechanism of micro-shift transmission clutch end.Left end planet carrier 94 among the figure, planet wheel 100, planet wheel shaft 93 and left and right two semiaxis 36,43 have constituted differential mechanism; Planet wheel shaft 101, right-hand member planet carrier 102, planet wheel 103 have constituted inversion component.104 is two-sided thread form dishes, be installed on the splined shaft of planet carrier 102 ends and can move axially, thread form dish 104 has three positions, left, center, right, when being in position, a left side, combine with shell 37, planet carrier 102 is fixed, the power of power output disc 105 through planet wheel 103 oppositely after, pass on the differential carrier 94; When thread form dish 104 was in right, oppositely assembly 101,102,103 rotated synchronously with power output disc 105, does not play acting in opposition; When thread form dish 104 is in meta, be equivalent to neutral, left and right two semiaxis 36,43 are because of the load effect stops, and planet carrier 102 rotates.Two-sided thread form dish 104 is by operating handle 95 controls, and its power comes from cylinder 38,52nd, air pipe interface.99 is needle bearing among the figure, the 42nd, and cabinet shell.
The integrated type micro-shift transmission that this case is introduced is integrated the expansion wheel apparatus of forward and backward two-stage diameter-changing wheel, and shared middle double conical surface folder rises dish and makees expansion wheel power plant; A shared cover gear shift device.This only possesses the condition of synchronous adjustment for different two-stage speed changers, could illustrate that design proposal is feasible.Below provide a form, speed changer is listed in the key data of 37 gears, in conjunction with the accompanying drawings 12, the feasibility of accompanying drawing 21 and accompanying drawing 23 proof design proposals.
The possibility of adjusting synchronously on the D direction at first is described;
According to mentality of designing, the driven diameter-changing wheel of prime has identical physical dimension with back level active diameter-changing wheel, two round end chain chain link mobility scales of two-wheeled wheel table all are 36 joints～72 joints, prime from 36 the joint increase to 72 the joint in, the back level is then reduced to 36 joints from 72, every increase by one joint of prime, the back level will reduce by a joint accordingly.Here counting statistics the numerical value that moves to left of telophragma (D direction), the result shows; Wheel watch chain joint whenever increases, subtracts a joint, and the axial displacement of telophragma is just with a fixed value change, and this value is exactly the D in the table
n-D
N-1, from table, can see D
n-D
N-1Value be fixed on 0.89～0.90.As seen, prime diameter-changing wheel wheel watch chain successively number increase, subtract the just compensation mutually of axial displacement that a joint was reduced, increased to a joint and a back level diameter-changing wheel wheel watch chain.So the diameter-changing wheel of two-stage speed changer can simultaneously operating in the D direction.
Secondly the possibility of adjusting synchronously on the d direction is described:
When the synchronous reducing of forward and backward two-stage diameter-changing wheel, two-stage speed changer centre distance separately also changes simultaneously.If middle main shaft that will move and motionless master and slave moving axis are arranged on the line, so when two diameter-changing wheel synchronous change wheel footpaths on the middle main shaft, the corresponding increase of centre distance meeting of two-stage speed changer, one reduces, be complementary on direction, but quantitatively can not compensate mutually, as can be seen from the table; As prime diameter-changing wheel joint number Z
1Increased in the process of 72 joints by 36 joints, prime centre distance d increases to 533.93 by 304, and value added is 229.93; Back level diameter-changing wheel joint number Z2 reduces to 36 joints by 72, and back level centre distance has reduced to 510 by 674.96, and reducing value is 164.93, and it increases, depreciation does not wait; In addition, number is in the process with the integer increase and decrease successively for diameter-changing wheel wheel watch chain, and each keeps off the also non-definite value of center distance tolerance; Preceding stage is an example, its center distance tolerance d
n-d
N-1Be exactly a variable, do not wait by 5.44 of 8.46 to 37 corresponding retainings of 2 retainings.
Above-mentioned contradiction can adopt the way of back level sizing follower below-center offset to be solved.Shown in Figure 23 (a); Will counterclockwise deflection 53 degree of the back relative horizontal line of level speed changer centre distance line o2o4.Like this, 1 retaining centre distance 674.96 and 37 retaining centre distance 510 at first are satisfied.Calculated data shows that after the level sizing wheel o4 below-center offset of back, if main spindle's in the middle of determining apart from the requirement of d according to prime speed changer computer center fully, the back level also can guarantee substantially in the centre distance of each gear so.Below use data declaration: in the reducing process, forward and backward level driving belt joint number is certain, is respectively 80 joints and 128 joints in this programme.According to back level diameter-changing wheel wheel watch chain number, driven sizing wheel wheel watch chain number and driving belt joint number successively successively initiatively, grade centre distance after just determining, this is referred to as theoretical center apart from l; And in fact, the position of middle main shaft determines that according to the centre distance of prime speed changer back level speed changer centre distance is passive definite, is called operating center distance s at this.Calculating shows: except that 1 retaining and 37 retainings, the value of l and s is also inequality; The operating center distance s of back level speed changer always less than theoretical center apart from l, a level driving belt will relax after the institute.The l of each gear correspondence
n-s
nValue to be called centre distance in shortage.To each retaining l
n-s
nValue is analyzed discovery, and this value increases with gear, is to increase the trend that afterwards subtracts earlier, and it reaches at 17 grades and is worth 15.82 most.Therefore find out that in conjunction with Figure 23 this is worth less than driving belt chain link pitch 20, can think that the back level driving belt slack that is caused by this value is little to the influence of transmission, can ignore.Support the reason of this argument to also have: 1, each wheel wheel footpath of back level speed changer is big, and wheel watch chain number successively is many, and driving belt and drive wheel cornerite are bigger; Contact points is more.2, this case belongs to the engagement type type of belt drive in the mechanical transmission, and is different with the speed changer of frictionally transmission, not enough and insensitive to the trace of centre distance.
The integrated type micro-shift transmission has the following advantages:
1. simple in structure, in light weight, cost is low.
2. the conversion gear does not need the cooperation of clutch, does not interrupt the normal delivery of power;
3. gear is close, and the velocity ratio common ratio is little, near the transmission effect of stepless speed variator;
4. mesh steadily between two round end carrier bars, reliable transmission can be transmitted big power;
5. main shaft drives gear shift mechanism need not the external world gear shift power is provided in the middle of utilizing;
6. can realize automatic speed changing in conjunction with simple electric controller;
Use the integrated type micro-shift transmission, can improve the fuel economy of automobile.Compare the same automobile that other speed changer is installed, have ready conditions and use the motor of smaller power.The imagination motor always operates at the rotation speed n that it sends peak output
pDown, as long as transmission ratio i
gCan be with speed of a motor vehicle u
aIn time adjust.The power of motor will be by the utilization of fullest.The integrated type micro-shift transmission needs to realize automatic speed changing in conjunction with simple electric controller; According to top imagination, the corresponding vehicle speed range of each velocity ratio, when the speed of a motor vehicle departs from corresponding velocity ratio, electric controller will be exchanged lug-latch and send the gear shift signal, the gear shift device will obtain the gear shift required drive from middle main shaft, finishes the gear shift operation in the process that transmission is normally carried out.
The on-stream gear shift operation of carrying out of integrated type micro-shift transmission energy does not need the cooperation of clutch, but clutch still is necessary, and at power intake a kind of double-action clutch is installed preferably.The function of the subsidiary viscosity clutch of said double-action clutch.When this clutch gently touched on the brake the pedal deceleration the driver, power also not exclusively interrupted, and clutch enters a kind of viscosity bonding state: the two ends combination force reduces; Allow big speed discrepancy.Clutch just separates fully when the driver is left behind the hand brake or Emergency braking, interrupts power.Adopt this device to be because: when when brake, the speed of a motor vehicle must reduce, and this requires the corresponding adjusting of integrated type micro-shift transmission velocity ratio is increased, for automobile quicken once more provide big starting torque to prepare.Because of the gear shift power of micro-shift transmission is taken from middle main shaft.This speed changer has the characteristics of unidirectional transmission; main shaft does not have the trend of counter-rotating in the middle of not allowing, and therefore when brake deceleration, the front end clutch needs by the adhesive bond function; the identical force direction that is subjected to when main shaft keeps with normal transmission in the middle of making can guarantee that so just gear shift operation carries out smoothly.
The speed governing characteristics of integrated type micro-shift transmission are; During gear shift, middle main shaft whenever turns around, the upper and lower adjustment of gear one retaining, and when fastest ratio 2.55 was transferred to maximum transmission ratio 10.2, main shaft rotated 37 circles in the middle of needing.A kind of situation is arranged: when running into Emergency braking here, pto may locking, middle main shaft has no chance to rotate 37 circles, at this moment just need be by rear end engaging and disengaging gear (seeing Figure 24), thread form dish 104 is placed the neutral position, make back level follower 53 break away from being connected of wheel after, finish gear shift again and operate, after velocity ratio adjusted to the required low gear of starting, vehicle was started to walk, is quickened.
The micro-shift transmission gearshift is carried out step by step, and this retaining mode of advancing of not interrupting power more becomes steadily with reliable transmission.
It may be noted that above a kind of variable drive wheel and this transmission device of taking turns of use of taking turns the footpath of having described, wherein the drive wheel working surface is the banded pulled surface with engagement pair proterties.Yet, it is contemplated that the pulled surface of other material and proterties also can constitute the pulled surface of this drive wheel.Therefore, meeting the various variable of the aforementioned principle of the invention takes turns the drive wheel in footpath and uses this transmission device of taking turns to be also contained in the scope of the present invention.
Claims (10)
1. diameter-variable driving wheel is by hitch frame (1), wheel table traction belt (3), expand wheel apparatus and the wheel apparatus that contracts is formed; Wherein hitch frame (1) is installed on the wheel body (5), and can move radially thereon; (3) one of traction belts of wheel table are connected on the hitch frame (1), and the axis coiling of (7) forms the drive wheel working surface around the shaft, and wheel table traction belt (3) passes through the transmission that hitch frame (1) is realized moment with wheel body (5); Under the cooperation of expanding the wheel apparatus and the wheel apparatus that contracts, hitch frame (1) moves radially on wheel body (5), to change the size of the arm of force between wheel table traction belt (3) and the rotating shaft (7), wheel table traction belt (3) is regulated the length that it participates in transmission with the change of hitch frame (1) position, reaches the purpose that changes drive wheel surface perimeter and drive wheel wheel radius.
2. diameter-variable driving wheel as claimed in claim 1 is characterized in that: described hitch frame (1) has the V-arrangement frame structure, and it is installed in the oblique hitch frame chute (10) on the wheel body (5); (3) one of wheel table traction belts are connected on the hitch frame (1) by towing pin (15), and the other end is connected with the backguy (2) that furls of the wheel apparatus that contracts by minor details (17); Interface at hitch frame (1) one side, wheel table traction belt coiling circumference is the reducing opening, and the reducing opening will be taken turns table traction belt (3) and is divided into working portion and inoperative part, and working portion coiled one circle forms the drive wheel working surface; Inoperative is partly reeled and is stored on the core wheel reel (4); The working surface that wheel table traction belt (3) participates in transmission is engagement or the friction surface with transmission agency; Hitch frame (1) in the determining positions of wheel on (5) radial line the size of diameter-changing wheel transmission pitch circle; Wheel table traction belt (3) changes wheel table girth according to the length of corresponding its working portion of adjusting of pitch circle size with the wheel change in radius.
3. diameter-variable driving wheel as claimed in claim 1, it is characterized in that: described expansion wheel apparatus adopts a kind of cone disk type folder to rise mechanism, rise dish (5) and rotating shaft (7) is formed by a pair of tapered clamp, the working surface that folder rises dish is a conical surface (9), and this conical surface and wheel table traction belt (3) be the conical surface of conehead pin (6) the formation sliding pair that matches upward; When the drive wheel Pitch radius need enlarge, two folders rise dish (5) and move in opposite directions along rotating shaft (7) axis, the reducing of its axial spacing makes conehead pin (6) rise dish (5) radial force at folder, and driven wheel table traction belt extends out to the wheel edge, reaches the purpose that increases the wheel footpath with this; The described wheel apparatus that contracts is formed by being connected in the terminal reel (4) that furls backguy (2) and be placed in the rotating shaft (7) of wheel table traction belt (3); In the clockwork spring caulking groove (20) of reel inside clockwork spring is housed, reel (4) is rotated with respect to rotating shaft (7).
4. diameter-variable driving wheel as claimed in claim 1 or 2 is characterized in that: the described table traction belt (3) of taking turns adopts two round end chain type tractive bands, and it saves (22) and two round end carrier bar (21) and conehead pin (6) by two round end main chains is that the master constitutes; Wheel table traction belt divides wide joint (12) and narrow joint (13) two-part from structure, and two-part connect with cranked link (23); Each chain link has identical cross section; The radius of arc of its two ends round end (R01) is identical, and concave arc (R1) is in the middle part, two blunt end circle centre position perforates, and each chain link hole thus connects into chain by pin (6).
5. diameter-variable driving wheel as claimed in claim 1, it is characterized in that: described expansion wheel apparatus can adopt spoke bar bracing type structure, wheel table traction belt (3-3) is propped up by support (30), spoke bar (26) two is hinged with spoke bar capstan winch (27) and support (30) respectively, a pair of spoke bar capstan winch (27) arranges that in the wheel body bilateral symmetry when two dishes were mobile in opposite directions, support (30) rose, to take turns table traction belt (3-3) and pull out, reach the purpose that enlarges the wheel footpath, increases wheel table girth.
6. transmission device, it uses diameter-variable driving wheel as claimed in claim 1 or 2, utilizes diameter-changing wheel and middle driving belt (14) can constitute variable speed drive; When deciding the radius wheel with a diameter-changing wheel and one and form variable speed drive, two-wheeled centre distance can be taken turns the corresponding adjustment of variation of radius with diameter-changing wheel; Diameter-changing wheel can be used as driving wheel or follower arbitrarily; Diameter-changing wheel goes to the non-cornerite zone of middle driving belt (14) at its reducing opening and expands wheel or the reducing operation of the wheel that contracts.
7. transmission device as claimed in claim 6 is characterized in that: diameter-variable driving wheel is a wheel table traction belt (3) with two round end chains, two round end chains (14) of pitch such as uses to make driving belt, constitutes the adjustable micro-shift transmission of velocity ratio trace; Diameter-changing wheel can change the wheel radius in transmission; In this process, constitute the two round end chain chain links of a circle of drive wheel working surface, its joint number is integer and changes with integer all the time; In transmission process, in the middle concave arc (R2) of the engaging-in driving belt of carrier bar round end (R01) (14) carrier bar of wheel table traction belt (3); The carrier bar round end (R02) of driving belt (14) is engaging-in takes turns in the middle concave arc (R1) of showing traction belt (3) carrier bar, and the engagement pair of Gou Chenging relies on the extruding transferring power between the carrier bar round end like this; Two round end carrier bar two hole circle hearts all are on drive wheel pitch circle and the driving belt chain link nodel line, and pitch circle and nodel line are tangent.
8. as claim 6 or 7 described speed changers, it is characterized in that: described two micro-shift transmissions can be composed in series the integrated type micro-shift transmission that is made of forward and backward two-stage micro-shift transmission; The shared cover gear shift device of prime speed changer and back level speed changer is regulated gear; On the main shaft (60), its physical dimension was identical, two diameter-changing wheel synchronous change transmission radius in the middle of the diameter-changing wheel of two-stage speed changer was installed in same; The prime speed changer is done driving wheel to decide radius wheel (58), and diameter-changing wheel (3-2) is made follower; Back level speed changer is done driving wheel with diameter-changing wheel (3-1), decides radius wheel (53) and does follower; Driving wheel (58) and follower (53) are fixed on the housing, and two diameter-changing wheels also move horizontally to adjust two-stage speed changer centre distance separately with middle main shaft (60) when carrying out the reducing operation; Follower (53) is with respect to the oblique inferior offset of horizontal alignment.
9. integrated type micro-shift transmission as claimed in claim 8, it is characterized in that: described two diameter-changing wheel coaxial arrangement, the expansion wheel apparatus of two cover diameter-changing wheels is as one, and it coils (69) by rising at the left side of middle main shaft (60) axial restraint folder, right side folder rises dish (70) and can press from both sides liter dish (73) at the axially movable middle double conical surface of middle main shaft (60) and form; Two radius crossing two diameter-changing wheel reducing openings respectively have fixed angle, and this can be in and the non-cornerite district of driving belt separately two-wheeled reducing opening simultaneously in the several angle scope, in this angular range, can carry out the reducing operation simultaneously to two-wheeled; When regulating gear, gear shift rotating shaft (40) and gear shift auxiliary spindle (41) rotate synchronously, and main shaft (60) occurred level moves in the middle of driving, and two cover speed changers master and slave drive wheel centre distance separately also is changed simultaneously; Main shaft was fastened in the middle of fork plate (55) was installed in, slide in the oblique chute (35) of the shift fork guide plate (34) on its top on casing, under the middle main shaft (60) of horizontal motion drives, the shift fork (67) of fork plate (55) lower end promotes middle double conical surface folder liter dish (73) and axially is subjected to displacement along middle main shaft (60), reaches the purpose of regulating two diameter-changing wheel Pitch radiuss simultaneously.
10. integrated type micro-shift transmission as claimed in claim 8 or 9, it is characterized in that: described micro-shift transmission relies on gear shift device (48), obtains the gear shift required drive from middle main shaft system; The left side folder that middle main shaft is fastened rises dish (69) avris two gear shift cams (54,54 '), and it promotes pair of push rods (84) to-and-fro motion on the gear shift device (48) in rotation process; When the needs gear shift, gear shift backguy (80) pulling gear shift plate (81) presses down synchronous pin (82), when synchronous pin snaps in the breach of claw plate (91), claw plate (91) is driven occurred level by push rod (84) and moves, in this process, ratchet (86) will promote the tooth (46) in the gear shift rotating shaft (40), and gear shift rotating shaft (40) is rotated; Gear shift rotating shaft (40) utilizes synchronously again, and band (32) drives gear shift auxiliary spindle (41); Gear shift rotating shaft (40) and auxiliary spindle (41) be when rotating synchronously, the spiral chute on it (47) and (58) be fixed on a pair of pin (57) effect that main shaft is fastened, main shaft (60) occurred level moves in the middle of common the promotion, realizes gear shift operation; When needs gear shift rotating shaft backward rotation, can operate the identical device in separated time below in the device of transferring the files; Gear shift device (48) two mechanisms of transferring the files up and down can not be operated simultaneously.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2005100710177A CN1865733A (en) | 2005-05-20 | 2005-05-20 | Diameter-variable diving wheel and driving mechanism equipped therewith |
| PCT/CN2006/001043 WO2006122507A1 (en) | 2005-05-20 | 2006-05-19 | Variable-dimeter transmission wheel, speed-varied device and automatic stepless transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
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| CNA2005100710177A CN1865733A (en) | 2005-05-20 | 2005-05-20 | Diameter-variable diving wheel and driving mechanism equipped therewith |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200610080816 Division CN1880804A (en) | 2005-05-20 | 2005-05-20 | Diameter-variable driving wheel and full-automatic micro-shift transmission |
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| Publication Number | Publication Date |
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| CN1865733A true CN1865733A (en) | 2006-11-22 |
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| CNA2005100710177A Pending CN1865733A (en) | 2005-05-20 | 2005-05-20 | Diameter-variable diving wheel and driving mechanism equipped therewith |
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| CN (1) | CN1865733A (en) |
| WO (1) | WO2006122507A1 (en) |
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| DE4111195A1 (en) * | 1990-04-14 | 1991-10-17 | Gerd Korge | Multistaged switch gear - consists of gear rim with auxiliary gear rim, with drive chain or belt and links |
| WO1998011364A1 (en) * | 1996-09-09 | 1998-03-19 | Enrico Nino | A stepless speed change gear |
| JP2000046133A (en) * | 1998-07-24 | 2000-02-18 | Kenji Mimura | Speed change gear |
| DE19918760A1 (en) * | 1999-04-24 | 2000-10-26 | Volkswagen Ag | Infinitely variable transmission for motor vehicles has transmission chain engaging around shaft in polygonal shape, and small planet wheels in corners of polygon |
| FR2797670B1 (en) * | 1999-08-17 | 2001-12-14 | Ameris Internat Business | SPEED VARIATION MOTION TRANSMISSION DEVICE |
| DE10010741A1 (en) * | 2000-03-04 | 2002-04-04 | Volkswagen Ag | Infinitely variable change-speed gear esp. for motor vehicles has drive wheel with two facing taper wheels at adjustable axial distance and connected to torque-holding hub of drive wheel |
| AU2002360863A1 (en) * | 2001-11-16 | 2003-05-26 | Johannes Jacobus Naude | Infinitely variable transmission machine |
-
2005
- 2005-05-20 CN CNA2005100710177A patent/CN1865733A/en active Pending
-
2006
- 2006-05-19 WO PCT/CN2006/001043 patent/WO2006122507A1/en active Application Filing
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| CN104343914A (en) * | 2014-09-16 | 2015-02-11 | 谢瑞成 | Variable-speed transmission mechanism for relay transmission of variable-diameter gears |
| CN104763789A (en) * | 2015-02-08 | 2015-07-08 | 北京工业大学 | Oscillating-tooth infinitely variable speed transfer case |
| CN106286776A (en) * | 2015-06-10 | 2017-01-04 | 但永强 | Flat thread adjustable type variable external diameter belt pulley |
| CN107269791A (en) * | 2017-04-24 | 2017-10-20 | 沈阳理工大学 | A kind of linear velocity half-convergency speed mode buncher |
| CN108869698A (en) * | 2018-07-16 | 2018-11-23 | 东阳市天齐科技有限公司 | Synchronous wheel construction |
| CN108869698B (en) * | 2018-07-16 | 2020-02-07 | 深圳市仕瑞达自动化设备有限公司 | Synchronous wheel structure |
| CN109139834B (en) * | 2018-10-30 | 2024-05-24 | 赵良红 | Variable-diameter transmission disc, control mechanism thereof and variable-speed transmission device |
| CN109139834A (en) * | 2018-10-30 | 2019-01-04 | 赵良红 | A kind of variable-diameter drive plate and its control mechanism, speed change transfer device |
| CN110644488A (en) * | 2019-09-26 | 2020-01-03 | 侯德萌 | Transmission ratio adjustable equidistance pile driver |
| CN110541925A (en) * | 2019-09-29 | 2019-12-06 | 梁恩 | Stepless speed variator |
| CN110541925B (en) * | 2019-09-29 | 2024-04-12 | 梁恩 | Continuously variable transmission |
| WO2021115024A1 (en) * | 2019-12-10 | 2021-06-17 | 郑福建 | Variable-diameter chain ring wheel and variable-diameter chain ring wheel transmission |
| CN110985636A (en) * | 2019-12-10 | 2020-04-10 | 郑福建 | Reducing chain ring wheel and reducing chain ring wheel transmission |
| CN114857226A (en) * | 2022-01-21 | 2022-08-05 | 谭钢 | Electric stepless automatic transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2006122507A1 (en) | 2006-11-23 |
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