CN106662230A - Continuous variable transmission with uniform input-to-output ratio that is non-dependent on friction - Google Patents
Continuous variable transmission with uniform input-to-output ratio that is non-dependent on friction Download PDFInfo
- Publication number
- CN106662230A CN106662230A CN201480079073.2A CN201480079073A CN106662230A CN 106662230 A CN106662230 A CN 106662230A CN 201480079073 A CN201480079073 A CN 201480079073A CN 106662230 A CN106662230 A CN 106662230A
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- China
- Prior art keywords
- gear
- input
- input disc
- tooth bar
- bunchers
- Prior art date
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Classifications
-
- 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
- F16H35/00—Gearings or mechanisms with other special functional features
- F16H35/02—Gearings or mechanisms with other special functional features for conveying rotary motion with cyclically varying velocity ratio
-
- 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
- F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
- F16H29/20—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action the intermittently-acting members being shaped as worms, screws, or racks
-
- 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
- F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
- F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
- F16H19/04—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack
- F16H19/043—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack for converting reciprocating movement in a continuous rotary movement or vice versa, e.g. by opposite racks engaging intermittently for a part of the stroke
-
- 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
- F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
-
- 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
- F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
- F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
-
- 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
- F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
- F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
- F16H29/08—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of the path of movement, the location of the pivot, or the effective length, of an oscillating connecting member
-
- 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
- F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
- F16H29/12—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between rotary driving and driven members
- F16H29/14—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between rotary driving and driven members in which the transmission ratio is changed by adjustment of an otherwise stationary guide member for the intermittently-driving members
-
- 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
- F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
- F16H29/12—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between rotary driving and driven members
- F16H29/16—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between rotary driving and driven members in which the transmission ratio is changed by adjustment of the distance between the axes of the rotary members
- F16H29/18—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between rotary driving and driven members in which the transmission ratio is changed by adjustment of the distance between the axes of the rotary members in which the intermittently-driving members slide along approximately radial guides while rotating with one of the rotary members
-
- 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
- F16H35/00—Gearings or mechanisms with other special functional features
- F16H2035/003—Gearings comprising pulleys or toothed members of non-circular shape, e.g. elliptical gears
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/15—Intermittent grip type mechanical movement
- Y10T74/1503—Rotary to intermittent unidirectional motion
- Y10T74/1508—Rotary crank or eccentric drive
- Y10T74/1515—Rack and pinion transmitter
- Y10T74/1516—Adjustable throw
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
Abstract
The main object of this invention is to provide a uniform and steady output, when the input is uniform and steady, with the ability to transmit high torque without depending on friction or friction factor. Many of the continuous variable transmissions that is in the market today are friction dependent therefor lacks the ability to transmit high torque. Those continuous variable transmissions, which are non-friction dependent does not have a uniform and steady output when the input is uniform and steady. This design aids reduction in the overall size and economically mass produced. This design can be easily integrated into any system. This design is very versatile and can be used ranging from light duty to heavy duty. This design allows replacement of existing regular transmission, requiring very little modification. This design offers the option of stationary co-axial input and output.
Description
Cross-Reference to Related Applications
Provisional application
Application number：61788563
Title：Buncher
Background technology
Patent US 5603240 and US 20100199805 use some features used in the design.
Advantages of the present invention includes：
Patent US 5603240 is not coaxially input to output, therefore cannot be used for needing the application of the configuration.Output with
Gear ratio change and move.Therefore, the design can not be used when fixed output is needed.New invention provides fixed and coaxial
Input and output shaft.Envelope (envelope) used in prior art is much greater.
US 20100199805 provides a kind of sine output, and using several modules, is intended merely to providing stable and equal
" ripple (ripple) " is caused to minimize during even input.Therefore, can not use when needs are stablized and uniformly export and be somebody's turn to do
Design.New invention input for it is stable and uniform when provides stable and uniformly exports.This can pass through as little as 3 modules
Realize.
The content of the invention
The main object of the present invention be input for it is uniform stably when uniform stable output is provided, with not
The ability of transfer high torque by friction or coefficient of friction.In the market many bunchers depend on friction, therefore
Lack the ability of transfer high torque.Those bunchers for not relying on friction do not have when input is uniform stable
Uniform stable output.The design helps reduce overall size, and economically contributes to a large amount of productions.This is designed to hold
Change places and be incorporated to any system.The design is very general, and use range can be from light load to heavy load.The design allows to replace
Existing conventional transmission device is changed, and needs very little modification.The design provides the coaxial input of fixation and the selection of output.
Description of the drawings
Fig. 1-CVT general assembly part perspective views；
CVT general assembly part perspective views during Fig. 2-make frame transparent, show part inside sub-assemblies it is total
Body is configured；
Fig. 3-frame-same section of main housing-two is bolted at together to form a main housing：
A. it is shown specifically the perspective view of main housing side；
B. it is shown specifically the perspective view of main housing opposite side；
Fig. 4-frame-extension sleeve guide (Guide) perspective view；
Fig. 5-frame-intersection tooth bar guide perspective view；
Fig. 6-input shaft perspective view；
Fig. 7-intermediate gear shaft perspective view；
Fig. 8-power connection shaft perspective view；
Fig. 9-support shaft perspective view；
Figure 10-show intersects two perspective views of tooth bar assembly and orthographic projection view, show in detail input axial trough and
Crank cotter way, the orientation of tooth bar, show in detail prong (prongs)：
A- top views；
B- has an X-rayed Fig. 1；
C- has an X-rayed Fig. 2；
D- front views；
E- side views；
F- rearviews；
G- is shown specifically the enlarged drawing from prong；
Figure 11-little gear：
A- front views；
B- side views；
C- top views；
D- perspective views；
Figure 12-pinion shaft：
A- front views；
B- side views；
C- perspective views；
Fig. 5-frame-intersection tooth bar guide perspective view；
Fig. 6-input shaft perspective view；
Fig. 7-intermediate gear shaft perspective view；
Fig. 8-power connection shaft perspective view；
Fig. 9-support shaft perspective view；
Figure 10-show intersects two perspective views of tooth bar assembly and orthographic projection view, show in detail input axial trough and
Crank cotter way, the orientation of tooth bar, show in detail prong (prongs)：
A- top views；
B- has an X-rayed Fig. 1；
C- has an X-rayed Fig. 2；
D- front views；
E- side views；
F- rearviews；
G- is shown specifically the enlarged drawing of prong；Figure 11-little gear：
A- front views；
B- side views；
C- top views；
D- perspective views；
Figure 12-pinion shaft：
A- front views；
B- side views；
C- perspective views；
Figure 20-speed compares cam：
A- front views；
B- top views；
C- perspective views；
Figure 21-non-circular gear (driven)：
A- top views；
B- front views；
C- perspective views；
Figure 22-non-circular gear (active)：
A- top views；
B- front views；
C- perspective views；
Figure 23-imitated (Dummy) crank-pin：
A- top views；
B- front views；
C- perspective views；
Figure 24-crank-pin：
A- top views；
B- front views；
C- side views；
D- perspective views；
Figure 25-middle circle gear C 2-C3：
A- front views；
B- side views；
C- perspective views；
Figure 26-supporting gear C4a-C5b：
A- front views；
B- side views；
C- perspective views；
Figure 27-middle circle gear C 4-C5：
A- front views；
B- side views；
C- perspective views；
Figure 28-middle circle gear C 1：
A- front views；
B- side views；
C- perspective views；
Figure 29-pad (Spacer)：
A- front views；
B- top views；
C- perspective views；
Figure 30-for the gear shift control-rod (Lever) of spiral groove mechanism：
A- front views；
B- side views；
C- top views；
D- perspective views；
Figure 31-helicla flute：
A- front views；
B- side views；
C- perspective views；
Figure 32-static differential lasso：
A- front views；
B- side views；
C- sectional views；
D- perspective views；
Figure 33-dynamic differential lasso：
A- front views；
B- side views；
C- sectional views；
D- perspective views；
The perspective view of Figure 34-sleeve-input-oblique；
Figure 35 to 43- shows the motion/position on tooth bar assembly, and crank-pin is with input disc spins：Show each
The individual stage：
Closer to axis, input disc is 0 ° to Figure 35-crank-pin；
Closer to axis, input disc is 45 ° to Figure 36-crank-pin；
Closer to axis, input disc is 90 ° to Figure 37-crank-pin；
At midpoint, input disc is 0 ° to Figure 38-crank-pin；
At midpoint, input disc is 45 ° to Figure 39-crank-pin；
At midpoint, input disc is 90 ° to Figure 40-crank-pin；
Figure 41-crank-pin is farthest from gear, and input disc is 0 °；
Figure 42-crank-pin is farthest from gear, and input disc is 45 °；
Figure 43-crank-pin is farthest from gear, and input disc is 90 °；
Exploded view-the perspective view of Figure 44-description Introduced Malaria, is shown specifically non-circular gear and idler gear to input disc
Configuration and gear train；
Figure 45 to 46- speed shows how cam changes the back of the body that pins position is put than the perspective view of cam, input disc and crank-pin
After operate：
Figure 45-input disc side (for the sake of clarity, speed is more transparent than cam and input disc illustrates)；
Figure 46-speed compares cam side；
Figure 47 to 50, shows the operation of epicyclic transmission：
The perspective view of Figure 47-epicyclic transmission；For the sake of clarity, mainframe is semi-transparent is explicitly shown；
The perspective view of Figure 48-show epicyclic transmission, shows in detail the circular groove in mainframe, in order to clear
For the sake of, mainframe is semi-transparent to be explicitly shown (closing)；
Figure 49, shows the front view of epicyclic transmission, for the sake of clarity so that mainframe is transparent；
Figure 50, shows the side view of epicyclic transmission, for the sake of clarity so that mainframe is transparent；
The exploded view of Figure 51-show differential attachment, shows the configuration and operation (perspective view) of part；
Figure 52 to 57- describes the speed of differential attachment different phase than variable speed operation, shows part section with explanation function
And interior details：
Figure 52-differential attachment (part section) view 1；
Figure 53-differential attachment (part section) view 2；
Figure 54-differential attachment (part section) view 3；
Figure 55-differential attachment (part section) view 4；
Figure 56-differential attachment (part section) view 5；
Figure 57-differential attachment (part section) view 6；
Figure 58-assembly, shows the operation-spiral groove mechanism (decomposition) of gear shift；
The top view of the operation of the flexible guide of Figure 59-explanation；
Figure 60-show in detail telescoping mechanism so that the side of primary and secondary is transparent illustrating details；
Figure 61 to 62- input discs, the assembly for intersecting tooth bar assembly, crank-pin and crank pin holder, illustrate crank
The behind principle of pin holder function：
Figure 61-be located at input slot in the middle of when crank-pin and crank pin holder；
Crank-pin and crank pin holder when Figure 62-crank pin holder exits input slot；
The exploded view (little gear part section to illustrate interior details) of Figure 63-unilateral bearing assembly；
Figure 64-unilateral bearing assembly；
Figure 65-power connector assembly；
Figure 66-assembly, shows the principle that vibration is eliminated；
Figure 67-vibration eliminating machine：Sub-assemblies；
Figure 68-complete CVT assemblies, shows the orientation of module and the orientation of tooth bar：Illustrate how 4 modules place；
Figure 69 to 72- when public not rounded driving gear and two not rounded driven gears are used together, non-circular gear position
Selection；
Figure 69-non-circular gear is placed as 135 °；
Figure 70-non-circular gear is placed as 45 °；
Figure 71-non-circular gear is placed as 45 ° of (-)；
Figure 72-non-circular gear is placed as 135 ° of (-)；
Figure 73 to 75- shows in detail the output for how realizing constant homogeneous：
The assembly orientation of Figure 73-individual module；
Figure 74-show the chart that the single output and combination of each tooth bar are always exported, shows with lap
Constant homogeneous are exported；
The graphic representation of Figure 75-output with lap and the joint sequency of a complete cycle；
Figure 76 to 79- describes drive shift (forward), reverse gear (reverse), neutral (neutral) and park position
(park) helical gear assembly：
Figure 76-for forward gear clutch engagement；
Figure 77-for back gear clutch engagement；
Figure 78-for neutral gear clutch engagement；
Figure 79-for " park position " clutch engagement；
Figure 80-using the principle of the multiple contacts between idler gear elimination non-circular gear：
A- top views；
B- front views；
Figure 81-coaxial the output element with internal gear：
A- front views；
B- side cutaway views；
C- perspective views；
The configuration of Figure 82-show in detail coaxial output block in assembly；
Figure 83-for calculate driving gear non-functional part radius equation；
The mathematical derivation of Figure 84-non-circular gear shape so that the linear velocity of tooth bar 64 is constant.
Specific embodiment
For brief description, the present invention is buncher (CVT).Different from existing CVT designs, this is specifically designed disobeys
Rely friction transmission power.At present most of CVT rely on friction transmission power, therefore can not need to transmit high power under low speed
Where use.Due to the advantage, the present invention can be used for needing where high torque (HT) transmission.It is designed to realize together using this
Axle is input into and exports.
The operation of the CVT can operate description by following single order.
A) axis of the crank-pin (Figure 23) with an offset distance around input disc (Figure 14) rotates, and the offset distance can be by
Modification.[principle described in the operation is present in another patent US 20100199805.However, this sentence it is simpler and tight
The envelope for gathering by diverse method be adapted for how using the principle, how to change the skew etc..]
B) the skew crank-pin 42 blocks (caged) in the groove of tooth bar assembly (Figure 10), constrains the tooth bar assembly,
So that the tooth bar is merely able to be moved up in the side parallel to tooth bar 64.By the way that another groove is oriented perpendicularly to into motion side
To by the purely linear back and forth movement that the convert rotational motion of crank-pin 42 is tooth bar 64.The mechanism is industrially commonly known as
" scotch yoke (scotch yoke) mechanism ".The distance (stroke) of the linear reciprocation arrives the axle of input disc 16 with crank-pin 42
The radial distance of line is directly proportional.
C) tooth bar 64 is connected with little gear (Figure 11), and the linear movement of tooth bar 64 is converted into little gear 47 by little gear
Rocking vibration.
D) by using the clutch of ratchet mechanism/unilateral bearing/computer controls, the rocking vibration is converted into unidirectionally
Rotation.
A primary object of the present invention realizes constant and uniform output angle when being constant and uniform in input angular velocity
Speed.However, using above-mentioned steps, this can not be realized, because output is sinusoidal.By the angular displacement of adjustment input disc 16
Rate of change, can realize uniform and stable output.By using one group of non-circular gear, (Figure 22) of active and driven (figure
21) rate of change of the angular displacement on input disc 16 can, be changed.Some middle Knucle-gears are then passed through, by driven non-circular gear 9
Output be delivered to input disc 16.
By the profile of the given active non-circular gear 8 of equation, when radius " r " is represented as the function of θ：R (θ)=R*K*
CTR/ [R*K+f (θ)], wherein " K " is the constant for depending on all constant tooth radius, the speed ratio of " R " for needed for, the speed ratio is
Ratio between the variation in angular displacement rate of the output in input and input disc 16 on active non-circular gear 8.
The ideal value of " R " is generally 1." K " results from the radius of idler gear, and its product for being equal to driven gear radius is removed
With the product of driving gear radius.The ideal value of " K " is generally 1." CTR " is the centre-to-centre spacing of two non-circular gears 8 and 9.This is
What the available envelope based on assembly was selected.
F (θ) can be sin θ or cos θ.Two formula produce identical and tradable profile, except they are rotated by 90 °
In addition.
The profile of driven non-circular gear 9 is given by formula r (θ)=CTR- { R*K*CTR/ [R*K+f (θ)] }.Used
The generation of these contour shapes and parameter is explained in detail in subsequent topic.
In order to help understand the present invention, design creates CAD model, and as demonstrated below.
It is used herein to be characterized as：
It is 1 that the value of " R " is selected.
It is 1 that the value of " K " is selected.
Public input shaft (Fig. 6) and active non-circular gear 8 are used for into all four module.
By public intersection tooth bar assembly 44, input disc 16, driven non-circular gear 9, middle Knucle-gear, crank-pin 42, speed
It is used for two modules than changeable mechanism than cam (Figure 20) and speed.
Two tooth bars 64 are located at and intersect on tooth bar assembly 44, with 180 ° of phase shift.
Place the assembly of another identical module so that first assembly of the second assembly of module with regard to module
Lateral inversion is simultaneously rotated by 90 °.
Part list：
1) frame-main casing
2) frame-intersection tooth bar guide
3) frame-flexible guide
4) input shaft
5) bearing of input shaft
6) intermediate gear shaft
7) idler gear axle bearing
8) non-circular gear (active)
9) non-circular gear (driven)
10) middle circle gear C 1
11) middle circle gear C 2-C3
12) middle circle gear C 4-C5
13) bearing-lasso (static and dynamic)
14) bearing-Knucle-gear C2-C3
15) bearing-Knucle-gear C4-C5
16) input disc
17) bearing-input disc
18) speed compares cam
19) bearing-speed compares cam
20) intermediate support Knucle-gear C4a-C5a
21) support shaft
22) bearing-support shaft
23) speed is than change control-rod-planetary mechanism
24) sleeve-input disc-oblique
25) static differential lasso
26) static differential lasso straight-tooth wheel bearing
27) static differential lasso straight-tooth wheel shaft
28) a) static differential lasso bevel pinion
B) static differential lasso bevel gear wheel
29) static differential lasso spur gear
30) pad
31) dynamic differential lasso
32) dynamic differential lasso straight-tooth wheel bearing
33) dynamic differential lasso straight-tooth wheel shaft
34) a) dynamic differential lasso bevel pinion
B) dynamic differential lasso bevel gear wheel
35) dynamic differential lasso spur gear
36) universal joint
37) helicla flute
38) disk-input disc of fluting
39) compression spring
40) thrust bearing
41) speed is than change control-rod-spiral groove mechanism
42) crank-pin
43) crank-pin is copied
44) tooth bar assembly is intersected
45) primary extension sleeve
46) secondary extension sleeve
47) little gear
48) pinion shaft
49) pinion bearing
50) unilateral bearing
51) output chain gear/gear
52) power connection shaft
53) power connector axle bearing
54) power connector sprocket/gear
55) tooth bar is copied
56) wheel-vibration cancellation
57) lasso-wheel-vibration cancellation
58) for the input shaft of helical bevel gear
59) helical bevel gear
60) clutch-park position/neutral/reverse gear
61) output shaft
62) idler gear-non-circular gear connector
63) guide-idler gear-non-circular gear connector
64) tooth bar
65) the coaxial output element with internal gear
The assembly of part, the description of sub-assemblies and their function：
The description of total structure：
Input shaft (Fig. 6) is arranged on two bearings of input shaft 5, and is placed on the center (Fig. 3) of frame-main casing.Input
Disk 16 is arranged on input shaft 4, and is clipped in tooth bar assembly (Figure 10) and speed than between cam (Figure 20), crank-pin 42 is stuck in groove
In.Crank-pin 42 has a main body, and the body shape picture has the rectangular prism of the round prism of both sides extension.In them one
It is individual play a part of cam-follower and cause its with speed than cam-engaged, another play a part of crank-pin 42 and cause its with
The tooth bar 64 intersected on tooth bar assembly 44 is engaged.It is arranged on input shaft 4 parallel to the active non-circular gear 8 of input disc 16.
Intermediate gear shaft (Fig. 7) is arranged on two constant gear axle bearings 7, and each main housing 1 has a constant tooth
Wheel bearing 7.Intermediate gear shaft 6 is placed with distance " CTR " parallel to input shaft 4, and the distance " CTR " is used to produce non-knuckle-tooth
The shape of wheel.From input shaft 4 power assembly of input disc 16 is transferred to according to form presented below.
Driven non-circular gear 9 and idler gear C2-C3 (Figure 25) are arranged on input shaft 4, idler gear C1 (Figure 28) and
Idler gear C4-C5 (Figure 27) is arranged on constant gear shaft 6.Active non-circular gear 8 is directly installed on input shaft 4, driven
Non-circular gear 9 and idler gear C1 10 are directly installed on together on intermediate gear shaft 6.Other gears are placed within the bearing simultaneously
On the axle of each of which.
Tooth bar assembly 44 is only being moved freely through along on the direction of tooth bar 64, and its motion is subject to frame-tooth bar to be oriented to
The constraint of part 2.A set of extension sleeve of primary and secondary is placed on the either side of tooth bar assembly 44.This will reduce tooth bar assembling
Overall size needed for body 44 and frame main housing 1.Prong is placed on into the either side of tooth bar assembly 44, another prong is put
Put on secondary sleeve 46, to pull and extend extension sleeve, the extension sleeve is collapsed by the main body of tooth bar assembly 44
(collapsed).Frame is flexible-and guide (Fig. 4) blocks these extension sleeves.
Tooth bar 64 is coupled with unilateral bearing assembly (Figure 64), and the unilateral bearing assembly is by being placed on pinion shaft
(Figure 12) little gear 47 on is constituted.The pinion shaft 48 is arranged on the flexible guide 3 of the frame with pinion bearing 49.
Gear or sprocket wheel are arranged on the pinion shaft 48 by unilateral bearing 50, and are placed parallel to little gear 47.Power connection shaft
Assembly (Figure 65) is placed parallel to unilateral bearing assembly (Figure 64).Power connector assembly is by power connection shaft (Fig. 8) group
Into the power connection shaft is arranged on two bearings, and described two bearings are placed on frame-flexible guide 3.Gear or
Sprocket wheel is placed on every one end of power connection shaft.The power of pinion shaft 48 is delivered to power and connects by the gear or sprocket wheel
Connect.
The operation of main CVT and principle：
When input disc 16 rotates, by " scotch yoke " mechanism, crank-pin 42 is caused on the direction parallel to tooth bar 64
Intersect the movement of tooth bar assembly.The distance of motion operation be proportional to the axis of crank-pin 42 and the axis of input disc 16 away from
From.By changing the distance, the tooth bar assembles the distance of running body, and this is referred to as " stroke ", can be changed.Due to acting
It is constant, it is the product (F* strokes) of the distance that the power for applying is multiplied by operation.For shorter stroke, the power of applying
Bigger, for longer stroke, the power of applying is less.However, motion is to swing back and forth.Subsequently, from the line of tooth bar 64
The power that property is moved back and forth is transferred to little gear 47 as oscillating motion.The torque that the oscillating motion is produced is proportional to tooth bar 64 and applies
Plus power.This is transferred to output chain gear/tooth by the clutch or ratchet mechanism of the either computer controls of unilateral bearing 50
Wheel is with one-directional rotation.The one-directional rotation is further communicated to wheel.
From engine/power source to the power transmission configuration of input disc 16：
By using one group of non-circular gear, (Fig. 8) of active and driven (Fig. 9), change the angular displacement on input disc 16
Rate of change.The output of input shaft 4 is transmitted by one group of non-circular gear, 5 middle Knucle-gears is then passed through by the defeated of input shaft 4
Go out to be delivered to input disc 16.Not rounded driving gear 8 is directly installed on input shaft 4.Driven non-circular gear 9 is arranged on idler gear
On axle (Fig. 7), it is arranged on two bearings 7 and is placed in two main housings 1.
Middle circle gear C 1 10 is arranged on intermediate gear shaft 6, is directly connected to driven non-circular gear 9.Idler gear
C2-C3 (Figure 25) is arranged on input shaft 4, is rotated freely together with bearing 14.Idler gear C4-C5 (Figure 26) is arranged on centre
On gear shaft 6, intermediate gear shaft 6 is rotated freely together with bearing 15, and idler gear C5 drives input disc 16.Select in the middle of these
The radius of gear so that input disc 16 completes once to rotate when active non-circular gear (Figure 22) completes once to rotate.It should expire
Sufficient condition-rC2/rCl=nl, rC4/rC3=n2, rdisc/rC5=nl*n2, K value will be 1.
When profile interfere/is contacted more simultaneously, the behind reason of Knucle-gear is needed between non-circular gear：
According to for the selected value of variable " R ", " K " and " CTR ", the shape of non-circular gear can be with any given time point
With multiple contact points.From the equation of non-circular gear profile the radius of driven non-circular gear 9 is can be seen that less than input shaft 4, its
Zero point is reached installed in wide overlying regions and on two positions.Furthermore, it is possible to due to contour shape, driven non-circular gear 9
There can be multiple contact points in the given time with active non-circular gear 8.This can be by inserting two by interval Knucle-gear 62
Eliminated between individual non-circular gear.Which increase the distance between two non-circular gears and eliminate and go up at any given time
The problem of multiple contact points.
Using the principle of gear ratio change cam behind：
In order to change the speed for being input to output ratio, the position of crank-pin 42 must change.This can be convex by rotation rotating ratio
Wheel disc 18 realizes that speed has groove than cam disc 18, and the groove has certain profile.When speed is revolved than cam disc 18 with regard to input disc 16
When turning, the profile forces the moving in the radial direction in disk axis of crank-pin 42.This is because the axis of crank-pin 42 is through defeated
Enter the groove of groove and speed than cam disc 18 of disk 16.When axis of the crank-pin 42 closer to input disc 16, stroke shortens, due to doing
Work(is constant, so power increases.Similarly, as crank-pin 42 is away from the axis of input disc 16, stroke is longer, due to acting perseverance
It is fixed, so power declines.However, challenge herein is fast than the synchronous rotation in the normal operation period of cam disc 18 and input disc 16 to cause
Turn, when gear ratio change is needed, input disc 16 and speed there should be relative angular speed than cam disc 18.By using described below
One of them in three mechanisms, when needing, input disc 16 and speed can than the relative angular speed between cam disc 18
Realize.
The method for changing gear ratio：
1. planetary mechanism：
One group of intermediate support Knucle-gear C4a and C5a (Figure 26) axially connects and in public support shaft (Fig. 9).C4a
Identical with Knucle-gear C4, C5a is identical with Knucle-gear C5.The motion of the common axis is constrained by circular groove/track, itself and input
The constant distance of disk 16 and the fast rotation axis than cam disc.Gear 4a is radially connected to gear C 3, and gear C 5a radially connects
Speed is connected to than cam disc 18.Gear ratio change control-rod-the planetary mechanism (Figure 37) being articulated in frame causes the position of support shaft 21
Putting can move along groove.When the position is moved, input disc 16 and speed are than having relative angular displacement between cam disc 18.
2. spiral groove mechanism：
Helicla flute input disc lasso (Figure 38) with distortion profile is axially coupled to input disc 16.Matching spiral fluted is turned round
The groove of bent profile is opened in speed than on cam disc 18, and with the coaxial placement of input disc 16.When speed than cam disc 18 and input disc 16 it
Between distance keep it is constant when, input disc 16 and speed than the synchronous rotary of cam disc 18.When input disc 16 and speed than cam disc 18 it
Between distance when being changed, input disc 16 and speed are than the relative angular speed between cam disc 18 as speed is forced to than cam disc 18
Rotate with regard to input disc 16 and change.The axial translation is realized using gear ratio change control-rod-spiral groove mechanism (Figure 40), it is described
Gear ratio change control-rod-spiral groove mechanism is promoted towards input disc 16 and is connected to thrust bearing 40 of the speed than cam disc 18.Place
It is set to rebound than the compression spring (Figure 39) between cam disc 18 in input disc 16 and speed.
3. differential attachment：
By sleeve-input disc to inclined-plane (Figure 32), static lasso bevel gear wheel 28b is axially coupled to input disc 16.With
The static differential lasso (Figure 32) that bevel gear wheel 28b coaxially separates by thrust bearing 40 with regard to bevel gear wheel 28b independently from
By rotating.Constrain static differential lasso 25 to move axially with regard to bevel gear wheel 28b.The static lasso axle 27 for rotating freely perpendicular to
The axis of static differential lasso 25 is placed in bearing 26, and bearing 26 is placed in static differential lasso 25.Static lasso conelet
It is connected to static lasso axle 27, static lasso bevel pinion gear 128a and the static differential axial stiffness of lasso spur gear 29
128a is paired with static lasso bevel gear wheel 28b.
Similarly,
Dynamic bevel gear wheel (Figure 17) is parallel described fast than cam disc coaxial placement so that their synchronous rotaries, but permits
Perhaps along the displacement of axis between them.It is dynamic with the dynamic lasso bevel gear wheel 28a coaxial placements separated by thrust bearing 40
The differential lasso of state (Figure 33) is independently rotated freely with regard to dynamic lasso bevel gear wheel 34b.Constraint dynamic differential lasso 31 with regard to
Dynamic lasso bevel gear wheel 34a axial movements.Axle of the dynamic lasso axle 33 for rotating freely perpendicular to the dynamic differential lasso
Line is placed in bearing 32, and bearing 32 is placed in dynamic differential lasso 31, and dynamic lasso axle 33 has to be placed on its axis
Universal joint 36.It is straight that dynamic lasso bevel pinion 34a is connected to dynamic lasso with the dynamic axial stiffness of lasso spur gear 35
Gear shaft 33, dynamic lasso bevel pinion 34a is paired with dynamic lasso bevel gear wheel 34b.Universal joint 36 is that dynamic lasso is straight
Gear shaft 33 and the small coning gear shaft are common, it is allowed to little mismatch.
Pad makes two spur gears keep contact.The pad (Figure 29) is with regard to the free earth's axis of dynamic lasso straight-tooth wheel shaft 33
To movement.
Herein static differential lasso 25 be with dynamic differential lasso 31 as and it is interchangeable.
It is as described below for power transfer path by the configuration：
A. static state lasso bevel gear wheel 28a causes static lasso bevel pinion 28b to rotate.
B. static lasso bevel pinion 28 causes static lasso axle 27 to rotate.
C. static lasso axle 27 causes static lasso spur gear 29 to rotate.
D. static lasso spur gear 29 causes dynamic lasso spur gear 35 to rotate.
E. dynamic lasso spur gear 35 causes dynamic lasso axle 33 to rotate.
F. dynamic lasso axle 33 causes dynamic lasso bevel pinion 34a rotations through universal joint 36.
G. dynamic lasso bevel pinion 34a causes dynamic lasso bevel gear wheel 34b to rotate.
H. dynamic lasso bevel gear wheel 34b causes speed to rotate than cam disc 18.
Because described two bevel gear wheels, described two bevel pinions, the spur gear distinguish the same and equivalently-sized, when
When dynamic differential lasso 31 is static, speed is synchronous with input disc 16 than the angular speed of cam disc 18.With regard to static differential sleeve
When circle 25 rotates dynamic differential lasso 31, input disc 16 and speed will be than there is relative angular displacement between cam disc 18.
Behind principle compact to design is made using extension sleeve：
For the operation of the design, it is straight that the value of the length of the input slot of tooth bar assembly is necessarily equal to 2* strokes+input shaft
+ 2* minimum material thickness+2* in footpath reach the distance of tooth bar guide.The whole length must be guided by tooth bar guide.Due to
Tooth bar guide must also accommodate the track of tooth bar 64, and the opening portion of the tooth bar guide should have at least input disc 16
Otherwise when tooth bar 64 is run to when side reaches distalmost end, it will can't reach the width of diameter.Flexible guide causes support member to prolong
Stretch, therefore, the whole length of tooth bar assembly can be reduced " distance for reaching tooth bar guide ".This also enables main casing 1
Enough reduce the distance and shorter.It is provided with prong in the design of tooth bar assembly and second sleeve to extend extension sleeve.Tooth
The main body of bar assembly causes extension sleeve to cave in.
The use of slider guide part or the principle of operation function behind：
The crank-pin is less than input shaft 4.Because two grooves intersect, the crank-pin is possible to slip into input axial trough
In.This is by using slider guide part (Figure 13) elimination more than input axial trough.It is set to surround (enclosing) crank-pin 42
Crank cotter way in float.
Realize the design of the principle, the lap of power transmission：
In order to ensure from module seamlessly transitting to next module, in the short time, two modules are all movable
And engage when the output of both reaches the value of constant homogeneous.When it is still in functional areas, the first module is unclamped, and
Second module is located at well functional areas.
Module and their trim designs and constraint：
All four module shares a public input shaft and a public not rounded driving gear.Two modules are shared
Public input disc 16 and gear shift.Tooth bar is placed with regard to next in 90 ° of phase shifts.In order to be adapted to this, from
Dynamic non-circular gear 9 is orientated 45 °, and the phase place of relative another not rounded driven gear of driven non-circular gear 9 is 45 °.And due to
Non-circular gear is symmetrical, and it can also be orientated 135 °.This increases 90 ° of phase shifts between tooth bar.
The principle that intermodule power is transmitted or connected：
When module is run in order, they must be connected before power is delivered to wheel.This is connected by using power
Spindle 52 realizes that power connection shaft 52 has gear or sprocket wheel to connect the output of each module so that it has continuously
Power is to wheel.Power is also transmitted in order.
Back gear mechanism：
The output of power connection shaft 52 is coupled with the input shaft 4 of helical bevel gear differential attachment.Therefore, these are helical gear
Export toward rightabout rotation.If the differential attachment of output shaft 61 has with regard to output helical bevel gear coaxially put with gap
Put, so as to independently rotate freely with regard to exporting helical bevel gear.With clutch two lassos are placed on output shaft 61,
Described two lassos are allowed coaxially to move.Enable to described two lassos and any one the output helical teeth toward rightabout rotation
Bevel gear connects.When causing one of lasso to be connected with specific output helical bevel gear by clutch, output shaft 61 will
Rotate in specific direction.If the connection is switched to another output helical gear, its direction will invert.
Neutral gear mechanism：
When lasso does not have to be connected with any one output helical bevel gear, lasso and output shaft 61 do not suffer restraints,
Therefore, they are rotated freely in any direction and as the effect of " neutral " gear.
Parking gear mechanism：
When lasso is connected with two output helical bevel gears, lasso is constrained and as " park position " gear when rotating
Effect.
Offset feature and the mechanism of vibration：
1. crank-pin is copied：When input disc 16 rotates, the off-center placement of crank-pin.This is unbalance to cause vibration.For
The vibration is offset, crank-pin is copied with 180 ° same of distance separated.This is by the phase of mobile crank-pin at the same speed than convex
Wheel movement.The motion is as the motion of crank-pin.So that cam path is the same separately 180 °.
2. the static load that counter vibrates：As input disc 16 rotates, intersect tooth bar assembly oscillating movement, the vibration fortune
It is dynamic to cause vibration.It passes through appropriate mass vibration in the opposite direction and is eliminated.This is connect by fixed wheel and tooth bar 64
Touch and realize, it will be with rotating back and forth.Separated with 180 ° with appropriate mass and wheel and contact and will offset the vibration.
Coaxial input and output select feature：
When needing coaxial input and exporting, this can realize that output block 65 has internal tooth by adding output block 65
Wheel, the internal gear is paired with power connector gear.Bearing is placed between input shaft 4 and coaxial output block 65 so that it
Independent rotation.
Constraint：
As K=1 and R=1, application conditions are：
The number of teeth of active non-circular gear (Figure 22) should be identical with the number of teeth of driven non-circular gear (Figure 21), it means that it
Girth be identical, that is to say, that even if momentary rate can be differed, they be also and meanwhile complete 1 time rotation.Can replace
Ground is changed, the part of required form is not followed, that is, using the part of least radius " r ", the second setting energy of non-circular gear
Enough optionally for Parallel Implementation purpose.
Using rc2/rcl=nl, rc4/rc3=n2, rdisc/rc5=nl*n2.
Expect but and optional：(rvl+rv2)=(rc3+rc4)=(rc5+rdisc)=(rcl+rv2)=ctr.This
The placement of all actives and driven gear on two common axis will be allowed, they one of them is input shaft 4.
Mathematical derivation：
Main purpose is to determine the mathematic(al) representation of non-circular gear shape so that vTooth bar(linear speed of tooth bar 64) is normal
Amount.
Wherein：
ωOutput=ωDisk*rGear*f(θ)
Wherein,
ωInput- input angular velocity
The angular speed of-active non-circular gear
The angular speed of-driven non-circular gear
The angular speed of-constant gear 1
The angular speed of-constant gear 2
The angular speed of-constant gear 3
The angular speed of-constant gear 4
The angular speed of-constant gear 5
ωDiskThe angular speed of-disk
ωOutputThe Output speed of-output
The radius of-active non-circular gear
The radius of-driven non-circular gear
The radius of-constant gear 1
The radius of-constant gear 2
The radius of-constant gear 3
The radius of-constant gear 4
The radius of-constant gear 5
rDiskThe radius of-disk
rSkewThe radial position of-crank-pin
R- is input to the angular speed ratio of output
K- (ratio of the radius product of driven gear and driving gear)
Centre-to-centre spacing between two non-circular gears of CTR-
F (θ)-sin θ or cos θ
Claims (28)
1. a kind of buncher, including：
At least one module, the module includes：
Relative to the input shaft with reference to frame rotation,
One input disc, has flank profil on the input disc border, a groove is limited in radial directions, and the input disc passes through one group
Non-circular gear is simultaneously connected to the input shaft through at least one substantially circular gear so that the input disc is completed
" R " rotates, and for active non-circular gear relative to the reference frame around rotation axis rotation each time, and when described
During input disc spins, " R " is the inverse of integer or integer,
One crank-pin, the crank-pin is stuck in the groove so that intersect the movement of tooth bar assembly, the intersection tooth bar assembly
By at least one tooth bar, be arranged essentially parallel to a groove for the input shaft of the tooth bar, substantially with described first
Vertical second groove for the crank-pin of individual groove is constituted, and
One little gear, the little gear is arranged on pinion shaft and couples with the tooth bar, by the clutch of computer controls
Either unilateral bearing or ratchet mechanism cause gear or sprocket wheel rotation to device.
2. buncher according to claim 1, wherein, when not rounded driving gear funtion part shape according to work
Be rf (θ)=R*K*CTR/ [R*K+f (θ)] when being indicated for the radius of the function of angle, when not rounded driven gear with actively
During Gear Contact, not rounded driven gear is shaped as rf (θ)=CTR- { R*K*CTR/ [R*K+f (θ)] }, and CTR is non-circular gear
Between centre-to-centre spacing, " R " for needed for the angular displacement rate between input disc and active non-circular gear speed ratio, " K " results from example
Product the taking advantage of divided by the radius of driving gear of the radius parameter such as each input disc and gear and the radius equal to driven gear
Product, f (θ) is cos θ or sin θ.
3. buncher according to claim 1, wherein, by radiusGiven active
The shape of the non-functional part of gear, θfFor real number so thatMore than the radius of input shaft 4, the funtion part of driving gear is
>=(360/N) °, wherein N are used number of modules.
4. buncher according to claim 2, wherein, non-circular gear piles up at least one of which, the institute in each module
The summation for having all effective efficiency parts of non-circular gear pair is >=360 °, and is placed such that the funtion part of each module
Have an effect with a lap successively.
5. buncher according to claim 1, wherein, circular idler gear is placed on actively and driven non-knuckle-tooth
Between wheel, its axis is restricted to the line movement only along connection non-circular gear center, with eliminate at any given time due to
Multiple contact points and issuable problem.
6. buncher according to claim 1, wherein, speed of the flank profil substantially as input disc is put than cam
It is set to its border and closes on input disc, when rotation is substantially synchronized, keeps substantially permanent between crank-pin and the axis of input disc
Fixed distance, otherwise changes the distance.
7. buncher according to claim 6, wherein, by using a mechanism, change input disk axis and crank
The distance between pin, thus changes the displacement of the lines of tooth bar.
8. buncher according to claim 7, wherein, the mechanism includes bevel-gear sett, the pair of cone tooth
One of them of wheel is coaxially connected to the input disc, and another causes active spur gear to rotate and causes successively substantially identical
The rotation of driven spur gear, the driven spur gear separated by using pad with the distance for setting, the driven spur gear according to
It is secondary so that the rotation of the second pair of bevel gear, second pair of bevel gear is substantially as bevel-gear sett and final coaxially connected
Compare cam to the speed.
9. buncher according to claim 8, wherein, universal joint is placed on active spur gear and drive bevel gear
Axle axis crosspoint, or the crosspoint of the axis of the axle of driven spur gear and driven wheel of differential, or while place
In above-mentioned two crosspoint.
10. buncher according to claim 8, wherein, when the axis of each spur gear does not have relative movement, institute
State input disc and the speed is substantially synchronized rotation than cam, be not otherwise so rotation.
11. bunchers according to claim 7, wherein, the input disc is axially coupled to helicla flute lasso, described
Speed limits the hole of the profile with the matching lasso than cam and substantially by coaxial placement so that the speed than cam and
The input disc is spaced a distance.
12. bunchers according to claim 11, wherein, when the separate speed than cam and the input disc away from
From when being held substantially constant, the speed is substantially synchronized rotation than cam and the input disc, when the distance is modified not
Synchronous rotary.
13. bunchers according to claim 7, wherein, most latter two Knucle-gear is replicated and with the speed than convex
Wheel pairing is parallel with the input disc, and to move along groove, the groove is substantially with the axis of the input disc to its axis
Constant distance.
14. bunchers according to claim 13, wherein, when the axis of the Knucle-gear for being replicated be kept substantially it is quiet
When only, the input disc and the speed are substantially synchronized rotation than cam, otherwise so do not rotate.
15. bunchers according to claim 1, wherein, the little gear being installed on pinion shaft and the tooth bar
Couple and transfer power to the pinion shaft, the pinion shaft by the clutch of computer controls, unilateral bearing or
Ratchet mechanism transfers power to successively gear or sprocket wheel.
16. bunchers according to claim 15, wherein, only when the little gear rotates in particular directions simultaneously
And each non-circular gear is at functional areas, the pinion shaft is just connected to the sprocket wheel by the clutch of the computer controls
Or gear.
17. bunchers according to claim 15, wherein, it is fixed when the input disc completes about once to rotate
To the module so that their non-circular gear has successively lap in functional area, it is ensured that when any given
Between at least one module in the functional areas, therefore complete about a cycle.
18. bunchers according to claim 17, wherein, the overlap between every a pair of adjacent blocks of the module
Part is substantially the same.
19. bunchers according to claim 15, wherein, the transmission is further included each output gear
Or the output of output chain gear is connected to Next multiple power connection shafts.
20. bunchers according to claim 1, wherein, the intersection tooth bar assembly further includes at least one
Individual flexible guide sleeve, the flexible guide sleeve by intersection tooth bar assembly guiding for only in the frame of groove in
Move in single dimension, therefore allow to reduce frame dimensions.
21. bunchers according to claim 1, wherein, the slider guide part with substantially rectangular cross-sectional configuration groove is put
Put in the groove of the crank-pin of the intersection tooth bar assembly to eliminate the crank-pin to the landing in the groove of the input shaft,
The substantially rectangular cross-sectional configuration groove is longer than the width of the groove of the input shaft.
22. bunchers according to claim 1, wherein, the intersection tooth bar assembly further limits appropriate matter
The static load of amount and the wheel of the static load is transmitted the motion to from the tooth bar, the static load is intersecting tooth bar with described
The essentially the inverse side of assembly moves up, to offset due to the vibration of the oscillating movement of the tooth bar.
23. bunchers according to claim 1, wherein, static load limit substantially with the weight of the crank-pin
The same weight, and the vibration in the square upward sliding contrary with the motion of the crank-pin to offset due to eccentric rotary.
24. bunchers according to claim 1, wherein, the power transmission pinion shaft is further assembled with one
Body is coupled, and the assembly includes input helical gear, multiple substantially coaxial output helical bevel gears and through axle, described
Multiple substantially coaxial output helical bevel gears have a through hole, the through hole be located substantially on it is substantially staggered relatively each other in
In the heart so that they substantially rotate in directions opposite each other, it is described basic with the output helical bevel gear through axle
Upper coaxial placement, multiple substantially coaxial lassos are configured to engage and independently move with output helical bevel gear one of them described
It is dynamic.
25. bunchers according to claim 24, wherein, when the lasso with it is described output helical bevel gear its
In one connection when, one of them of the lasso rotates in particular directions, and when lasso by it is described connection be converted to it is another
Change direction during individual output helical bevel gear.
26. bunchers according to claim 24, wherein, when the lasso does not bore tooth with any one output helical teeth
During wheel connection, the lasso is unrestricted, therefore rotates freely through in any direction and as the effect of " neutral gear " gear.
27. bunchers according to claim 24, wherein, when the lasso and two output helical bevel gears all connect
When connecing, the lasso is constrained when rotating and as the effect of " park position " gear.
28. bunchers according to claim 19, wherein, will with the gear or sprocket wheel of the input shaft coaxial placement
Power from the power connector is delivered to output block.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/US2014/031136 WO2015142323A1 (en) | 2014-03-18 | 2014-03-18 | Continuous variable transmission with uniform input-to-output ratio that is non-dependent on friction |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106662230A true CN106662230A (en) | 2017-05-10 |
| CN106662230B CN106662230B (en) | 2019-08-20 |
Family
ID=54141697
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201480079073.2A Active CN106662230B (en) | 2014-03-18 | 2014-03-18 | With the stepless transmission for being uniformly input to output speed ratio independent of friction |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US9970520B2 (en) |
| EP (1) | EP3120046A4 (en) |
| JP (1) | JP6454456B2 (en) |
| CN (1) | CN106662230B (en) |
| CA (1) | CA2962854C (en) |
| WO (1) | WO2015142323A1 (en) |
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| CN110805673A (en) * | 2019-12-16 | 2020-02-18 | 哈尔滨理工大学 | Impact-resistant mechanical stepless speed changer |
| CN111919049A (en) * | 2018-02-27 | 2020-11-10 | 迪特尔·格哈德·法尔尼 | Continuously variable transmission and method for operating a continuously variable transmission |
| CN114423966A (en) * | 2020-02-12 | 2022-04-29 | R·R·拉金德兰 | Infinitely variable transmission with uniform input-output ratio independent of friction |
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| EP2880336B1 (en) * | 2012-08-03 | 2019-10-16 | Transmission CVT Corp Inc. | Over clamping protection method and clamping mechanism therefor |
| CN104989799B (en) * | 2015-05-14 | 2018-02-02 | 深圳市南博自动化设备有限公司 | Linear reciprocating motion turns unidirectional circular motion apparatus |
| CN107893839A (en) * | 2017-09-06 | 2018-04-10 | 金永军 | Increase rotating speed increase power machine |
| CN107725131A (en) * | 2017-11-07 | 2018-02-23 | 重庆润通科技有限公司 | Adjustable type cam drive mechanism |
| CN114992303B (en) * | 2022-05-30 | 2024-04-12 | 武汉理工大学 | Unidirectional displacement compensation device for actuating cylinder |
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| JP2006046424A (en) * | 2004-08-02 | 2006-02-16 | Toyota Motor Corp | Gear type continuously variable transmission |
| US7056254B1 (en) * | 2005-07-20 | 2006-06-06 | Fragnito Frank A | Non-slip continuously variable transmission |
| GB0517201D0 (en) * | 2005-08-22 | 2005-09-28 | Torotrak Dev Ltd | Driving and steering of motor vehicles |
| US8425364B2 (en) * | 2006-04-10 | 2013-04-23 | Derek Lahr | Cam-based infinitely variable transmission |
| US8534146B2 (en) * | 2006-07-26 | 2013-09-17 | Iowa State University Research Foundation, Inc. | Geared, continuously variable speed transmission |
| US7878935B2 (en) * | 2007-11-26 | 2011-02-01 | Derek Lahr | Continuously variable transmission with external cam |
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| US20100064831A1 (en) * | 2008-09-15 | 2010-03-18 | Lee Gary D | Infinitely variable transmission with hybrid accelerator |
| US9506545B2 (en) * | 2013-03-15 | 2016-11-29 | John W. Klovstadt | Continuously variable transmission having a periodic displacement waveform with a constant velocity portion |
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2014
- 2014-03-18 EP EP14886662.7A patent/EP3120046A4/en not_active Withdrawn
- 2014-03-18 CN CN201480079073.2A patent/CN106662230B/en active Active
- 2014-03-18 CA CA2962854A patent/CA2962854C/en active Active
- 2014-03-18 US US13/261,970 patent/US9970520B2/en active Active
- 2014-03-18 JP JP2017500799A patent/JP6454456B2/en active Active
- 2014-03-18 WO PCT/US2014/031136 patent/WO2015142323A1/en active Application Filing
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| US5440945A (en) * | 1993-04-19 | 1995-08-15 | Penn; Jay P. | Hardgeared infinitely variable transmission |
| CN1133083A (en) * | 1993-08-30 | 1996-10-09 | 艾姆博里治公司 | Transmission mechanism |
| US5603240A (en) * | 1994-03-04 | 1997-02-18 | Klovstad; John W. | Mechanical transmission continuously variable from forward to reverse |
| FR2841957B1 (en) * | 2002-07-05 | 2004-10-15 | Philippe Alain Marec | CAM MECHANICAL CONTINUOUS TORQUE DRIVE |
| CN103282694A (en) * | 2010-12-29 | 2013-09-04 | 赵闰奎 | Chain belt-type variable transmission |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111919049A (en) * | 2018-02-27 | 2020-11-10 | 迪特尔·格哈德·法尔尼 | Continuously variable transmission and method for operating a continuously variable transmission |
| CN110805673A (en) * | 2019-12-16 | 2020-02-18 | 哈尔滨理工大学 | Impact-resistant mechanical stepless speed changer |
| CN114423966A (en) * | 2020-02-12 | 2022-04-29 | R·R·拉金德兰 | Infinitely variable transmission with uniform input-output ratio independent of friction |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2015142323A1 (en) | 2015-09-24 |
| EP3120046A4 (en) | 2017-12-20 |
| CA2962854C (en) | 2021-08-24 |
| JP6454456B2 (en) | 2019-01-16 |
| JP2017508939A (en) | 2017-03-30 |
| EP3120046A1 (en) | 2017-01-25 |
| CN106662230B (en) | 2019-08-20 |
| CA2962854A1 (en) | 2015-09-25 |
| US20150267794A1 (en) | 2015-09-24 |
| US9970520B2 (en) | 2018-05-15 |
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